JP2017115815A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor reduced in noise.SOLUTION: An outflow hole 71a provided on one side of a muffler member 6 and an outflow hole 71b provided on the other side of the muffler member 6 are arranged asymmetrically with respect to a virtual plane A. Therefore, a refrigerant passage from a discharge hole 223 to the outflow hole 71b and a refrigerant passage from the discharge hole 223 to the outflow hole 71a are asymmetrical with respect to the virtual plane A. Accordingly, vibrations of a refrigerant respectively flowing both sides of the muffler member 6 are prevented from being simultaneously increased by resonance with vibration of a motor. As a result, a compressor can be reduced in noise.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a compressor that compresses a refrigerant.

The compressors described in Patent Documents 1 and 2 compress the refrigerant inside the casing.
The casing accommodates a rotor for compressing the refrigerant, and the rotor is connected to a rotating shaft portion that is an output shaft of the motor. The rotating shaft portion penetrates the casing.
The periphery of the rotating shaft portion of the casing is covered with a muffler member. A muffler chamber for reducing noise generated by the compressor is formed between the facing surfaces of the casing and the muffler member.
The casing is provided with a discharge hole. The muffler member is provided with two outflow holes. The refrigerant is discharged from the inside of the casing through the discharge hole to the muffler chamber, and flows out of the casing through one of the two outflow holes from the muffler chamber.

The shape of the muffler chamber is symmetric with respect to an imaginary plane passing through the center of the discharge hole and the axis of the rotary shaft. The two outflow holes are arranged symmetrically with respect to the virtual plane, and the axis of the rotating shaft portion is on a straight line connecting the two outflow holes. Therefore, the refrigerant path from the discharge hole to each of the two outflow holes is symmetric with respect to the virtual plane.
At this time, the refrigerant flowing out through one outflow hole and the refrigerant flowing out through the other outflow hole serve as symmetrical sound sources, and the vibration of the refrigerant is offset. As a result, noise can be reduced.

JP 2009-250111 A JP 2010-242541 A

However, in the case of the compressors described in Patent Documents 1 and 2, noise may increase abruptly when the rotational speed of the motor is changed.
The cause of the sudden increase in noise is that the vibration of the refrigerant flowing from the discharge hole to one outflow hole and the vibration of the refrigerant flowing from the discharge hole to the other outflow hole increase simultaneously due to resonance with the vibration of the motor. It is. That is, at the time of resonance, noise cannot be effectively reduced even if the vibration is canceled by a symmetric sound source.

  This invention is made | formed in view of such a situation, The main objective is to provide the compressor made quiet.

  The compressor according to the present embodiment includes a rotor for compressing a refrigerant, a rotating shaft portion to which the rotor is coupled, and a rotating shaft portion that rotatably supports the rotor. A compressor comprising: a casing in which a refrigerant is compressed; and a muffler member that covers a periphery of the rotating shaft portion of the casing and forms a muffler chamber for reducing noise between the casing and the casing. Are provided with discharge holes through which the refrigerant discharged from the casing into the muffler chamber passes, and the muffler member has a plurality of outflow holes through which the refrigerant flowing out of the muffler chamber passes. The same number of holes are provided on one side and the other side of the virtual plane passing through the opening center of the hole and the axis of the rotation shaft portion, and the outflow hole provided on the one side of the muffler member; Provided on the other side And it is being outflow hole, characterized in that it is arranged asymmetrically with respect to the virtual plane.

  The compressor according to the present embodiment is characterized in that a plurality of the outflow holes are provided on each of the one side and the other side of the muffler member.

  The compressor according to the present embodiment is characterized in that the inner diameter of each outflow hole is 5 mm or less.

  In the compressor according to the present embodiment, the one side and the other side of the muffler chamber are each provided with a narrowing portion that partially narrows the flow of the refrigerant, and the one side and the other side of the muffler member, respectively. In addition, there is an outflow hole arranged at a position where the distance from the narrowing portion is 10 mm or less.

In the compressor according to the present embodiment, the outflow hole provided on one side of the muffler member and the outflow hole provided on the other side of the muffler member are arranged asymmetrically with respect to the virtual plane.
Therefore, the vibration of the refrigerant flowing on both sides of the muffler member is prevented from increasing simultaneously due to resonance with the vibration of the motor. As a result, the compressor can be silenced.

