CN105090105A - Centrifugal fan and impeller thereof - Google Patents
Centrifugal fan and impeller thereof Download PDFInfo
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- CN105090105A CN105090105A CN201510373325.9A CN201510373325A CN105090105A CN 105090105 A CN105090105 A CN 105090105A CN 201510373325 A CN201510373325 A CN 201510373325A CN 105090105 A CN105090105 A CN 105090105A
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- impeller
- wheel disc
- boss
- back side
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Abstract
The invention discloses a centrifugal fan and an impeller of the centrifugal fan. The impeller comprises an impeller disc, and the impeller disc is provided with a front face facing the air inlet direction and a back face opposite to the front face. A reinforcing portion is arranged on the back face of the impeller disc so that deformation in rotation of the impeller is reduced, and when the impeller is designed, no large impeller top gaps need to be left; and air leakage caused by the too large impeller top gaps is avoided, and on the premise that safety is ensured, the efficiency of the impeller is improved.
Description
Technical field
The present invention relates to fluid machinery technical field, particularly a kind of centrifugal blower and impeller thereof.
Background technique
Centrifugal blower is converted to the principle of potential energy according to kinetic energy, utilizes the impeller of High Rotation Speed to be accelerated by gas, then slows down, changes the flow direction, make kinetic energy be converted to pressure potential, and the body thus the pressure improving gas is supplied gas side by side, it is a kind of driven fluid machinery.Centrifugal blower is widely used in factory, mine, tunnel, cooling tower, vehicle, the ventilation of boats and ships and building, dust discharge and cooling; The ventilation of boiler and industrial furnace and air inducing; Cooling in the apparatus of air conditioning and domestic electric appliance and ventilation; The oven dry of cereal and selecting and recommending; The inflation of wind-tunnel wind regime and Hovercraft and propelling etc.
As shown in Figure 1, Fig. 1 is the sectional view of centrifugal blower in prior art to a kind of typical centrifugal blower.Centrifugal blower is primarily of compositions such as impeller 1 ＇, shape ring 2 ＇, main shaft 3 ＇, bearing transmission mechanism and motors, and wherein, impeller is the monolithic construction be made up of blade 11 ＇ and wheel disc 12 ＇, and impeller 1 ＇ is installed on main shaft 3 ＇ by center hole.During centrifugal blower work, gas is from axially entering impeller 1 ＇, and when flowing through impeller 1 ＇, under the effect of blade 11 ＇, direction is by axially changing into radial direction, and gas pressure raises and discharges.Wherein, air-flow path is formed by shape ring 2 ＇ and blade 11 ＇ top.
Usually, leave blade tip clearance A ＇ between blade 11 ＇ and shape ring 2 ＇, its size has material impact to the efficiency of centrifugal blower and reliability.When this blade tip clearance A ＇ is too small, easily collides between blade 11 ＇ and shape ring 2 ＇ and cause security incident, when blade tip clearance A ＇ is excessive, may Leakage Gas be caused, and reduce the efficiency of blade.
During existing centrifugal blower design blade tip clearance, usually rule of thumb using the value of the 0.3--0.5% of impeller diameter as blade tip clearance, and do not adopt other any measure, this design method can be avoided colliding between blade 11 ＇ and shape ring 2 ＇, but, the blade tip clearance that this design method obtains is comparatively large, easily causes Leakage Gas and reduces the efficiency of impeller.
In view of the defect that above-mentioned impeller exists, urgently provide a kind of impeller that efficiency is higher under the prerequisite of guarantee Security.
Summary of the invention
For solving the problems of the technologies described above, object of the present invention is for providing a kind of centrifugal blower and impeller thereof.This impeller arranges reinforcing part at the wheel disc back side, improve the rigidity of impeller, due to the distortion that centrifugal motion causes during reduction vane rotary, thus do not need to reserve larger blade tip clearance when making this Impeller Design, under the prerequisite ensureing Security, improve the efficiency of impeller.
For realizing object of the present invention, the invention provides a kind of impeller, comprising wheel disc, described wheel disc has towards the front of airintake direction and the back side on the other side; The back side of described wheel disc is provided with reinforcing part.
Alternatively, the described wheel disc back side is provided with boss, and described boss is described reinforcing part.
Alternatively, described wheel disc has wheel disc center line, and described boss is annular, and its center line is described wheel disc center line.
Alternatively, the diameter of described boss is the half of described wheel diameter, and the height of described boss is the 3%-4% of described wheel diameter, and the thickness of described boss is the 2%-4% of described wheel diameter.
In existing centrifugal blower, affect the Security of impeller for avoiding blade and shape ring to collide, usually using the value of the 0.3--0.5% of impeller diameter as blade tip clearance, and the blade tip clearance value that this design method obtains is usually larger, easily cause gas leakage, and reduce the efficiency of impeller.In the present invention, by arranging reinforcing part at the wheel disc back side, improve the rigidity of impeller, distortion during vane rotary is reduced, and therefore, the blade tip clearance reserved required in Impeller Design process reduces, effectively avoid and that cause air loss excessive due to blade tip clearance, thus improve the efficiency of impeller.
In order to realize object of the present invention, the present invention also provides a kind of centrifugal blower, and comprise housing and be positioned at the impeller of its inside, shape ring and main shaft, described impeller is installed on described main shaft, described shape ring is fixed on described housing, and described shape ring and described impeller form air-flow path; Described impeller is above-described impeller.
Accompanying drawing explanation
Fig. 1 is the structural representation of centrifugal blower in prior art;
Fig. 2 is the sectional view of a kind of embodiment of impeller provided by the present invention.
In Fig. 1:
Impeller 1 ＇, blade 11 ＇, wheel disc 12 ＇, shape ring 2 ＇, main shaft 3 ＇;
Blade tip clearance A ＇
In Fig. 2:
Wheel disc 1, mounting hole 11, boss 2;
Wheel disc center line X.
Embodiment
In order to solve the problems of the technologies described above, first core of the present invention is for providing a kind of impeller, this impeller arranges reinforcing part at the wheel disc back side, improve the rigidity of impeller, the distortion caused due to centrifugal motion when reducing vane rotary, thus do not need to reserve larger blade tip clearance when making this Impeller Design, improve the efficiency of impeller.Another core of the present invention is for providing a kind of centrifugal blower comprising this impeller.
In order to make those skilled in the art understand technological scheme of the present invention better, below in conjunction with the drawings and specific embodiments, the present invention is described in further detail.
In a kind of embodiment, the invention provides a kind of impeller, comprise wheel disc 1, this wheel disc 1 has towards the front of airintake direction and the back side on the other side, and in addition, the back side of wheel disc 1 is provided with reinforcing part.During centrifugal blower work, impeller is in High Rotation Speed state, and the design of this reinforcing part can improve the rigidity of impeller, thus the distortion that reduction impeller causes due to centrifugal motion.
In vane rotary process, because centrifugal action makes impeller deform, meanwhile, bearing generation play, makes impeller also play occur, and this distortion of impeller and play are difficult to control.Therefore, for avoiding in vane rotary process, the impeller caused due to this distortion and play and shape ring collide, and ensure the Security of equipment, when Impeller Design, usually between impeller and shape ring, leave blade tip clearance.
In existing centrifugal blower, as shown in Figure 1, collide for avoiding blade 11 ＇ and shape ring 2 ＇ and affect the Security of equipment, usually using the value of the 0.3--0.5% of impeller diameter as blade tip clearance, and the blade tip clearance value that this design method obtains is usually larger, easily cause gas leakage, and reduce the efficiency of impeller.
In the present invention, by arranging reinforcing part at wheel disc 1 back side, improve the rigidity of impeller, distortion during vane rotary is reduced, therefore, the blade tip clearance that reserves required in Impeller Design process reduces, and effectively avoids and that cause air loss excessive due to blade tip clearance, thus improves the efficiency of impeller.
Particularly, wheel disc 1 back side is provided with stiffening rib, and this stiffening rib is above-mentioned reinforcing part.
The moment of inertia that stiffening rib can improve impeller is set at wheel disc 1 back side, thus improves the rigidity of impeller, reduce distortion during vane rotary.Meanwhile, by can be calculated optimum shape and the size of stiffening rib, thus this stiffening rib is made to have the effect of best raising impeller stiffness.Based on this object, the various stiffening ribs that related domain is conventional can be adopted, such as I-steel, band steel etc.
Be appreciated that, be not limited in, at wheel disc 1 back side, stiffening rib be set to improve the rigidity of impeller, also can increase the wall thickness of impeller or adopt the material of more high elastic modulus to realize, but, when impeller wall thickness increases, its weight also increases usually, improve vane rotary time energy consumption and reduce its Security; And impeller adopts the higher material of Young's modulus to increase cost.Therefore, in the present embodiment, preferably adopt the mode that stiffening rib is set at wheel disc 1 back side to improve the rigidity of impeller.
In addition, the mode that wheel disc 1 back side arranges stiffening rib can also improve its intensity while raising impeller stiffness, thus improves the working life of impeller.
More specifically, wheel disc 1 back side can be provided with boss 2, and this boss 2 is above-mentioned stiffening rib.In addition, this boss 2 is one-body molded with wheel disc 1.
The design of this boss 2 is simple compared to the reinforcing rib structure of other structures such as I-steel, is easy to realize.
Further, wheel disc 1 has wheel disc center line X, and this boss 2 can be annular, and its center line can be wheel disc center line X.As shown in Figure 2, have mounting hole 11 in the middle part of this impeller, by this mounting hole 11, make impeller be installed on main shaft, annular boss 2 is concentric with this mounting hole 11, and is positioned at outside mounting hole 11.
Be appreciated that, this boss 2 is not limited in as annular, based on the object reducing impeller stiffness, can be the boss 2 of arbitrary shape, such as, can be some small boss be symmetrically distributed in outside mounting hole 11, now, the distortion of impeller can be reduced equally, especially significantly can reduce the axial deformation of impeller, but, can reduce the effect of radial deformation.And the annular boss 2 in the present embodiment can reduce axial deformation and the radial deformation of impeller to greatest extent.
Further, the diameter of this annular boss 2 can be the half of wheel disc 1 diameter, highly can be 3.75% of wheel disc 1 diameter, and thickness can be 3% of wheel disc 1 diameter.
It should be noted that, boss 2 herein highly refers to the size of boss 2 axis, and boss 2 thickness refers to the size of boss 2 radial direction.Meanwhile, above-mentioned boss 2 is of a size of an optimum value, when impeller arranges the boss 2 of this size, the distortion of impeller can be reduced to greatest extent, but the size of boss 2 is not limited in this, size in the reasonable scope all has the effect of the distortion reduced in impeller high-speed rotation.
In addition, above-mentioned boss 2 diameter, highly, the optimum value of thickness obtains respectively by ANSYS numerical simulation.Be the impeller of 200mm for a wheel diameter, its back side arranges a boss, and this boss diameter is 100mm, is highly 7.5mm, and thickness is 6mm.All ANSYS numerical simulation is carried out to the impeller arranging this optimal size boss and the impeller that do not arrange boss, and compare its result, can obtain, after the boss of above-mentioned optimal size is set, the distortion of impeller reduces half compared to the impeller not arranging boss, and the flow analysis of gas calculates in gas channel, the efficiency of this impeller improves 3%.
On this basis, when wheel disc 1 back side arranges boss 2, the value of blade tip clearance during Impeller Design no longer adopts the method for the value of the 3%-5% getting impeller diameter, now, adopts following methods accurately to determine the value of blade tip clearance.First, for the impeller of specific wheel diameter, calculate the optimal size of this size lower convex platform, and set up the impeller pattern that this size boss is set; Then, by the amount of deformation of this impeller of ANSYS numerical simulation calculation; Finally, being added simulating the amount of deformation obtained with the shifting amount of vane rotary process middle (center) bearing, obtaining the value of blade tip clearance.In this process, because the amount of deformation of impeller reduces, then required reserved blade tip clearance correspondingly reduces, the more important thing is, the method can the more accurate value must determining blade tip clearance, under the prerequisite ensureing device security, avoid causing because blade tip clearance is excessive equipment to leak gas, thus improve the efficiency of impeller.
Further, impeller is shaping by milling, makes this boss 2 one-body molded with impeller.This boss 2 also can be welded in wheel disc 1 back side, but integrated impeller is not owing to existing weld seam, and its strength and stiffness all comparatively welding fabrication are high.
The present invention also provides a kind of centrifugal blower, comprise housing and be positioned at the impeller of its inside, shape ring and main shaft, wherein, impeller is installed on main shaft, and shape ring is fixed on housing, and shape ring and impeller form air-flow path, to make gas from when axially entering centrifugal blower, in this air-flow path, the flow direction of gas is by axially changing into radial direction, gas pressure raises and discharges, thus the kinetic energy realizing gas is converted to pressure potential.Wherein, this impeller is the impeller described in above any embodiment.Because above-mentioned impeller has above-mentioned technique effect, the centrifugal blower with this impeller also has identical technique effect, repeats no more herein.
