CN1164619A - DC blasting vane wheel - Google Patents

DC blasting vane wheel Download PDF

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Publication number
CN1164619A
CN1164619A CN97102053A CN97102053A CN1164619A CN 1164619 A CN1164619 A CN 1164619A CN 97102053 A CN97102053 A CN 97102053A CN 97102053 A CN97102053 A CN 97102053A CN 1164619 A CN1164619 A CN 1164619A
Authority
CN
China
Prior art keywords
vane wheel
blade
blasting vane
decided
periodicity
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN97102053A
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Chinese (zh)
Other versions
CN1076448C (en
Inventor
吉桥淳
大茑胜久
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of CN1164619A publication Critical patent/CN1164619A/en
Application granted granted Critical
Publication of CN1076448C publication Critical patent/CN1076448C/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention aims to reduce the noise of specific frequency domain of the rotation sound of a direct current blast impeller. The direct current blast impeller of the invention is provided with a plurality of clapboards 3 which are perpendicular to a rotary shaft, and a plurality of vanes 1 which are configured among the clapboards 3. The installation positions of the vanes 1 are changed periodically according to a specific formula.

Description

DC blasting vane wheel
The present invention relates to DC blasting vane wheel, this impeller can suppress the especially generation of low-frequency band noise of impeller rotation sound.
Existing air conditioner indoor unit 5 as shown in Figure 7, lower portion is being provided with exhaust nozzle 7 in the front of casing 6, and air suction inlet 8 is being set above it, is disposing heat exchanger 9 at these air suction inlet 8 rear sides.To carry out heat exchange by heat exchanger 9 from the air that air suction inlet 8 imports by the DC blasting vane wheel 4 that is configured between casing 6 and the heat exchanger 9, become cold wind or warm braw, be blown into indoor from air nozzle 7 again.
As shown in Figure 8, above-mentioned DC blasting vane wheel has perpendicular to several dividing plates 3 of running shaft with periodic intervals and is installed in several blades 1 between aforementioned barriers.In order to lower the sound that produces when impeller 4 rotates, the fan rotation sound (hereinafter referred to as NZ sound) relevant with blade quantity, once there were many schemes to be suggested, for example: open the Japanese patent gazette spy and promptly once to have disclosed a kind of impeller in clear 60-17296 number, the installation interval aperiodicity of the blade 1 of this impeller is disposing randomly.
Existing blasting vane wheel structure as above-mentioned, Fig. 9 represents that blade installation has the level of noise frequency analysis result of periodic impeller at interval.Figure 10 represents that above-mentioned spy opens the level of noise frequency analysis result of the acyclic impeller in blade installation interval of clear 60-17296 communique announcement.As seen, open shown in the clear 60-17296 communique, can lower the NZ sound, as shown in figure 10, newly produced the following low frequency noise of 600Hz again though blade is installed according to the spy.
Figure 10 is to simulating the result according to the frequency analysis of following formula (2) when disposing blade randomly.
Formula (2)
θ k＝θ k0＋dθ×(rnd(δ)-δ/2)
In the formula, θ k: the arrangement angles of determining the blade installation position
θ k0: the arrangement angles during with impartial arranged spaced
D θ: the blade space angle degree during impartial arranged spaced
Rnd (): random numbers produces function
δ: torsional deformation coefficient
K: the blade that will be configured in the benchmark angle this blade numbering during as O
When the blade 1 of DC blasting vane wheel 4 by stabilizer 10 near the time, because of the variation in pressure trigger noise that blade 1 produces, torsional deformation coefficient δ is big more, corresponding the diminishing of noise coherence between the blade 1, its NZ sound will reduce more.In addition, the fan rotation sound (hereinafter referred to as the N sound) of impeller self generation but generates highlightedly in low-frequency band.
The object of the present invention is to provide a kind ofly can reduce the NZ sound, and suppress the DC blasting vane wheel of low-frequency band (600Hz is following) N sound noise simultaneously.
The DC blasting vane wheel of claim 1 of the present invention, its blade installation position is a starting point with the reference vanes, according to the following formula decision, determines the arrangement angles θ of blade installation position kWith following formula 3 decision, in the formula, the blade of establishing the blade that is configured in the benchmark angle and being 0 o'clock is numbered k, and the arrangement angles variable quantity is α, and periodicity is β.
Formula 3
θ k＝θ k0＋α·dθ·Sin(β·θ0k)
In the formula, θ k: the arrangement angles of determining the blade installation position
θ k0: the arrangement angles during with impartial arranged spaced
α: arrangement angles variable quantity coefficient
D θ: the blade space angle degree when being configured to all uniformly-spaced
β: periodicity
θ 0: benchmark angle between blade
K: the blade numbering of the blade that will be configured in the benchmark angle during as O
The DC blasting vane wheel of claim 2 of the present invention, its periodicity β is decided to be the natural number more than 2.
The DC blasting vane wheel of claim 3 of the present invention, its periodicity β is decided to be the natural number more than 2 and is even number.
The DC blasting vane wheel of claim 4 of the present invention, its arrangement angles variable quantity α is decided to be the rational of 0＜α＜1 scope.
The DC blasting vane wheel of claim 5 of the present invention forms the blade screw angle.
The DC blasting vane wheel of claim 6 of the present invention is provided with helix angle and periodicity β is decided to be natural number more than 2.
The DC blasting vane wheel of claim 7 of the present invention is provided with helix angle and periodicity β is decided to be the natural number more than 2 and is even number.
The DC blasting vane wheel of claim 8 of the present invention is provided with helix angle and arrangement angles variable quantity α is decided to be the rational of 0＜α＜1 scope.
Fig. 1 is the sectional view of the expression embodiment of the invention 1 DC blasting vane wheel.
Fig. 2 is the air conditioner sectional view that expression is assembled with the DC blasting vane wheel of the embodiment of the invention 1.
Fig. 3 is the leaf position and the sinusoidal curve comparative illustration figure of the embodiment of the invention 1.
Fig. 4 is the level of noise frequency analysis result's of the expression embodiment of the invention 1 DC blasting vane wheel a performance plot.
Fig. 5 is the explanatory drawing of the helix angle of the expression embodiment of the invention 5 DC blasting vane wheels.
Fig. 6 is the DC blasting vane wheel level of noise frequency analysis result's who is provided with helix angle of the expression embodiment of the invention 5 a performance plot.
Fig. 7 represents the indoor set of existing air conditioner.
Fig. 8 represents existing DC blasting vane wheel.
Fig. 9 is the level of noise frequency analysis fruiting characteristic figure that the existing blade installation of expression has periodically variable DC blasting vane wheel at interval.
Figure 10 is the level of noise frequency analysis result's of the existing DC blasting vane wheel of expression a performance plot.
Below, with reference to the description of drawings embodiments of the invention.
Embodiment 1
Fig. 1 represents embodiments of the invention 1.Among Fig. 1,1 expression blade, 2 expression reference vanes, 3 expression dividing plates, θ represents to determine the arrangement angles of blade installation position, the impeller that 4 expressions are made up of blade 1, reference vanes 2 and dividing plate 3.The blade installation position is determined by the position angle formula shown in the formula 4.
Formula 4
θ k＝θ k0＋α·dθ·Sin(β·θ0k)
In the formula, θ k: the arrangement angles of determining the blade installation position
θ k0: the arrangement angles during with impartial arranged spaced
α: arrangement angles variable quantity coefficient
D θ: the blade space angle degree when being configured to all uniformly-spaced
β: periodicity
θ 0: configuration baseline angle between blade
K: the blade numbering of the blade that will be configured in the benchmark angle during as O
In present embodiment 1, arrangement angles variable quantity factor alpha=0.2, periodicity β=2, blade space angle degree d θ=2 л/35 during impartial arranged spaced, during the arrangement angles θ 0k=2 л when being configured to all uniformly-spaced * k/35, obtain the arrangement angles of determining this blade installation position.
Fig. 2 has represented to assemble the air conditioner of the embodiment of the invention 1 impeller 4.The indoor set of 5 expression air conditioners, 6 expression casings, 7 expression air ejiction openings, 8 expression air suction inlets, 9 expression heat exchangers, 10 expression stabilizers.Explanatory drawing when Fig. 3 represents the position of blade 1 of the embodiment of the invention 1 and sinusoidal curve contrast.
DC blasting vane wheel in the embodiment of the invention 1, owing to change the mounting point of blade 1 periodically, so, as shown in Figure 4, the NZ sound is modulated, peak value is disperseed, thereby lowered noise, and, owing to kept the coherence of 1 in blade, so the N sound that produces of blade self also is suppressed separately.
Embodiment 2
The DC blasting vane wheel of the embodiment of the invention 2 is in the foregoing description 1, and periodicity β is decided to be natural number more than 2.Its result, modulating action increases, and can fully obtain periodic effects.
Embodiment 3
The DC blasting vane wheel of the embodiment of the invention 3 is in the foregoing description 1, and periodicity β is decided to be the natural number more than 2 and is decided to be even number.Its result also can obtain simultaneously mechanical balance.
Embodiment 4
The DC blasting vane wheel of the embodiment of the invention 4 is in the foregoing description 1, arrangement angles variable quantity factor alpha is decided to be the rational of 0＜α＜1 scope.Like this, blade neither can become equalization at interval, also can be not overlapping between the adjacent vanes.
Embodiment 5
As shown in Figure 5, additional helixangle ' can lower the NZ sound is a known technology.The DC blasting vane wheel of the embodiment of the invention 5 is that this known technology is used for embodiment 1.Like this, can lower the NZ sound more.
Embodiment 6
The DC blasting vane wheel of the embodiment of the invention 6 is in the foregoing description 5, and periodicity β is decided to be natural number more than 2.Its result, modulating action increases, and can fully obtain periodic effects.
Embodiment 7
The DC blasting vane wheel of the embodiment of the invention 7 is in the foregoing description 5, and periodicity β is decided to be the natural number more than 2 and is decided to be even number.Its result has also obtained mechanical balance simultaneously.
Embodiment 8
The DC blasting vane wheel of the embodiment of the invention 8 is in the foregoing description 5, arrangement angles variable quantity factor alpha is decided to be the rational of 0＜α＜1 scope.Like this, blade can not become equalization at interval, and adjacent vanes can be not overlapping yet.
The DC blasting vane wheel of claim 1 of the present invention has perpendicular to several dividing plates of rotating shaft and is configured in several blades between the dividing plate, because the installation site of blade is by arranged spaced shown in the formula 5
Formula 5
   θ k＝θ k0＋α·dθ·Sin(β·θ0·k)
In the formula, θk: the arrangement angles of determining the blades installation position
     θ k0: the arrangement angles during with impartial arranged spaced
α: arrangement angles variable quantity coefficient
D θ: the blade space angle degree when being configured to all uniformly-spaced
β: periodicity
θ 0: configuration baseline angle between blade
K: the blade numbering of the blade that will be configured in the benchmark angle during as O
Make the blades installation position do to change periodically, so, the NZ sound is played modulating action, thereby Peak value is disperseed, noise reducing, simultaneously, owing to kept interlobate correlation, so blade The N sound that self produces is also suppressed.
The DC blasting vane wheel of claim 2 of the present invention is owing to be decided to be periodicity β more than 2 Natural number, so, sufficient periodic effects can be obtained.
The blasting vane wheel of the generation of claim 3 of the present invention is owing to be decided to be periodicity β more than 2 Natural number and be decided to be even number, so, can also obtain the mechanical balance of blasting vane wheel.
The DC blasting vane wheel of claim 4 of the present invention, because of α=0 o'clock, Cheng Jun leaf uniformly-spaced Sheet can not reduce the NZ sound, in addition, α=1 o'clock, adjacent blades can be overlapping, so, with α The rational that is decided to be 0＜α＜1 scope, like this, spacing with blades can be unimpartial, and adjacent blades is also Can be not overlapping.
The blasting vane wheel of claim 5 of the present invention is owing to be to be provided with the DC blasting leaf of helical angle Add the structure of claim 1 in the wheel, so, as shown in Figure 8, suppressed further only to use The peak value sound that helical angle structure shown in Figure 5 can not suppress fully.
The DC blasting vane wheel of claim 6 of the present invention is owing to be provided with helical angle and with periodicity β Be decided to be the natural number more than 2, so, periodically produce an effect can fully be obtained.
The DC blasting vane wheel of claim 7 of the present invention is owing to be provided with helical angle and with periodicity β Be decided to be the natural number more than 2 and be even number, so the machinery that can obtain DC blasting vane wheel is flat Weighing apparatus.
The DC blasting vane wheel of claim 8 of the present invention is owing to be provided with helical angle and with arrangement angles The α of variable quantity system is decided to be the rational of 0＜α＜1 scope, so it is equal that spacing with blades can not be Deng, adjacent blades can be not overlapping yet.

Claims (8)

1. DC blasting vane wheel has perpendicular to several dividing plates of running shaft and is configured in several blades between this dividing plate, it is characterized in that arranged spaced shown in the following formula 1 is pressed in the mounting point of blade
Formula 1
θ k＝θ k0＋α·dθ·Sin(β·θ0) k
In the formula, θ k: the arrangement angles of determining the blade installation position
θ k0: the arrangement angles during with impartial arranged spaced
α: arrangement angles variable quantity coefficient
D θ: the blade space angle degree when being configured to all uniformly-spaced
β: periodicity
θ 0: configuration baseline angle between blade
K: the blade numbering of the blade that will be configured in the benchmark angle during as O
2. DC blasting vane wheel as claimed in claim 1 is characterized in that, periodicity β is decided to be natural number more than 2.
3. DC blasting vane wheel as claimed in claim 1 is characterized in that, periodicity β is decided to be the natural number more than 2 and is even number.
4. DC blasting vane wheel as claimed in claim 1 is characterized in that, arrangement angles variable quantity factor alpha is decided to be the rational of 0＜α＜1 scope.
5. DC blasting vane wheel as claimed in claim 1 is characterized in that, is formed with helix angle.
6. DC blasting vane wheel as claimed in claim 5 is characterized in that, periodicity β is decided to be natural number more than 2.
7. DC blasting vane wheel as claimed in claim 5 is characterized in that, periodicity β is decided to be the natural number more than 2 and is even number.
8. DC blasting vane wheel as claimed in claim 5 is characterized in that, arrangement angles variable quantity factor alpha is decided to be the rational of 0＜α＜1 scope.
CN97102053A 1996-01-18 1997-01-15 DC blasting vane wheel Expired - Lifetime CN1076448C (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP6447/1996 1996-01-18
JP00644796A JP3484854B2 (en) 1996-01-18 1996-01-18 Once-through fan
JP6447/96 1996-01-18

Publications (2)

Publication Number Publication Date
CN1164619A true CN1164619A (en) 1997-11-12
CN1076448C CN1076448C (en) 2001-12-19

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ID=11638682

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Application Number Title Priority Date Filing Date
CN97102053A Expired - Lifetime CN1076448C (en) 1996-01-18 1997-01-15 DC blasting vane wheel

Country Status (8)

Country Link
EP (1) EP0785362B1 (en)
JP (1) JP3484854B2 (en)
KR (1) KR100216104B1 (en)
CN (1) CN1076448C (en)
AU (1) AU680173B1 (en)
DE (1) DE69625322T2 (en)
ES (1) ES2191080T3 (en)
HK (1) HK1000496A1 (en)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100501170C (en) * 2006-09-11 2009-06-17 广东科龙电器股份有限公司 Through-flow fan impeller
CN104132004A (en) * 2014-08-04 2014-11-05 绿田机械股份有限公司 Cooling fan used for diesel engine
CN104153905A (en) * 2014-08-04 2014-11-19 绿田机械股份有限公司 Air-cooled inclined type diesel engine
CN104422029A (en) * 2013-09-06 2015-03-18 日立空调·家用电器株式会社 Air conditioner indoor unit and air conditioner using the indoor unit
CN105849416A (en) * 2013-12-27 2016-08-10 大金工业株式会社 Multi-blade fan
CN106837859A (en) * 2017-02-13 2017-06-13 美的集团股份有限公司 Draught fan impeller and centrifugal blower
CN108916078A (en) * 2018-07-16 2018-11-30 大连碧蓝节能环保科技有限公司 Helical blade centrifugal blower

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TW377393B (en) * 1998-03-30 1999-12-21 Sanyo Electric Co Air coondition
KR100315518B1 (en) * 1999-09-10 2001-11-30 윤종용 Crossflow fan for an air conditioner
JP4075264B2 (en) * 2000-01-28 2008-04-16 セイコーエプソン株式会社 Axial fan, centrifugal fan, and electronic equipment using them
WO2004029463A1 (en) * 2002-09-24 2004-04-08 Toshiba Carrier Corporation Cross flow fan and air conditioner with the fan
US8881396B2 (en) 2011-02-07 2014-11-11 Revcor, Inc. Method of manufacturing a fan assembly
EP2696078B1 (en) * 2012-08-09 2019-10-02 MTU Aero Engines AG Bladed rotor for a turbomachine and corresponding assembly method
US9995316B2 (en) 2014-03-11 2018-06-12 Revcor, Inc. Blower assembly and method
CN105020176A (en) * 2015-08-20 2015-11-04 珠海格力电器股份有限公司 Fan blade and centrifugal ventilator
CN110206753B (en) * 2018-06-29 2024-07-09 华帝股份有限公司 Centrifugal wind wheel for range hood
US11274677B2 (en) 2018-10-25 2022-03-15 Revcor, Inc. Blower assembly

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DE2322734A1 (en) * 1973-05-05 1974-11-21 Buderus Eisenwerk FAN
JPS6017296A (en) * 1983-07-08 1985-01-29 Matsushita Electric Ind Co Ltd Vane wheel of crossing current blower
JP3349722B2 (en) * 1992-08-25 2002-11-25 東芝キヤリア株式会社 Indoor unit of air conditioner and packing method thereof
US5266007A (en) * 1993-03-01 1993-11-30 Carrier Corporation Impeller for transverse fan
KR970009834B1 (en) * 1994-02-08 1997-06-18 엘지전자 주식회사 Impeller of cross fan
DE4421604C1 (en) * 1994-06-21 1995-04-13 Siemens Ag Side-passage compressor
JPH0890397A (en) * 1994-09-21 1996-04-09 Kawasaki Steel Corp Grinding structure for detecting minute defect in steel plate

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100501170C (en) * 2006-09-11 2009-06-17 广东科龙电器股份有限公司 Through-flow fan impeller
CN104422029A (en) * 2013-09-06 2015-03-18 日立空调·家用电器株式会社 Air conditioner indoor unit and air conditioner using the indoor unit
CN105849416A (en) * 2013-12-27 2016-08-10 大金工业株式会社 Multi-blade fan
CN105849416B (en) * 2013-12-27 2017-05-10 大金工业株式会社 Multi-blade fan
CN104132004A (en) * 2014-08-04 2014-11-05 绿田机械股份有限公司 Cooling fan used for diesel engine
CN104153905A (en) * 2014-08-04 2014-11-19 绿田机械股份有限公司 Air-cooled inclined type diesel engine
CN104153905B (en) * 2014-08-04 2016-08-17 绿田机械股份有限公司 A kind of air-cooled inclined type diesel engine
CN106837859A (en) * 2017-02-13 2017-06-13 美的集团股份有限公司 Draught fan impeller and centrifugal blower
CN108916078A (en) * 2018-07-16 2018-11-30 大连碧蓝节能环保科技有限公司 Helical blade centrifugal blower

Also Published As

Publication number Publication date
KR970059509A (en) 1997-08-12
HK1000496A1 (en) 2003-04-25
KR100216104B1 (en) 1999-08-16
EP0785362B1 (en) 2002-12-11
JPH09195979A (en) 1997-07-29
ES2191080T3 (en) 2003-09-01
EP0785362A1 (en) 1997-07-23
JP3484854B2 (en) 2004-01-06
DE69625322T2 (en) 2003-10-16
DE69625322D1 (en) 2003-01-23
CN1076448C (en) 2001-12-19
AU680173B1 (en) 1997-07-17

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