CN104863819B - Design method of compressor silencing structure - Google Patents
Design method of compressor silencing structure Download PDFInfo
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- CN104863819B CN104863819B CN201510160820.1A CN201510160820A CN104863819B CN 104863819 B CN104863819 B CN 104863819B CN 201510160820 A CN201510160820 A CN 201510160820A CN 104863819 B CN104863819 B CN 104863819B
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- 238000000034 method Methods 0.000 title claims abstract description 36
- 238000013461 design Methods 0.000 title abstract description 13
- 230000030279 gene silencing Effects 0.000 title abstract 6
- 230000004044 response Effects 0.000 claims description 29
- 239000002826 coolant Substances 0.000 claims description 19
- 230000008030 elimination Effects 0.000 claims description 15
- 238000003379 elimination reaction Methods 0.000 claims description 15
- 230000009467 reduction Effects 0.000 claims description 10
- 239000000463 material Substances 0.000 claims description 8
- 238000004088 simulation Methods 0.000 claims description 5
- 238000001228 spectrum Methods 0.000 claims description 4
- 239000003507 refrigerant Substances 0.000 claims description 3
- 241000208340 Araliaceae Species 0.000 claims description 2
- 235000005035 Panax pseudoginseng ssp. pseudoginseng Nutrition 0.000 claims description 2
- 235000003140 Panax quinquefolius Nutrition 0.000 claims description 2
- 235000008434 ginseng Nutrition 0.000 claims description 2
- 230000003584 silencer Effects 0.000 abstract description 5
- 230000001603 reducing effect Effects 0.000 abstract 1
- 230000005404 monopole Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000010009 beating Methods 0.000 description 2
- 238000012827 research and development Methods 0.000 description 2
- 125000000174 L-prolyl group Chemical group [H]N1C([H])([H])C([H])([H])C([H])([H])[C@@]1([H])C(*)=O 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000003086 colorant Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 201000004960 glottis neoplasm Diseases 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000003908 quality control method Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
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Abstract
The invention discloses a design method of a compressor silencing structure, which comprises the following steps: constructing a three-dimensional model of the silencer with a fully-sealed cavity structure; solving the acoustic parameters of the dipole acoustic mode of the totally-sealed cavity structure in the three-dimensional model of the silencer; obtaining opening position parameters of the tail pipe resonant cavity according to the solved acoustic parameters of the dipole acoustic mode; and obtaining the structural parameter relation of the tail pipe resonant cavity according to the target muffling frequency of the muffler, wherein the natural frequency of the tail pipe resonant cavity is the same as the target muffling frequency of the muffler, the amplitude is the same, and the phases are opposite. The design method of the compressor silencing structure is simple and feasible and has low cost. The compressor silencing structure designed by the method greatly reduces the vortex noise, impact noise and flapping noise of the exhaust port of the silencer, and the silencing and noise reducing effect of the compressor silencing structure is greatly improved compared with that of the traditional silencer.
Description
Technical field
The present invention relates to Compressor Technology field, more particularly to a kind of method for designing of compressor noise-reducing structure.
Background technology
Noise is the leading indicator of the quality control of air-conditioner, and wherein, the noise major part of air-conditioner is from compression
The noise of machine.Therefore, the noise of compressor is efficiently controlled, is the powerful guarantee of air-conditioner quality.And the totality of compressor is made an uproar
In sound, exhaust noise accounts for the largest percentage, and therefore, the exhaust mode of compressor has a significant impact to compressor overall noise.
Traditional compressor suppresses DIPOLE MODE noise using phase interference type deafener.Which passes through deafener
Two air vents are arranged in the wave amplitude of DIPOLE MODE, under the premise of the acoustic pressure amplitude of two air vents and phase place identical,
So that the dipole glottis neoplasms amplitude that two air vents evoke is equal, opposite in phase, so as to cancel out each other.
The very big limitation of presence is applied in the design of above-mentioned traditional compressor silencer in practice, on the one hand, reality processing
When it is difficult to ensure that two air vent acoustic pressure amplitudes of deafener are identical with phase place；On the other hand, the gases at high pressure that discharges in the pump housing,
Easily vortex is formed in air vent throttleng surface, produce eddy current crack, and radiate by air vent.Additionally, traditional deafener
By upper surface aerofluxuss so that high pressure, the air-flow of high speed easily impact motor, so as to producing strong impact, patting noise.
Content of the invention
It is based on this, it is necessary to for the defect and deficiency of prior art, there is provided a kind of design side of compressor noise-reducing structure
Method, the compressor noise-reducing structure designed by the method, can effectively reduce deafener air vent eddy current crack and impact,
Noise, and simple structure is patted, is easy to process.
The method for designing of the compressor noise-reducing structure provided for realizing the object of the invention, comprises the following steps：
Build the deafener threedimensional model of hermetically sealed cavity structure；
The acoustics for solving the dipole acoustic mode of the described hermetically sealed cavity structure in the deafener threedimensional model is joined
Number；
According to the parameters,acoustic for solving the dipole acoustic mode for arriving, obtain tailpipe resonant cavity opens up position
Parameter；
According to the target frequency of noise elimination of the deafener, the structural parameters relation of the tailpipe resonant cavity, institute is obtained
The natural frequency for stating tailpipe resonant cavity is identical with the target frequency of noise elimination of the deafener, and amplitude is identical, opposite in phase.
Wherein in one embodiment, the method for designing of the compressor noise-reducing structure of the present invention is further comprising the steps of：
According to noise spectrum and the default target noise reduction value of compressor, the target for obtaining the deafener is eliminated the noise frequently
Rate.
Wherein in one embodiment, the dipole for solving the described hermetically sealed cavity structure in deafener threedimensional model
The parameters,acoustic of sub- acoustic mode, comprises the following steps：
The deafener threedimensional model is imported acoustics simulation analysis module, is produced according to the air vent of the compressor
Monopole is responded, and sets up the dipole acoustic mode of the hermetically sealed cavity structure；
The material ginseng of the hermetically sealed cavity structure, in the dipole acoustic mode of the hermetically sealed cavity structure, is set
Number, obtains the parameters,acoustic of the dipole acoustic mode.
Wherein in one embodiment, the material parameter of the hermetically sealed cavity structure includes refrigerant type, exhaust pressure
Power, pressure of inspiration(Pi), delivery temperature, suction temperature, coolant speed, coolant density, and coolant impedance.
Wherein in one embodiment, the parameters,acoustic of the dipole acoustic mode include the natural frequency of dipole,
Phase place, the minimum position of response when the maximum position of response, response maximum amplitude, response maximum amplitude, response minimum amplitude,
And phase place during response minimum amplitude.
Wherein in one embodiment, the structural parameters of the tailpipe resonant cavity include sectional area, volume and length
Degree.
Wherein in one embodiment, the natural frequency of the tailpipe resonant cavity and the tailpipe resonant cavity
Structural parameters meet relationship below：
Wherein, l is the length of the tailpipe resonant cavity, and V is the volume of the tailpipe resonant cavity, and A is described
The sectional area of tailpipe resonant cavity, c be coolant speed, ωrNatural frequency for the tailpipe resonant cavity.
Beneficial effects of the present invention：The method for designing of the compressor noise-reducing structure of the present invention, by building hermetically sealed cavity
The deafener threedimensional model of structure, the sound of the dipole acoustic mode of the hermetically sealed cavity structure in solution deafener threedimensional model
Parameter is learned, obtain tailpipe resonant cavity opens up location parameter and structural parameters relation, it is ensured that tailpipe resonant cavity
Natural frequency is identical with the target frequency of noise elimination of deafener, and amplitude is identical, opposite in phase, completes to set compressor noise-reducing structure
Meter, its simple possible, low cost.The compressor noise-reducing structure designed by the method, greatly reduces deafener air vent
Eddy current crack and impact, beating noise, its noise elimination noise reduction effect have larger lifting compared with conventional muffler.
Description of the drawings
In order that the purpose of the method for designing of the compressor noise-reducing structure of the present invention, technical scheme and advantage are more clear bright
In vain, below in conjunction with concrete drawings and the specific embodiments, the method for designing of the compressor noise-reducing structure of the present invention is carried out further
Describe in detail.
Fig. 1 is the flow chart of one embodiment of the method for designing of the compressor noise-reducing structure of the present invention；
Fig. 2 is the hermetically sealed cavity structure of the method for designing design of the compressor noise-reducing structure of the present invention shown in Fig. 1
Muffler structure schematic diagram；
Fig. 3 is the noise-reducing structure schematic diagram of the method for designing design of the compressor noise-reducing structure of the present invention shown in Fig. 1；
A-A schematic diagrams of the Fig. 4 for Fig. 3；
Fig. 5 is the noise-reducing structure of the method for designing design of the compressor noise-reducing structure using the present invention shown in Fig. 1 and biography
Noise spectrum comparison diagram after system deafener noise reduction.
Specific embodiment
The method for designing of the compressor noise-reducing structure of present invention offer is provided in detail below in conjunction with embodiment.Need
Bright, in the case where not conflicting, the feature in embodiment and embodiment in the application can be mutually combined.
The method for designing of the compressor noise-reducing structure provided referring to Fig. 1, the present invention, comprises the following steps：
S100, builds the deafener threedimensional model of hermetically sealed cavity structure.
In step S100, the deafener threedimensional model for building hermetically sealed cavity structure can adopt 3 d modeling software (example
Such as, the Solidworks of the Pro/Engineer softwares of U.S. parameters technology company research and development or the research and development of solidworks companies of the U.S.
Software etc.) realize, process is realized for prior art, no longer redundant later herein.
It should be strongly noted that the deafener three-dimensional mould built in the method for designing of the compressor noise-reducing structure of the present invention
Type is hermetically sealed cavity structure, as shown in Fig. 2 not designing air vent on cavity 10, it is ensured that deafener cavity structure
Integrity, contributes to lifting sound-deadening and noise-reducing effect.
S200, the parameters,acoustic of the dipole acoustic mode of the hermetically sealed cavity structure in solution deafener threedimensional model.
Firstly, it is necessary to illustrate, the monopole in the present invention refers to the point source of a pulsation mass, in static stream
In body, the sensing of its all directions is uniform.For compressor pump, the coolant that discharges from cylinder exhaust port is considered as list
Extremely sub- sound source.Correspondingly, monopole response refers to the hermetically sealed cavity structure of deafener under the effect of monopole sound source, the sound of generation
Should.
Dipole in the present invention, refers to, interacts and produce
Raw noise source.For compressor pump, as air velocity is very high, excludes from air vent, act directly on deafener inwall,
Deafener is vertically reflected to monopole sound source, forms sound source of the dipole in reflecting interface.
Dipole acoustic mode in the present invention refers to that the dipole that deafener noise is produced acts on the complete close of deafener
In envelope cavity structure, the hermetically sealed cavity structure is excited to produce vibration, so as to the acoustic mode (natural frequency and the vibration that inspire
Form).
According to the monopole response that compresser cylinder air vent is produced, using acoustics simulation analysis software, you can disappeared
The parameters,acoustic of the dipole acoustic mode of the hermetically sealed cavity structure in sound device threedimensional model.
Wherein, the parameters,acoustic of dipole acoustic mode include dipole natural frequency, response maximum position, response
Phase place, the minimum position of response when maximum amplitude, response maximum amplitude, response minimum amplitude, and during response minimum amplitude
Phase place.And the color cloud picture that the maximum position for responding, the minimum position for responding can be obtained after being calculated by acoustic mode
Embodied, different colors represents the of different sizes of acoustic mode response.For example：Response is minimum, is represented with blueness；Response is most
Greatly, represented with redness；In minimum and the different response magnitudes between maximum, represented with the tone between blue and redness.
S300, according to the parameters,acoustic for solving the dipole acoustic mode for arriving, obtain tailpipe resonant cavity opens up position
Put parameter.
Referring to Fig. 3 and Fig. 4, the deafener threedimensional model built in the method for designing of the compressor noise-reducing structure of the present invention is
Hermetically sealed cavity structure, is not designed air vent on cavity 10, but is designed on the upper flange 20 being engaged with deafener
Groove so as to form tailpipe resonant cavity 30 with the hermetically sealed cavity structure of deafener, ensureing deafener cavity structure
Integrity.Tailpipe resonant cavity 30 can be designed as one end unlatching, the pipeline configuration of other end volume.Using tailpipe
Resonant cavity 30 replaces the design of traditional cavity air vent, can reduce the vortex of conventional muffler air vent, effectively reduces pressure
High frequency (7000-10000Hz) eddy current crack of contracting machine；Simultaneously, it is to avoid the air-flow of conventional muffler is rushed with the strong of motor
Hit, pat, effectively reduce having pressed the low frequency (0-50Hz) of compressor to clap the noise that shakes, noise reduction is lifted as shown in Figure 5.
According to the parameters,acoustic of the dipole acoustic mode solved in step S200, open in the region for responding relatively small
If the structure of resonant cavity of tailpipe, can the color cloud picture for obtaining be calculated by acoustic mode to determine tailpipe resonant cavity knot
Structure opens up the region blue region of minimum (for example respond), and the direction of its notch is that the cross-section center for responding Minimum Area is cut
At line.By corresponding with region position open channels on upper flange, you can realize tailpipe structure of resonant cavity.Noise reduction
While also add the cavity volume of deafener, improve the discharge capacity of compressor unit volume, and the refrigeration to compressor
Amount has certain lifting.
S400, according to the target frequency of noise elimination of deafener, obtains the structural parameters relation of tailpipe resonant cavity, exhaust tail
The natural frequency in pipe resonance chamber is identical with the target frequency of noise elimination of deafener, and amplitude is identical, opposite in phase.
Referring to Fig. 4, the structural parameters of tailpipe resonant cavity include sectional area, volume and length.Tailpipe resonates
The natural frequency in chamber meets relationship below with the structural parameters of tailpipe resonant cavity：
Wherein, length of the l for tailpipe resonant cavity, volumes of the V for tailpipe resonant cavity, A resonate for tailpipe
The sectional area in chamber, c be coolant speed, ωrNatural frequency for tailpipe resonant cavity.
The present invention behind the position for determining tail pipe resonant cavity by step S300, by the sectional area to tail pipe resonant cavity,
The design (changing resonant frequency, amplitude and phase place that sectional area, volume can change tail pipe resonant cavity) of volume and length, obtains
Tail pipe resonant cavity parameters,acoustic (resonant frequency, amplitude and phase place) so that tail pipe resonant cavity produce natural frequency with disappear
The target frequency of noise elimination of sound device (can be the intrinsic frequency of the acoustic mode of the hermetically sealed cavity structure immediately arrived at after software emulation
Rate) identical, amplitude (response amplitude under natural frequency) is identical, phase place (the response phase angle under natural frequency) conversely,
So as to cancel out each other, farthest reduce the noise of compressor target frequency bands.
As a kind of embodiment, the idol of the hermetically sealed cavity structure in deafener threedimensional model in step S200, is solved
The parameters,acoustic of extremely sub- acoustic mode, specifically includes following steps：
Deafener threedimensional model is imported acoustics simulation analysis module by S210, according to the list that the air vent of compressor is produced
Extremely son response, sets up the dipole acoustic mode of hermetically sealed cavity structure；
S220, in the dipole acoustic mode of hermetically sealed cavity structure, arranges the material parameter of hermetically sealed cavity structure,
Obtain the parameters,acoustic of dipole acoustic mode.
Wherein, the material parameter of hermetically sealed cavity structure includes but is not limited to refrigerant type, pressure at expulsion, pressure of inspiration(Pi)
Power, delivery temperature, suction temperature, coolant speed, coolant density, and coolant impedance.
For example：Deafener threedimensional model is imported LMS Virtual.Lab acoustics simulation analysis softwares, according to compressor
The monopole response that air vent is produced, you can set up the dipole acoustic mode of hermetically sealed cavity structure.Hermetically sealed cavity is set
The material parameter (coolant speed, coolant density, coolant impedance etc.) of structure, after being input into the material parameter in table 1 below -1, from software
In can directly obtain the parameters,acoustic of deafener cavity dipole acoustic mode.
| Cold-producing medium | R410A |
| Pressure at expulsion | 3.35 |
| Pressure of inspiration(Pi) | 1 |
| Delivery temperature | 110 |
| Suction temperature | 35 |
| Coolant speed | 190.6 |
| Coolant density | 96.6 |
| Coolant impedance | 18411.96 |
Table 1-1
As a kind of embodiment, the method for designing of the compressor noise-reducing structure of the present invention, before step S400, go back
Comprise the following steps：
S400 ', according to noise spectrum and the default target noise reduction value of compressor, the target for obtaining deafener is eliminated the noise frequently
Rate.
Step 400 ' the deafener threedimensional model that step S100 builds hermetically sealed cavity structure can also be arranged on before.I.e.
The target frequency of noise elimination of deafener can be first set, and the noise reduction of hermetically sealed cavity structure is then built according to the target frequency of noise elimination
Device threedimensional model, so, the natural frequency of the acoustic mode of the hermetically sealed cavity structure immediately arrived at after software emulation is i.e.
Target frequency of noise elimination for deafener.
The method for designing of the compressor noise-reducing structure of the present invention, soft by being emulated by means of 3 d modeling software and acoustics
Part, builds the deafener threedimensional model of hermetically sealed cavity structure, the hermetically sealed cavity structure in solution deafener threedimensional model
The parameters,acoustic of dipole acoustic mode, obtain tailpipe resonant cavity open up location parameter and structural parameters relation, really
The natural frequency for protecting tailpipe resonant cavity is identical with the target frequency of noise elimination of deafener, and amplitude is identical, opposite in phase, and it is right to complete
The design of compressor noise-reducing structure.Its simple possible, low cost.The method does not design air vent on cavity, but with
Groove is devised on the upper flange that deafener is engaged so as to tailpipe resonance is formed with the hermetically sealed cavity structure of deafener
Chamber, to ensure the integrity of deafener cavity structure.
The compressor noise-reducing structure designed by this method, simple structure are easy to process, and greatly reduce deafener aerofluxuss
The eddy current crack of mouth and impact, beating noise, its noise elimination noise reduction effect have larger lifting compared with conventional muffler.Meanwhile, aerofluxuss
The design of tail pipe resonant cavity, increased the cavity volume of deafener, so as to improve the discharge capacity of compressor unit volume, further
Improve the refrigerating capacity of compressor.
Above example only expresses the several embodiments of the present invention, and its description is more concrete and detailed, but can not
Therefore the restriction to the scope of the claims of the present invention is interpreted as.It should be pointed out that for the person of ordinary skill of the art,
Without departing from the inventive concept of the premise, some deformations and improvement can also be made, these belong to the protection model of the present invention
Enclose.Therefore, the protection domain of patent of the present invention should be defined by claims.
Claims (7)
1. a kind of method for designing of compressor noise-reducing structure, it is characterised in that comprise the following steps：
Build the deafener threedimensional model of hermetically sealed cavity structure；
Solve the parameters,acoustic of the dipole acoustic mode of described hermetically sealed cavity structure in the deafener threedimensional model；
According to the parameters,acoustic for solving the dipole acoustic mode for arriving, obtain tailpipe resonant cavity opens up position ginseng
Number；
According to the target frequency of noise elimination of the deafener, the structural parameters relation of the tailpipe resonant cavity, the row is obtained
The natural frequency of gas tail pipe resonant cavity is identical with the target frequency of noise elimination of the deafener, and amplitude is identical, opposite in phase.
2. the method for designing of compressor noise-reducing structure according to claim 1, it is characterised in that further comprising the steps of：
According to noise spectrum and the default target noise reduction value of compressor, the target frequency of noise elimination of the deafener is obtained.
3. the method for designing of compressor noise-reducing structure according to claim 1 and 2, it is characterised in that the solution noise reduction
The parameters,acoustic of the dipole acoustic mode of the described hermetically sealed cavity structure in device threedimensional model, comprises the following steps：
The deafener threedimensional model is imported acoustics simulation analysis module, according to the one pole that the air vent of the compressor is produced
Son response, sets up the dipole acoustic mode of the hermetically sealed cavity structure；
The material parameter of the hermetically sealed cavity structure, in the dipole acoustic mode of the hermetically sealed cavity structure, is set,
Obtain the parameters,acoustic of the dipole acoustic mode.
4. the method for designing of compressor noise-reducing structure according to claim 3, it is characterised in that the hermetically sealed cavity knot
The material parameter of structure includes refrigerant type, pressure at expulsion, pressure of inspiration(Pi), delivery temperature, suction temperature, coolant speed, coolant
Density, and coolant impedance.
5. the method for designing of compressor noise-reducing structure according to claim 1 and 2, it is characterised in that the dipole sound
The parameters,acoustic for learning mode includes the natural frequency of dipole, the maximum position of response, response maximum amplitude, response maximum amplitude
When phase place, response minimum position, response minimum amplitude, and response minimum amplitude when phase place.
6. the method for designing of compressor noise-reducing structure according to claim 1 and 2, it is characterised in that the tailpipe
The structural parameters of resonant cavity include sectional area, volume and length.
7. the method for designing of compressor noise-reducing structure according to claim 1 and 2, it is characterised in that the tailpipe
The natural frequency of resonant cavity meets relationship below with the structural parameters of the tailpipe resonant cavity：
Wherein, l is the length of the tailpipe resonant cavity, and V is the volume of the tailpipe resonant cavity, and A is the aerofluxuss
The sectional area of tail pipe resonant cavity, c be coolant speed, ωrNatural frequency for the tailpipe resonant cavity.
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| CN201510160820.1A CN104863819B (en) | 2015-04-07 | 2015-04-07 | Design method of compressor silencing structure |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108151283A (en) | 2017-12-04 | 2018-06-12 | 北京小米移动软件有限公司 | Prepare method, silencing means and the air purifier of silencing means |
| CN108204666A (en) * | 2017-12-18 | 2018-06-26 | 青岛海尔空调电子有限公司 | For the air conditioner chassis design method of vibration and noise reducing |
| CN113554999A (en) * | 2020-04-26 | 2021-10-26 | 上海新微技术研发中心有限公司 | Silencing sensor, silencing earmuffs and silencing implementation method |
| CN113266568B (en) * | 2021-06-22 | 2023-01-31 | 广东美芝制冷设备有限公司 | Suction and exhaust structure, compressor and refrigeration equipment |
| CN113790506B (en) * | 2021-09-16 | 2022-07-19 | 珠海格力电器股份有限公司 | Method for solving noise of air conditioner outdoor unit |
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| CN1260447A (en) * | 1999-01-14 | 2000-07-19 | 三星电子株式会社 | Exhausting silencing apparatus for air-tight rotary compressor |
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| JP2010242541A (en) * | 2009-04-02 | 2010-10-28 | Daikin Ind Ltd | Muffler member and compressor with muffler member |
| JP2012215158A (en) * | 2011-04-01 | 2012-11-08 | Mitsubishi Electric Corp | Compressor, refrigeration cycle apparatus having the compressor thereon |
| CN102789518A (en) * | 2012-06-18 | 2012-11-21 | 珠海格力电器股份有限公司 | Compressor silencer optimization design method |
| JP2014077410A (en) * | 2012-10-11 | 2014-05-01 | Mitsubishi Heavy Ind Ltd | Compressor |
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2015
- 2015-04-07 CN CN201510160820.1A patent/CN104863819B/en not_active Expired - Fee Related
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1260447A (en) * | 1999-01-14 | 2000-07-19 | 三星电子株式会社 | Exhausting silencing apparatus for air-tight rotary compressor |
| KR20050097340A (en) * | 2004-04-01 | 2005-10-07 | 엘지전자 주식회사 | Muffler for hermetic type compressor |
| CN1763378A (en) * | 2004-10-21 | 2006-04-26 | 乐金电子(天津)电器有限公司 | Compressors muffler with resonance cavity |
| CN201037455Y (en) * | 2007-04-29 | 2008-03-19 | 上海日立电器有限公司 | Contracted cavity structure silencer |
| CN101644265A (en) * | 2008-08-04 | 2010-02-10 | 上海日立电器有限公司 | Method for reducing low-frequency noise of compressor |
| JP2010242541A (en) * | 2009-04-02 | 2010-10-28 | Daikin Ind Ltd | Muffler member and compressor with muffler member |
| JP2012215158A (en) * | 2011-04-01 | 2012-11-08 | Mitsubishi Electric Corp | Compressor, refrigeration cycle apparatus having the compressor thereon |
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| JP2014077410A (en) * | 2012-10-11 | 2014-05-01 | Mitsubishi Heavy Ind Ltd | Compressor |
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