CN113446237B - Centrifugal ventilator with semi-open type ternary impeller - Google Patents

Centrifugal ventilator with semi-open type ternary impeller Download PDF

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Publication number
CN113446237B
CN113446237B CN202110671544.0A CN202110671544A CN113446237B CN 113446237 B CN113446237 B CN 113446237B CN 202110671544 A CN202110671544 A CN 202110671544A CN 113446237 B CN113446237 B CN 113446237B
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China
Prior art keywords
impeller
disc
volute
side plate
blades
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CN113446237A (en
Inventor
杨徽
陈雨彬
肖康
王政道
张炜
朱祖超
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Zhejiang Sci Tech University ZSTU
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Zhejiang Sci Tech University ZSTU
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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
    • 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
    • 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
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • 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
    • 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
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

Abstract

The invention discloses a centrifugal ventilator with a semi-open type ternary impeller, which comprises a volute, a rotary shaft and a rotary shaft, wherein the volute is provided with a front side plate and a rear side plate; one end of the current collector is connected with the front side plate, and the other end of the current collector extends into the volute from the front side plate; the impeller assembly is arranged in the volute, and comprises an impeller arranged in the volute and a rotating shaft which is connected with the impeller and driven by a motor; the impeller comprises an impeller rear disc rotatably arranged in the volute, a plurality of blades connected with the impeller rear disc and an impeller front disc positioned on one side of the impeller rear disc close to the front side plate; the blades are positioned between the impeller front disc and the impeller rear disc, and a gap is reserved between the front edges of the blades and the impeller front disc; the impeller front disc is connected with one end of the current collector, which is far away from the front side plate, and the impeller front disc and the current collector are integrally cast or connected in a seamless mode. The invention reduces the resistance loss of the air flow to the blades near the wheel cover by casting the front disc of the impeller and the current collector integrally, thereby achieving the effect of high rotation speed ratio.

Description

Centrifugal ventilator with semi-open type ternary impeller
Technical Field
The invention belongs to the technical field of fans, and particularly relates to a centrifugal ventilator with a semi-open type ternary impeller.
Background
The centrifugal fan is a machine which increases the pressure of gas and discharges the gas by means of input mechanical energy, and is a driven fluid machine. The centrifugal fan has wide application range, is large in mine ventilation, boiler induced air and chemical processes, is small in industrial furnace air blowing, air conditioning, building ventilation and the like, does not need to adopt a ventilator, is important matched equipment for industrial production, and is also a large household of energy consumption.
The impeller of traditional centrifugal fan adopts closed structure, and the impeller front shroud closely pastes the blade, has the clearance between with the fan spiral case, and fan high pressure side air can flow back to the low pressure side through this clearance to cause the energy loss of fan, increase the noise of fan, produce the interference to the air inlet flow field of fan, reduce the air outlet volume and the wind pressure of fan.
On large-scale equipment such as engines, a centrifugal ventilator for internal heat exchange needs to be installed to achieve the purpose of rapid heat dissipation. The working space is narrow, the required rotating speed is large, and the requirement of high efficiency is not satisfied by the traditional centrifugal fan at present.
Disclosure of Invention
The invention provides a centrifugal ventilator with a semi-open type ternary impeller, which is small in energy loss and aims to overcome the defects of the prior art.
In order to achieve the above purpose, the present invention adopts the following technical scheme: a centrifugal ventilator with semi-open type ternary impeller comprises
A volute having a front side plate and a rear side plate;
one end of the current collector is connected with the front side plate, and the other end of the current collector extends into the volute from the front side plate;
the impeller assembly is arranged in the volute, and comprises an impeller arranged in the volute and a rotating shaft which is connected with the impeller and driven by a motor;
the impeller comprises an impeller rear disc rotatably arranged in the volute, a plurality of blades connected with the impeller rear disc and an impeller front disc positioned on one side of the impeller rear disc close to the front side plate; the blades are positioned between the impeller front disc and the impeller rear disc, and a gap is reserved between the front edges of the blades and the impeller front disc; the impeller front disc is connected with one end of the current collector, which is far away from the front side plate, and the impeller front disc and the current collector are integrally cast or connected in a seamless mode.
Optionally, the curvature of the blade top profile of the blade is the same as that of the profile of the impeller front disc, and the clearance between the blade top of the blade and the impeller front disc is set to be 0.5-1 mm. By arranging the gaps, the resistance loss of the air flow to the blades near the wheel cover is reduced, and therefore the effect of high rotation speed ratio is achieved.
Optionally, a gap between the tip of the blade and the impeller front plate is set to be 0.75mm.
Optionally, the inlet angle of the blade is 30 ° and the outlet angle of the blade is 90 °.
Optionally, the blades are three-dimensionally streamlined and have uniform twist directions, and the twist angle of the blades is 30 ° from the impeller inlet to the impeller back plate. The twisting direction of each blade is consistent, so that the inlet impact loss of each blade and the separation loss of the tail edge of the blade are reduced, and the best aerodynamic performance of the blade is achieved.
Optionally, the plurality of blades includes long blades and short blades, and the long blades and the short blades are staggered and arranged at intervals. Through long, short blade interval setting, utilize the effect that short blade shunted the air current to avoid the formation of the air current vortex between the long blade to improve the output efficiency of impeller air current.
Alternatively, the impeller is a three-stream impeller, and the impeller inlet has an outer diameter D 1 Diameter D of impeller of 84mm 2 105mm.
Optionally, a volute tongue is arranged at the outlet of the volute, the volute tongue adopts a short tongue, and the clearance t between the top end of the volute tongue and the outer circumference of the impeller is 0.05-0.10D 2 =8.5 mm, the radius of the volute tongue tip arc is r=4 mm. The volute tongue is arranged to prevent gas from circularly flowing in the volute, and the volute tongue adopts a short tongue, so that the fan is suitable for fans with high rotating speeds; the radius of the arc at the top end of the volute tongue is set to be 4mm, so that the noise of the fan is reduced.
Optionally, the impeller rear disc is horn mouth shape, and impeller rear disc is close to preceding curb plate one side and is equipped with the water conservancy diversion head, and this water conservancy diversion head links to each other with the rotation axis is close to current collector one end. The rear disc of the impeller is arranged in a horn mouth shape, and the flow guide head is arranged, so that air flow can smoothly enter the impeller, and resistance is reduced.
Optionally, the distance between the rear of the impeller and the rear side plate is set to 7-12% of the width between the front side and the rear side plate. By limiting the distance between the rear side plate and the rear side plate of the impeller, vortex is avoided, flow loss is caused, and noise is reduced.
In summary, the beneficial effects of the invention are as follows:
1. the front disc of the impeller and the current collector are integrally cast or seamlessly connected, and a gap is reserved between the front disc and the blades, so that the structure is simple, the processing is convenient, the air at the high pressure side can not flow back to the low pressure side when the fan operates, the resistance loss of air flow to the blades near the wheel cover can be reduced, the effect of high rotation speed ratio is achieved, the noise of the fan can be reduced, and the air output and the air pressure of the fan can be improved;
2. the whole centrifugal ventilator has the advantages of small appearance, simple and reasonable structure, suitability for occasions with various space restrictions, high-speed and high-pressure effects and high operation efficiency.
Drawings
Fig. 1 is a perspective view of the present invention.
Fig. 2 is a cross-sectional perspective view of fig. 1.
Fig. 3 is a front view of fig. 1, as seen in the direction of the outlet of the volute.
Fig. 4 is a front view of the overall impeller structure of fig. 1.
Fig. 5 is an enlarged view at a in fig. 4.
Fig. 6 is a perspective view of a part of the structure of the impeller of fig. 1.
Fig. 7 is a front view of fig. 6.
Detailed Description
In order to enable those skilled in the art to better understand the present invention, the following description will make clear and complete descriptions of the technical solutions in the embodiments of the present invention with reference to the accompanying drawings in the embodiments of the present invention.
Referring to fig. 1 and 2, a centrifugal ventilator with a semi-open three-way impeller comprises a volute 10, an air inlet conduit 20, an air inlet 21, a collector 31, and an impeller assembly; the volute 10 is a metal shell and is provided with a front side plate 11 and a rear side plate 12; the air inlet conduit 20 is arranged on the front side plate 11, the air inlet conduit 20 is arranged vertical to the front side plate 11, and an air inlet 21 communicated with the space in the volute 10 is formed in the air inlet conduit 20; one end of the collector 31 is connected with the front side plate 11 or the air inlet conduit 20, and the other end extends into the volute 10 from the front side plate 11 to guide the air entering the impeller assembly; the impeller assembly is mounted within the volute 10 for increasing the gas pressure and exhausting the gas.
Referring specifically to fig. 1-4 and 6, the impeller assembly includes an impeller and a rotating shaft 41 connected to the impeller; the impeller adopts a semi-open impeller, is arranged in the volute 10 and comprises an impeller rear disc 42, blades and an impeller front disc 44; the impeller rear disc 42 is rotatably arranged in the volute 10, and the impeller rear disc 42 is in a horn-shaped shape; a plurality of the blades are welded on the impeller rear disc 42 and rotate synchronously with the impeller rear disc 42, the blades are positioned between the impeller front disc 44 and the impeller rear disc 42, and a gap is reserved between the blades and the impeller front disc 44; the impeller front disc 44 is positioned on one side of the impeller rear disc 42, which is close to the front side plate 11, the impeller front disc 44 is connected with one end of the current collector 31, which is close to the rear side plate 12, and is integrally cast or seamlessly connected with the current collector 31, no gap exists between the impeller front disc 44 and the current collector 31, the structure is simple, the processing is convenient, and the eddy current loss of the air flow at the inlet end of the impeller can be reduced; the rotation shaft 41 is in anti-rotation connection with the impeller rear disc 42 and is driven to rotate by a motor (not shown);
referring to FIG. 6, in some embodiments, the impeller is configured as a three-way impeller, converting a conventional one-way or two-way structure into a three-way structure, the impeller having an inlet outside diameter D 1 Diameter D of impeller =84 mm 2 =105 mm. Based on Computational Fluid Dynamics (CFD) technology, a flow field formed by a working medium when the working medium passes through the inside of the impeller is subjected to fine and accurate analysis, so that the shape of a blade most suitable for the working medium when the working medium passes through the impeller is generated, the flow field is improved, vortex in the impeller is reduced or eliminated, smooth gas flow in the impeller is ensured, and the working efficiency is greatly improved.
Referring to fig. 4 and 6, in some embodiments, the plurality of blades include long blades 431 and short blades 432, the long blades 431 and the short blades 432 are all three-way blades, the long blades 431 and the short blades 432 are arranged at intervals in a staggered manner, and the effect of the short blades 432 on the air flow splitting is utilized to avoid the formation of air flow vortex between the long blades 431, so that the output efficiency of the impeller air flow is improved; preferably, the number of long vanes 431 is 7, and the number of short vanes 432 is 7.
Referring to fig. 4 and 5, in some embodiments, the contour of the impeller front disc 44 is consistent with the curvature of the blade top line of the long blade 431 and the short blade 432 (the curvature of the impeller front disc is consistent with the curvature of the blade top of each blade), and the gaps between the front edges of the long blade 431 and the short blade 432 and the impeller front disc 44 are 0.5 mm-1 mm, so that the resistance loss of the airflow to the blades near the impeller front disc 44 is reduced, and the effect of high rotation speed ratio is achieved; preferably, the gap is set to 0.75mm, and the effect is optimal.
Referring to fig. 4, 6 and 7, in some embodiments, the long blade 431 and the short blade 432 have circular arc blade roots and are welded on the rear disc; the top ends of each long blade 431 and each short blade 432 are respectively perpendicular to the central axis, gas axially enters the impeller, the inlet angle of the blade is 30 degrees, the outlet angle of the blade is 90 degrees, and the torsion angle of each blade is 30 degrees from the inlet of the impeller to the impeller rear disc 42, so that the impeller is in a three-dimensional streamline shape; the twisting direction of each blade is consistent, so that the inlet impact loss of each blade and the separation loss of the tail edge of the blade are reduced, and the best aerodynamic performance of the blade is achieved.
Referring to fig. 1-4 and 6, in some embodiments, the diameter of the rotating shaft 41 is 20mm, the length of the rotating shaft is 47mm, a flow guiding head 51 is connected to one end of the outer diameter of the rotating shaft 41 near the current collector 31, and the flow guiding head 51 is located on one side of the impeller rear disc 42 near the front side plate 11, and the flow guiding head 51 is in a shape of a bullet, so that air flow can enter the impeller more smoothly, and resistance can be reduced.
Referring to fig. 1 and 6, in some embodiments, the front and rear side plates 11 and 12 of the volute 10 are drawn by archimedes spiral method, and the impeller outlet diameter D 2 Standard polar equation for archimedes' spiral is r (θ) =a+b×θ, =105 mm, pitch 42.86 mm; wherein b is an archimedes spiral coefficient representing the amount of increase (or decrease) in pole diameter per 1 degree of rotation; θ is the polar angle in degrees, representing the total number of degrees the archimedes spiral turns through; the variable a will change the spiral shape, b controls the distance between spirals, and b is typically constant.
Referring to fig. 1 and 3, in some embodiments, a volute tongue 13 is provided at the outlet of the volute 10, and the volute tongue 13 is a short tongueFor ventilators with high specific rotational speeds. The clearance t between the top end of the volute tongue 13 and the outer circumference of the impeller is (0.05-0.10) D 2 =8.5 mm, the radius of the arc at the tip of the volute tongue 13 is r=4 mm. The outlet of the volute 10 adopts a diffuser pipe, the height H1 of the outlet of the volute 10 is 85.7mm, the width L is 65mm, and the upper and lower heights H2 = 164.04mm of the whole volute 10 can achieve the diffusion effect.
Referring to fig. 2, in some embodiments, the distance between the impeller rear disc 42 and the rear side plate 12 is about 10% of the width of the front side plate 11 and the rear side plate 12, avoiding vortex generation, causing flow loss, and reducing noise; preferably, the impeller rear disc 42 is 5mm from the rear side plate 12.
The impeller is smaller with the spiral case design size for the structure of whole fan design is little and efficient, and then occupation space is little, is applicable to the occasion of multiple space restriction, and simple structure is reasonable, and the rotational speed is up to 27974rpm, can reach high speed ratio effect, and the total pressure is up to about 10000pa, and is with low costs, and the practicality is strong. Under the same working condition, the static pressure efficiency of the whole machine at the design working condition point of the traditional centrifugal fan is about 65%, and the static pressure efficiency of the whole machine running at the design working condition point can reach 70%.
The above-described embodiments do not limit the scope of the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the above embodiments should be included in the scope of the present invention.

Claims (7)

1. A centrifugal ventilator with semi-open type ternary impeller comprises
A volute (10) having a front side plate (11) and a rear side plate (12);
a current collector (31) with one end connected with the front side plate (11), and the other end of the current collector (31) extends from the front side plate (11) into the volute (10);
the impeller assembly is arranged in the volute (10) and comprises an impeller arranged in the volute (10) and a rotating shaft (41) connected with the impeller and driven by a motor;
the method is characterized in that: the impeller comprises an impeller rear disc (42) rotatably arranged in the volute (10), a plurality of blades connected with the impeller rear disc (42) and an impeller front disc (44) positioned on one side of the impeller rear disc (42) close to the front side plate (11); the blades are positioned between the impeller front disc (44) and the impeller rear disc (42), and a gap is formed between the front edge of the blades and the impeller front disc (44); the impeller front disc (44) is connected with one end of the current collector (31) far away from the front side plate (11), and the impeller front disc (44) and the current collector (31) are integrally cast or connected in a seamless manner;
the impeller is a three-way flow impeller, the curvature of the profile line of the blade top of the blade is the same as that of the profile line of the impeller front disc (44), and the gap between the blade top of the blade and the impeller front disc (44) is set to be 0.5 mm-1 mm;
the impeller rear disc (42) is in a horn mouth shape, a flow guide head (51) is arranged on one side of the impeller rear disc (42) close to the front side plate (11), and the flow guide head (51) is connected with one end of the rotating shaft (41) close to the current collector (31);
the distance between the impeller rear disc (42) and the rear side plate (12) is set to 7-12% of the width between the front side plate (11) and the rear side plate (12).
2. A centrifugal fan with a semi-open three-way impeller according to claim 1, wherein: the clearance between the tip of the blade and the impeller front plate (44) is set to 0.75mm.
3. A centrifugal fan with a semi-open three-way impeller according to claim 1, wherein: the inlet angle of the blade is 30 ° and the outlet angle of the blade is 90 °.
4. A centrifugal fan with a semi-open three-way impeller according to claim 1, wherein: the blades are three-dimensionally streamlined and uniformly twisted, and have a twist angle of 30 ° from the impeller inlet to the impeller back plate (42).
5. A centrifugal fan with a semi-open three-way impeller according to claim 1, wherein: the plurality of blades comprises long blades (431) and short blades (432), and the long blades (431) and the short blades (432) are arranged at staggered intervals.
6. A centrifugal fan with a semi-open three-way impeller according to claim 1, wherein: the impeller is a three-way impeller, and the outer diameter D of the inlet of the impeller 1 Diameter D of impeller of 84mm 2 105mm.
7. A centrifugal fan with a semi-open three-way impeller according to claim 6, wherein: a volute tongue (13) is arranged at the outlet of the volute (10), the volute tongue (13) adopts a short tongue, and a gap t between the top end of the volute tongue (13) and the outer circumference of the impeller is (0.05-0.10) D 2 The radius of the arc at the top end of the volute tongue (13) is r=4mm.
CN202110671544.0A 2021-06-17 2021-06-17 Centrifugal ventilator with semi-open type ternary impeller Active CN113446237B (en)

Priority Applications (1)

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CN202110671544.0A CN113446237B (en) 2021-06-17 2021-06-17 Centrifugal ventilator with semi-open type ternary impeller

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Application Number Priority Date Filing Date Title
CN202110671544.0A CN113446237B (en) 2021-06-17 2021-06-17 Centrifugal ventilator with semi-open type ternary impeller

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CN113446237B true CN113446237B (en) 2023-05-16

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CN114320962A (en) * 2021-11-10 2022-04-12 浙江环誉泵业科技有限公司 Cooling fan

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CN102562651A (en) * 2012-03-08 2012-07-11 江苏大学 High-efficiency wind-powered centrifugal pump impeller
CN203488441U (en) * 2013-06-08 2014-03-19 叶成铭 Low-noise fan
CN106402020A (en) * 2016-10-31 2017-02-15 广东威灵电机制造有限公司 Impeller and fan having same
CN207349143U (en) * 2017-10-23 2018-05-11 上海瑞晨环保科技有限公司 A kind of noise elimination high-speed centrifugal fan

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