CN112253536A - Centrifugal impeller and ventilator thereof - Google Patents
Centrifugal impeller and ventilator thereof Download PDFInfo
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- CN112253536A CN112253536A CN202011184686.6A CN202011184686A CN112253536A CN 112253536 A CN112253536 A CN 112253536A CN 202011184686 A CN202011184686 A CN 202011184686A CN 112253536 A CN112253536 A CN 112253536A
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- 230000004323 axial length Effects 0.000 claims description 5
- 239000000411 inducer Substances 0.000 claims description 2
- 230000006698 induction Effects 0.000 claims 3
- 230000000052 comparative effect Effects 0.000 description 15
- 230000003068 static effect Effects 0.000 description 12
- 238000000926 separation method Methods 0.000 description 6
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 238000003466 welding Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000008676 import Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000009191 jumping Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000010030 laminating Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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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
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
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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
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/16—Centrifugal pumps for displacing without appreciable compression
-
- 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
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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
- F04D29/30—Vanes
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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
- F04D29/60—Mounting; Assembling; Disassembling
- F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
- F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/626—Mounting or removal of fans
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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 relates to a centrifugal impeller, which comprises a front disc, a rear disc and a plurality of blades uniformly clamped between the front disc and the rear disc, wherein a space enclosed by adjacent blades, the front disc and the rear disc is an airflow channel in the impeller, airflow axially enters the impeller from the front disc and flows out from the periphery of the impeller after passing through a flow channel between the blades, the front disc sequentially comprises a straight inlet section, a main body arc-shaped section, a straight outlet section and an outlet flanging section from an airflow inlet to an outlet, the straight inlet section is in a straight cylinder shape, the straight outlet section is in a circular ring shape, the inlet end of the main body arc-shaped section is in tangential connection with the straight inlet section, and the outlet end of the main body arc-shaped section is in tangential connection with the straight outlet section.
Description
Technical Field
The invention relates to the technical field of ventilators, in particular to a centrifugal impeller and a ventilator comprising the centrifugal impeller.
Background
The centrifugal impeller mainly comprises a rear disk, a front disk and a plurality of blades arranged between the rear disk and the front disk, wherein an inner hole of the front disk is an impeller inlet. The basic form of the front disk is a straight front disk, a conical front disk and an arc front disk. The cross-sectional shape of the front disc has a large influence on the flow state in the blade flow channel, so that the performance of the ventilator is remarkably influenced, and the impeller with high efficiency mostly adopts an arc-shaped front disc (usually adopting an arc shape). Generally, the radius r of the inboard front end of the front disk should be as large as possible to reduce separation and loss of the impeller inlet flow when turning. However, the enlarged radius of the front end of the front disc can cause the increase of the volume of the impeller, increase the cost and limit the use occasions, so that the length and the arc shape of the front disc of the impeller are improved in a limited range as much as possible, the front disc of the impeller can be more suitable for the airflow characteristics of a centrifugal impeller compared with the existing arc-shaped front disc of the impeller, the airflow turns smoothly, the flow field tends to be stable as much as possible, and the vortexes and the separation of the gas are reduced.
Disclosure of Invention
The centrifugal impeller has an airflow characteristic that, at the impeller inlet side, after a main airflow enters the impeller from the axial direction, the main airflow flows by two large turns: one is turning at 90 degrees from axial direction to radial direction, and the other is turning in circumferential direction formed by the action of rotating blades of the impeller on gas, namely, the gas flow near the inner diameter of the front disk is usually uneven, so that gas flow separation is easy to generate, the flow field in the impeller is further deteriorated, the efficiency of the impeller on the gas is influenced, and further, the pressure of the ventilator is reduced, and the power consumption is increased. Therefore, the arc turning radius at the inner diameter of the front disc is designed to be larger as much as possible, so that the airflow turns smoothly, and the flow field tends to be stable as much as possible, thereby reducing the swirl and separation of the gas.
