CN211288092U - Flange, compressor and air conditioner - Google Patents
Flange, compressor and air conditioner Download PDFInfo
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- CN211288092U CN211288092U CN201921796237.XU CN201921796237U CN211288092U CN 211288092 U CN211288092 U CN 211288092U CN 201921796237 U CN201921796237 U CN 201921796237U CN 211288092 U CN211288092 U CN 211288092U
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Abstract
The utility model provides a flange, compressor and air conditioner. The flange comprises an exhaust pipeline, wherein a silencing hole is arranged on the inner wall of the exhaust pipeline and is of a blind hole structure; when the air flow in the exhaust pipeline passes through the opening of the silencing hole, the silencing hole reduces the noise of the air flow. The pipe wall of the flange exhaust pipeline is provided with a blind hole-shaped silencing hole, and through the blind hole silencing principle, an air column in the blind hole vibrates under the action of sound pressure, so that the energy consumption is reduced to reduce exhaust noise.
Description
Technical Field
The utility model belongs to the technical field of the compressor, concretely relates to flange, compressor and air conditioner.
Background
Noise of a household air conditioner is an important factor affecting the comfort index of residents, and noise generated by a compressor is a main source of noise in an air conditioning system. The noise component of the compressor is complex, and mainly comprises pneumatic noise, mechanical noise and electromagnetic noise, wherein the pneumatic noise mainly occurs in an exhaust area, the air flow speed near an exhaust valve seat of the compressor is high, the flow channel structure is complex, the interaction of the air flow and a solid wall surface is severe, and the significant air flow noise is formed.
In the prior art, it is disclosed that a plurality of square holes are arranged in an upper end surface of a discharge port and an inner shaft groove of an exhaust port of an upper flange of a compressor, and turbulence is generated in the square holes to move a boundary layer structure to the outside of the discharge port, increasing an effective flow area of refrigerant gas, so that the refrigerant gas can be smoothly discharged from a cylinder through the discharge port.
However, the above solution has the following problems: the structure of the square hole easily causes the problem of noise generated by secondary vortex; the scheme does not consider the influence of the actual flow direction on the arrangement of the holes, and can further excite extra noise; this scheme does not have rational design quad slit size, can increase the clearance volume at the gas vent design recess, reduces the performance of compressor.
SUMMERY OF THE UTILITY MODEL
Therefore, the to-be-solved technical problem of the present invention is to provide a flange, a compressor and an air conditioner, which can reduce the pneumatic noise of the exhaust.
In order to solve the problems, the utility model provides a flange, which comprises an exhaust pipeline, wherein the inner wall of the exhaust pipeline is provided with silencing holes, and the silencing holes are arranged in a blind hole structure; when the air flow in the exhaust pipeline passes through the opening of the silencing hole, the silencing hole reduces the noise of the air flow.
Preferably, the silencing holes are arranged in a plurality and are circumferentially arranged along the exhaust pipeline.
Preferably, the plurality of muffling holes are divided into at least two groups, each group of muffling holes are arranged along the circumferential direction, and the plurality of groups of muffling holes are arranged along the axial direction of the exhaust pipeline.
Preferably, two adjacent groups of the silencing holes are arranged in a staggered mode along the circumferential direction.
Preferably, the cross-sectional shape of the muffling hole is one or more of a circle, a triangle and an ellipse.
Preferably, when the muffling holes are circular holes, the number n and the diameter D of the muffling holes are equal to each other1And hole depth h1The following relationship exists with the displacement volume v of the exhaust conduit:
preferably, a distance between a group of the muffling holes closest to the first end face of the exhaust duct and the first end face is L1The distance between a group of the silencing holes closest to the second end face of the exhaust pipeline and the second end face is L2On the development of the inner peripheral surface of the exhaust duct, the axial distance between two adjacent groups of the muffling holes is L3The minimum circumferential distance between two adjacent groups of the silencing holes is L4The included angle between the central connecting line of the silencing holes arranged in a staggered way and the vertical axis passing through the center of one of the silencing holes is α, and the distance between the adjacent silencing holes in the same group is L5The diameter of the exhaust pipeline is D, and the axial height of the exhaust pipeline is H; wherein L is more than or equal to 0.2mm1＝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。
Preferably, 30 DEG-alpha-60 deg.
Preferably, the relationship of the displacement v to the diameter D is:
according to another aspect of the present invention, there is provided a compressor including the flange as described above.
Preferably, the compressor comprises an upper flange, and a blind hole is formed in the inner wall of an air outlet of the upper flange.
According to still another aspect of the present invention, there is provided an air conditioner including the flange as described above or the compressor as described above.
The utility model provides a flange, which comprises an exhaust pipeline, wherein the inner wall of the exhaust pipeline is provided with silencing holes, and the silencing holes are of blind hole structures; when the air flow in the exhaust pipeline passes through the opening of the silencing hole, the silencing hole reduces the noise of the air flow. The exhaust duct wall of the flange is provided with a blind hole-shaped silencing hole, and through the blind hole silencing principle, an air column in the blind hole vibrates under the action of sound pressure, so that the energy consumption is reduced to reduce exhaust noise.
Drawings
Fig. 1 is an exploded view of a pump body component according to an embodiment of the present invention;
FIG. 2 is a block diagram of an upper flange according to an embodiment of the present invention;
fig. 3 is a partial cross-sectional view of an upper flange according to an embodiment of the present invention;
fig. 4 is an axial cross-sectional view of the exhaust port of the upper flange according to an embodiment of the present invention;
fig. 5 is another schematic structural view of the muffling hole in the exhaust port of the upper flange according to the embodiment of the present invention;
fig. 6 is a schematic depth view of the muffling hole of the embodiment of the present invention;
fig. 7 is a schematic view of an expanded structure of the exhaust port according to the embodiment of the present invention;
FIG. 8 is a noise data diagram of the upper flange exhaust port of the embodiment of the present invention without the muffling hole;
FIG. 9 is a noise data diagram of the upper flange exhaust port of the present invention with muffling holes;
fig. 10 is a graph showing the variation of the performance parameter (COP) and the noise reduction amount (Δ dB) with the number of the noise reduction holes of the single cylinder compressor according to the embodiment of the present invention.
The reference numerals are represented as:
1. a pump body screw; 2. a muffler; 3. an upper flange; 31. an exhaust port; 311. a silencing hole; 4. a spring; 5. sliding blades; 6. a roller; 7. a cylinder; 8. a crankshaft; 9. and a lower flange.
Detailed Description
Referring to fig. 1 to 10 in combination, according to an embodiment of the present invention, a flange includes an exhaust duct, a muffling hole 311 is formed on an inner wall of the exhaust duct, and the muffling hole 311 is a blind hole structure; the muffling hole 311 reduces airflow noise when the airflow passes through the opening of the muffling hole 311 in the exhaust duct.
Under the condition that the exhaust pipeline can generate pneumatic noise, the inner wall of the exhaust pipeline is provided with the silencing hole 311 with a blind hole structure, and by utilizing the silencing principle of the blind hole, when exhaust passes through an orifice, an air column in the blind hole generates vibration under the action of sound pressure, and the friction damping of the vibration converts part of sound energy into heat energy to be dissipated, so that the noise generated by the exhaust is reduced.
In addition, the acoustic impedances of the muffling hole 311 and the exhaust pipe suddenly change, and a part of the sound energy is reflected back, so that a phase difference is generated between the transmitted sound wave and the reflected wave, and the sound waves interfere with each other, thereby achieving the purpose of muffling.
In order to achieve the pneumatic noise elimination effect more quickly, the silencing holes 311 are provided in plural numbers, and are arranged uniformly along the circumferential direction of the exhaust duct. In particular, the plurality of muffling holes 311 are divided into at least two groups, the muffling holes 311 of each group are arranged along the circumferential direction, and the plurality of groups of muffling holes 311 are arranged along the axial direction. Preferably, two adjacent groups of the muffling holes 311 are staggered in the circumferential direction.
The cross-sectional shape of the muffling hole 311 is one or a combination of a circle, a triangle and an ellipse, which can achieve a good muffling effect, and especially when the sound wave frequency is the same as the natural frequency of the muffling hole, the vibration speed is maximized, and at this time, the sound energy is consumed the most, and the muffling effect is optimal.