1 is a longitudinal sectional view schematically showing a configuration of a compressor according to a first embodiment. It is a longitudinal section showing the composition near the casing with which a compressor is provided. It is sectional drawing which shows schematically the structure of the lid | cover which a casing has. It is a top view which shows schematically the structure of the muffler member attached to the lid | cover. It is a characteristic view for comparing the sound pressure level of the noise of 20 kHz or less emitted from the compressor according to Embodiment 1 and the compressor used as a comparative example. It is a characteristic view for comparing the sound pressure level of the noise of 1.6 kHz or less emitted from the compressor according to Embodiment 1 and the compressor used as a comparative example. 6 is a plan view schematically showing a configuration of a muffler member included in a compressor according to Embodiment 2. FIG. It is a characteristic view for comparing the sound pressure level of the noise which each of the compressor concerning Embodiment 2 and the compressor used as a comparative example emits. FIG. 6 is a plan view schematically showing a configuration of a muffler member included in a compressor according to a third embodiment.

  Hereinafter, the present invention will be described in detail with reference to the drawings illustrating embodiments thereof.

Embodiment 1.
FIG. 1 is a longitudinal sectional view schematically showing the configuration of the compressor according to the first embodiment.
In the figure, reference numeral 1 denotes a compressor, and the compressor 1 includes a casing 2, a rotor 3, a housing 4, and a motor 5.
FIG. 2 is a longitudinal sectional view schematically showing the configuration in the vicinity of the casing 2.

First, the casing 2 will be described with reference to FIGS. 1 and 2.
The casing 2 includes a casing body 21 and lids 22 and 23.
The casing body 21 has a cylindrical shape. A suction port 211 is provided in the peripheral wall of the casing body 21. The suction pipe 11 is connected to the suction port 211.

FIG. 3 is a cross-sectional view schematically showing the configuration of the lid 22.
Here, the lids 22 and 23 will be described with reference to FIGS.
The lids 22 and 23 each have a disk shape. Cylindrical bosses 221 and 231 project from the centers of the lids 22 and 23. Bearings 222 and 232 are arranged on the inner peripheral surfaces of the bosses 221 and 231.
The lid 22 closes one end opening of the casing body 21 with the boss 221 facing outward. Similarly, the lid 23 closes the other end opening of the casing body 21 with the boss 231 facing outward.

The casing 2 accommodates the rotor 3. The rotor 3 has a cylindrical shape. The rotor 3 is connected to the rotating shaft portion 31.
An eccentric portion 31 a is integrally provided in the middle of the rotational shaft portion 31 in the axial direction. The eccentric portion 31 a has a cylindrical shape that is eccentric with respect to the rotating shaft portion 31. The rotor 3 is coaxially fitted on the eccentric part 31a.

The rotating shaft portion 31 is inserted through the boss 221, the casing body 21, and the boss 231. The rotating shaft portion 31 is rotatably supported by bearings 222 and 232, respectively. That is, the rotating shaft portion 31 is rotatably supported by the casing 2. The rotating shaft portion 31, the casing body 21, and the bosses 221 and 231 are arranged coaxially. The rotating shaft portion 31 extends outside the boss 221.
The lid 22 is provided with a circular discharge hole 223. The discharge hole 223 is separated from the boss 221 by an appropriate length toward the peripheral edge side of the lid 22.

FIG. 4 is a plan view schematically showing the configuration of the muffler member 6 attached to the lid 22.
Next, the configuration of the muffler member 6 will be described with reference to FIGS.
The muffler member 6 has a dish shape. The muffler member 6 has a bottom wall 61, a side wall 62, and a flange 63.
The bottom wall 61 has a cross plate shape.
A circular through hole 611 is provided at the center of the bottom wall 61. The inner diameter of the through hole 611 is approximately the same as the outer diameter of the boss 221.

The side wall 62 protrudes in a direction intersecting the bottom wall 61 over the entire circumference of the peripheral edge of the bottom wall 61.
The flange 63 protrudes outward over the entire circumference of the tip of the side wall 62. The collar 63 has a flat plate shape with a circular outer shape. The flange 63 is provided with four circular bolt holes 631, 631,.