On the other hand, inside the impeller, each fluid passage between the blades is surrounded by two adjacent blades, a front disk and a rear disk: the shape of the front disk, with the vane profile established, determines the axial width and flow area of the vane passage at each diameter, with a significant effect on the flow conditions within the vane passages, and it is generally desirable to create a uniformly decelerated flow within the vane passages so that the flow exits the impeller at a lower velocity at the tips at the vane outer diameter, with the width of the vane passages from the impeller inner diameter to the impeller outer diameter being progressively larger for centrifugal impellers, and the front disk being designed to be inclined toward the rear disk, i.e., with increasing diameter, the width of the vanes progressively decreasing-the vane exit width b-for constant velocity or deceleration flow passages2Less than the width b of the blade inlet1。
Based on the flow characteristics of the gas flow in the impeller, the invention mainly improves the structures of the inlet section and the inner main body section of the impeller by design, so as to reduce the axial turning of the gas flow at the inlet of the impeller to the radial direction and the turning of the gas in the circumferential direction caused by the rotation of the impeller, thereby reducing the vortex and the separation. On the basis of the front disc with the circular arc-shaped cross section, which is widely used at present, the invention further optimizes the gas flowing state at the inlet of the impeller and in the blade channel of the impeller by optimizing the shape of the arc-shaped cross section of the front disc so as to improve the efficiency of the impeller for applying work to the gas and further improve the pneumatic performance and efficiency of the impeller and the ventilator.
The invention realizes the purpose through the following technical scheme:
the utility model provides a centrifugal impeller, the impeller includes front bezel, back plate and evenly presss from both sides and establishes a plurality of blades between front bezel and the back plate, and the space that adjacent blade and front bezel, back plate enclose is the airflow channel in the impeller, and the air current is followed the axial of front bezel gets into the impeller, through the runner between the blade after, from the impeller periphery outflow, the front bezel is followed the air current and is establishedImport to the export, include straight import section, main part segmental arc, straight export section, export turn-ups section in proper order, straight import section is straight tube-shape, and straight export section is the ring form, the entrance point of main part segmental arc with straight import section is tangent to be connected, the exit end of main part segmental arc with straight export section is tangent to be connected, and the head plate hole diameter is D0With a straight outlet section having an internal diameter D2。
Further, the generatrix of the arc segment of the main body in rectangular coordinates satisfies the following equation:
＋ 
u is the radial width of the main body arc section, v is the axial height of the main body arc section, an x axis of a rectangular coordinate is obtained by passing an axial parallel line of the impeller at the outlet end of the main body arc section, a y axis of the rectangular coordinate is obtained by passing a radial parallel line of the impeller at the inlet end of the main body arc section, and the intersection point of the x axis and the y axis is an origin O of the rectangular coordinate, wherein x and y satisfy the following conditions: x is more than or equal to 0 and less than or equal to v, and y is more than or equal to u and less than or equal to 0.
Further, a straight line connecting the inlet end and the outlet end of the arc-shaped section of the main body forms an angle θ =30 ° -40 °, u =0.5 × (D) with the radial center line of the impeller2~D0) V = u × tg θ, and the horizontal distance from the origin O to the inner plane of the rear disk is "b2+ v ", the perpendicular distance from the origin O to the impeller center line is" 0.5 XD2”。
Further, the ratio of the axial height of the main body arc section to the radial width of the main body arc section is 0.6-0.8.
Further, the axial length s of the straight inlet section satisfies: s = (0.01 to 0.02) × D2Wherein D is2Is the outer diameter of the blade.
A ventilator comprises a centrifugal impeller and an air inlet, wherein the impeller is sleeved outside the air inlet, and the axial overlapping length of the impeller and the air inlet is t1Satisfies the following conditions: t is t1=(0.01~0.02)×D2。
Compared with the prior art, the invention has the following beneficial effects:
the arc-shaped section of the front disc main body not only considers that the turning of the gas just after entering the impeller needs the radius of the turning part of the front disc to be as large as possible, but also considers the gradual transition from small to large of the channel area between the blades, so that the flow of the gas from the front end of the flow blade to the front end of the flow blade after entering the impeller is obviously improved to a certain extent, and the working efficiency and the performance parameters of the impeller are improved.
The invention improves the gas separation and swirl caused by the change of the gas flow from axial to radial when entering the impeller mainly by adding a straight inlet section on the front disk of the impeller. And, the straight inlet section is added at the inlet of the front disc, and the following functions are also realized:
1. the rigidity of the front disc is increased, and the inner ring of the front disc can bear the fatigue load caused by the long-term running of the impeller and is not easy to tear;
2. the roundness of the inlet ring is increased, and the radial clearance t between the air inlet and the impeller during assembly is better ensured3The circumferential direction is uniform;
3. the roundness of the inlet ring is increased, and because the front disc forms a straight cylinder section when the die is used for drawing, profiling and processing, the contraction and resilience of the front disc are smaller, so that under the condition of assembling and welding the impeller, the positioning is more accurate from the process, and the jumping and dynamic balance of the impeller are better ensured, as shown in figure 1;
4. because the front disk is in a conical arc shape as a whole, when the air inlet and the impeller are assembled, the axial position of the air inlet and the impeller deviates to one side of the impeller, so that the radial fit clearance between the air inlet and the impeller is obviously increased, namely the internal leakage of the ventilator is obviously increased, and the pressure of the ventilator is obviously reduced. At present, because the annular inlet ring has a certain axial length s, when the axial position of the air inlet and the impeller during assembly is slightly deviated (particularly slightly deviated towards the inner side of the impeller), the radial clearance between the air inlet and the impeller is obviously increased, so that the leakage in the ventilator is increased, the outlet flow is reduced, the pressure is reduced and the power consumption is increased, as shown in fig. 2;
5. the addition of the straight inlet section means that the axial heights of the front disc and the impeller are slightly increased, so that when the ventilator is assembled, compared with the straight section without the inlet, the axial installation position of the air inlet moves outwards by a distance s, and the distance t between the tail end of the air inlet and the front end of the blade2And s is increased, so that the impeller inlet airflow is stabilized, and a better inlet airflow condition is provided for the blades to efficiently apply work to the air.
Drawings
FIG. 1 is a schematic view of the center positioning of a front disk during assembly welding of an impeller according to the present invention;
FIG. 2 is a diagram illustrating a prior art front plate inlet with an arc shape matching with an air inlet;
FIG. 3 is an assembly view of the ventilator of the present invention;
FIG. 4 is a block diagram of the impeller of the ventilator of the present invention;
FIG. 5 is a schematic view of the inner side generatrix of the front disk of the impeller of the ventilator of the present invention;
FIG. 6 is a graph comparing the static pressures of example 2 and comparative sample 1;
FIG. 7 is a graph comparing the static pressure efficiency of example 2 with that of comparative sample 1;
FIG. 8 is a graph comparing the static pressures of example 3 and comparative sample 2;
fig. 9 is a graph comparing the static pressure efficiency of example 3 with that of comparative sample 2.
The reference numerals are explained below:
1. an impeller; 2. an air inlet; 3. a large disc; 4. a mandrel; 11. a rear disc; 12. a blade; 13. and a front disc.
Detailed Description
The invention will be further described with reference to the accompanying drawings in which:
example 1
This example illustrates the effect of adding a straight inducer at the entrance of the front disc.
As shown in fig. 1, when the back plate 11, the blades 12 and the front plate 13 of the centrifugal impeller are assembled and welded, the center of the front plate is positioned by the vertical mandrel 4 and the large disc 3, wherein the mandrel is the axial center line of the impeller 1, the gap between the large disc and the inner wall of the inlet end of the front plate is delta, and the front plate is positioned in both the horizontal direction and the vertical direction. The front disc of the prior art, the circle is inhomogeneous because shrink deformation when the mould die mould is pressed in the front disc, has the ellipticity of certain degree, can entangle big disc for guaranteeing the minimum internal diameter of front disc, must turn the big disc external diameter car little, cause the uneven and front disc pitch arc of circumferential direction mass distribution of front disc and the laminating of blade pitch arc not tight of front disc, be connected with the deformation by force during the welding, it is big with initial dynamic unbalance amount to have to beat, must rely on the whole plastic of impeller to guarantee to beat and dynamic balance precision is qualified. Compared with the prior art, the roundness of the inner circle of the front disc is better, the value of the process gap delta can be smaller, the possible degree of deviation of the center of the front disc from the center of the impeller is smaller, the center positioning of the front disc can be more accurate, the arc line of the front disc is more attached to the arc line of the edge of the front end of the blade, the deformation during welding is small, the mass eccentricity of the front disc and the impeller part is smaller, and therefore the impeller is small in jumping and high in dynamic balance precision.
In addition, in the assembly of the air inlet 2 and the impeller 1, when the inlet of the front disk is an arc line in the prior art, due to errors caused in the assembly process, the depth of the air inlet sleeved into the front disk is slightly different, namely the axial overlapping is different, and a radial gap t between the air inlet and the front disk is caused3Is significantly increased. As shown in fig. 2, when the inlet of the front disc is an arc, when the axial overlapping length of the air inlet and the front disc is 6mm, the radial gap between the air inlet and the front disc is 4.2 mm. When the air inlet axially extends into 8mm towards the front disc, the radial clearance between the air inlet and the front disc is 4.6mm, and the radial clearance is increased by 0.4 mm. At high impeller speeds, the 0.4mm clearance has a significant effect on airflow, which tends to increase leakage, decrease outlet flow, decrease pressure and increase power consumption in the fan.
In the application, the straight inlet section is added at the inlet of the front disc, and the straight inlet section has a certain axial length s, so that the axial position of the air inlet and the impeller during assembly is not slightly deviated, and particularly, when the straight inlet section slightly deviates towards the inner side of the impeller, the radial gap between the straight inlet section and the impeller is obviously increased. In the length range of the straight inlet section, the air inlet moves in the axial direction, and the radial clearance between the air inlet and the front disc is unchanged.
Further, as shown in fig. 3, the addition of the straight inlet section means that the axial height of the front disc and the impeller is increased, so that when the ventilator is assembled, compared with the straight section without the inlet, the axial installation position of the air inlet is moved outward by a distance s, which is the axial length of the straight inlet section and is equivalent to the distance t between the tail end of the air inlet and the front end of the blade2And s is increased, so that the impeller inlet airflow is stabilized, and a better inlet airflow condition is provided for the blades to efficiently apply work to the air.
Example 2
This example illustrates the function of the arcuate section of the body.
Compared with the comparative sample machine 1, the ventilator of the embodiment 2 of the invention has the same parts except the different section arcs of the main arc segment, and the matched motor and the running rotating speed are also the same. The cross section of the main body arc segment of the comparative prototype 1 is an arc, and the cross section of the main body arc segment of the embodiment 2 is a main body arc segment curve of the invention, and comprises a straight inlet segment 'ab', a main body arc segment 'bc', a straight outlet segment 'cd' and an outlet flanging segment 'def'.
The relevant dimensions for example 2 and comparative sample 1 are as follows:
D2=526.6 mm
D0=352.5 mm
D3=566 mm
s=6 mm
u=87 mm
v=53.5 mm
θ=31.6°
v/u=0.615
the performance curves of example 2 and comparative prototype 1 are compared in FIGS. 6-7; the comparison of the performance parameters of the working points with the same air volume is shown in the table 1.
TABLE 1
| Rotating speed (r/min) | Air volume (m)3/h） | Static pressure (Pa) | Static pressure efficiency (%) | |
| |
1780 | 8424 | 851.6 | 66.5 |
| Example 2 | 1780 | 8424 | 884.7 | 68.5 |
Under the working condition of the same air volume, compared with a comparative sample machine 1, the static pressure of the embodiment 2 is improved by 33.1Pa, and the static pressure efficiency is improved by 2%.
Example 3
This embodiment specifies the role of the arcuate section of the body by another impeller size.
Compared with the comparative sample machine 2, the embodiment 3 of the invention has the advantages that the rest parts of the ventilator are completely the same except that the section arc lines of the main arc line section are different, and the matched motor and the running rotating speed are also the same. The cross-sectional shape of the main body arc segment of comparative prototype 2 was an arc, and the cross-sectional shape of the main body arc segment of example 3 was a main body arc segment curve of the present invention.
The relevant dimensions for example 3 and comparative sample 2 are as follows:
D2=639.6 mm
D0=444 mm
D3=716 mm
s=7 mm
u=97.8 mm
v=68 mm
θ=34.8°
v/u=0.695
the performance curves of example 3 and comparative sample 2 are compared and shown in FIGS. 8-9; the comparison of the performance parameters of the working points with the same air volume is shown in the table 1.
TABLE 2
| Rotating speed (r/min) | Air volume (m)3/h） | Static pressure (Pa) | Static pressure efficiency (%) | |
| |
1450 | 13230 | 845.4 | 70.2 |
| Example 3 | 1450 | 13230 | 872.5 | 71.8 |
Under the working condition of the same air volume, the static pressure of the embodiment 3 is improved by 27.1Pa and the static pressure efficiency is improved by 1.6 percent compared with the comparison sample machine 2.
And (4) conclusion:
the improved scheme of the invention is mainly characterized in that the front end air inlet condition of the blades in the impeller is improved and the flow field in the channel between the blades is optimized by optimizing the arc shape of the section of the front disc, so that the efficiency of the impeller on gas work is improved, the performance and efficiency of the ventilator are obviously improved, the energy consumption and noise are reduced, the main characteristic size and the process machining mode of the impeller are not changed, and the impeller has certain economic and social values.
The foregoing illustrates and describes the principles, general features, and advantages of the present invention. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are described in the specification and illustrated only to illustrate the principle of the present invention, but that various changes and modifications may be made therein without departing from the spirit and scope of the present invention, which fall within the scope of the appended claims.
Claims (6)
1. The utility model provides a centrifugal impeller, the impeller includes that head disk, back plate and even clamp are established a plurality of blades between head disk and the back plate, the space that adjacent blade and head disk, back plate enclose is the airflow channel in the impeller, and the air current is followed head disk axial gets into the impeller, through the runner between the blade after, flows from the impeller periphery, its characterized in that, head disk from airflow inlet to export, includes straight induction zone, main part segmental arc, straight export section and export turn-ups section in proper order, straight induction zone is straight tube-shape, and straight export section is the ring form, the entrance point of main part segmental arc with straight induction zone is tangent to be connected, the exit end of main part segmental arc with straight export section is tangent to be connected.
2. The centrifugal impeller of claim 1, wherein the inside of the arcuate segment of the bodyThe generatrix in rectangular coordinates satisfies the following equation:
＋
u is the radial width of the main body arc section, v is the axial height of the main body arc section, an x axis of a rectangular coordinate is obtained by passing through an axial parallel line of the impeller at the outlet end of the main body arc section, and a y axis of the rectangular coordinate is obtained by passing through a radial parallel line of the impeller at the inlet end of the main body arc section, wherein x and y satisfy: x is more than or equal to 0 and less than or equal to v, and y is more than or equal to u and less than or equal to 0.
3. The centrifugal impeller according to claim 2, wherein the arc-shaped section of the main body of the front disk is inclined from the inner diameter to the outer diameter toward the rear disk side, and the angle of inclination of the front disk with respect to the plane of the rear disk is θ, θ =30 ° -40 °.
4. The centrifugal impeller as claimed in claim 2, wherein the ratio of the axial height of the arcuate section of the main body to the radial width of the arcuate section of the main body is 0.6 to 0.8.
5. A centrifugal impeller according to claim 1, wherein the axial length s of the flat inducer satisfies: s = (0.01 to 0.02) × D2Wherein D is2Is the outer diameter of the blade.
6. A ventilator, the ventilator includes the centrifugal impeller of claim 1-5, characterized by, also include the air intake, the impeller cover is established outside the air intake, the impeller with the axial overlap length t of air intake is1，t1Satisfies the following conditions: t is t1=(0.01~0.02)×D2。
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011184686.6A CN112253536A (en) | 2020-10-30 | 2020-10-30 | Centrifugal impeller and ventilator thereof |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011184686.6A CN112253536A (en) | 2020-10-30 | 2020-10-30 | Centrifugal impeller and ventilator thereof |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115351512A (en) * | 2022-09-05 | 2022-11-18 | 山东省章丘鼓风机股份有限公司 | Machining method for conical arc-shaped air inlet of ventilator |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5478201A (en) * | 1994-06-13 | 1995-12-26 | Carrier Corporation | Centrifugal fan inlet orifice and impeller assembly |
| US6042335A (en) * | 1998-05-04 | 2000-03-28 | Carrier Corporation | Centrifugal flow fan and fan/orifice assembly |
| CN102162466A (en) * | 2010-02-23 | 2011-08-24 | 日本电产株式会社 | Centrifugal fan impeller and moulding method thereof |
| CN102162465A (en) * | 2010-02-23 | 2011-08-24 | 日本电产株式会社 | Impeller and centrifugal fan |
| CN103362862A (en) * | 2013-07-02 | 2013-10-23 | 浙江亿利达风机股份有限公司 | Front disk and fan impeller |
| CN203756593U (en) * | 2013-12-31 | 2014-08-06 | 顿力集团有限公司 | High-efficient centrifugal wind wheel |
| CN204783820U (en) * | 2015-02-11 | 2015-11-18 | 依必安派特穆尔芬根有限两合公司 | Fan rotor and fan |
| CN206889341U (en) * | 2017-03-21 | 2018-01-16 | 苏州工业园区星德胜电机有限公司 | A kind of centrifugal blower movable vane wheel |
| CN109441876A (en) * | 2018-12-26 | 2019-03-08 | 浙江科贸智能机电股份有限公司 | To centrifugal fan after a kind of no spiral case |
| CN109973410A (en) * | 2019-04-11 | 2019-07-05 | 浙江科贸智能机电股份有限公司 | A kind of no spiral case centrifugal fan |
| CN213450988U (en) * | 2020-10-30 | 2021-06-15 | 浙江科贸智能机电股份有限公司 | Centrifugal impeller and ventilator thereof |
-
2020
- 2020-10-30 CN CN202011184686.6A patent/CN112253536A/en active Pending
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5478201A (en) * | 1994-06-13 | 1995-12-26 | Carrier Corporation | Centrifugal fan inlet orifice and impeller assembly |
| US6042335A (en) * | 1998-05-04 | 2000-03-28 | Carrier Corporation | Centrifugal flow fan and fan/orifice assembly |
| CN102162466A (en) * | 2010-02-23 | 2011-08-24 | 日本电产株式会社 | Centrifugal fan impeller and moulding method thereof |
| CN102162465A (en) * | 2010-02-23 | 2011-08-24 | 日本电产株式会社 | Impeller and centrifugal fan |
| CN103362862A (en) * | 2013-07-02 | 2013-10-23 | 浙江亿利达风机股份有限公司 | Front disk and fan impeller |
| CN203756593U (en) * | 2013-12-31 | 2014-08-06 | 顿力集团有限公司 | High-efficient centrifugal wind wheel |
| CN204783820U (en) * | 2015-02-11 | 2015-11-18 | 依必安派特穆尔芬根有限两合公司 | Fan rotor and fan |
| CN206889341U (en) * | 2017-03-21 | 2018-01-16 | 苏州工业园区星德胜电机有限公司 | A kind of centrifugal blower movable vane wheel |
| CN109441876A (en) * | 2018-12-26 | 2019-03-08 | 浙江科贸智能机电股份有限公司 | To centrifugal fan after a kind of no spiral case |
| CN109973410A (en) * | 2019-04-11 | 2019-07-05 | 浙江科贸智能机电股份有限公司 | A kind of no spiral case centrifugal fan |
| CN213450988U (en) * | 2020-10-30 | 2021-06-15 | 浙江科贸智能机电股份有限公司 | Centrifugal impeller and ventilator thereof |
Non-Patent Citations (1)
| Title |
|---|
| 续魁昌主编: "《风机手册》", 31 May 1999 * |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115351512A (en) * | 2022-09-05 | 2022-11-18 | 山东省章丘鼓风机股份有限公司 | Machining method for conical arc-shaped air inlet of ventilator |
| CN115351512B (en) * | 2022-09-05 | 2023-11-10 | 山东省章丘鼓风机股份有限公司 | Machining method of conical arc-shaped air inlet of ventilator |
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