The following analysis was performed with the noise cancellation hole 311 as a circular hole:
after the pipe wall of the exhaust pipeline is provided with the silencing holeAlthough noise is reduced, the number n and the diameter D of the sound-deadening holes 311 are reduced by increasing the clearance volume after the hole is opened to deteriorate the performance1And hole depth h1The following relationship exists with the displacement volume v of the exhaust conduit:
thereby achieving the best noise reduction performance.
And the distance between the group of the silencing holes closest to the first end face of the exhaust pipeline and the first end face is L1, and the distance between the group of the silencing holes closest to the second end face of the exhaust pipeline and the second end face is L2On the development of the inner peripheral surface of the exhaust duct, the axial distance between two adjacent groups of the muffling holes is L3The minimum circumferential distance between two adjacent groups of the silencing holes is L4The included angle between the central connecting line of the silencing holes arranged in a staggered way and the vertical axis passing through the center of one of the silencing holes is α, and the distance between the adjacent silencing holes in the same group is L5The diameter of the exhaust pipeline is D, and the axial height of the exhaust pipeline is H; wherein L is more than or equal to 0.2mm1＝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。
For two circumferential arrangements arranged in a staggered manner, the included angle alpha has a better value range: alpha is more than or equal to 30 degrees and less than or equal to 60 degrees.
The pressure loss in the exhaust pipe is a function of the flow velocity squared, which is formulated as follows:
wherein, upsilon is Mc,
therefore, under the conditions of given temperature and mass density, the pressure loss depends on the Mach number, and the Mach number M is less than or equal to 0.3.
The effective flow area is:
the calculation relation between the flow Q and the displacement V is as follows:
q ═ Vf, f frequency (3)
Effective flow area A and geometric flow area AeThe relationship between them is:
coefficient of contraction kappaeAn empirical value of 0.6 was taken.
According to the formulas (2), (3) and (4), the Mach number M is not more than 0.3, and the relation between the discharge volume V and the diameter D is obtained as follows:
the utility model discloses from producing the pneumatic noise source and starting, design blind hole form bloop 311 on exhaust duct's inner wall, through the parameter of rationally designing the bloop, under the prerequisite of guaranteeing the compressor performance, solved the problem that the noise exceeds standard under the high frequency condition of compressor especially variable frequency compressor.
According to an embodiment of the present invention, a compressor includes the flange as described above.
The pump body explosion diagram of the compressor is shown in fig. 1 and comprises a silencer 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, wherein the silencer 2, the upper flange 3, the cylinder 7 and the lower flange 9 are fixed together by the pump body screw 1 through a preset screw hole, the cylinder 7, the roller 6 and the sliding vane 5 jointly surround to form a crescent compression cavity, the rotation of the crankshaft 8 drives the roller 6 to rotate along the wall of the cylinder 7 to work and enable the sliding vane 5 to reciprocate, and therefore the volume is changed, and air intake, compression and exhaust processes of a refrigerant are achieved.
The exhaust gas after the refrigerant compression is done is discharged into the compressor shell through the exhaust port 31 of the upper flange 3, and because the exhaust pressure is high, the air flow speed near the exhaust valve seat is high, the flow channel structure is complex, the interaction of the air flow and the solid wall surface is severe, and obvious air flow noise exists at the exhaust port 31 of the compressor.
The inner wall of the exhaust port 31 of the upper flange 3 is provided with a blind hole, noise data before and after the upper flange 3 is opened is compared, four small holes with the diameter of 1mm are uniformly distributed on the middle plane of the side wall of the upper flange 3, the hole depth is 0.8mm, as shown in comparison before and after opening of figures 8 and 9, the noise value after opening is lower than the data before opening, and particularly within the range of 800 plus 2500Hz, the noise improvement condition is better.
The performance parameter (COP) and the noise reduction amount (Delta dB) of a single-cylinder compressor are shown in the graph of the change along with the number of the small holes, as can be seen from the graph 10, the COP is reduced along with the increase of the number of the small holes, and the Delta dB is opposite, and when the number of the small holes is 10-17, the noise reduction effect is achieved, and the influence on the performance is not obvious.