Next, attachment of the muffler member 6 to the lid 22 will be described.
The muffler member 6 uses bolts 64, 64,... Inserted into bolt holes 631, 631,... With the boss 221 fitted in the through hole 611 and the flange 63 in contact with the peripheral edge of the outer surface of the lid 22. And bolted to the lid 22. As a result, the muffler member 6 covers the lid 22 (that is, the periphery of the rotating shaft portion 31 of the casing 2) from the outside.
As a result, the bottom wall 61 faces the outer surface of the lid 22 and faces the discharge hole 223. Further, the side wall 62 rises outward from the outer surface of the lid 22.

By attaching the muffler member 6 to the lid 22, a muffler chamber 65 is formed between the opposed surfaces of the muffler member 6 and the lid 22.
The muffler chamber 65 is surrounded by the outer surface of the lid 22, the outer peripheral surface of the boss 221, the inner surface of the bottom wall 61, and the inner surface of the side wall 62. The shape of the muffler chamber 65 is symmetric with respect to an imaginary plane A passing through the opening center 22a of the discharge hole 223 and the axis 31b of the rotation shaft portion 31.
Hereinafter, one side having the virtual plane A as a boundary is referred to as a left side, and the other side having the virtual plane A as a boundary is referred to as a right side.

Next, details of the muffler chamber 65 will be described. The muffler chamber 65 is divided into four compartments 81, 82a, 82b, 83 corresponding to the four sides of the cross of the bottom wall 61. The compartments 81, 82 a, 83, 82 b are arranged side by side in the circumferential direction of the rotary shaft portion 31.
Each of the compartments 81 and 83 has a symmetrical shape with respect to the virtual plane A. The compartment 81 communicates with the inside of the casing 2 through the discharge hole 223.
The compartment 82a is arranged on the left side, and the compartment 82b is arranged on the right side. The compartments 82a and 82b are symmetrical with respect to the virtual plane A.

Further, the muffler chamber 65 has four narrowing portions 84a, 84b, 85a, 85b. The narrowing-down portion 84a is a communication path that communicates the compartments 81 and 82a. The narrowing-down portion 84b is a communication passage that communicates the compartments 81 and 82b. The narrowing-down portion 85a is a communication passage that communicates the compartments 82a and 83. The narrowing-down portion 85b is a communication path that communicates the compartments 82b and 83. The narrowing portions 84 a, 85 a, 85 b, 84 b are juxtaposed in the circumferential direction at a position corresponding to the peripheral edge portion of the through hole 611.
The separation distance between the side wall 62 facing each of the narrowing portions 84a, 84b, 85a, 85b and the outer peripheral surface of the boss 221 is such that the side wall 62 facing each of the compartments 81, 82a, 82b, 83, and the outer peripheral surface of the boss 221. Shorter than the separation distance between.

The bottom wall 61 is provided with four circular outflow holes 71a, 72a, 71b, 72b.
The outflow holes 71a and 72a are provided on one side of the muffler member 6 with the virtual plane A as a boundary, and the outflow holes 71b and 72b are provided on the other side of the muffler member 6 with the virtual plane A as a boundary. Yes. The outflow holes 71a, 72a, 71b, 72b are arranged asymmetrically with respect to the virtual plane A.

  More specifically, the outflow holes 71a and 72a are provided in the bottom wall 61 facing the compartment 82a. The outflow holes 71 a and 72 a are both arranged in a range closer to the compartment 81 than the compartment 83. The outflow hole 71a is disposed in the vicinity of the narrowing portion 84a and is spaced apart from the narrowing portion 85a. The outflow hole 72a is spaced apart from both the narrowed portions 84a and 85a.

  Outflow holes 71b and 72b are provided in the bottom wall 61 facing the compartment 82b. Both the outflow holes 71 b and 72 b are arranged in a range closer to the compartment 83 than the compartment 81. The outflow hole 71b is disposed in the vicinity of the narrowing portion 85b and is spaced apart from the narrowing portion 84b. The outflow hole 72b is spaced apart from both of the narrowed portions 84b and 85b.

Next, the housing 4 will be described with reference to FIGS. 1 and 2. Below, the up-down direction of FIG.1 and FIG.2 is demonstrated as the up-down direction of the compressor 1. FIG.
The housing 4 includes a housing body 41 and a lid 42.
The casing body 41 has a bottomed cylindrical shape that opens upward. The casing main body 21 is fitted in the casing main body 41 coaxially. The lid 22 is disposed on the upper side, and the lid 23 is disposed on the lower side.

