JPH10184542A - Muffler for closed type compressor, and closed type compressor provided with muffler - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a silent closed type compressor by selectively reducing discordant noise of a plurality of specific frequency generating resonance inside a closed container. SOLUTION: A compressor body consisting of a compression mechanism element taking in refrigerant gas from a refrigerating cycle along with lubricating oil and compressing it, and a rotatory-driving motor element is accommodated inside a closed container. In such a closed type compressor, a muffler 13 fitted to a cylinder head 5 of the compression mechanism element is provided with an intake part 20 opened into the closed container so as to take in refrigerant gas inside the container, a refrigerant gas intake passage 12 communicating from the intake part 20 up to a connecting pipe 11 connected to the cylinder head 5 of the compression mechanism element, and two resonance chambers 16, 22 provided along the intake passage 12 and communicating with the intake passage 12 by throttle parts 17, 22. These resonance chambers 16, 22 reduce sound of specific frequency (400Hz, 600Hz) of two resonance spaces surrounding around the compressor body inside the closed container.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electric compressor driven by an electric motor for use in a refrigerating cycle including a refrigerating air conditioner, and more particularly, to a compressor or an electric motor housed in a closed container. BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improved silencer for a hermetic compressor for reducing noise during operation of the hermetic compressor, and a hermetic compressor provided with the silencer.

[0002]

2. Description of the Related Art Conventionally, a so-called hermetic compressor is widely used as an electric compressor used in a refrigeration cycle including a refrigeration air conditioner. This hermetic compressor is shown in the attached Figure 1.
As shown in FIG. 2 and FIG. 13, a motor element 2 composed of a stator 2a and a rotor 2b, a cylinder 3, a piston 4, a cylinder head 5, a head cover 6, etc. are provided inside a closed container 1 for storing a lubricating oil 100 at the bottom. And a compressor element 60 composed of a compressor element 60 and a compressor element 60, which are arranged above and below a frame 8 on which a bearing portion for rotatably supporting the crankshaft 7 is formed. It is housed in support. Therefore, in such a hermetic compressor, a plurality of spaces are formed between the hermetic container 1 and the compressor main body. That is, inside the sealed container 1, there are a space 10-1 which horizontally surrounds the periphery of the compressor main body and a hemispherical space 10-2 which extends vertically including the space. One space is formed. Also,
One end of the connecting pipe 11 is connected via a head cover 6 to a suction port provided in the cylinder head 5 of the compressor element 60, and the other end of the connecting pipe 11 has an opening inside the sealed container 1. A silencer 13 for silencing suction noise of a gas refrigerant having a suction portion 20 is connected.

In the hermetic compressor having such a structure, when the crankshaft 7 is rotationally driven by the electric motor element 2, the eccentric movement of the crankpin 71 of the compressor element causes
Through the slider 41, the piston 4 reciprocates in the cylinder 3, and the suction, compression, and discharge strokes are sequentially repeated.
In the suction stroke of the piston 4, the refrigerant gas filling the space in the closed container 1 is sucked from the opening of the suction part 20, and passes through a suction flow path including the silencer 13, the connection pipe 11, and the head cover 6, It reaches the suction valve closing the suction port of the cylinder head 5, pushes it open and flows into the cylinder 3. The silencer 13 is provided for the purpose of silencing the vibration noise of the suction valve and the pulsating sound of the sucked refrigerant gas generated during the suction stroke.

[0004] In the silencer 13, as shown in FIG. 14, the refrigerant gas flows from the suction portion 20 of the silencer 13, passes through the suction passage 12, and is connected to the outlet of the silencer 11. It reaches the pipe 11 and is then sucked into the cylinder 3 via the cylinder head 5. The muffler 13 is provided with only one so-called resonance chamber 21, and a resonance hole 21 for communicating with the resonance chamber 21 through the suction passage 12 is provided in the middle of the suction passage 12. ing. And according to such a configuration, this silencer 13
The resonance chamber 21 serves to silence the low-frequency sound generated as the vibration sound of the suction valve of the cylinder head 5 or the pulsating sound of the refrigerant gas. The structure of the muffler in such a compressor is described in, for example, Japanese Patent Publication No. 58-1560.
No. 5, JP-A-64-12086 and JP-A-6-74153.

