CN204003618U - The noise reducing casing assembly of centrifugal blower - Google Patents
The noise reducing casing assembly of centrifugal blower Download PDFInfo
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- CN204003618U CN204003618U CN201420469029.XU CN201420469029U CN204003618U CN 204003618 U CN204003618 U CN 204003618U CN 201420469029 U CN201420469029 U CN 201420469029U CN 204003618 U CN204003618 U CN 204003618U
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- spiral case
- snail tongue
- arc
- vortex board
- hush pipe
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Abstract
The utility model is specifically related to the spiral case assembly of centrifugal blower, comprise spiral case, be arranged on spiral case and with the integrated snail tongue of spiral case and diffusion outlet section, and be connected to the hush pipe on described diffusion outlet section, described snail tongue is spirogyrate ear shape snail tongue, on described spiral case, be also provided with the anti-vortex board of arc, the width of the anti-vortex board of this arc and the width of spiral case adapt, one end of the anti-vortex board of described arc is connected between diffusion outlet section and snail tongue, the other end of the anti-vortex board of arc is free end, this free end is near impeller and be positioned at the below of spiral case air-out passage, on the outer side surface of described spiral case and snail tongue, be all coated with sound-absorbing material coating, described snail tongue is greater than the axial width of spiral case along the axial width of spiral case, the length of described hush pipe is 0.4-1.6 rice, and hush pipe inner side is provided with quieter material layer, by changing the structure of spiral case assembly and installing anti-vortex board and hush pipe additional, has reduced the noise of centrifugal blower in the time of work, has reached the effect that noise control pollutes.
Description
Technical field
The utility model relates to the spiral case assembly on centrifugal blower, is specifically related to the improvement to spiral case modular construction.
Background technique
Snail tongue noise is the key factor that affects centrifugal blower noise, and the main cause that causes blower snail tongue noise is due to the discharge air-flow of centrifugal impeller and snail tongue interact.For the centrifugal blower of traditional single spiral tougue spiral case, the spacing of its snail tongue and impeller outer edge has an optimum range.Spacing is too little, and air flow stream is crossed the gap of snail tongue and impeller outer edge, can produce howling; Spacing strengthens, although air-flow makes moderate progress to the impact condition of snail tongue, some air-flow can ceaselessly circulate with impeller in spiral case, produces low frequency oscillation or sympathetic response, causes noise to increase.Therefore, snail tongue structure has formed a main source of blower fan loss and noise.
Meanwhile, near centrifugal blower impeller shroud, air-flow mainly flows vertically, and near impeller middle part and hub disk, air-flow changes Radial Flow gradually into.Therefore,, near shroud, flow parameter changes greatly, easily forms maelstrom district.Common centrifugal blower spiral case diffusion exit length shorter (being generally 0.1-0.3 rice), vortex easily forms near snail tongue, has increased noise thereby impact snail tongue wall.Vortex has formed another main source of blower fan loss and noise.
Some centrifugal blowers are connected with certain length baffler or hush pipe on diffusion outlet section, but its main purpose is to reduce noise by structure itself or the quieter material being filled in wherein, in order to save material and space, therefore length is generally shorter, for 0.1-0.2 rice, prevent that the effect of vortex generation is bad.
Model utility content
The purpose of this utility model is to provide a kind of noise reducing casing assembly that can effectively reduce centrifugal blower noise.
For achieving the above object, the technological scheme that the utility model adopts is: comprise spiral case, be arranged on spiral case and with the integrated snail tongue of spiral case and diffusion outlet section, and be connected to the hush pipe on described diffusion outlet section, it is characterized in that: described snail tongue is spirogyrate ear shape snail tongue, on described spiral case, be also provided with the anti-vortex board of arc, the width of the anti-vortex board of this arc and the width of spiral case adapt, one end of the anti-vortex board of described arc is connected between diffusion outlet section and snail tongue, the other end of the anti-vortex board of arc is free end, this free end is near impeller and be positioned at the below of spiral case air-out passage, on the outer side surface of described spiral case and snail tongue, be all coated with sound-absorbing material coating, described snail tongue is greater than the axial width of spiral case along the axial width of spiral case, the length of described hush pipe is 0.4-1.6 rice, and hush pipe inner side is provided with quieter material layer.
Preferably: described quieter material layer is aluminum fiber composite sheet.
Preferably: described sound-absorbing material coating is polyurethane coating.
Preferably: the anti-vortex board of described spiral case and arc is one-body molded.
Preferably: the anti-vortex board of described arc is upper arch arc plate.
The utlity model has following beneficial effect:
1. compared with traditional inner concave shape snail tongue, snail tongue is spirogyrate ear shape snail tongue, and the gap that has increased snail tongue and impeller, can effectively reduce snail tongue noise.Simultaneously, because the axial width of this snail tongue is greater than the axial width of spiral case, even at the gap smaller part of impeller edge and snail tongue, in the case of not changing the spacing of impeller edge and snail tongue, also increased the buffer space of air-flow, reduce the impact of air-flow to snail tongue, thereby reduced snail tongue noise.
2. because air-out passage below is provided with the anti-vortex board of arc, can stops that the gas backstreaming of air-out passage is near snail tongue, thereby avoid vortex to produce near snail tongue.Meanwhile, according to fluid mechanics principle, the hush pipe being connected on diffusion outlet section is increased diffusion outlet section, can further reduce scope and the intensity of vortex, and makes vortex away from snail tongue, thereby further reduces noise.
3. because spiral case and snail tongue outside scribble sound-absorbing material coating, and hush pipe inner side is provided with as quieter material layer, further improved the noise reduction of spiral case assembly.
4. the noise producing due to centrifugal blower is mainly low-frequency noise, and preferably aluminum fiber composite sheet is as quieter material layer inside hush pipe.Aluminum fiber composite sheet quality is little, is convenient to mounting arrangements, and compared with current domestic and international low frequency absorption material, in the time that low-frequency noise is administered, overall cost is low, has good Technical Economy.In addition, aluminum fiber composite sheet has certain mechanical strength, not climate environmetal impact, and in high humility area, acoustic absorptivity does not decline because of moist, and heat-transfer effect is good simultaneously, is beneficial to equipment cooling.
5. preferred sound-absorbing material coating is polyurethane coating, and this coating has excellent acoustically effective to low-frequency noise equally, and coating is convenient, and cost performance is high.Meanwhile, this coating also has good waterproof and wear-resisting property, can protect better spiral case, has extended the working life of spiral case.
6. the anti-vortex board of arc and spiral case are one-body molded, are convenient to processing and fabricating.Upper arch also makes it in the anti-eddy current function of guarantee self, increase the space between snail tongue and impeller, is conducive to the reduction of noise.
Brief description of the drawings
Fig. 1 is structural representation of the present utility model.
Embodiment
As shown in Figure 1, a kind of noise reducing casing assembly of centrifugal blower, comprise spiral case 1, be arranged on spiral case 1 and with the integrated snail tongue 101 of spiral case 1 and diffusion outlet section 102 and be connected to the hush pipe 2 on described diffusion outlet section 102, wherein: snail tongue 101 is spirogyrate ear shape snail tongue, and its axial width along spiral case 1 is greater than the axial width of spiral case 1.Therefore,, compared with traditional inner concave shape snail tongue, this shape has increased the gap of snail tongue 101 with impeller 4, can effectively reduce snail tongue 101 noises.In addition, because this snail tongue 101 is greater than the axial width of spiral case 1 along the axial width of spiral case 1, even at the gap smaller part of impeller 4 edges and snail tongue 101, in the case of not changing the spacing of impeller 4 edges and snail tongue 101, also increased the buffer space of air-flow, reduce the impact of air-flow to snail tongue 101, thereby reduced the noise of snail tongue 101.
On spiral case 1, be also provided with the anti-vortex board 103 of arc, the width of the anti-vortex board 103 of this arc and the width of spiral case 1 adapt, one end is connected between diffusion outlet section 102 and snail tongue 101, the other end of the anti-vortex board 103 of arc is free end, and this free end is near the air-out passage of spiral case 1 and be positioned at the below of spiral case 1 air-out passage.Therefore, this structure can stop that the gas backstreaming of air-out passage is near snail tongue 101, thereby avoids vortex to produce near snail tongue 101.
In addition,, according to fluid mechanics principle, the length that increases hush pipe 2 can reduce scope and the intensity of vortex, and makes vortex away from snail tongue 101, thereby further reduces noise.Therefore,, compared with common baffler, the length of the utility model hush pipe 2 is longer.In experiment several times of the present utility model, the centrifugal blower model of employing is CZ-180W type, air quantity 408(m
3/ min), diffusion outlet section 102 length are 0.15 meter, actual measurement operational noise 62dB(A) (method of measurement is the average of getting three different time point measurements, and the described time point of measuring for three times is respectively start latter 30 minutes, 60 minutes and 120 minutes).Keep blower former state, only joint noise reduction pipe 2 on the diffusion outlet section 102 of its spiral case 1, described hush pipe 2 length are respectively 0.2 meter, 0.5 meter, 1 meter and 1.5 meters.Experimenter redeterminates operational noise and is respectively 60 dB(A), 55 dB(A), 53 dB(A) and 53 dB(A) (method of measurement is all identical with the method for above-mentioned surveying work noise).Visible noise reduction is directly proportional to the length of hush pipe 2, and (in experiment, is 0.2 meter) more in short-term when the length of hush pipe 2, and noise reduction is not obvious.But for blower used in experiment, hush pipe 2 length of preferred version are 0.5 meter, because the only 2dB(A that reduced of the hush pipe 2 of 1 meter more) noise, length has but increased by one times, not only make the cost of material of hush pipe 2 also increase by one times, and longer pipeline also can make wind energy cause more loss, cost performance is not high.Therefore, select the hush pipe 2 of 0.5 meter to there is best cost performance.Equally, for the centrifugal blower of other different models, according to experiment and hydromechanical principle, the effect of noise reduction is relevant with the length three of diffusion outlet section 102 to length, the air quantity of blower of hush pipe 2, the effect of noise reduction is also relevant to the intensity of former noise, researcher in this field can select hush pipe 2 length according to actual conditions, but unsuitable long or too short.If hush pipe 2 is long, can causes too much wind energy loss and increase too much manufacture cost; If hush pipe 2 is too short, the DeGrain of noise reduction.Researcher in this field can be determined by experiment hush pipe 2 length of tool cost performance.
The noise producing due to centrifugal blower is mainly low-frequency noise, and the preferred aluminum fiber composite sheet of the utility model is arranged on hush pipe 2 inner sides as quieter material layer 201.Aluminum fiber composite sheet quality is little, is convenient to mounting arrangements, and compared with current domestic and international low frequency absorption material, in the time that low-frequency noise is administered, overall cost is low, has good Technical Economy.In addition, aluminum fiber composite sheet has certain mechanical strength, not climate environmetal impact, and in high humility area, acoustic absorptivity does not decline because of moist, and heat-transfer effect is good simultaneously, is beneficial to equipment cooling.
In addition, the utility model is also coated with sound-absorbing material coating 3 on the outer side surface of spiral case 1 and snail tongue 101.Preferred sound-absorbing material coating 3 is polyurethane coating, and this coating has excellent acoustically effective to low-frequency noise equally, and coating is convenient, and cost performance is high.Meanwhile, this coating also has good waterproof and wear-resisting property, can protect better spiral case 1, has extended the working life of spiral case 1.
Further preferably, the anti-vortex board of arc 103 and spiral case 1 be with one-body molded and be upper arch arc plate, thereby be convenient to whole spiral case 1 assembly of processing and fabricating.Go up arch and also make it in the anti-eddy current function of guarantee self, increase the space between snail tongue 101 and impeller 4, be conducive to the reduction of noise simultaneously.
Claims (5)
1. the noise reducing casing assembly of a centrifugal blower, comprise spiral case (1), be arranged on spiral case (1) upper and with the integrated snail tongue of spiral case (1) (101) and diffusion outlet section (102), and be connected to the hush pipe (2) on described diffusion outlet section (102), it is characterized in that: described snail tongue (101) is spirogyrate ear shape snail tongue, on described spiral case (1), be also provided with the anti-vortex board of arc (103), the width of the width of the anti-vortex board of this arc (103) and spiral case (1) adapts, one end of the anti-vortex board of described arc (103) is connected between diffusion outlet section (102) and snail tongue (101), the other end of the anti-vortex board of arc (103) is free end, this free end is near impeller (4) and be positioned at the below of spiral case (1) air-out passage, on the outer side surface of described spiral case (1) and snail tongue (101), be all coated with sound-absorbing material coating (3), described snail tongue (101) is greater than the axial width of spiral case (1) along the axial width of spiral case (1), the length of described hush pipe (2) is 0.4-1.6 rice, and hush pipe (2) inner side is provided with quieter material layer (201).
2. noise reducing casing assembly according to claim 1, is characterized in that: described quieter material layer (201) is aluminum fiber composite sheet.
3. noise reducing casing assembly according to claim 1, is characterized in that: described sound-absorbing material coating (3) is polyurethane coating.
4. want the noise reducing casing assembly described in any one in 1 to 3 according to right, it is characterized in that: described spiral case (1) is one-body molded with the anti-vortex board of arc (103).
5. want the noise reducing casing assembly described in any one in 1 to 3 according to right, it is characterized in that: the anti-vortex board of described arc (103) is upper arch arc plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420469029.XU CN204003618U (en) | 2014-08-20 | 2014-08-20 | The noise reducing casing assembly of centrifugal blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420469029.XU CN204003618U (en) | 2014-08-20 | 2014-08-20 | The noise reducing casing assembly of centrifugal blower |
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| Publication Number | Publication Date |
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| CN204003618U true CN204003618U (en) | 2014-12-10 |
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| CN201420469029.XU Expired - Fee Related CN204003618U (en) | 2014-08-20 | 2014-08-20 | The noise reducing casing assembly of centrifugal blower |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108953228A (en) * | 2018-10-24 | 2018-12-07 | 奥克斯空调股份有限公司 | Blower and air conditioner |
| CN109323436A (en) * | 2018-10-11 | 2019-02-12 | 珠海格力电器股份有限公司 | Flexible structure, flexible structure for air conditioner air duct assembly and air conditioner |
| CN109790851A (en) * | 2016-09-19 | 2019-05-21 | 法雷奥热***公司 | Air inlet shell and corresponding motor vehicles heating, ventilation and/or air-conditioning device |
| CN110439831A (en) * | 2018-05-02 | 2019-11-12 | 现代自动车株式会社 | Flow performance Optimization-type bidirectional blower |
| CN110966245A (en) * | 2019-12-18 | 2020-04-07 | 珠海格力电器股份有限公司 | Pump body structure for reducing hydraulic excitation and centrifugal pump |
| CN111207114A (en) * | 2020-03-13 | 2020-05-29 | 空气动力学国家重点实验室 | Exhaust expander structure for reducing pneumatic noise of fan |
-
2014
- 2014-08-20 CN CN201420469029.XU patent/CN204003618U/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109790851A (en) * | 2016-09-19 | 2019-05-21 | 法雷奥热***公司 | Air inlet shell and corresponding motor vehicles heating, ventilation and/or air-conditioning device |
| CN110439831A (en) * | 2018-05-02 | 2019-11-12 | 现代自动车株式会社 | Flow performance Optimization-type bidirectional blower |
| CN110439831B (en) * | 2018-05-02 | 2022-08-30 | 现代自动车株式会社 | Flow performance optimized bidirectional blower |
| CN109323436A (en) * | 2018-10-11 | 2019-02-12 | 珠海格力电器股份有限公司 | Flexible structure, flexible structure for air conditioner air duct assembly and air conditioner |
| CN108953228A (en) * | 2018-10-24 | 2018-12-07 | 奥克斯空调股份有限公司 | Blower and air conditioner |
| CN108953228B (en) * | 2018-10-24 | 2024-05-10 | 奥克斯空调股份有限公司 | Fan and air conditioner |
| CN110966245A (en) * | 2019-12-18 | 2020-04-07 | 珠海格力电器股份有限公司 | Pump body structure for reducing hydraulic excitation and centrifugal pump |
| CN111207114A (en) * | 2020-03-13 | 2020-05-29 | 空气动力学国家重点实验室 | Exhaust expander structure for reducing pneumatic noise of fan |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20141210 Termination date: 20190820 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |