CN205533205U - Compressor and air conditioner with same - Google Patents

Abstract

The utility model provides a compressor and air conditioner with same, the compressor, include: quiet set of body has quiet set of backpressure hole, noise elimination portion sets up on quiet set of body, and noise elimination portion is linked together with quiet set of backpressure hole so that the pressure fluctuation of the quiet set of downthehole production of backpressure reduces. Set up noise elimination portion on quiet set of body, reduced the quiet set of discharge pressure pulsation that the backpressure is downthehole effectively, and then reduced the exhaust noise of compressor, reach the mesh of the noise of reduction compressor complete machine to the effectual quality that promotes the compressor.

Description

Compressor and air conditioner with same

Technical Field

The utility model relates to a compressor technical field particularly, relates to a compressor and have its air conditioner.

Background

A scroll compressor in the related art is shown in fig. 1 and 2, and is mainly composed of a pump body portion and a motor portion. The pump body part comprises a static disc 1, a movable disc 2, a cross sliding ring 3, an upper bracket 4, a compressor shell 5 and the like. The motor drives the crankshaft to rotate in the scroll compressor, the eccentric part on the crankshaft drives the movable disk to rotate, the movable disk cannot rotate under the action of the cross sliding ring 3, and the movable disk 2 does rotary translation without rotation by taking the center of the static disk 1 as a rotation center. The movable plate 2 and the stationary plate 1 form a periodic compression chamber engaged with each other, thereby achieving suction, compression and discharge of gas. The movable plate 2 is always in a floating state during operation, which is mainly balanced by the back pressure chamber 9. A back pressure hole 6 and a back pressure hole 7 are formed in the movable disc 2, and gas in the middle compression cavity sequentially passes through the back pressure hole 6, the back pressure hole 7 and a back pressure cavity communicating hole 8 in the static disc to introduce airflow into a back pressure cavity 9, so that the movable disc 2 is in an axially balanced state.

Because the pressure of the middle compression cavity is different from that of the back pressure cavity 9, when the middle compression cavity is communicated with the back pressure cavity 9, large pressure pulsation can be generated, the exhaust noise of the scroll compressor can be increased due to the pressure pulsation, and the quality problem of the compressor is influenced.

SUMMERY OF THE UTILITY MODEL

The utility model discloses a main aim at provides a compressor and have its air conditioner to solve the big problem of compressor noise among the prior art.

In order to achieve the above object, according to an aspect of the present invention, there is provided a compressor including: the static disc body is provided with a static disc back pressure hole; the silencing part is arranged on the static disc body and communicated with the static disc back pressure hole so as to reduce pressure pulsation generated in the static disc back pressure hole.

Further, the muffler portion includes: a resonant cavity; and one end of the connecting channel is communicated with the resonance cavity, and the other end of the connecting channel is communicated with the static disc backpressure hole.

Further, the muffling frequency of the muffling portion is f_rAnd, in addition,

$f_r=\frac{c}{2\mathrm{\π}}\sqrt{\frac{S}{(t+0.85d)V}},$

wherein c is the sound velocity in the refrigerant; t is the length of the connecting channel; d is the diameter of the cross section of the connecting channel; v is the volume of the resonant cavity; s is the area of the cross section of the connecting channel.

Further, the muffling amount of the muffling portion is TL, and,

$TL=10\×\lg \[1+{\left(\frac{\sqrt{\frac{S}{(t+0.85d)}V}}{2S_0(\frac{f}{f_r}-\frac{f_r}{f})}\right)}^2\],$

wherein t is the length of the connecting channel; d is the diameter of the cross section of the connecting channel; v is the volume of the resonant cavity; s is the area of the cross section of the connecting channel; f. of_rIs the muffling frequency of the muffling portion; f is the frequency of the sound inside the back pressure hole of the static disc; s₀The area of the longitudinal section of the back pressure hole of the static disc.

Further, the resonant cavity is a closed accommodating cavity which is arranged in the static disc body.

Further, the connecting channel is arranged in the static disc body.

Further, the connecting passage is a communicating groove provided on the surface of the stationary disc body.

Further, the resonance cavity is a groove concavely arranged on the surface of the static disc body.

Further, the compressor further includes: the movable disk body, the rotary translation of no rotation is done to the movable disk body in the compressor, and the movable disk body has movable disk backpressure hole, and when the rotary translation of no rotation was done to the movable disk body, the silence portion was kept away from to movable disk backpressure hole.

Further, when the movable disc body does the rotary translation without rotation, the projection of the motion track of the back pressure hole of the movable disc on the fixed disc body is a track, and the silencing part is arranged far away from the outer side of the track.

According to another aspect of the present invention, there is provided an air conditioner, comprising a compressor, wherein the compressor is the above compressor.

Use the technical scheme of the utility model, a compressor is provided, this compressor includes quiet dish body and noise elimination portion. The static disc body is provided with a static disc backpressure hole, and the silencing part is arranged on the static disc body and communicated with the static disc backpressure hole so as to reduce pressure pulsation generated in the static disc backpressure hole. The silencing part is arranged on the static disc body, so that exhaust pressure pulsation in the back pressure hole of the static disc is effectively reduced, the exhaust noise of the compressor is reduced, the purpose of reducing the noise of the whole compressor is achieved, and the quality of the compressor is effectively improved.

Drawings

The accompanying drawings, which form a part of the present application, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:

fig. 1 is a schematic view showing a structure of a compressor in the prior art;

FIG. 2 shows an enlarged schematic view of the structure at A in FIG. 1;

fig. 3 shows a schematic structural view of an embodiment of the muffling portion on the static disc of the compressor according to the present invention;

FIG. 4 is an enlarged schematic view of the structure at B in FIG. 3;

Fig. 5 is a schematic sectional view showing the sound deadening portion on the stationary disk in fig. 4; and

fig. 6 shows a graph of the amount of sound muffling of the compressor according to the present invention as a function of the sound frequency inside the compressor.

Wherein the figures include the following reference numerals:

1. a stationary disc; 2. a movable plate; 3. a cross slip ring; 4. an upper bracket; 5. a housing; 6. a back pressure hole; 7. a back pressure hole; 8. a back pressure chamber communication hole; 9. a back pressure chamber;

10. a stationary disc body; 11. a static disc backpressure hole; 20. a sound deadening portion; 21. a resonant cavity; 22. a connecting channel; 30. a movable disc body; 31. a dynamic disc back pressure hole; 32. a trajectory.

Detailed Description

It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.

As shown in fig. 3 and 4, according to an embodiment of the present invention, there is provided a compressor including a stationary plate body 10 and a muffler portion 20. The stationary disc body 10 has a stationary disc back pressure hole 11. The sound deadening portion 20 is provided in the stationary disk main body 10, and the sound deadening portion 20 communicates with the stationary disk back pressure hole 11 to reduce pressure pulsation generated in the stationary disk back pressure hole 11.

In the embodiment, the silencing part 20 is arranged on the static disc body 10, so that the exhaust pressure pulsation in the static disc back pressure hole 11 is effectively reduced, the exhaust noise of the compressor is further reduced, and the purpose of reducing the noise of the whole compressor is achieved. Thereby the quality of compressor has effectively been promoted. The muffler portion 20 has a simple structure, is low in cost, and is easy to process and implement.

Wherein the sound-deadening portion 20 includes a resonance chamber 21 and a connecting passage 22. One end of the connecting passage 22 communicates with the resonance chamber 21, and the other end of the connecting passage 22 communicates with the stationary disc back pressure hole 11. When the gas in the static disc back pressure hole 11 is excited by the sound wave, the gas in the connecting channel 22 flows towards the inner direction of the resonant cavity 21 and the direction of the connecting channel 22 far away from the resonant cavity 21, so that the loss of sound energy in the static disc back pressure hole 11 is caused, and the purpose of silencing the compressor is achieved.

Through a plurality of experimental researches, when the back pressure cavity is communicated with the middle compression cavity of the compressor, the pressure pulsation is increased in a frequency range of 500-1000Hz, which indicates that the frequency range pulsation can be generated in the back pressure hole 11 of the static disc, and the pressure pulsation can increase the exhaust noise of the compressor and radiate outwards through the shell of the compressor, thereby causing the problem of large overall noise of the compressor. Meanwhile, the operation of the movable disc is not stable, the power consumption of the compressor is increased, and the performance of the compressor is influenced.

When the gas in the middle compression cavity of the compressor is introduced into the back pressure cavity, and the noise frequency component in the back pressure hole 11 of the static disc is consistent with the natural frequency of the resonant cavity 21, the sound energy attenuation of the back pressure hole 11 of the static disc reaches the maximum. Thereby achieving the purpose of reducing exhaust pulsation and exhaust noise.

In the present embodiment, the muffling frequency of the resonant cavity 21 is mainly determined by the length of the connecting channel 22, the cross-sectional area of the connecting channel 22 and the volume of the resonant cavity 21. The sound attenuation frequency of the sound attenuation part 20 is represented as f_rThen, there are:

$f_r=\frac{c}{2\mathrm{\π}}\sqrt{\frac{S}{(t+0.85d)V}},$

when the amount of sound attenuation of the sound attenuation portion 20 is TL, there is,

$TL=10\×\lg \[1+{\left(\frac{\sqrt{\frac{S}{(t+0.85d)}V}}{2S_0(\frac{f}{f_r}-\frac{f_r}{f})}\right)}^2\],$

where c is the sound velocity in the refrigerant, t is the length of the connecting channel 22, d is the diameter of the cross section of the connecting channel 22, V is the volume of the resonance chamber 21, S is the area of the cross section of the connecting channel 22, f_rThe sound-deadening frequency of the sound-deadening portion 20, f is the frequency of the sound inside the back pressure hole 11 of the stationary disk, S₀The area of the longitudinal section of the stationary disc back pressure hole 11. The silencing quantity curve of the silencing structure is shown in fig. 6, the structure can well reduce exhaust noise generated when the back pressure holes are communicated, and particularly 800Hz is more obvious.

Preferably, the resonance cavity 21 may be a closed accommodation cavity opened in the stationary disk body 10. This makes the resonance chamber 21 have a good silencing effect on the noise generated when the static disc back pressure hole 11 communicates with the back pressure hole on the dynamic disc body 30. Of course, the resonance chamber 21 can also be a groove concavely disposed on the surface of the static disc body 10, and the open side of the groove must be sealed with the dynamic disc body 30 to achieve effective sound attenuation. The resonance chamber 21 may also be a cylindrical cavity or a spherical cavity provided in the stationary disk body 10.

Further, the connecting passage 22 may also be provided in the stationary plate body 10. This can increase the sealability between the connection passage 22 and the resonance chamber 21. Of course, the connection passage 22 may be a communication groove provided between the static disc back pressure hole 11 and the resonance chamber 21, or a through hole provided in the static disc body 10 and located at a certain height above the static disc body 10 and communicating with the resonance chamber 21 and the static disc back pressure hole 11. That is, the resonance chamber 21 may be opened at any position communicating with the back pressure hole 11 of the stationary disk as long as the noise reduction frequency, the noise reduction amount, and the occurrence of the blow-by are satisfied. Of course, the connecting passage 22 may also be a communicating groove provided on the surface of the stationary disk body 10. Likewise, the open sides of the communication grooves should be sealed against the cam plate body 30 to optimize the sound damping effect of the resonance chamber 21.

Wherein, the movable disk body 30 does the rotary translation of no rotation in the compressor, and movable disk body 30 has movable disk backpressure hole 31, and when movable disk body 30 does the rotary translation of no rotation, movable disk backpressure hole 31 is kept away from noise cancelling part 20. The arrangement effectively avoids the air leakage of the compressor when the dynamic disc back pressure hole 31 is communicated with the noise elimination part 20, thereby influencing the noise elimination effect of the noise elimination part 20. As shown in fig. 4 and 5, when the movable disk main body 30 performs the rotational translation without rotating, a projection of a movement locus of the movable disk back pressure hole 31 on the stationary disk main body 10 is a locus 32, and the sound deadening portion 20 is disposed away from an outer side of the locus 32.