For the different cross-sectional shapes of the muffling holes 311, table 1 shows the acoustic power ratios of the muffling holes 311 with different cross-sectional shapes and the exhaust ports 31 of the upper flange 3; acoustic power LPFor an index for measuring the noise of the compressor, the smaller the sound power value is, the lower the noise generated by the compressor is, LOFor the reference sound power value, the schemes are all that four small holes are uniformly distributed on the side wall of the upper flange 3, the hole depth is 1mm, and the result shows that the noise reduction value of the round small holes is optimal.
TABLE 1 noise values for different scenarios
| Scheme(s) | Acoustic power ratio LP/LO |
| Original scheme (non-hole) | 10 |
| Round hole (phi 1mm, hole depth 1mm) | 9.4 |
| Triangle (equilateral triangle, side length and hole depth 1mm) | 9.75 |
According to an embodiment of the present invention, an air conditioner includes the flange as described above or the compressor as described above.
It is easily understood by those skilled in the art that the above embodiments can be freely combined and superimposed without conflict.
The above description is only exemplary of the present invention and should not be taken as limiting the scope of the present invention, as any modifications, equivalents, improvements and the like made within the spirit and principles of the present invention are intended to be included within the scope of the present invention. The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, a plurality of modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (12)
1. A flange is characterized by comprising an exhaust pipeline, wherein a silencing hole (311) is formed in the inner wall of the exhaust pipeline, and the silencing hole (311) is of a blind hole structure; the muffling hole (311) reduces airflow noise when airflow in the exhaust duct passes through the opening of the muffling hole (311).
2. The flange according to claim 1, wherein the muffling hole (311) is provided in plurality, arranged along a circumferential direction of the exhaust duct.
3. The flange according to claim 2, wherein said muffling holes (311) are divided into at least two groups, each group of said muffling holes (311) being arranged in a circumferential direction, and a plurality of groups of said muffling holes (311) being arranged in an axial direction of said exhaust pipe.
4. A flange according to claim 3, wherein two adjacent sets of said muffling holes (311) are staggered in the circumferential direction.
5. The flange according to claim 2, 3 or 4, wherein the cross-sectional shape of the muffling hole (311) is one or more of a combination of a circle, a triangle and an ellipse.
6. Flange according to claim 5, wherein the number n and diameter D of the muffling holes (311) are circular holes when the muffling holes (311) are provided as circular holes1And hole depth h1With the displacement volume v of the exhaust duct:
the relationship (2) of (c).
7. The flange according to claim 6, wherein a group of said muffling holes closest to the first end face of said exhaust pipe is at a distance L from the first end face1The distance between a group of the silencing holes closest to the second end face of the exhaust pipeline and the second end face is L2On the development of the inner peripheral surface of the exhaust duct, the axial distance between two adjacent groups of the muffling holes is L3The minimum circumferential distance between two adjacent groups of the bloop (311) is L4The included angle between the central line of the silencing holes (311) arranged in a staggered way and the vertical axis passing through the center of one of the silencing holes is α, and the distance between the adjacent silencing holes (311) in the same group is L5The diameter of the exhaust pipeline is D, and the axial height of the exhaust pipeline is H; wherein L is more than or equal to 0.2mm1＝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。
8. A flange according to claim 7, characterized in that 30 ° ≦ α ≦ 60 °.
9. A flange according to claim 7, wherein the displacement v and the diameter D are:
the relationship (2) of (c).
10. A compressor, characterized in that it comprises a flange according to any one of claims 1 to 9.
11. The compressor according to claim 10, characterized in that the compressor comprises an upper flange (3), and a blind hole is arranged on the inner wall of the exhaust port (31) of the upper flange (3).
12. An air conditioner characterised by comprising a flange as claimed in any one of claims 1 to 9 or a compressor as claimed in any one of claims 10 to 11.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921796237.XU CN211288092U (en) | 2019-10-24 | 2019-10-24 | Flange, compressor and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921796237.XU CN211288092U (en) | 2019-10-24 | 2019-10-24 | Flange, compressor and air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN211288092U true CN211288092U (en) | 2020-08-18 |
Family
ID=72011248
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921796237.XU Active CN211288092U (en) | 2019-10-24 | 2019-10-24 | Flange, compressor and air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN211288092U (en) |
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2019
- 2019-10-24 CN CN201921796237.XU patent/CN211288092U/en active Active
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