CN207989259U - Compressor and its denoising structure - Google Patents
Compressor and its denoising structure Download PDFInfo
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- CN207989259U CN207989259U CN201820326369.5U CN201820326369U CN207989259U CN 207989259 U CN207989259 U CN 207989259U CN 201820326369 U CN201820326369 U CN 201820326369U CN 207989259 U CN207989259 U CN 207989259U
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Abstract
The utility model provides a kind of compressor and its denoising structure, can improve the noiseproof feature of compressor, and may insure refrigeration efficiency while noise reduction.The denoising structure of the utility model includes a helmholtz resonance chamber, the helmholtz resonance chamber includes neck and cavity, the neck is set to the side of the cavity and is connected to the cavity, wherein, the neck is opened in the form of through-hole on the cylinder cap of compressor, and the cavity is opened in the form of blind hole on the cylinder of compressor.Preferably, the cavity is obtained a fabrication hole intrinsic on cylinder in such a way that part blocks.
Description
Technical field
The utility model is related to compressors, more particularly to a kind of denoising structure.
Background technology
Existing compressor will produce prodigious noise at runtime, and noise mostlys come from three aspects：Mechanical noise,
Air power noise and electromagnetic noise.The mechanism of different noises, generation is different, and residing frequency range also differs.For place
In the noise of low frequency, noise reduction is generally carried out using muffler.
Compressor is commonly configured with muffler and bottom silencer, these mufflers, can also while gas is discharged
Play good Noise Reduction.But for being in the noise (noise near such as 3000Hz) of high band, these mufflers
Noise reduction is just undesirable.For this purpose, the existing structure by adjusting compressor housing reduces the noise of high band, for example, plus
The lower cover of compressor is fabricated to spherical shape, or increase bloop etc. by thick compressor housing.
However, in some cases, producing little effect the structure for changing compressor housing carrys out noise reduction, and change pressure
It is inconvenient that the shape of contracting casing body can also generate the installation of compressor, can also influence the normal operation of compressor.In addition to this, existing
Have also reduces the noise of high band without good method in technology.
Utility model content
In view of this, the purpose of this utility model is to provide a kind of compressor and its denoising structure, compression can be improved
The noiseproof feature of machine, and may insure refrigeration efficiency while noise reduction.
Therefore, one side according to the present utility model provides a kind of compressor, including a cylinder, the end of the cylinder
A cylinder cap is provided at face, and the compressor further includes a denoising structure.
Further, other side according to the present utility model provides a kind of denoising structure of compressor, the noise reduction knot
It includes neck and cavity that structure, which has a helmholtz resonance chamber, the helmholtz resonance chamber, and the neck is set to the cavity
Side and be connected to the cavity；Wherein, the neck is opened in the form of through-hole on the cylinder cap, and the cavity is with blind
The form in hole is opened on the cylinder.
It is preferably, solid on the cylinder that there are one fabrication holes, and and the cavity constructed on the basis of the fabrication hole
At.
Preferably, the fabrication hole is through-hole, and the cavity is obtained by the fabrication hole in such a way that part blocks.
Preferably, the fabrication hole is location hole.
Preferably, the neck is set to the region that thickness is most thin on the cylinder cap.
Preferably, the depth of the neck is equal to the minimum thickness of the cylinder cap.
Preferably, the cylinder cap is equipped with a gas vent, and the neck is opened near the gas vent.
Preferably, the aperture of the neck and depth are much smaller than 1/10th of wave length of sound.
Preferably, the calculation formula of the depth of the cavity is：
Wherein：C is the velocity of sound in coolant media；D is the effective aperture of neck；L is the effective depth of neck；D is cavity
Effective aperture；δ is the correction amount at the eck of neck,frFor target noise reduction frequency.
Preferably, the compressor includes upper cylinder and lower cylinder, endface of the upper cylinder far from the lower cylinder
It is provided with a upper cylinder cover, endface of the lower cylinder far from the upper cylinder is provided with cylinder cap；Wherein, the upper cylinder
On cavity and the upper cylinder cover on neck limits one helmholtz resonance chamber of formation jointly, and/or, on the lower cylinder
Cavity and the lower cylinder cap on neck limits one helmholtz resonance chamber of formation jointly.
According to technical solution provided by the utility model, cavity is opened up on the cylinder of compressor and on the cylinder cap of cylinder
Neck is opened up, and a helmholtz resonance chamber is collectively formed by the neck and the cavity, the helmholtz resonance chamber structure
At the denoising structure of compressor.Since the noise that helmholtz resonance chamber can be directed to different frequency range carries out noise reduction process, because
This, can play preferable noise reduction sound absorption.
In a preferred embodiment, the cavity constructed on the basis of a fabrication hole intrinsic on cylinder and
At not only reducing cost, and can ensure the volume of the compression chamber of cylinder, ensure the refrigeration efficiency of compressor.
Description of the drawings
Attached drawing does not constitute the improper restriction to this utility model for more fully understanding the utility model.Wherein：
Fig. 1 is the structural schematic diagram for the compressor that one embodiment of the utility model provides；
Fig. 2 is the structure principle chart for the helmholtz resonance chamber that one embodiment of the utility model provides；
Fig. 3 is the curve graph for the noise reduction that one embodiment of the utility model provides.
In figure：
Compressor -10, upper cylinder -11, upper cylinder cover -111, lower cylinder -12, lower cylinder cap -121, neck -01, cavity -02.
Specific implementation mode
Below in conjunction with the drawings and specific embodiments to the utility model proposes compressor and its denoising structure make it is further
It is described in detail.According to following explanation, will be become apparent from feature the advantages of the utility model.It should be noted that attached drawing be all made of it is non-
Often simplified form and use non-accurate ratio, only to it is convenient, lucidly aid in illustrating the utility model embodiment
Purpose.
Singulative "a", "an" and "the" as used in this specification includes plural reference, unless interior
In addition appearance explicitly points out outer.Term "or" as used in this specification be typically with the meaning including "and/or" and into
Enforcement, in addition in addition non-content explicitly points out.
It is the structural schematic diagram for the compressor that one embodiment of the utility model provides, pressure therein referring initially to Fig. 1
Contracting machine 10 includes two cylinders, is upper cylinder 11 (close to the motor of compressor) and (electricity far from compressor of lower cylinder 12 respectively
Machine), intermediate bulkhead (not shown) is provided between the upper cylinder 11 and lower cylinder 12.
In addition, upper end surface of the upper cylinder 11 far from lower cylinder 12 is provided with upper cylinder cover 111, the lower cylinder 12 is remote
Lower cylinder cap 121 is provided at lower face from upper cylinder 11.Here, " upper and lower " is not as the relative position to two cylinders
It limits, in practice with the adjustment of the installation direction of compressor 10, the relative position of two cylinders also changes therewith, such as
When being horizontally arranged compressor 10 in figure, the upper cylinder 11 and lower cylinder 12 can control arrangement, or can also be other
Arrangement is not especially limited.
Compressor therein includes but not limited to duplex cylinder compressor shown in Fig. 1, can also be single cylinder compressor,
This only makees signal to be further described the denoising structure of the present embodiment to describe conveniently with duplex cylinder compressor, but not with
This is as the restriction to compressor arrangement.
Further, in order to improve the noiseproof feature of compressor, the compressor 10 further includes a denoising structure, and the drop
There are one helmholtz resonance chambers for structure of making an uproar tool.
Fig. 2 is the structure principle chart for the helmholtz resonance chamber that one embodiment of the utility model provides, as shown in Fig. 2, its
In helmholtz resonance chamber include neck 01 and cavity 02, the neck 01 is set to the side of cavity 02 and connects with cavity 02
Logical, in actual use, the other end of the neck 01 is also connected to an acoustical passage.In the present embodiment, the acoustical passage is
The exhaust passage of compressor 10, the specific exhaust passage may include cylinder cap.
Obviously, the neck 01 forms a pore-throat being in communication with the outside, and the cavity 02 forms a closed cavity, when
When the depth of the neck 01 is much smaller than wave length of sound with aperture, the air column in the neck 01 can be regarded as one it is invisible
The mass block of change, and the cavity 02 is considered as an elastomer.When sound wave enters the hole eck of neck 01, will push
Air column in neck 01 does piston motion, and the air in cavity 02 is caused alternately to be compressed and expanded, and as sound wave is done
Elastic vibration.When frequency of sound wave is identical with intrinsic frequency in cavity 02, the air column in the neck 01 is due to meeting of resonating
Generate judder.In vibration processes, the sidewall friction sound energy consumption amount of air column and neck 01, to play noise reduction sound absorption
Effect.
For this purpose, the helmholtz resonance chamber of the denoising structure of the present embodiment is configured according to structure shown in Fig. 2.
With continued reference to Fig. 1, in one embodiment, the neck 01 is opened in the form of through-hole on upper cylinder cover 111, together
Shi Suoshu cavitys 02 are opened in the form of blind hole on upper cylinder 11.When actual exhaust air, 11 compressed gas of the upper cylinder
Upper cylinder cover 111 can be drained into, at this point, the compressed gas at least part for draining into upper cylinder cover 111 can be by the neck on upper cylinder cover 111
01 enters the cavity 02 in upper cylinder 11, to carry out noise reduction to 11 compressed gas of upper cylinder by the helmholtz resonance chamber
Sound absorption is handled, and noise when upper cylinder 11 is vented is reduced with this.
In another embodiment, the neck 01 can be opened on lower cylinder cap 121 in the form of through-hole, while the chamber
Body 02 is opened in the form of blind hole on lower cylinder 12.Therefore, when actual exhaust air, 12 compressed gas of the lower cylinder can be arranged
To lower cylinder cap 121, and then the gas at least part for draining into upper cylinder cover 121 can be by under the entrance of the neck 01 on lower cylinder cap 121
Cavity 02 in cylinder 12, to carry out noise reduction sound absorption to 12 compressed gas of lower cylinder by the helmholtz resonance chamber
Reason reduces noise when lower cylinder 12 is vented with this.
In other embodiments, the compressor 10 at least has there are two helmholtz resonance chamber, and a Helmholtz is total
The chamber that shakes includes the neck 01 being set on upper cylinder cover 111 and the cavity 02 on upper cylinder 11, another helmholtz resonance
Chamber includes the neck 01 being set on lower cylinder cap 121 and the cavity 02 on lower cylinder 12, realizes upper cylinder 11 under with this
The noise reduction process that cylinder 12 is vented.
Therefore, cavity is opened up on the cylinder of compressor, while opening up neck on the corresponding cylinder cap of the cylinder, by neck
A helmholtz resonance chamber is collectively formed with cavity, since helmholtz resonance chamber can not only play preferable noise reduction sound absorption
Effect, and it is more preferable for the assimilation effect of high band noise, therefore, the noiseproof feature of compressor can be improved, reduce compression
Noise when machine is vented.
Further, in order to reduce cost, preferably, constructed on the fabrication hole intrinsic on cylinder of the cavity 02 and
At, the fabrication hole is preferably through-hole, and then the cavity 02 can also be obtained by the fabrication hole in such a way that part blocks,
Thus, it is smaller to the structural modification of original cylinder, cost can be reduced.It is furthermore preferred that the fabrication hole is location hole,
Since location hole will not impact the volume of the compression chamber of cylinder, thereby it can be assured that the refrigeration efficiency of compressor.
In the present embodiment, the location hole can be located near the venthole of cylinder, and the aperture of the location hole is, for example,
Therefore 9.62mm can obtain the cavity 02 of blind hole form, and the aperture of the cavity 02 is excellent by partly blocking the location hole
Choosing is identical as the aperture of location hole.
According to the position of location hole, the position near cylinder cap upper air-vent can be chosen and open up neck 01.Optionally, the cylinder
The region near the gas vent covered is the region that thickness is most thin on cylinder cap, may be provided with air bleeding valve in the region, therefore,
For structure and purpose easy to process, which can neither be thinned, and cannot thicken, for this purpose, it is preferred that the neck 01
Depth design is equal with the minimum thickness of cylinder cap, such as the minimum thickness of cylinder cap can be 3.26mm, as a result, the neck 01
Depth be also 3.26mm.In addition, a through-hole can be obtained by way of drilling, to form the neck 01.
In the present embodiment, no matter for upper cylinder 11 or lower cylinder 12, can intrinsic at least one fabrication hole, the fabrication hole
Position can correspond to the region that thickness is most thin on cylinder cap, and the gas vent on cylinder cap may be disposed at the most thin region of thickness of cylinder cap.
In the present embodiment, the depth of the neck 01 and aperture are much smaller than wave length of sound, particularly, in high band noise
In, be greater than or the noise frequency range equal to 3000Hz in, the minimum wavelength of sound wave can reach 50mm and (be based on compressor refrigerant
In the velocity of sound be 191.8m/s), therefore, in high band noise, the diameter of the neck 01 be less than wave length of sound ten/
One.
Further, according to the sound absorption principle of helmholtz resonance chamber, only when the frequency of noise and resonant cavity (denoising structure
Cavity 02) intrinsic frequency it is identical when, the effect of denoising structure competence exertion sound absorption.So in the present embodiment, institute
The intrinsic frequency for stating denoising structure is identical as the frequency of compressor noise.The frequency of noise can be obtained by pertinent instruments measurement
, and the intrinsic frequency f of denoising structurerIt can be determined by following formula：
In above-mentioned formula (1), c is the velocity of sound (velocity of sound in such as coolant media) in medium, and d is the effective aperture of neck, l
For the effective depth of neck, H is the effective depth of cavity, and D is the effective aperture of cavity, and δ is the correction amount at the eck of neck,
Wherein：
In the present embodiment, the depth l of the neck 01 can be equal to the minimum thickness of cylinder cap, the aperture of the neck 01
D is less than 1/10th of wave length of sound, and the aperture D of the cavity 02 is equal to the aperture of fabrication hole on cylinder, these are known
Amount, and the intrinsic frequency f of helmholtz resonance chamberrGenerally equal to target noise reduction frequency (need the frequency of the noise of elimination, can
Rule of thumb obtain, such as the high-frequency noise of 3000Hz), therefore, according to formula (1), the calculating that can obtain the depth of cavity 02 is public
Formula：
In one embodiment of the utility model, the aperture of the cavity 02 is equal to the aperture of fabrication hole, it may be determined that is
9.62mm, while the aperture of the neck 01 is equal to the minimum thickness of cylinder cap, it may be determined that it is 3.26mm, therefore, when target noise reduction
When frequency is determined as 3000Hz, in compressor coolant media, the velocity of sound can be identified as 191.8m/s, for this purpose, the most small echo of sound wave
Length can be determined as 50mm, and the aperture as a result, based on the neck 01 need to be less than 1/10th of the minimum wavelength of sound wave, therefore
And the aperture of the neck 01 can be identified as being less than 5mm, such as be designed as 4.5mm, it, can be with thus, according to above-mentioned formula (3)
The depth H that cavity 02 is calculated is 3.33mm.Specifically, the geometric parameter of above-mentioned helmholtz resonance chamber can refer to such as following table
Lattice：
In addition, according to formula (1) it is found that noise for different frequency range, by the neck for changing helmholtz resonance chamber
Aperture, depth can adjust target noise reduction frequency, alternatively, can also by change helmholtz resonance chamber cavity aperture,
Depth also can adjust target noise reduction frequency, be achieved in the processing to different frequency range noise.
In addition, refering to Fig. 3, proved by experiment, for compressor 10 provided in this embodiment, near 3000Hz, the pressure
The noise of contracting machine 10 is lowered about 4 decibels, and noise OA is lowered about 2 decibels, therefore, noise reduction compared to existing compressor
Effect is more apparent.It should be noted that in Fig. 3, abscissa is noise frequency, unit Hz, and ordinate is noise, unit dB, and
The curve of square mark is the noise curve of the compressor of the present embodiment in figure, i.e. the curve of figure intermediate cam shape mark is existing
Compressor noise curve.
Finally, it is worth mentioning at this point that, the denoising structure of the present embodiment is very effective for the noise for absorbing high band, example
Such as it is not less than the noise of 3000Hz, while the denoising structure processes hole preferably on the cylinder of compressor and corresponding cylinder cap and is
Can, without changing the shape of compressor housing or increasing the thickness of compressor housing, which not only simplifies the systems of compressor
Make technique, but also be convenient for the installation of compressor and ensure the stability of compressor operating, particularly, additionally it is possible to ensure compression
The refrigeration efficiency of machine.
In turn, according to the utility model embodiment provide technical solution, opened up on the cylinder of compressor cavity and
Neck is opened up on the cylinder cap of cylinder, a helmholtz resonance chamber is collectively formed by neck and cavity, the helmholtz resonance chamber
Constitute the denoising structure of compressor.Since the noise that helmholtz resonance chamber can be directed to different frequency range carries out noise reduction process,
Therefore, it is possible to play preferable noise reduction sound absorption.
In a preferred embodiment, the cavity is obtained by fabrication hole intrinsic on cylinder in such a way that part blocks
, in this way, will not be influenced too much to the structure of existing cylinder and cylinder cap, and minimum cylinder volume will not be impacted, because
This may insure refrigeration efficiency.
It should be noted last that above example is merely intended for describing the technical solutions of the present application, but not for limiting the present application, to the greatest extent
Pipe is described in detail the utility model with reference to preferred embodiment, it will be understood by those of ordinary skill in the art that, it can be with
The technical solution of the utility model is modified or replaced equivalently, without departing from technical solutions of the utility model spirit and
Range.
Claims (10)
1. a kind of denoising structure of compressor, the compressor includes a cylinder, and the endface of the cylinder is provided with a cylinder cap,
It is characterized in that, it includes neck and cavity that the denoising structure, which has a helmholtz resonance chamber, the helmholtz resonance chamber,
The neck is set to the side of the cavity and is connected to the cavity；Wherein, the neck is opened in institute in the form of through-hole
It states on cylinder cap, the cavity is opened in the form of blind hole on the cylinder.
2. the denoising structure of compressor as described in claim 1, which is characterized in that fabrication hole there are one solid on the cylinder,
And the cavity constructs on the basis of the fabrication hole.
3. the denoising structure of compressor as claimed in claim 2, which is characterized in that the fabrication hole is through-hole, the cavity
It is obtained in such a way that part blocks by the fabrication hole.
4. the denoising structure of compressor as claimed in claim 3, which is characterized in that the fabrication hole is location hole.
5. the denoising structure of compressor as described in claim 1, which is characterized in that the depth of the neck is equal to the cylinder cap
Minimum thickness.
6. the denoising structure of compressor as claimed in claim 5, which is characterized in that the cylinder cap is equipped with a gas vent, institute
Neck is stated to be opened near the gas vent.
7. the denoising structure of compressor as described in claim 1, which is characterized in that the aperture of the neck and depth are remote small
In 1/10th of wave length of sound.
8. the denoising structure of compressor as described in claim 1, which is characterized in that the calculation formula of the depth of the cavity
For：
Wherein：C is the velocity of sound in coolant media；D is the effective aperture of neck；L is the effective depth of neck；D is having for cavity
Imitate aperture；δ is the correction amount at the eck of neck,frFor target noise reduction frequency.
9. the endface of a kind of compressor, including a cylinder, the cylinder is provided with a cylinder cap, which is characterized in that the compression
Machine further includes the denoising structure as described in any one of claim 1-8.
10. compressor as claimed in claim 9, which is characterized in that the compressor includes upper cylinder and lower cylinder, it is described on
Endface of the cylinder far from the lower cylinder is provided with a upper cylinder cover, endface setting of the lower cylinder far from the upper cylinder
There is cylinder cap；
Wherein, the cavity on the upper cylinder limits with the neck on the upper cylinder cover and forms a helmholtz resonance jointly
Chamber, and/or, the cavity on the lower cylinder limits jointly with the neck on the lower cylinder cap forms a helmholtz resonance
Chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820326369.5U CN207989259U (en) | 2018-03-09 | 2018-03-09 | Compressor and its denoising structure |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820326369.5U CN207989259U (en) | 2018-03-09 | 2018-03-09 | Compressor and its denoising structure |
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| Publication Number | Publication Date |
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| CN207989259U true CN207989259U (en) | 2018-10-19 |
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ID=63826607
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| CN201820326369.5U Active CN207989259U (en) | 2018-03-09 | 2018-03-09 | Compressor and its denoising structure |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109915375A (en) * | 2019-04-17 | 2019-06-21 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly and compressor |
| CN111238018A (en) * | 2020-03-03 | 2020-06-05 | 青岛海信日立空调系统有限公司 | Refrigerating equipment |
| CN115142999A (en) * | 2022-08-02 | 2022-10-04 | 哈尔滨工程大学 | Booster air inlet silencer with adjustable cavity space structure |
-
2018
- 2018-03-09 CN CN201820326369.5U patent/CN207989259U/en active Active
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109915375A (en) * | 2019-04-17 | 2019-06-21 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly and compressor |
| CN111238018A (en) * | 2020-03-03 | 2020-06-05 | 青岛海信日立空调系统有限公司 | Refrigerating equipment |
| CN115142999A (en) * | 2022-08-02 | 2022-10-04 | 哈尔滨工程大学 | Booster air inlet silencer with adjustable cavity space structure |
| US20240044306A1 (en) * | 2022-08-02 | 2024-02-08 | Harbin Engineering University | Turbocharger air intake silencer with adjustable cavity space structure |
| US11905916B1 (en) * | 2022-08-02 | 2024-02-20 | Harbin Engineering University | Turbocharger air intake silencer with adjustable cavity space structure |
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