CN1061133C - A cross flow fan impeller - Google Patents
A cross flow fan impeller Download PDFInfo
- Publication number
- CN1061133C CN1061133C CN94117934A CN94117934A CN1061133C CN 1061133 C CN1061133 C CN 1061133C CN 94117934 A CN94117934 A CN 94117934A CN 94117934 A CN94117934 A CN 94117934A CN 1061133 C CN1061133 C CN 1061133C
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- CN
- China
- Prior art keywords
- impeller
- air
- angle
- cross
- blade
- 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.)
- Expired - Fee Related
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Classifications
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- 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
Abstract
A crossflow fan impeller is acquired by setting an inner and outer diameter ratio Di/Do within 0.75-0.80, a Beta angle within 17dgrees-27 dgrees and a blade distance and a string length ratio T/L within 0.60-0.70, which is capable of significantly reducing 3 db of the unexpected heard noise and is in favor of forming a big air flow. The crossflow fan impeller of the utility model comprises a front grid, a radiator, a crossflow fan device, a balancer and a back guide device.
Description
The present invention relates generally to a kind of cross-flow fan, particularly relate to a kind of can reduce significantly by the optimal design characteristic of foundation laboratory data betide wherein do not wish audible noise that occurs and the cross-flow fan that forms a large amount of air streams.
Usually, the traditional separated type air regulator shown in Fig. 1 to 3 comprises a cross-flow fan 10, and it has a preceding grid 1 that has a plurality of air suction inlets 2 on it.Below preceding grid 1, be provided with a radiator 3.The cylindrical return ventilation machine impeller 4 that is arranged on radiator 3 belows comprises a supporting blades framework 7, and this supporting blades framework has a plurality of blades 15 that centrally are fixed on this framework circumferential surface.A pre-position of grid 1 inside before balace weight 5 is arranged on regularly is so that prevent air adverse current herein.The back guiding device 6 that the top is connected with an end of preceding grid is arranged on the rear of fan impeller, is used to guide the moving air that comes out from cross-flow fan impeller 4.
Explain the operation of above-mentioned traditional cross-flow fan now.
When cross-flow fan 10 runnings, the air regulator air outside sucks by the air suction inlet of preceding grid 1.Inhaled air is in the heating of radiator 3 places and flow to impeller 4.Thus, at impeller 4 places, air obtains mobilization force and is guiding the outside that flows to air regulator by back guiding device 6, produces not wish the audible noise that occurs.
Usually, pay very big effort and come shape by adjusting back guiding device 6 and balace weight 5 and mounting point etc. to reduce not wish the audible noise that occurs.But, owing to do not wish that the level of the audible noise that occurs is proportional with air mass flow and static pressure thereof, so that when producing big air mass flow, do not wish that the increase of the audible noise that occurs is directly proportional with the increase of the revolution of impeller 4 at the revolution of increase impeller 4.
Therefore, one object of the present invention is to provide a kind of improved cross-flow fan.
Another object of the present invention is to provide a kind of can reduce the cross-flow fan that betides noise wherein significantly.
A further object of the present invention is to provide a kind of can being beneficial to reach the cross-flow fan that produces the required air mass flow of air regulator with greater efficiency.
To achieve these goals, cross-flow fan according to the present invention comprises a preceding grid, and it is arranged on the top of air conditioner main body, has the opening of a plurality of suction air on it; A radiator that is arranged on preceding grid below; An impeller, it is arranged on the below of radiator and has a supporting blades framework, is provided with a plurality of blades on the circumferential surface of this framework; A balace weight on the predetermined part of grid internal surface, is used to prevent air inversion before it is arranged on; And guiding device after, its top is connected with an end of preceding grid, be used to guide the air that flows through the cross-flow fan impeller, wherein, the inside/outside of described impeller footpath ratio is in 0.75～0.78 the scope, between 21 °～27 °, and the blde pitch of its blade-chord length ratio is in 0.60～0.70 scope in the angle that forms between the tangent line of the tangent to periphery of the position fan impeller on the fan impeller circumference and blade.
Can be easier to understand purpose of the present invention and feature with reference to following detailed description and accompanying drawing to one embodiment of the present of invention, among the figure:
Fig. 1 is the viewgraph of cross-section of the cross-flow fan of the traditional separated type air regulator of expression;
Fig. 2 A is the plan view of expression impeller shown in Figure 1;
Fig. 2 B is the side view of expression impeller shown in Figure 1;
Fig. 3 A is the detail drawing of the blade of expression impeller;
Fig. 3 B is the enlarged view of the blade of expression impeller;
Fig. 4 A is the viewgraph of cross-section of expression cross-flow fan impeller, shows the bigger inside/outside footpath ratio of fan impeller.
Fig. 4 B is the viewgraph of cross-section of expression cross-flow fan impeller, shows the less inside/outside footpath ratio of fan impeller;
Fig. 5 A to 5C represents performance plot based on laboratory data according to the different inside/outside footpath ratio of impeller;
Fig. 6 A to 6C is according at the angle β that a bit forms between tangent line of the tangent to periphery of the impeller at place and blade 15 on the circumference of fan impeller 4
0Expression is based on the performance plot of laboratory data; And
Fig. 7 is the performance plot of the different blde pitches-chord length ratio of expression impeller.
Please referring to Fig. 3 to 4, explanation is according to improved cross-flow fan of the present invention now.
At first, eliminating is to the explanation of the structure identical with above-mentioned conventional construction of cross-flow fan.
According to one embodiment of present invention, disclose one group of laboratory data that is shown in the table 1, described laboratory data is the shape by change fan impeller 4, but keeps the shape of back guiding device 6 and balace weight 5 to obtain.
Table 1
| | | | ||
| Under the identical condition of flowage structure | Flow strength | 13．8CMM | 11．9CMM | 9．29CMM |
| Static pressure | 5．0mmAg | 3．9mmAg | 2．6mmAg |
* rpm (RPM): 1000
Under the identical situation of flowage structure, static pressure is shown in Table 1 significantly with respect to the change of the shape of fan impeller 4.
Therefore, according to one embodiment of present invention,, can realize lower noise occurred level and bigger air mass flow with a method by changing the shape of fan impeller.
At first, according at the angle β that a bit forms between tangent line of the tangent to periphery of the fan impeller at place and ventilating vane 15 on the circumference of fan impeller 4
0, the flow velocity of air changes significantly in the apical margin part of blade 15.
In addition, the inside/outside footpath ratio Di/Do that depends on impeller 4 as the length L of each ventilating vane 15 of a principal element that changes air mass flow.In addition, equally also the curvature of the ventilating vane 15 of another principal element of conduct change air mass flow changes according to the inside/outside footpath ratio Di/Do of impeller 4, can make the pressure change of moving air like this.
Therefore, at the air-flow character at impeller 4 places inside/outside footpath ratio Di/Do and angle beta according to impeller 4
0And change described angle β
0Be formed between the tangent line of circumference of impeller tangent line of a bit locating on the circumference of impeller 4 and blade 15.
In addition, the chord length L of (or blde pitch) T of the distance between the blade and interior bent blades also is the principal element that changes the air mass flow in the cross-flow fan 10 of air regulator, that is to say that air mass flow depends on the ratio T/L of blde pitch and chord length.
Therefore, air mass flow and undesirable noise are according to above-mentioned factors vary.
Following table is represented angle β
0, angle B
iAnd the relation between the ratio T/L of blde pitch that changes according to inside/outside footpath ratio Di/Do and chord length, wherein angle β
iBe formed on the inner circumference of impeller 4 internal diameters a bit between tangent line of the tangent to periphery of the impeller 4 at place and blade 15.
| Impeller | Angle β 0 | Inside/outside footpath ratio Di/D 0 | The chord length of blade | T／L |
| 17° | 0．77 | 14．24 | 0．630 | |
| 2 | 19° | 0．77 | 14．07 | 0．638 |
| 3 | 21° | 0．77 | 13．90 | 0．646 |
| 4 | 21° | 0．75 | 15．10 | 0．595 |
| 5 | 21° | 0．80 | 12．10 | 0．742 |
| 6 | 23° | 0．77 | 13．74 | 0．654 |
| 7 | 25° | 0．77 | 13．59 | 0．661 |
* angle β
0Be set at 90 °
According to above-mentioned laboratory data, for reducing undesirable audible noise level effectively and being beneficial to for the bigger air mass flow of generation angle β
0Optimum value should be 21 °, and the optimum value of inside/outside footpath ratio Di/Do should be 0.77.
Please referring to Fig. 5 to 7, ratio Di/Do is 0.77 in the inside/outside footpath, angle β
0The rpm (RPM) that is 21 ° and impeller 4 is the description of carrying out under 800～1200 the condition based on laboratory data to these figure.
Fig. 5 A is illustrated in angle β
0Be made as 21 °, rpm (RPM) was made as 800 o'clock, static pressure, air mass flow, the characteristic that noise level changes with inside/outside footpath ratio Di/Do.As shown in the figure, when the inside/outside footpath of impeller 4 ratio Di/Do is 0.77, can obtain optimum.
Fig. 5 B is illustrated in angle β
0Be made as 21 °, rpm (RPM) was made as 1000 o'clock, static pressure, the characteristic that air mass flow and noise level change with inside/outside footpath ratio Di/Do.As shown in the figure, when the inside/outside of impeller footpath ratio Di/Do was 0.77, it is identical that air mass flow and Di/Do equal 0.75 o'clock situation, but noise level is relative with static pressure higher.In this case, noise level generally speaking is low.
Fig. 5 C represents static pressure, air mass flow, the characteristic that noise level changes with inside/outside footpath ratio Di/Do.As shown in the figure, when inside/outside footpath ratio Di/Do was 0.77, air mass flow and noise level and air mass flow were to compare relative higher at 0.75 o'clock.In this case, noise level generally speaking is low.
Therefore, the optimum value of inside/outside footpath ratio Di/Do is 0.77.
Fig. 6 A is illustrated in inside/outside footpath ratio Di/Do is made as 0.77, and RPM was made as 800 o'clock, static pressure, and air mass flow and noise level are with the angle β of blade
0The characteristic that changes.As shown in the figure, as angle β
0When being positioned at 17 ° to 21 ° scope, the variation of noise level and air mass flow and static pressure thereof are proportional, still, and as angle β
0During greater than 21 °, noise level significantly increases, and air mass flow and static pressure obviously reduce.
Fig. 6 B is illustrated in inside/outside footpath ratio Di/Do is made as 0.77, and RPM is made as 1000 o'clock static pressures, air mass flow, and noise level is with the angle β of blade
0The characteristic that changes.As shown in the figure, as angle β
0When being positioned at 17 ° to 23 ° scope, noise level is with angle β
0Increase and reduce, still, as angle β
0When surpassing 23 °, air mass flow and static pressure step-down, on the contrary, noise level obviously uprises.
Fig. 6 C is illustrated in inside/outside footpath ratio Di/Do is made as 0.77, and RPM was made as 1200 o'clock, static pressure, and air mass flow, noise level is with the angle β of blade
0The characteristic that changes.As shown in the figure, as angle β
0When being positioned at 17 ° to 21 ° scope, the change of noise level and air mass flow and static pressure are proportional, still, and as angle β
0When surpassing 21 °, air mass flow reduces, and on the contrary, noise level is higher relatively.
Therefore, no matter the revolution size of impeller, at angle β
0Can obtain lower noise level during for about 21 °, and shown high air mass flow and required static pressure.
In inside/outside footpath ratio Di/Do is in 0.75～0.80 scope, angle β
0When being in 17 °～27 ° the scope, obtain the optimal design characteristic of impeller.
Simultaneously, because interlobate apart from inside/outside footpath ratio Di/Do and the number of blade variation of T according to impeller, and the chord length L of interior bent blades is according to the inside/outside footpath ratio Di/Do of impeller and the angle β of blade
0Change, therefore can know, the optimal design demand of cross-flow fan depends on the inside/outside footpath ratio Di/Do of impeller, the angle β of blade
0Ratio T/L with blde pitch and chord length.
When Fig. 7 is illustrated in outer diameter D o with impeller and is made as 100mm, static pressure, air mass flow, noise level is with the characteristic of the blde pitch-chord length rate of change of blade.As shown in the figure, the best blde pitch-chord length rate value of blade is in 0.60～0.70 scope.
Therefore, according to the present invention, be in 0.75～0.80 the scope angle β by making inside/outside footpath ratio Di/Do
0Be in 17 °～27 ° the scope, and the ratio T/L of blde pitch-chord length is in 0.60～0.70 the scope, can obtain best cross-flow fan impeller, it can be significantly reduces the noise of undesirable audible 3db and is beneficial to and produces big air mass flow.
Claims (1)
1. cross-flow fan comprises:
A preceding grid, it is arranged on the top of air conditioner main body, has the opening of a plurality of suction air on it;
A radiator that is arranged on preceding grid below;
An impeller, it is arranged on the below of radiator and has a supporting blades framework, is provided with a plurality of blades on the circumferential surface of this framework;
A balace weight on the predetermined part of grid internal surface, is used to prevent air inversion before it is arranged on; And
Guiding device after one, its top is connected with an end of preceding grid, is used to guide the air that flows through cross-flow fan, it is characterized in that,
The inside/outside of described impeller footpath ratio is in 0.75～0.78 the scope, between 21 °～27 °, and the blde pitch of its blade-chord length ratio is in 0.60～0.70 scope in the angle that forms between the tangent line of the tangent to periphery of the position fan impeller on the fan impeller circumference and blade.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR23968/93 | 1993-11-11 | ||
| KR23968/1993 | 1993-11-11 | ||
| KR1019930023968A KR950014611A (en) | 1993-11-11 | 1993-11-11 | High wind flow pendulum |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1106897A CN1106897A (en) | 1995-08-16 |
| CN1061133C true CN1061133C (en) | 2001-01-24 |
Family
ID=19367875
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN94117934A Expired - Fee Related CN1061133C (en) | 1993-11-11 | 1994-11-11 | A cross flow fan impeller |
Country Status (2)
| Country | Link |
|---|---|
| KR (1) | KR950014611A (en) |
| CN (1) | CN1061133C (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4549416B2 (en) * | 2008-10-22 | 2010-09-22 | シャープ株式会社 | Cross-flow fan, blower and impeller molding machine |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2942773A (en) * | 1953-07-17 | 1960-06-28 | Paul Pollrich & Comp | Fans |
| US3223313A (en) * | 1964-02-04 | 1965-12-14 | Lau Blower Co | Air moving device |
| JPS52150806A (en) * | 1976-06-09 | 1977-12-14 | Matsushita Electric Ind Co Ltd | Motor fan |
| EP0021435A1 (en) * | 1979-06-27 | 1981-01-07 | Black & Decker Inc. | Air-powered motor and a rotor therefor |
| US4472409A (en) * | 1981-11-05 | 1984-09-18 | Byk Gulden Lomberg Chemische Fabrik Gesellschaft Mit Beschrankter Haftung | 2-Pyridylmethyl thio(sulfinyl)benzimidazoles with gastric acid secretion inhibiting effects |
| CN1041204A (en) * | 1988-06-17 | 1990-04-11 | 松下电器产业株式会社 | The impeller of multiblade blower |
| CN2123632U (en) * | 1992-02-13 | 1992-12-02 | 湘潭华盛空调环保工程有限公司 | Ternary centrifugal double wind square housing air machine for air conditioner |
-
1993
- 1993-11-11 KR KR1019930023968A patent/KR950014611A/en not_active Application Discontinuation
-
1994
- 1994-11-11 CN CN94117934A patent/CN1061133C/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2942773A (en) * | 1953-07-17 | 1960-06-28 | Paul Pollrich & Comp | Fans |
| US3223313A (en) * | 1964-02-04 | 1965-12-14 | Lau Blower Co | Air moving device |
| JPS52150806A (en) * | 1976-06-09 | 1977-12-14 | Matsushita Electric Ind Co Ltd | Motor fan |
| EP0021435A1 (en) * | 1979-06-27 | 1981-01-07 | Black & Decker Inc. | Air-powered motor and a rotor therefor |
| US4472409A (en) * | 1981-11-05 | 1984-09-18 | Byk Gulden Lomberg Chemische Fabrik Gesellschaft Mit Beschrankter Haftung | 2-Pyridylmethyl thio(sulfinyl)benzimidazoles with gastric acid secretion inhibiting effects |
| CN1041204A (en) * | 1988-06-17 | 1990-04-11 | 松下电器产业株式会社 | The impeller of multiblade blower |
| CN2123632U (en) * | 1992-02-13 | 1992-12-02 | 湘潭华盛空调环保工程有限公司 | Ternary centrifugal double wind square housing air machine for air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1106897A (en) | 1995-08-16 |
| KR950014611A (en) | 1995-06-16 |
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| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |