CN107036332A - Refrigeration plant and compressor cabin design method - Google Patents
Refrigeration plant and compressor cabin design method Download PDFInfo
- Publication number
- CN107036332A CN107036332A CN201710191260.5A CN201710191260A CN107036332A CN 107036332 A CN107036332 A CN 107036332A CN 201710191260 A CN201710191260 A CN 201710191260A CN 107036332 A CN107036332 A CN 107036332A
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- China
- Prior art keywords
- perforated plate
- compressor
- cabin
- refrigeration plant
- thickness
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 27
- 238000000034 method Methods 0.000 title claims abstract description 10
- 230000015572 biosynthetic process Effects 0.000 claims abstract description 7
- 238000004080 punching Methods 0.000 claims description 12
- 230000006835 compression Effects 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 5
- 230000009467 reduction Effects 0.000 abstract description 10
- 238000010521 absorption reaction Methods 0.000 description 5
- 230000008901 benefit Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000003993 interaction Effects 0.000 description 2
- 230000008092 positive effect Effects 0.000 description 2
- 238000013016 damping Methods 0.000 description 1
- 210000004209 hair Anatomy 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Soundproofing, Sound Blocking, And Sound Damping (AREA)
Abstract
The invention discloses a kind of refrigeration plant and compressor cabin design method.Refrigeration plant, including casing and compressor, cabin is provided with the casing, the compressor is arranged in the cabin, the both sides of the compressor are additionally provided with perforated plate, some through holes are offered on the perforated plate, air cavity, the perforated plate and air chamber body formation resonance sound-absorbing structure are formed between the perforated plate and the bulkhead of the cabin.The noise of reduction refrigeration plant is realized to improve user experience.
Description
Technical field
The present invention relates to refrigeration plant, more particularly to a kind of refrigeration plant and compressor cabin design method.
Background technology
At present, refrigeration plant（Refrigerator, refrigerator etc.）Cabin is generally provided with casing, compressor is placed in cabin.
In actual use, when compressor works in cabin, its noise produced is broadly divided into structure-borne sound and air-borne sound two
Point, wherein, structure-borne sound is due to that the vibration of compressor is delivered to refrigeration plant by flowing back to tracheae and compressor rubber blanket
On casing, the noise then given off due to hull vibration；The noise that air-borne sound goes out mainly due to compressor own radiation
It is delivered in cabin after multiple reflections through cabin heat dissipation grid outside the casing of refrigeration plant.Generally, it is empty
Gas sound is much larger than structure-borne sound.Therefore, reduction compressor air sound is to reduce the key of compressor noise.China Patent No.
2005201133280, which disclose a kind of sound arrester of compressor, uses the blimp with through hole to cover compressor, and due to
Compressor noise is mainly distributed on middle low frequency, and blimp is typically smaller than for the acoustic absorptivity of Middle and low frequency noise within 1000Hz
0.5, the acoustic absorptivity that 400Hz low-frequency noise is less than for frequency is even more to be less than 0.3, it is impossible to effectively absorb compressor noise.
How to design a kind of small refrigeration plant to improve user experience of noise is the technical problems to be solved by the invention.
The content of the invention
The invention provides a kind of refrigeration plant and compressor cabin design method, realize the noise of reduction refrigeration plant with
Improve user experience.
To reach above-mentioned technical purpose, the present invention is realized using following technical scheme：
Cabin is provided with a kind of refrigeration plant, including casing and compressor, the casing, the compressor is arranged on the machine
In storehouse, the both sides of the compressor, which are additionally provided with perforated plate, the perforated plate, offers some through holes, the perforated plate and institute
State formation air cavity between the bulkhead of cabin, the perforated plate and air chamber body formation resonance sound-absorbing structure.
Further, two perforated plates are divided into the first perforated plate and the second perforated plate, first perforated plate and institute
State the punching rate of the second perforated plate, thickness of slab, through-hole aperture and/or distance is different between the bulkhead of the cabin.
Further, the perforated plate include multiple daughter board bodies linked together, the punching rate of the different daughter board bodies,
Thickness of slab, through-hole aperture and/or distance is different between the bulkhead of the cabin.
Further, the punching rate of the perforated plate is 0.5%-20%, the thickness of slab 0.2mm-15mm of the perforated plate；It is described
The through-hole aperture 0.2mm-8mm of perforated plate.
The present invention also provides a kind of compressor cabin design method, comprises the following steps：
Noise peak frequency f under step 1, test compression machine working conditionp；And compressor is measured between cabin two side
Apart from L；
Step 2, according to formula, the parameter of perforated plate is chosen, and cause；
Wherein, c is the velocity of sound, and P is the punching rate of perforated plate, and T is the thickness of slab of perforated plate.
Further, when the aperture d of perforated plate is less than 1mm, T=t+0.8+PL/3；When the aperture d of perforated plate is more than
During 1mm, T=t+0.8d；Wherein, t is the actual (real) thickness of perforated plate.
Further, P span is 0.5%-20%, and t span is 0.2mm-15mm.
Compared with prior art, advantages and positive effects of the present invention are：By the both sides for being located at compressor in cabin
Set and some through holes are offered on perforated plate, perforated plate, perforated plate and air chamber body formation resonance sound-absorbing structure work as sound wave incident
During to the resonance sound-absorbing structure, the motion of via hollow gas can be caused, and the air in air cavity plays a part of spring, gives
Air in through hole provides restoring force, and under the interaction of sound wave and the hollow gas of air cavity, the air in through hole is in through hole
It is middle to move back and forth, when the frequency of incident acoustic wave is equal to the intrinsic frequency f of resonance sound-absorbing structure0When, system resonates, in through hole
Air can be violent reciprocating motion, and with the hole wall friction of through hole, acoustic energy almost all is changed into heat energy, so as to realize
The reduction noise of effect；Compared to prior art, without compressor is integrally covered, it is to avoid because compressor covered cause radiating compared with
Difference and need extra configuration ventilating fan, in addition, resonance sound-absorbing structure can have higher sound absorption to the noise of a certain frequency range
Ability, in sound absorption crest frequency f0The acoustic absorptivity at place can reach 1, realize the noise of reduction refrigeration plant to improve user's body
The property tested.
Brief description of the drawings
In order to illustrate more clearly about the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
There is the accompanying drawing used required in technology description to be briefly described, it should be apparent that, drawings in the following description are this hairs
Some bright embodiments, for those of ordinary skill in the art, without having to pay creative labor, can be with
Other accompanying drawings are obtained according to these accompanying drawings.
Fig. 1 is structural representation Fig. 1 of refrigeration plant incubator embodiment of the present invention;
Fig. 2 is structural representation Fig. 2 of refrigeration plant incubator embodiment of the present invention；
Fig. 3 is structural representation Fig. 3 of refrigeration plant incubator embodiment of the present invention.
Embodiment
To make the purpose, technical scheme and advantage of the embodiment of the present invention clearer, below in conjunction with the embodiment of the present invention
In accompanying drawing, the technical scheme in the embodiment of the present invention is clearly and completely described, it is clear that described embodiment is
A part of embodiment of the present invention, rather than whole embodiments.Based on the embodiment in the present invention, those of ordinary skill in the art
The every other embodiment obtained under the premise of creative work is not made, belongs to the scope of protection of the invention.
As shown in figure 1, the present embodiment refrigeration plant, including casing 1 and compressor 2, cabin is provided with the casing 1
11, the compressor 2 is arranged in the cabin 11, and the both sides of the compressor 2 are additionally provided with perforated plate 3, the perforated plate
Some through holes are offered on 3（It is unmarked）, air cavity 30, institute are formed between the bulkhead of the perforated plate 3 and the cabin 11
State perforated plate 3 and the air cavity 30 formation resonance sound-absorbing structure.
Specifically, the present embodiment refrigeration plant utilizes the sound absorption principle of resonance sound-absorbing structure, wherein, lead on perforated plate 3
Equivalent to one mass m of air in hole, air chamber body equivalent to connected spring k, air in through hole with it is logical
Friction between hole is equivalent to damp c, and therefore, the air in through hole, the air in air cavity and through-hole wall are formed together
Spring-mass damping system, the intrinsic frequency of the system is f0, can be according to the running of compressor 2 using above-mentioned principle
The frequency noise f of middle generationpTo select the specification of perforated plate 3, to cause the resonance sound-absorbing structure frequency f formed in cabin 110With
The frequency noise f of compressor 2pMatch, after the noise that compressor 2 gives off incides the resonance sound-absorbing structure, frequency f0It is attached
Near noise can be absorbed by resonance sound-absorbing structure, change into heat energy, so as to reduce the noise being radiated on the outside of refrigeration plant
Level, so as to realize the purpose of resonance sound-absorbing.Compared with using conventional compression cabin, the present embodiment refrigeration plant compressor noise
Peak value is substantially reduced, and the noise peak reduction 10dB of compressor at 250Hz, total noise of centrifuge is reduced to 34dB by 40dB, reduced
6dB, noise reduction is obvious.
Wherein, unlikely one of the noise peak that compressor 2 is produced, often there is two peak values, even more than peak value, so
Two perforated plates 3 in the present embodiment can carry out structure design for different frequency, as shown in Fig. 2 two 3 points of perforated plates
For the first perforated plate and the second perforated plate, the punching rate of first perforated plate and second perforated plate, thickness of slab, through-hole aperture
And/or distance is different between the bulkhead of the cabin, specifically, by change perforated plate 3 and cabin 11 distance or aperture,
The parameters such as thickness of slab, punching rate make the frequency of perforated plate 3 separately design in f0、f1.Or, as shown in figure 3, to same perforated plate 3
Frequency-division section design is carried out, the perforated plate 3 includes multiple daughter board bodies 31 linked together, the perforation of the different daughter board bodies 31
Rate, thickness of slab, through-hole aperture and/or distance is different between the bulkhead of the cabin 10, specifically, for example：By the upper half of perforated plate 3
Design in frequency f in portion0, lower half is designed in frequency f1, you can realize the noise reduction to two peak values.Wherein, the perforated plate
Punching rate be 0.5%-20%, the thickness of slab 0.2mm-15mm of the perforated plate；The through-hole aperture 0.2mm-8mm of the perforated plate.
The present invention also provides a kind of compressor cabin design method, comprises the following steps：
Noise peak frequency f under step 1, test compression machine working conditionp；And compressor is measured between cabin two side
Apart from L.Specifically, the noise peak frequency of test compression machine in the operating condition, and measure compressor both sides in cabin
Using space.
Step 2, according to formula, the parameter of perforated plate is chosen, and cause, wherein, c is
The velocity of sound, P is the punching rate of perforated plate, and T is the thickness of slab of perforated plate.Specifically, when the aperture d of perforated plate is less than 1mm, T=t+
0.8+PL/3；When the aperture d of perforated plate is more than 1mm, T=t+0.8d；Wherein, t is the actual (real) thickness of perforated plate, P value model
Enclose for 0.5%-20%, t span is 0.2mm-15mm.
Compared with prior art, advantages and positive effects of the present invention are：By the both sides for being located at compressor in cabin
Set and some through holes are offered on perforated plate, perforated plate, perforated plate and air chamber body formation resonance sound-absorbing structure work as sound wave incident
During to the resonance sound-absorbing structure, the motion of via hollow gas can be caused, and the air in air cavity plays a part of spring, gives
Air in through hole provides restoring force, and under the interaction of sound wave and the hollow gas of air cavity, the air in through hole is in through hole
It is middle to move back and forth, when the frequency of incident acoustic wave is equal to the intrinsic frequency f of resonance sound-absorbing structure0When, system resonates, in through hole
Air can be violent reciprocating motion, and with the hole wall friction of through hole, acoustic energy almost all is changed into heat energy, so as to realize
The reduction noise of effect；Compared to prior art, without compressor is integrally covered, it is to avoid because compressor covered cause radiating compared with
Difference and need extra configuration ventilating fan, in addition, resonance sound-absorbing structure can have higher sound absorption to the noise of a certain frequency range
Ability, in sound absorption crest frequency f0The acoustic absorptivity at place can reach 1, realize the noise of reduction refrigeration plant to improve user's body
The property tested.
Finally it should be noted that：The above embodiments are merely illustrative of the technical solutions of the present invention, rather than its limitations；Although
The present invention is described in detail with reference to the foregoing embodiments, it will be understood by those within the art that：It still may be used
To be modified to the technical scheme described in foregoing embodiments, or equivalent substitution is carried out to which part technical characteristic；
And these modifications or replace, do not make appropriate technical solution essence depart from the present invention embodiment technical scheme spirit and
Scope.
Claims (7)
1. being provided with cabin in a kind of refrigeration plant, including casing and compressor, the casing, the compressor is arranged on described
In cabin, it is characterised in that the both sides of the compressor are additionally provided with perforated plate, the perforated plate and offer some through holes,
Air cavity is formed between the bulkhead of the perforated plate and the cabin, the perforated plate is inhaled with air chamber body formation resonance
Acoustic form.
2. refrigeration plant according to claim 1, it is characterised in that two perforated plates are divided into the first perforated plate and
The punching rate of two perforated plates, first perforated plate and second perforated plate, thickness of slab, through-hole aperture and/or with the cabin
Bulkhead between distance it is different.
3. refrigeration plant according to claim 1, it is characterised in that the perforated plate includes multiple sons linked together
Plate body, the punching rates of the different daughter board bodies, thickness of slab, through-hole aperture and/or distance is different between the bulkhead of the cabin.
4. refrigeration plant according to claim 1, it is characterised in that the punching rate of the perforated plate is 0.5%-20%, institute
State the thickness of slab 0.2mm-15mm of perforated plate；The through-hole aperture 0.2mm-8mm of the perforated plate.
5. a kind of compressor cabin design method, it is characterised in that comprise the following steps：
Noise peak frequency f under step 1, test compression machine working conditionp；And compressor is measured between cabin two side
Apart from L；
Step 2, according to formula, the parameter of perforated plate is chosen, and cause；
Wherein, c is the velocity of sound, and P is the punching rate of perforated plate, and T is the thickness of slab of perforated plate.
6. compressor cabin design method according to claim 5, it is characterised in that when the aperture d of perforated plate is less than
During 1mm, T=t+0.8+PL/3；When the aperture d of perforated plate is more than 1mm, T=t+0.8d；Wherein, t is the actual thickness of perforated plate
Degree.
7. compressor cabin design method according to claim 5, it is characterised in that P span is 0.5%-20%,
T span is 0.2mm-15mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710191260.5A CN107036332A (en) | 2017-03-28 | 2017-03-28 | Refrigeration plant and compressor cabin design method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710191260.5A CN107036332A (en) | 2017-03-28 | 2017-03-28 | Refrigeration plant and compressor cabin design method |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107036332A true CN107036332A (en) | 2017-08-11 |
Family
ID=59533788
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710191260.5A Pending CN107036332A (en) | 2017-03-28 | 2017-03-28 | Refrigeration plant and compressor cabin design method |
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| Country | Link |
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| CN (1) | CN107036332A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112283809A (en) * | 2020-10-30 | 2021-01-29 | 青岛海信日立空调系统有限公司 | Outdoor air conditioner |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2844492Y (en) * | 2005-07-11 | 2006-12-06 | 福建省泉州市力达机械有限公司 | Composite-plated sound absorber of multi-stage compressor |
| CN101205937A (en) * | 2006-12-20 | 2008-06-25 | 株式会社日立产机系统 | Diagonal flow fan |
| CN101793213A (en) * | 2009-02-04 | 2010-08-04 | 通用汽车环球科技运作公司 | Noise reducing system |
| CN105222474A (en) * | 2015-11-06 | 2016-01-06 | 青岛海尔股份有限公司 | Adopt the refrigerator of linear compressor |
-
2017
- 2017-03-28 CN CN201710191260.5A patent/CN107036332A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2844492Y (en) * | 2005-07-11 | 2006-12-06 | 福建省泉州市力达机械有限公司 | Composite-plated sound absorber of multi-stage compressor |
| CN101205937A (en) * | 2006-12-20 | 2008-06-25 | 株式会社日立产机系统 | Diagonal flow fan |
| CN101793213A (en) * | 2009-02-04 | 2010-08-04 | 通用汽车环球科技运作公司 | Noise reducing system |
| CN105222474A (en) * | 2015-11-06 | 2016-01-06 | 青岛海尔股份有限公司 | Adopt the refrigerator of linear compressor |
Non-Patent Citations (1)
| Title |
|---|
| 陈永校等: "《电机噪声的分析和控制》", 30 June 1987, 浙江大学出版社 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112283809A (en) * | 2020-10-30 | 2021-01-29 | 青岛海信日立空调系统有限公司 | Outdoor air conditioner |
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Application publication date: 20170811 |