[0005]

According to the hermetic compressor of the prior art constructed as described above, due to its structure, the vibration noise of the suction valve and the pulsation noise of the gas during the suction stroke are reduced. It is possible to mute the sound in some specific frequency bands. However, two or more spaces are formed between the sealed container 1 and the compressor body housed therein, and in these spaces,
When a specific standing wave (air column resonance) exists in each case, noise in a frequency band that is not sufficiently muted by the silencer causes resonance, thereby increasing the operating noise of the hermetic compressor. Among these, the most prominent resonance is the resonance generated in the space 10-1 formed around the compressor body described above, and is a sound having a frequency of which one wavelength is equal to the average circumference of the space. . For example, according to an experiment conducted by the present inventors, a sound in a frequency band of about 400 Hz resonates, and is thereby increased to generate noise. Further, even in the hemispherical space 10-2 extending upward from the periphery of the compressor body, about 600H
Sound in a frequency band of about z is generated as noise due to resonance.

The noise that induces the resonance is mainly radiated from the suction section 20 of the silencer 13. However, the silencer 13 in the above-described conventional technique is designed only to be installed in a narrow space from the viewpoint of reducing the size and weight of the compressor.
It was not enough to reduce the sound in the frequency band causing these resonances. Further, the silencer 13 in the above-mentioned prior art does not reduce the resonance frequency corresponding to the resonance frequency generated in the plurality of spaces 10-1 and 10-2 in the closed casing 1 of the closed type compressor.

In the conventional silencer 13 described above, only one resonance chamber 21 connected in the middle of the suction section 20 is formed separately from the silencer 13 and is then separated. The muffler 13 has a structure to be attached to the wall surface of the muffler 13 which forms the gas refrigerant passage 12.
3, the number of parts increases, and the number of manufacturing steps increases.

In view of the above, the present invention has been made in view of the above-mentioned problems in the prior art. Vibration noise and pulsation noise in a specific frequency band radiated from the suction unit 20 are reduced by taking into account resonance caused by a plurality of spaces formed in the closed container, and are generated by resonance in the closed container. To provide a silencer for a hermetic compressor capable of significantly reducing noise caused by noise, and to further provide a hermetically sealed hermetic compressor using the silencer to significantly reduce operating noise. It is intended for.

In the present invention, in addition to the above objects,
It is another object of the present invention to provide a silencer for a hermetic compressor that can be assembled at a lower cost with a relatively small number of man-hours.

[0010]

According to the present invention, in order to achieve the above object, first, a compressor element for sucking and compressing a refrigerant gas in a refrigeration cycle together with lubricating oil in a closed container is provided. Or in a hermetic compressor containing a compressor body consisting of a motor element that rotationally drives the muffler, a muffler attached to a refrigerant suction port of the compressor element, wherein the muffler is opened in the hermetic container and A suction port for sucking the refrigerant gas in the container, and a passage communicating from the suction port to a suction portion of the compressor element, wherein the passage is provided through respective throttles provided along the passage. A plurality of resonators are formed by a plurality of resonance chambers communicating with the section, and the plurality of resonators are formed in a plurality of resonance spaces formed around the compressor body inside the closed container. Providing hermetic compressor silencer that is configured to reduce more specific frequency noise response.

Further, according to the present invention, in the silencer for a hermetic compressor described above, a partition plate is arranged at a part of a passage communicating from the suction port to a suction portion of the compressor element. A resonance chamber and a throttle section were formed, thereby forming a part of the plurality of resonators.

Further, according to the present invention, in the silencer for a hermetic compressor described above, the partition plate in which the resonance chamber is formed is bent to form a throttle portion of the resonator, and the length of the bent portion is set. Adjust the silencing frequency accordingly.