Above a kind of centrifugal blower provided by the present invention and impeller thereof are all described in detail.Apply specific case herein to set forth principle of the present invention and mode of execution, the explanation of above embodiment just understands method of the present invention and core concept thereof for helping.It should be pointed out that for those skilled in the art, under the premise without departing from the principles of the invention, can also carry out some improvement and modification to the present invention, these improve and modify and also fall in the protection domain of the claims in the present invention.
Claims (5)
1. an impeller, comprises wheel disc (1), and described wheel disc (1) has towards the front of airintake direction and the back side on the other side; It is characterized in that, the back side of described wheel disc (1) is provided with reinforcing part.
2. impeller according to claim 1, is characterized in that, described wheel disc (1) back side is provided with boss (2), and described boss (2) is described reinforcing part.
3. according to the impeller described in claim 2, it is characterized in that, described wheel disc (1) has wheel disc center line (X), and described boss (2) is annular, and its center line is described wheel disc center line (X).
4. impeller according to claim 3, it is characterized in that, the diameter of described boss (2) is the half of described wheel disc (1) diameter, the height of described boss (2) is the 3%-4% of described wheel disc (1) diameter, and the thickness of described boss (2) is the 2%-4% of described wheel disc (1) diameter.
5. a centrifugal blower, comprise housing and be positioned at the impeller of its inside, shape ring and main shaft, described impeller is installed on described main shaft, and described shape ring is fixed on described housing, and described shape ring and described impeller form air-flow path; It is characterized in that, the impeller of described impeller according to any one of claim 1-4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510373325.9A CN105090105A (en) | 2015-06-30 | 2015-06-30 | Centrifugal fan and impeller thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510373325.9A CN105090105A (en) | 2015-06-30 | 2015-06-30 | Centrifugal fan and impeller thereof |
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| CN105090105A true CN105090105A (en) | 2015-11-25 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510373325.9A Pending CN105090105A (en) | 2015-06-30 | 2015-06-30 | Centrifugal fan and impeller thereof |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110701101A (en) * | 2019-10-14 | 2020-01-17 | 中国北方发动机研究所(天津) | Compressor impeller with elastic table |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1224807A (en) * | 1998-01-27 | 1999-08-04 | 三菱重工业株式会社 | Cooling fan for air-cooled engine |
| CN201187477Y (en) * | 2008-04-24 | 2009-01-28 | 湖北省风机厂有限公司 | Impeller apparatus of gas centrifugal blower |
| JP2010019262A (en) * | 2009-10-19 | 2010-01-28 | Daikin Ind Ltd | Air blower, air conditioner and air cleaner using the same |
| CN102400952A (en) * | 2010-09-15 | 2012-04-04 | 徐跃 | Centrifugal fan impeller with windproof ring |
| CN203230624U (en) * | 2013-04-08 | 2013-10-09 | 合肥晶弘电器有限公司 | Centrifugal fan rotor, centrifugal fan and air cooling refrigerator |
| CN103821767A (en) * | 2014-03-13 | 2014-05-28 | 上海诺地乐通用设备制造有限公司 | Single-stage high-speed centrifugal blower air inlet shell pouring babbitt alloy layer structure |
-
2015
- 2015-06-30 CN CN201510373325.9A patent/CN105090105A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1224807A (en) * | 1998-01-27 | 1999-08-04 | 三菱重工业株式会社 | Cooling fan for air-cooled engine |
| CN201187477Y (en) * | 2008-04-24 | 2009-01-28 | 湖北省风机厂有限公司 | Impeller apparatus of gas centrifugal blower |
| JP2010019262A (en) * | 2009-10-19 | 2010-01-28 | Daikin Ind Ltd | Air blower, air conditioner and air cleaner using the same |
| CN102400952A (en) * | 2010-09-15 | 2012-04-04 | 徐跃 | Centrifugal fan impeller with windproof ring |
| CN203230624U (en) * | 2013-04-08 | 2013-10-09 | 合肥晶弘电器有限公司 | Centrifugal fan rotor, centrifugal fan and air cooling refrigerator |
| CN103821767A (en) * | 2014-03-13 | 2014-05-28 | 上海诺地乐通用设备制造有限公司 | Single-stage high-speed centrifugal blower air inlet shell pouring babbitt alloy layer structure |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110701101A (en) * | 2019-10-14 | 2020-01-17 | 中国北方发动机研究所(天津) | Compressor impeller with elastic table |
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Application publication date: 20151125 |
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