Because the movable disc body 30 does non-rotation rotary translation around a circle with a certain radius. Therefore, any point on the movable disc body 30 makes a rotary translation around the circle, and the movement track 32 of the movable disc backpressure hole 31 of the movable disc body 30. If the resonant cavity 21 silencing structure is designed in the motion track of the dynamic disc backpressure hole 31, the dynamic disc backpressure hole 31 is communicated with the resonant cavity 21, which causes the dynamic disc backpressure hole 31, the resonant cavity 21 and the connecting channel 22 in the compression cavity to leak gas into the back pressure cavity of the compressor, so that the performance of the compressor is reduced, and the silencing part 20 of the compressor can only be opened in the area outside the motion track of the dynamic disc backpressure hole 31.

Therefore, the exhaust pressure pulsation generated when the middle compression cavity of the compressor is communicated with the back pressure cavity can be effectively reduced, so that the noise generated by the exhaust pressure pulsation is reduced, and the noise of the whole compressor is greatly reduced. After the exhaust pressure pulsation is reduced, the movable disc body 30 can better stably run under the balance action of the supporting force and the back pressure force of the axial gas, the power consumption of the compressor is reduced, and the performance of the compressor is effectively improved.

The compressor in the above-mentioned embodiment can also be used in air conditioner technical field, namely according to the utility model discloses a further aspect provides an air conditioner. The air conditioner comprises a compressor, and the compressor is the compressor in the embodiment.

While the invention has been described with respect to the preferred embodiments, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (11)

1. A compressor, comprising:

a stationary disc body (10) having a stationary disc back pressure hole (11);

the silencing part (20) is arranged on the static disc body (10), and the silencing part (20) is communicated with the static disc back pressure hole (11) so that pressure pulsation generated in the static disc back pressure hole (11) is reduced.

2. Compressor, in accordance with claim 1, characterized in that said muffling portion (20) comprises:

a resonant cavity (21);

a connecting passage (22), one end of the connecting passage (22) is communicated with the resonant cavity (21), and the other end of the connecting passage (22) is communicated with the static disc backpressure hole (11).

3. Compressor according to claim 2, characterized in that the muffling frequency of the muffling portion (20) is f_rAnd, in addition,

$f_r=\frac{c}{2\mathrm{\π}}\sqrt{\frac{S}{(t+0.85d)V}},$

wherein,

c is the sound velocity in the coolant;

t is the length of the connecting channel (22);

d is the diameter of the cross section of the connecting channel (22);

v is the volume of the resonance cavity (21);

s is the area of the cross section of the connecting channel (22).

4. Compressor according to claim 2, characterized in that the amount of sound deadening of the sound deadening portion (20) is TL, and,

$TL=10\×\lg \[1+{\left(\frac{\sqrt{\frac{S}{(t+0.85d)}V}}{2S_0(\frac{f}{f_r}-\frac{f_r}{f})}\right)}^2\],$

wherein,

t is the length of the connecting channel (22);

d is the diameter of the cross section of the connecting channel (22);

V is the volume of the resonance cavity (21);

s is the area of the cross section of the connecting channel (22);

f_ris the muffling frequency of the muffling portion (20);

f is the frequency of the sound inside the static disc backpressure hole (11);

S₀the area of the longitudinal section of the back pressure hole (11) of the static disc is shown.

5. Compressor according to claim 2, characterized in that said resonance chamber (21) is a hermetic housing chamber opening inside said static disc body (10).

6. Compressor according to claim 2, characterized in that said connecting channel (22) is provided inside said static disc body (10).

7. Compressor according to claim 2, characterized in that said connecting channel (22) is a communicating groove provided on the surface of said static disc body (10).

8. Compressor according to claim 2, characterized in that said resonance chamber (21) is a groove concavely provided on the surface of said static disc body (10).

9. The compressor of claim 1, further comprising:

the movable disc body (30) does non-rotation rotary translation in the compressor, the movable disc body (30) is provided with a movable disc backpressure hole (31), and when the movable disc body (30) does non-rotation rotary translation, the movable disc backpressure hole (31) is far away from the sound eliminating part (20).

10. The compressor of claim 9, wherein when the movable disc body (30) performs a non-self-rotating rotary translation, a projection of a motion track of the movable disc back pressure hole (31) on the stationary disc body (10) is a track (32), and the sound deadening portion (20) is disposed away from an outer side of the track (32).

11. An air conditioner comprising a compressor, wherein the compressor is as claimed in any one of claims 1 to 10.