[0013] In addition, in the silencer for a hermetic compressor described above, a resonance chamber forming a part of the plurality of resonators is formed with a throttle portion communicating with the passage portion protruding into the resonance chamber. Thus, the silencing frequency of the resonator is adjusted by the length of the projecting portion.

According to the present invention, the silencer for a hermetic compressor described above is divided into a plurality of parts, molded from a resin material, and these parts are assembled and integrally formed.

According to the present invention, a compressor element for sucking and compressing a refrigerant gas in a refrigeration cycle together with a lubricating oil in a closed container or a rotary drive of the compressor element for achieving the above object. A hermetic compressor element containing a compressor main body, wherein a plurality of resonance spaces are formed around the compressor main body inside the hermetic container; A silencer attached to the suction port includes a plurality of resonance type silencers for reducing a plurality of specific frequency noises corresponding to a plurality of resonance spaces in the closed container. Is provided.

Further, according to the present invention, in the hermetic compressor described above, the plurality of resonance spaces in the hermetic container are provided between the inner wall of the hermetic container and the horizontal periphery of the compressor body. And a hemispherical second space extending upward from the first space.

According to the present invention, in the hermetic compressor described above, the plurality of specific frequency noises corresponding to the plurality of resonance spaces in the hermetic container are about 400 Hz and about 600 Hz, respectively. It has.

[0018]

Embodiments of the present invention will be described below with reference to the accompanying drawings. First, FIG. 3 shows the structure of a hermetic compressor according to an embodiment of the present invention. Here, similarly to the above, the hermetic compressor has a closed container 1 for storing lubricating oil. A frame 8 having bearings for supporting a crankshaft 7 includes a motor element 2 including a stator and a rotor and a compressor element 60 including a cylinder 3, a piston 4, a cylinder head 5, a head cover 6, and the like. Are supported and housed via an elastic body 9 such as a spring.

[0019] In such a hermetic compressor,
A plurality of resonance spaces are formed between the hermetic container 1 and the compressor main body, that is, a space surrounding the periphery of the compressor main body, and two resonance spaces 10-1 of a space formed above the compressor main body. 10-2 is that. The operation of the hermetic compressor having the above configuration is the same as that described above, and the description thereof is omitted here. Also,
Similarly to the above, the silencer 13 is provided for the purpose of silencing the vibration noise of the suction valve and the pulsating noise of the refrigerant gas generated during the suction stroke.

FIG. 1 shows a part of the compressor element 60 and the muffler 13 attached thereto, which are features of the hermetic compressor according to the embodiment of the present invention.
In the figure, reference numeral 14 denotes a substantially crescent-shaped cavity formed on the upper portion of the muffler 13.
Is connected to a connecting pipe 11 extending from the cylinder head 5 of the cylinder 3. Reference numeral 15 denotes a partition plate provided in the hollow portion 14 and bent into an approximately “L” shape in outer shape. The partition plate 15 is provided near a portion where the connecting pipe 11 is connected to the hollow portion 14.

Reference numeral 16 in the figure denotes a first volume chamber, and the first volume chamber 16 is provided with the silencer 13.
As is clear from FIG. 2 which is a cross-sectional view of the cavity 14, a hollow chamber (resonance chamber) formed by dividing the space in the cavity 14 by the partition plate 15. further,
Reference numeral 17 in the drawing denotes a first throttle unit, and this throttle unit 1
7 is a part of the folded partition plate 15 and the hollow portion 1
The cavity 14 and the first volume chamber (resonance chamber) 16 communicate with each other via the throttle 17. The first volume chamber (resonance chamber) 16 constitutes a first resonance type silencer 18 which is a resonator together with the throttle section 17.

Next, reference numeral 12 in FIG.
3 shows an end of the suction passage 12 provided in the hollow portion 1 of the silencer 13.
It communicates with 4. In addition, the passage 12 of the suction refrigerant gas
As shown in FIG. 1, the muffler 13 includes a horizontal portion 12-1 and a vertical portion 12-2 in the muffler 13, thereby forming a bent tube bent at a substantially right angle. Further, the suction portion 20 formed at the other end of the passage 12 is
Through which a refrigerant gas supplied from a refrigeration cycle, such as a refrigeration air conditioner, and filled in the closed container 1 is sucked.

Reference numeral 21 in the drawing denotes a second volume chamber,
The volume chamber 21 is a hollow chamber (resonance chamber) formed by being surrounded by the wall of the passage 12 which is the bent pipe, the outer wall of the muffler 13 and the like. Reference numeral 22 denotes a hole formed in the refrigerant gas suction passage 12, particularly, a wall of the horizontal portion 12-1. As is apparent from FIG. The second throttle portion is formed in communication with the chamber 21. In the figure, reference numeral 23 denotes a second resonance type silencer (resonator) composed of the second volume chamber 21 and the second throttle passage 22.

As described above, the silencer 13 includes the first resonance type silencer (resonator) 18 and the first resonance type silencer (resonator) 18 along the suction passage 12 through which the sucked gas refrigerant passes and the hollow portion 14. A first resonance chamber (volume chamber) 16 and a second resonance chamber (volume chamber) 21 forming two resonance-type silencers (resonators) 23 include:
Each of the first throttle unit 17 and the second throttle unit (hole) 22
It is structured to be communicated via the.

By the way, in such a resonance type silencer, generally, the frequency f of noise that can be silenced is:
It is determined by the volume V of the volume chamber serving as the resonance chamber of the silencer, the cross-sectional area S of the throttle, and its length L, and the frequency f is expressed as follows.

(Equation 1) Here, C is the speed of sound in the suction passage.

Therefore, in the present invention, the silencing frequency f1 of the first resonance type silencer 18 and the second resonance type silencer 23,
f2 is set to the resonance space 10-1, 10-in the closed container 1.
Adjust to match the resonance frequency of 2. Specifically, in the above embodiment, the first resonance type silencer 1
8 by appropriately adjusting the volume V1 of the first volume chamber (resonance chamber) 16 and the cross-sectional area S and its length L (see FIG. 2) of the constricted portion 17 to reduce the muffling frequency.
Frequency band of the resonance space 10-1 (for example, about 400H
z). On the other hand, the second resonance type silencer 2
3, the volume V2 of the second volume chamber (resonance chamber) 21, the cross-sectional area S of the throttle portion 22, and the length L thereof (in this case, the passage 1
By appropriately adjusting the thickness of the second wall, the silencing frequency is adjusted to the other frequency band (for example, about 600 Hz) of the resonance space in the closed container 1.

Next, a more specific structure of the silencer 13 whose operation principle has been described above will be described in detail with reference to FIGS. Note that the muffler 13 shown in these figures can be formed of a metal material or a resin material. However, here, it is formed of a heat insulating resin material. Thus, the silencer 13
Is made of a resin material, which enables relatively easy and inexpensive manufacture by injection molding or the like.
In addition, the performance of the hermetic compressor as a whole can be improved by its heat insulating function.

As shown in FIG. 6, the silencer 13 includes three parts 13-A and 13-B, and 13-C (shown in FIG. 8) provided therein. Have been. By assembling them, unlike the above-described conventional technology, a plurality of volume chambers (resonance chambers) can be integrally and easily manufactured in the muffler 13.

The silencer 13 according to this embodiment has the same shape as the connecting pipe 11 connected to the cylinder head 5 of the compression mechanism element of the compressor body and the shape of the suction portion 20 thereof, as shown in FIG. Although slightly different from the form,
It has a connecting pipe 11 and a refrigerant gas suction part 20 opened in the sealed container 1. In the middle of the passage from the suction section 20 to the outlet of the connecting pipe 11, a volume chamber (resonance chamber) for forming two resonance silencers is also provided. The vibration noise of the suction valve and the pulsation sound of the refrigerant gas generated during the suction stroke are suppressed.

That is, as is apparent from these figures, the connecting pipe 11 is attached to the cylinder head 5 of the compression mechanism element 60.
And a suction unit 20 connected to the silencer 13 through the cavity 14 and connected to the cavity 14 and opening into the closed container 1.
A suction passage 12 composed of a horizontal portion 12-1 and a vertical portion 12-2 is formed between the two. Further, a second volume chamber (resonance chamber) 21 is formed by the suction passage 12 for the suction gas refrigerant and the outer wall of the silencer 13, and the second volume chamber (resonance chamber) 21 is The suction passage 12 communicates with the suction passage 12 through a hole 22 that is a second throttle formed in a part of the wall of the horizontal portion 12-1 of the suction passage 12.

In addition, as clearly shown in FIGS. 7 and 8 attached hereto, the hollow portion 14 is formed in the substantially crescent-shaped hollow portion 14 above the silencer 13. There is provided a partition plate 15 which is integrally formed so as to protrude from the partition wall 13-C, which is a part to be formed, and which is bent into a substantially “L” shape in outer shape, whereby a first volume chamber (resonance chamber) is provided. 16 is separated from the cavity 14. Reference numeral 17 also denotes a throttle portion of the first volume chamber (resonance chamber) 16 formed by the bent portion of the partition plate 15.

FIG. 9 shows the silencing characteristics of the silencer 13 having the structure described above. In the graph of this figure, the characteristic curve N is the level of the noise from the compression mechanism element as the sound source, whereas the characteristic curve I is reduced by the silencing function of the silencer 13, ie, the silencer. 13 shows the level of noise radiated from the thirteen inlets 20. As is clear from this graph, according to the silencer 13, in the frequency f1 near 400 Hz, the frequency f2 near 600 Hz, and the frequency band between them, the sound volume reduction indicated by the arrow in the graph of FIG. (Indicated by RD) is remarkable. Thus, in the hermetic compressor in which the silencer 13 is attached to the compression mechanism, noise having a frequency of about 400 Hz to about 600 Hz is selectively reduced, and despite the existence of a plurality of resonance spaces in the sealed container 1. Therefore, resonance does not occur in the sealed container 1 due to these factors, and therefore, a quiet hermetic compressor can be obtained. Here, for comparison, the characteristics of the conventional silencer are shown by a characteristic curve III for comparison.

In the above description, the frequency f1 near 400 Hz and the frequency
Although it has been described that there are two spaces that generate standing waves at a frequency f2 near 0 Hz, even when a space that generates a standing wave exists at other frequencies, these other frequencies may be equal to the frequency f1. By setting the frequencies f1 and f2 so as to be located between the frequency f2 and the frequency f2, it is possible to greatly suppress the generation of noise at these other frequencies.

Further, in the above-described embodiment, the partition plate 15 which divides the above-mentioned substantially crescent-shaped hollow portion 14 to form a first volume chamber (resonance chamber) 18 is used as the partition plate 15 shown in FIG.
Only the members bent into the substantially “L” shape shown in FIGS. 7 and 8 have been described. However, according to the present invention, the partition plate is formed, for example, in a shape as shown by reference numeral 15 'in FIG.
The opening area S of -2 can also be increased. Alternatively, although not shown, the resonance chamber may be partitioned by a plate-shaped member instead of the bent partition plate 15, and an opening of a desired size may be provided in the plate-shaped member.

Further, in the above embodiment, the first
In order to adjust the frequency f of noise that can be silenced by the resonance type silencer 18 and the second resonance type silencer 23, for example, the volume V of the volume chamber (resonance chamber) or the cross-sectional area S In particular, in the first resonance type silencer 18, the length (L) of the narrowed portion is adjusted by the length of the bent portion of the “L” -shaped partition plate 15. This can also be adjusted. Further, in the second resonance type silencer 23, for example, as shown in FIGS. 4 and 8, the second throttle opening in a part of the wall forming the horizontal portion 12-1 of the intake passage 12 The part 22 to the volume chamber 21
The length (L) of the narrowed portion can be adjusted by adjusting the length (L) of the throttle portion.