A discharge pipe 12 is connected to the housing body 41. The inside of the housing 4 and the outside of the compressor 1 communicate with each other through the discharge pipe 12.
The suction pipe 11 passes through the peripheral wall of the housing body 41. The inside of the casing 2 and the outside of the compressor 1 communicate with each other through the suction port 211 and the suction pipe 11.

The lid 42 includes a bottomed cylinder 421 that opens downward, and a flange 422 that protrudes outward from the lower end of the bottomed cylinder 421.
The collar 422 is attached to the upper end portion of the housing body 41. As a result, the lid 42 closes the upper end opening of the housing body 41. The upper end portion of the rotating shaft portion 31 is inserted into the bottomed cylinder 421. The bottomed cylinder 421 and the rotating shaft portion 31 are arranged coaxially.

Next, the motor 5 will be described.
The motor 5 includes a stator 51 and a rotor 52.
The stator 51 has a coil. The stator 51 has an annular shape and is fitted and fixed to the bottomed cylinder 421.
The rotor 52 has a magnet. The rotor 52 has an annular shape, and is arranged coaxially with the stator 51 inside the bottomed cylinder 421.
The rotor 52 is coaxially fitted and fixed to the upper end portion of the rotating shaft portion 31. The rotor 52 and the rotating shaft portion 31 rotate integrally.

Next, the outline of the refrigerant flow in the compressor 1 will be described.
When the motor 5 is operated, the rotating shaft portion 31 rotates with the rotation of the rotor 52. Accordingly, the rotor 3 rotates.
The refrigerant inside the casing 2 is compressed by the rotation of the rotor 3. The compressed refrigerant is discharged into the muffler chamber 65 through the discharge hole 223. Further, due to the rotation of the rotor 3, the refrigerant is sucked into the casing 2 from the outside of the compressor 1 through the suction pipe 11 and the suction port 211.
The refrigerant discharged into the muffler chamber 65 flows out of the casing 2 inside the housing 4 and the outside of the muffler chamber 65 through any of the outflow holes 71a, 72a, 71b, 72b. 12 is discharged to the outside of the compressor 1.

Next, the flow of the refrigerant in the muffler chamber 65 will be described in detail with reference to FIGS. 3 and 4.
The refrigerant that has passed through the discharge hole 223 flows into the compartment 81.
The refrigerant in the compartment 81 passes through the narrowed portion 84a and flows into the compartment 82a, or passes through the narrowed portion 84b and flows into the compartment 82b.

  Since the narrowing portion 84a is narrower than each of the compartment 81 and the compartment 82a, the refrigerant flow from the compartment 81 to the compartment 82a is partially restricted. Similarly, the narrowing part 84b partially narrows the refrigerant flow from the compartment 81 to the compartment 82b. The refrigerant passing through the narrowing portions 84a and 84b is once compressed and then expanded.

  The refrigerant that has flowed into the branch chamber 82a flows out of the muffler chamber 65 through one of the outflow holes 71a and 72a. Similarly, the refrigerant that has flowed into the branch chamber 82b flows out of the muffler chamber 65 through one of the outflow holes 71b and 72b.

The refrigerant paths from the discharge hole 223 to the outflow holes 71a, 72a, 71b, 72b are asymmetric with respect to the virtual plane A.
The length of the refrigerant path from the discharge hole 223 to the outflow hole 71a is different from the length of the refrigerant path from the discharge hole 223 to each of the outflow holes 71b and 72b. Similarly, the length of the refrigerant path from the discharge hole 223 to the outflow hole 72a is different from the length of the refrigerant path from the discharge hole 223 to each of the outflow holes 71b and 72b.

Next, noise suppression by the muffler chamber 65 will be described.
5 and 6 are characteristic diagrams for comparing the sound pressure levels of noise generated by the compressor 1 and the compressors used as comparative examples. FIG. 5 shows the sound pressure level of noise below 20 kHz, and FIG. 6 shows the sound pressure level of noise below 1.6 kHz.
5 and 6, the horizontal axis represents the rotation speed [rpm] of the motor 5, and the vertical axis represents the A characteristic sound pressure level [dbA] of the noise. The relationship between the rotational speed and the sound pressure level in the case of the compressor 1 is shown by a solid line. The relationship between the rotational speed and the sound pressure level in the case of a compressor used as a comparative example is indicated by a broken line.
In the compressor 1 used for the experiment, the inner diameter of each of the outflow holes 71a and 71b is 3 mm, and the inner diameter of each of the outflow holes 72a and 72b is 4 mm.

Here, the compressor of the comparative example will be described.
The compressor of the comparative example has substantially the same configuration as the compressor 1.
However, the outflow holes of the comparative example are arranged one by one on the bottom wall 61 facing the compartment 82a and on the bottom wall 61 facing the compartment 82b. The inner diameter of the outflow hole of the comparative example is 7 mm. The two outflow holes of the comparative example are arranged symmetrically with respect to the virtual plane A, and the axis 31b of the rotation shaft portion is on a straight line connecting the two outflow holes. The refrigerant path from the discharge hole 223 to each of the two outflow holes of the comparative example is symmetric with respect to the virtual plane A. Therefore, the length of the refrigerant path from the discharge hole 223 to the left outflow hole of the comparative example is equal to the length of the refrigerant path from the discharge hole 223 to the right outflow hole of the comparative example.

Next, the sound pressure levels of the noises of the compressor 1 and the compressors of the comparative example are compared.
When the rotational speed of the motor 5 is changed in the range of about 3800 rpm to about 5800 rpm, the noise of the compressor 1 is 46.4 dbA to 49.4 dbA (in the case of FIG. 5) or 35.3 dbA to 42.8 dbA (in FIG. 6). The sound pressure level fluctuates within the range up to. The maximum sound pressure level is 49.4dbA or 42.8dbA at about 5600rpm.
On the other hand, when the number of rotations of the motor 5 is changed in the range from about 3800 rpm to about 5800 rpm, the noise of the compressor of the comparative example is from 45.3 dbA to 50.4 dbA (in the case of FIG. 5) or from 31.9 dbA to 47.1 dbA The sound pressure level fluctuates within the range (in the case of FIG. 6). The sound pressure level increases sharply at about 5600 rpm and reaches a maximum of 50.4 dbA or 47.1 dbA.

Next, noise suppression of the compressor 1 and the compressors of the comparative example will be described.
First, the case of the compressor of the comparative example will be described.
In the case of the compressor of the comparative example, the refrigerant flowing out through the left outflow hole and the refrigerant flowing out through the right outflow hole serve as symmetrical sound sources, and the vibration of the refrigerant is offset. As a result, noise can be reduced.
However, when the rotational speed of the motor 5 is about 5600 rpm, the sound pressure level peaks. This is because the vibration of the refrigerant flowing from the discharge hole 223 to the left outflow hole and the vibration of the refrigerant flowing from the discharge hole 223 to the right outflow hole increase simultaneously due to resonance with the vibration of the motor. That is, at the time of resonance, noise cannot be effectively reduced even if the vibration is canceled by a symmetric sound source.

Next, the case of the compressor 1 will be described.
In the case of the compressor 1 as well, when the rotational speed of the motor 5 is about 5600 rpm, a peak of the sound pressure level occurs. However, in the case of the compressor 1, the peak value of the sound pressure level is lower than in the case of the compressor of the comparative example. This is because the vibration of the refrigerant flowing from the discharge hole 223 to each of the outflow holes 71a and 72a and the vibration of the refrigerant flowing from the discharge hole 223 to each of the outflow holes 71b and 72b do not increase simultaneously due to resonance with the vibration of the motor. That is. That is, noise can be effectively suppressed during resonance.

In the case of the compressor 1, the sound pressure level other than at the time of resonance tends to be higher than that of the compressor of the comparative example, but is within a practical range.
Hereinafter, suppression of noise of the compressor 1 will be further described.

In the case of the compressor 1, on the left side of the muffler chamber 65, the vibrations of the refrigerant flowing out from the outflow holes 71a and 72a interfere with each other and cancel each other. In addition, the vibration energy of the refrigerant is reduced by friction between the refrigerant and the opening peripheral portions of the outflow holes 71a and 72a.
Also on the right side of the muffler chamber 65, the vibrations of the refrigerant flowing out from the outflow holes 71b and 72b interfere with each other and cancel each other. In addition, the vibration energy of the refrigerant is reduced by friction between the refrigerant and the opening peripheral edge of each of the outflow holes 71b and 72b.
As a result, as the number of outflow holes provided on the left side and the right side of the muffler member 6 increases, noise is more easily suppressed.

  Furthermore, the inner diameter of each of the outflow holes 71a and 72a is smaller than the inner diameter of the outflow hole of the compressor of the comparative example. Compared to the case where one large-diameter outflow hole is provided on the left side of the muffler chamber 65 as in the compressor of the comparative example, the small-diameter outflow holes 71a and 72a are provided in the muffler chamber 65 as in the compressor 1. Noise (especially high frequency components of noise) can be absorbed more efficiently when a plurality are provided on the left side. Similarly, also on the right side of the muffler chamber 65, high frequency components of noise can be efficiently absorbed.

Furthermore, the outflow hole 71a is disposed in the vicinity of the narrowing portion 84a. Specifically, the distance from the narrowing part 84a to the outflow hole 71a is 10 mm or less. Similarly, the outflow hole 71b is disposed in the vicinity of the narrowing portion 84b. In this case, the high frequency component of the noise caused by the refrigerant flowing out from the outflow holes 71a and 71b can be efficiently reduced.
On the other hand, the outflow hole 72a is separated from both the narrowed portions 84a and 85a. Specifically, the distance from each of the narrowed-down portions 84a and 85a to the outflow hole 72a exceeds 10 mm. Similarly, the outflow hole 72b is separated from both the narrowed portions 84b and 85b. In this case, the low frequency component of the noise caused by the refrigerant flowing out from each of the outflow holes 72a and 72b can be efficiently reduced.

Since the refrigerant passing through the narrowing portions 84a and 84b is once compressed and then expanded, the vibration energy of the refrigerant is reduced. Noise is suppressed by reducing the vibration energy of the refrigerant.
Further, the compartment 83 and the narrowing portion 85a function as a sound absorption chamber utilizing Helmholtz resonance, and reduce the vibration energy of the refrigerant flowing through the compartment 82a. Similarly, the compartment 83 and the narrowing portion 85b function as a sound absorption chamber, and the vibration energy of the refrigerant flowing through the compartment 82b is reduced.

By the way, the distance from the narrowing portion 84a to the outflow hole 71a is desirably 10 mm or less and 5 mm or more. On the other hand, the distance from the narrowed-down portions 84a and 85b to the outflow hole 72a is preferably more than 10 mm and not more than 15 mm.
If the outflow holes 71a and 72a are excessively separated from each other, the effect of interference and cancellation of the vibrations of the refrigerant flowing out of the outflow holes 71a and 72a is reduced. Therefore, it is desirable that the outflow holes 71a and 72a be separated appropriately.
The same applies to the outflow holes 71b and 72b.

Next, the inner diameter and the number of outflow holes will be described.
The inner diameter of each of the outflow holes 71a, 72a, 71b, 72b may be 5 mm or less. Desirably, the inner diameter of each of the outflow holes 71a and 71b is 2.5 mm or more and 3.5 mm or less, and the inner diameter of each of the outflow holes 71a and 72b is 3.5 mm or more and 5 mm or less.
The number of outflow holes arranged on the left side and the right side of the muffler member 6 may be the same number of three or more.

  The compressor 1 as described above can suppress a sudden increase in noise during resonance and reduce the peak value. That is, the compressor 1 can be silenced. Therefore, the compressor 1 is particularly suitable when the compressor 1 is provided in an air conditioner, a heat pump water heater, a refrigerator, or the like that is used by changing the rotation speed of the motor 5 over a wide range.

  Next, Embodiments 2 and 3 will be described. The compressor 1 according to the second and third embodiments has substantially the same configuration as the compressor 1 according to the first embodiment. Hereinafter, differences from the first embodiment will be described, and other parts corresponding to those of the first embodiment are denoted by the same reference numerals and description thereof will be omitted.

Embodiment 2. FIG.
FIG. 7 is a plan view schematically showing the configuration of the muffler member 6 provided in the compressor 1 according to the second embodiment. FIG. 7 corresponds to FIG.
The muffler member 6 is provided with outflow holes 72a and 72b, and no outflow holes 71a and 71b are provided. The inner diameter of each of the outflow holes 72a and 72b is 7 mm.

FIG. 8 is a characteristic diagram for comparing the sound pressure levels of noise generated by the compressor 1 and the compressors used as comparative examples.
The horizontal axis of FIG. 8 is the rotation speed [rpm] of the motor 5, and the vertical axis is the A characteristic sound pressure level [dbA] of noise of 1.6 kHz or less.
In FIG. 8, the relationship between the rotational speed and the sound pressure level in the case of the compressor 1 of the second embodiment is shown by a solid line.
Moreover, in FIG. 8, the relationship between the rotation speed and the sound pressure level in the case of the compressor 1 of Embodiment 1 is shown with the broken line as a comparative example.

As can be seen from FIG. 8, the compressor 1 of the first embodiment can reduce noise more than the compressor 1 of the second embodiment. This difference is due to the number of outflow holes.
Nevertheless, the compressor 1 according to the second embodiment can also suppress a sudden increase in noise during resonance and reduce the peak value, similarly to the compressor 1 according to the first embodiment. That is, the compressor 1 can be silenced. That is, the number of outflow holes arranged on the left side and the right side of the muffler member 6 is not limited to a plurality, and may be one.
It has been experimentally found that if the volume inside the casing 2 is reduced, the sound pressure level tends to decrease over the entire rotation speed.

Embodiment 3. FIG.
FIG. 9 is a plan view schematically showing the configuration of the muffler member 6 provided in the compressor 1 according to the third embodiment.
The bottom wall 61 is provided with six circular outflow holes 7a, 7a, 7a, 7b, 7b, 7b. The outflow holes 7a, the outflow holes 7b, and the outflow holes 7a and 7b have the same diameter. The inner diameter of each of the outflow holes 7a and 7b is, for example, 5 mm.
The outflow holes 7a, 7a,... Are provided in the bottom wall 61 facing the compartment 82a, and the outflow holes 7b, 7b,... Are provided in the bottom wall 61 facing the compartment 82b. The outflow holes 7a, 7a,... And the outflow holes 7b, 7b,. Specifically, the outflow holes 7a, 7a,... And the outflow holes 7b, 7b,.
The refrigerant paths from the discharge hole 223 to the outflow holes 7a, 7a, 7a, 7b, 7b, 7b are asymmetric with respect to the virtual plane A. Therefore, the length of the refrigerant path from the discharge hole 223 to each outflow hole 7a is different from the length of the refrigerant path from the discharge hole 223 to each outflow hole 7b.

  Similarly to the compressor 1 of the first embodiment, the compressor 1 as described above can also suppress a sudden increase in noise during resonance and reduce the peak value. That is, the compressor 1 can be silenced.

  Finally, the first to third embodiments will be summarized.

  The compressor 1 according to the present embodiment includes a rotor 3 for compressing a refrigerant, a rotary shaft portion 31 to which the rotor 3 is connected, and the rotary shaft portion 31 rotatably supported. A muffler that forms a muffler chamber 65 between the casing 2 in which the refrigerant is compressed and the periphery of the rotary shaft portion 31 of the casing 2 to reduce noise. In the compressor 1 including the member 6, the casing 2 is provided with a discharge hole 223 through which the refrigerant discharged from the inside of the casing 2 into the muffler chamber 65 passes. A plurality of outflow holes 7 a, 7 b, 71 a, 72 a, 71 b, 72 b through which the refrigerant flowing out from the muffler chamber 65 respectively passes through the opening center 22 a of the discharge hole 223 and the axis 31 b of the rotary shaft portion 31. Outflow holes 7a, 7b, 71a, 72a, 71b, 72b provided on the one side of the muffler member 6 and the other side are provided in equal numbers on one side and the other side with the surface A as a boundary. The outflow holes 7 a, 7 b, 71 a, 72 a, 71 b, 72 b provided in are arranged asymmetrically with respect to the virtual plane A.

  The compressor 1 according to the present embodiment is characterized in that a plurality of outflow holes 7a, 7b, 71a, 72a, 71b, 72b are provided on each of the one side and the other side of the muffler member 6. And

  The compressor 1 according to the present embodiment is characterized in that the inner diameters of the outflow holes 7a, 7b, 71a, 72a, 71b, 72b are 5 mm or less.

  The compressor 1 according to the present embodiment is provided with narrowing portions 84a and 85b for partially narrowing the flow of the refrigerant on each of the one side and the other side of the muffler chamber 65. On one side and the other side, there are outflow holes 71a and 71b arranged at positions where the distance from the narrowed portions 84a and 85b is 10 mm or less.

  In this embodiment, whether the refrigerant discharged to the muffler chamber through the discharge hole flows out of the muffler chamber through the outflow hole provided on one side with the virtual plane of the muffler member as a boundary. Or, it flows out from the muffler chamber through an outflow hole provided on the other side with the virtual plane of the muffler member as a boundary. The virtual plane passes through the opening center of the discharge hole and the axis of the rotation shaft.

The outflow hole provided on one side of the muffler member and the outflow hole provided on the other side of the muffler member are arranged asymmetrically with respect to the virtual plane. Therefore, the refrigerant path from the discharge hole to the outflow hole provided on one side of the muffler member and the refrigerant path from the discharge hole to the outflow hole provided on the other side of the muffler member are asymmetric with respect to the virtual plane. is there.
Therefore, the vibration of the refrigerant flowing on both sides of the muffler member is prevented from increasing simultaneously due to resonance with the vibration of the motor. As a result, the compressor can be silenced.

  In the present embodiment, the refrigerant flows out from each of the plurality of outflow holes on one side of the muffler member. The vibration of the refrigerant flowing out from each of the plurality of outflow holes interferes and cancels out. Similarly, on the other side of the muffler member, the vibrations of the refrigerant interfere and cancel each other. As a result, noise can be reduced.

  In the present embodiment, a plurality of small-diameter outflow holes are provided on one side and the other side of the muffler member. On the other hand, in the conventional compressor, one large-diameter outflow hole is provided on one side and the other side of the muffler member. Compared with the case where one large-diameter outflow hole is provided, noise (particularly, high-frequency components of noise) can be absorbed more efficiently when a plurality of small-diameter outflow holes are provided.

  In the present embodiment, it is possible to reduce the high-frequency component of noise when the outflow hole is arranged in the vicinity of the narrowing portion than when the outflow hole is separated from the narrowing portion.

The embodiment disclosed this time is to be considered as illustrative in all points and not restrictive. The scope of the present invention is not intended to include the above-described meanings, but is intended to include meanings equivalent to the claims and all modifications within the scope of the claims.
Moreover, as long as there exists an effect of this invention, the component which is not disclosed by Embodiment 1-3 may be contained in the compressor 1. FIG.
The constituent elements (technical features) disclosed in each embodiment can be combined with each other, and a new technical feature can be formed by the combination.

DESCRIPTION OF SYMBOLS 1 Compressor 2 Casing 223 Discharge hole 22a Opening center 3 Rotor 31 Rotating shaft part 31b Shaft center 6 Muffler member 65 Muffler chamber 7a, 7b, 71a, 72a, 71b, 72b Outflow hole 84a, 84b, 85a, 85b Restriction part A Virtual Plane

Claims (4)

A rotor for compressing the refrigerant;
A rotating shaft to which the rotor is coupled;
A casing that rotatably supports the rotating shaft, accommodates the rotor, and in which a refrigerant is compressed;
A compressor comprising: a muffler member that covers the periphery of the rotating shaft portion of the casing and forms a muffler chamber for reducing noise between the casing and the casing.
The casing is provided with a discharge hole through which the refrigerant discharged from the casing into the muffler chamber passes.
The muffler member includes a plurality of outflow holes through which the refrigerant flowing out of the muffler chamber passes, and one side and the other with a virtual plane passing through the opening center of the discharge hole and the axis of the rotating shaft as a boundary. The same number is provided on the side,
The outflow hole provided on the one side of the muffler member and the outflow hole provided on the other side are arranged asymmetrically with respect to the virtual plane.   The compressor according to claim 1, wherein a plurality of the outflow holes are provided on each of the one side and the other side of the muffler member.   The compressor according to claim 2, wherein the inner diameter of each outflow hole is 5 mm or less. On each of the one side and the other side of the muffler chamber, a narrowing part that partially narrows the flow of the refrigerant is provided,
4. The outflow hole arranged at a position where the distance from the narrowing portion is 10 mm or less on each of the one side and the other side of the muffler member, according to claim 1. Compressor.

Images