Further, in the above embodiment, the above-described FIG.
As shown in FIG. 8 to FIG.
It is constructed by assembling three parts 13-B and 13-C. However, at the time of assembly, in order to sufficiently achieve the noise reduction effect of the first resonance type silencer 18 and the second resonance type silencer 23, a resonance chamber (resonance chamber) formed between these members is required. Room) 16, 21
Sealing is important. Therefore, in the above-described embodiment, in particular, the part 13-C and the part 13-B are joined by an adhesive or melt-bonded by high-frequency heating. Also, regarding the partition plate 15 formed on the component 13-C,
The upper end surface is on the inner lower surface of the component 13-A, or
It is important to securely join to the inner side surface of the part 13-B.

For this purpose, as shown in the attached FIG. 11, the surface of one member (for example, the part 13-A
A concave portion 110 is provided on the inner bottom surface of the second member, and the other protrusion (for example, the partition plate 15) is accommodated in the concave portion 110 (FIG. 11A).
Alternatively, two rows of convex parts 111, 111 are formed, and the concave part 11 formed between these two rows of convex parts 111, 111 is formed.
The other protruding portion (for example, the partition plate 15) may be accommodated inside the 2 (FIG. 11B). Alternatively, the tip of the protruding portion (for example, the partition plate 15) is thinned to form the elastic portion 15-1.
It is also possible to press this from above with a flat part (for example, the inner lower surface of the part 13-A) to tightly fix it.
Note that the noise reduction characteristics of the silencer 13 when the above-described parts are not sufficiently sealed, that is, when leakage occurs, are shown by the characteristic curve II in FIG. In this case, in particular, there is no superiority to the characteristic III of the above-described conventional silencer with respect to noise in a frequency band in the vicinity of about 400 Hz to 600 Hz which is a problem as noise.

In the above embodiment, the resonance frequencies f1 and f2 of the first space 10-1 and the second space 10-2 in the closed container 1 are set to 400, respectively.
Although these frequencies have been described as being equal to 600 Hz, these frequencies change depending on the dimensions of the closed container 1 and the like. In this case, the resonance frequencies f1 and f2 also change. The silencing characteristics f1 and f2 of the container 13 may be changed as appropriate.

[0039]

As is apparent from the above detailed description, according to the silencer for a hermetic compressor and the hermetic compressor having the same according to the present invention, a plurality of resonance frequencies can be provided in a hermetic container. Even if there is a space where the noise is generated, the first resonance type silencer and the second resonance type silencer of the muffler attached to the compressor element may cause a noise of about 400H.
A silencer for a hermetic compressor capable of significantly suppressing noise in a frequency band near z to 600 Hz and thereby preventing resonance in a hermetic container is provided. By doing so, it is possible to provide a hermetic compressor capable of quiet operation.

[Brief description of the drawings]

FIG. 1 is a partially cutaway perspective view illustrating a principal part structure and a principle of a hermetic compressor having a muffler according to an embodiment of the present invention.

FIG. 2 is a sectional view taken along the line AA in FIG. 1 for explaining an internal structure of the muffler.

FIG. 3 is a partially cut perspective view showing the entire structure of a hermetic compressor provided with the muffler of the present invention.

FIG. 4 is a front view showing a more specific structure of the muffler of the present invention.

FIG. 5 is a side view of the muffler shown in FIG. 4;

FIG. 6 is an overall perspective view of the silencer shown in FIG. 4;

FIG. 7 is a perspective view of components constituting a lower portion of the muffler shown in FIG. 4 as viewed from above.

FIG. 8 is a sectional view taken along the line BB of some components of the muffler shown in FIG. 7;

FIG. 9 is a diagram showing a noise-reduction characteristic graph of the muffler of the present invention.

FIG. 10 is a view showing a modified example of the diaphragm in the muffler of the present invention.

FIG. 11 is a view for explaining various modifications of the connection structure of the diaphragm in the muffler of the present invention.

FIG. 12 is a cross-sectional view showing a structure of a hermetic compressor according to the related art.

FIG. 13 is a cross-sectional view showing another structure of the hermetic compressor according to the related art.

FIG. 14 is a cross-sectional view showing a structure of a muffler attached to the hermetic compressor according to the related art.

[Explanation of symbols]

 2 Motor element 5 Cylinder head 10-1, 10-2 Resonance space 60 Compressor element 11 Connecting pipe 12 Suction passage 13 Silencer 14 Cavity part 15 Partition plate 16 First volume chamber (Resonance chamber) 17 First throttle part 18 first resonance type silencer 21 second volume chamber (resonance chamber) 22 second throttle unit 23 second resonance type silencer

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Takeshi Odashima 800, Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture Inside the Cooling Division, Hitachi, Ltd. Hitachi, Ltd.

Claims (8)

[Claims] A closed type housing in which a compressor body for sucking and compressing a refrigerant gas in a refrigeration cycle together with lubricating oil or a motor element for rotating and driving the same in a closed container is provided. A muffler attached to a refrigerant suction port of the compressor element, wherein the muffler is opened in the closed container and sucks refrigerant gas in the container; and A passage portion communicating with the suction portion, a plurality of resonators are formed by a plurality of resonance chambers communicating with the passage portion through respective throttle portions provided along the passage portion, and
The plurality of resonators are configured to reduce a plurality of specific frequency noises corresponding to a plurality of resonance spaces formed around the compressor body inside the closed container. Silencer for hermetic compressor. 2. The muffler for a hermetic compressor according to claim 1, wherein a partition plate is arranged at a part of a passage portion communicating from the suction port to a suction portion of the compressor element, and a resonance chamber is provided. A muffler for a hermetic compressor, wherein a throttle portion is formed, thereby forming a part of the plurality of resonators. 3. The silencer for a hermetic compressor according to claim 2, wherein the partition plate forming the resonance chamber is bent to form a throttle portion of the resonator, and the silencer is reduced by the length of the bent portion. A silencer for a hermetic compressor characterized by adjusting the frequency. 4. The silencer for a hermetic compressor according to claim 1, wherein a throttle portion that communicates a resonance chamber forming a part of the plurality of resonators with the passage portion projects into the resonance chamber. A silencer for a hermetic compressor, wherein the silencer is formed and the silencing frequency of the resonator is adjusted by the length of the projecting portion. 5. A closed type muffler for a hermetic compressor according to claim 1, wherein said muffler for a hermetic compressor is divided into a plurality of portions and molded with a resin material, and these portions are assembled and integrally formed. Silencer for compressor. 6. A sealed container containing a compressor element for sucking and compressing refrigerant gas in a refrigeration cycle together with lubricating oil or an electric motor element for driving the compressor element in the closed container, Inside the container, in a hermetic compressor in which a plurality of resonance spaces are formed around the periphery of the compressor main body, a muffler attached to a suction port of the compressor element is provided inside the hermetic container. A hermetic compressor comprising a plurality of resonance silencers for reducing a plurality of specific frequency noises corresponding to a plurality of resonance spaces. 7. The hermetic compressor according to claim 6, wherein the plurality of resonance spaces in the hermetic container are formed in a horizontal direction between an inner wall of the hermetic container and a periphery of the compressor body. A hermetically-sealed compressor including a first space, and a hemispherical second space extending upward from the first space. 8. The hermetic compressor according to claim 7, wherein the plurality of specific frequency noises corresponding to the first and second resonance spaces in the closed container are about 400 Hz and about 600 Hz, respectively. A hermetic compressor characterized by having a frequency of: