CN209943142U - Efficient flow-protecting channel centrifugal fan - Google Patents
Efficient flow-protecting channel centrifugal fan Download PDFInfo
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Abstract
The utility model discloses an efficient guarantor's runner centrifugal fan, including centrifugal impeller, spiral case and front shroud, centrifugal impeller is located inside spiral case and the front shroud. The surface of the blade of the centrifugal impeller is provided with a raised flow protection channel sheet which is positioned on the windward side. The scheme adopts the flow-protecting channel sheet and the volute to improve the efficiency of the fan and reduce the size of the fan, so that the centrifugal fan has higher efficiency, more stable working characteristics and more compact appearance, and has more competitiveness compared with similar products.
Description
Technical Field
The utility model belongs to the centrifugal fan field, specifically speaking are guarantor runner centrifugal fan based on high-efficient pneumatic design.
Background
The centrifugal fan has the advantages of compact structure, large flow coefficient, high pressure rise coefficient and the like, and is widely used for ventilation, dust exhaust and cooling of factories, mines, tunnels, cooling towers, vehicles, ships and buildings; ventilation and draught of boilers and industrial furnaces; cooling and ventilation in air conditioning equipment and household appliances; drying and selecting grains; wind tunnel wind source and air cushion boat inflation and propulsion. Along with the improvement of the life quality of people and the improvement of the standard requirements of the industry on household appliances and equipment, the centrifugal fan has the advantages of high efficiency, stability and compactness and becomes the main development direction and pursuit target of the centrifugal fan.
The existing centrifugal fan mostly adopts a design without an air guide wheel. The function of the inducer of the centrifugal fan is to use the blades to change the air flow from axial air inlet to radial air outlet, because the supercharging ratio of the centrifugal fan is generally lower, the blades of the centrifugal fan are generally designed without the inducer for the reasons of simple structure, convenient processing, high flux and the like, and the blades of the centrifugal fan are straight blades. Although the design scheme is convenient to develop, process and manufacture and saves the processing cost, the problem exists that the axial conversion of the airflow into the radial direction is purely generated by the action of the bladeless section, the airflow is not guided to directly turn in a large angle, and an uneven airflow angle is easily generated at the front edge of the centrifugal blade, so that the adaptability of the attack angle of the straight blade in the pure radial section is poor, the pneumatic stability of the centrifugal fan is influenced, and in addition, the mutual mixing of the airflows can cause a part of energy dissipation, so that the efficiency of the centrifugal fan is reduced.
The main components of the centrifugal fan include a volute portion in addition to the impeller, the volute functioning to collect the airflow at the outlet of the impeller and provide a certain pressure rise. Conventional volutes are largely divided into two types: a constant-section volute and a variable-section volute. The flow cross section of the constant-section volute is not changed along the circumferential direction, the cross-sectional area is determined according to the maximum flow of the compressor, the structure is simple, the size is large, pressure rise is hardly provided, and in addition, because the airflow at the outlet of the impeller has circumferential nonuniformity, the volute with uniform circumferential direction conversely causes the flow loss of the airflow to be increased. The flow cross section of the variable cross-section volute is larger closer to the outlet along the circumferential direction, the external dimension of the variable cross-section volute is superior to that of the constant cross-section volute at the position of the minimum cross section, but the outlet cross section is not different from the constant cross-section volute, the overall dimension is reduced to a certain extent, and still certain limitation is realized.
Therefore, in order to solve the above technical problems, it is necessary to develop a new centrifugal fan, which has a simple structure and is convenient to process, and can realize the characteristics of high efficiency, stability and compactness by means of an advanced pneumatic design method.
Disclosure of Invention
The utility model provides an efficient guarantor's runner centrifugal fan, its purpose adopts simple structure just can realize the smooth guide to the air current in the centrifugal fan, makes centrifugal fan have higher efficiency, more stable operating characteristic and compacter appearance, makes this centrifugal fan compare the product of the same kind more competitive power.
The utility model provides a technical scheme that above-mentioned technical problem adopted does: an efficient flow-protection channel centrifugal fan comprises a centrifugal impeller, a volute and a front cover plate, wherein the centrifugal impeller is located inside the volute and the front cover plate. The surface of the blade of the centrifugal impeller is provided with a raised flow protection channel sheet which is positioned on the windward side. The scheme adopts the flow protection channel sheet and the volute to improve the efficiency of the fan and reduce the size of the fan.
In order to optimize the technical proposal, the utility model discloses still include following modified technical proposal.
The flow-retaining sheets are arranged at equal intervals along the height of the blades, and the number N1 of the flow-retaining sheets is 1 to 5.
The ratio of the thickness T1 of the flow-protection sheet to the thickness T2 of the blade is 0.3 to 3.0; the ratio of the length L1 of the flow-protection sheet to the length L2 of the blade is 0.1 to 0.4; the ratio of the width W1 of the flow channel maintaining sheet to the height W2 of the blade is 0.1 to 0.3.
The ratio of the installation distance D1 of the flow-protection sheet to the length L2 of the blade is 0.0 to 0.25.
The volute has a volute flow channel inside and surrounding the centrifugal impeller, and the volute flow channel is divided into a section gradual change section AC and a section approximate section AB.
The section approximating section AB is a flow passage having a similar sectional area between the section a and the outlet section B, and a ratio of an area R2 of any one section of the section approximating section AB to an area R1 of the section a is 0.95 to 1.05.
The connecting line of the center of the minimum section C in the section transition section AC and the axis center is a straight line PO, and the connecting line of the center of the section A and the axis center is a straight line QO; the angle formed by line PO and line QO POQ is 60-180 deg.
The connecting line of the center of the outlet section B and the axis center in the section approximate section AB is a straight line SO; the included angle SOP formed by the straight line SO and the straight line PO is 5-30 degrees.
Compared with the prior art, the utility model has the advantages of it is following:
1. the structure which is simple and low in processing difficulty is utilized, the flow of air flow in the impeller channel is optimized, the overall pneumatic stability and efficiency of the centrifugal fan are improved, and the centrifugal fan has higher reliability and economical efficiency;
2. the overall structure size of the centrifugal fan is optimized, the centrifugal fan is more compact, and the application range of the centrifugal fan is widened.
Drawings
FIG. 1 is an overall schematic view of a centrifugal fan with a flow protection channel.
FIG. 2 is an explanatory diagram of technical parameters of the channel-protecting sheet.
Fig. 3 is a schematic diagram of the structure of the volute.
Wherein the reference numerals are: the centrifugal impeller comprises a centrifugal impeller 1, blades 11, a flow protection channel sheet 2, a volute 3 and a front cover plate 4.
Detailed Description
Embodiments of the present invention are described in further detail below with reference to the accompanying drawings.
The utility model discloses a protect runner centrifugal fan mainly includes centrifugal impeller 1, protects runner piece 2, spiral case 3 and front shroud 4. The flow channel-retaining sheet 2 is fixed to the surface of the blade 11 of the centrifugal impeller 1 and is positioned on the windward side of the blade 11. The centrifugal impeller 1 is located inside the volute 3 and the front cover plate 4.
The conventional centrifugal fan impeller adopts a straight blade design, the front edge line of the straight blade is parallel to the axial direction, a smaller turning radius exists in the axial turning radial section of a fan inlet, the pressure at the position with a larger radius is larger than that at the position with a smaller radius so as to provide the centripetal force required by airflow turning, the total pressure of all meridional flow lines of the inlet is basically equal, the meridional speed of the airflow at the blade root of the inlet of the centrifugal fan is lower than that of the blade tip, and the straight blade design inevitably causes that the angle of the straight blade and the angle of the airflow cannot be completely matched along the blade height direction because the linear speed of the rotation of the straight blade under the same radius is the same, and the airflows along the blade height direction. The utility model discloses a set up the way of guarantor channel piece 2 at 11 windward sides of blade, can prevent the mixing of air current along the blade height direction to improve the mobile state in the centrifugal impeller 1.
As shown in fig. 2, the flow-retaining sheets 2 are arranged at equal intervals along the leaf height, and the number N1 is 1 to 5. The ratio of the thickness T1 of the flow-protection sheet 2 to the thickness T2 of the blade 11 is 0.3 to 3.0; the ratio of the length L1 of the flow-retaining strip 2 to the length L2 of the blade 11 is 0.1 to 0.4. The ratio of the width W1 of the flow-retaining strip 2 to the height W2 of the blade 11 is 0.1 to 0.3. The ratio of the installation distance D1 of the flow-protection plate 2 to the length L2 of the blade 11 is 0.0 to 0.25.
The conventional volute 3 is usually designed to be of a uniform section or a variable section, the uniform-section volute 3 is simple in structure, but is large in size, hardly provides pressure rise, and moreover, because the airflow at the outlet of the impeller has circumferential nonuniformity, the circumferentially uniform volute 3 conversely makes the flow loss of the airflow large. The overall size of the variable-section volute 3 is reduced, but the variable-section volute is still limited by the section of the outlet, and in addition, because the variable-section volute 3 provides a certain pressure rise, the outlet is easy to generate a backflow phenomenon, and the performance of the fan is reduced. The utility model discloses a spiral case 3 design has synthesized the characteristics of two kinds of spiral cases 3, adopts partial variable cross section design and partial accurate cross section design such as waiting, has compromise the inhomogeneity of circumference air current, has guaranteed sufficient pressure boost ability, is unlikely to again to the pressure rise too big export arouses the backward flow, and variable cross section spiral case 3 has obtained further reduction to its size simultaneously.
As shown in fig. 3, the volute 3 has a volute flow path inside around the centrifugal impeller 1, which is divided into a gradual cross-sectional segment AC and an approximate cross-sectional segment AB. The section approximating section AB is a flow passage having a similar sectional area between the section a and the outlet section B, and the ratio of the area R2 of any one of the sections to the area R1 of the section a is 0.95 to 1.05.
The connecting line of the center of the minimum section C in the section transition section AC and the axis center is a straight line PO, and the connecting line of the center of the section A and the axis center is a straight line QO; the angle formed by line PO and line QO POQ is 60-180 deg.
The connecting line of the center of the outlet section B and the axis center in the section approximate section AB is a straight line SO; the included angle SOP formed by the straight line SO and the straight line PO is 5-30 degrees.
In the specific implementation process, the following method is adopted to determine the specific design scheme:
1. when designing the centrifugal fan with the protective channel according to the utility model, the number of the protective channel pieces 2 is determined by adopting a Computational Fluid Dynamics (CFD) method, and the specific number can be 1, 2, 3, 4 or 5;
2. determining shape parameters of the flow protection channel sheet 2 by adopting a Computational Fluid Dynamics (CFD) method, and respectively determining the thickness, the length and the width of the flow protection channel sheet 2 according to the thickness of a blade 11, the length of the blade 11 and the height of the blade of the centrifugal impeller 1, wherein the ratio of the thickness T1 of the flow protection channel sheet 2 to the thickness T2 of the blade 11 of the centrifugal impeller 1 is in a range of 0.3-3.0; the ratio of the length L1 to the length L2 of the blades 11 of the centrifugal impeller 1 ranges from 0.1 to 0.4; the ratio of the width W1 to the height W2 of the blades 11 of the centrifugal impeller 1 ranges from 0.1 to 0.3;
3. determining the installation distance D1 of the flow-protection channel plate 2 by adopting a computational fluid dynamics CFD method, wherein the ratio of D1 to the length L2 of the blade 11 is in the range of 0.0 to 0.25;
4. designing a volute 3 by adopting a Computational Fluid Dynamics (CFD) method, determining the position of a starting section A of a flow protection channel, wherein the connecting line of the center of a minimum section C and the axis center is PO, the connecting line of the center of the section A and the axis center is QO, and an included angle POQ formed by PO and QO ranges from 60 degrees to 180 degrees;
5. and determining the position of the outlet section B by adopting a Computational Fluid Dynamics (CFD) method, wherein the connecting line of the center of the outlet section B and the center of the axis is SO, and the included angle SOP formed by SO and PO ranges from 5 degrees to 30 degrees.
While the preferred embodiments of the present invention have been illustrated, various changes and modifications may be made by those skilled in the art without departing from the scope of the present invention.
Claims (8)
1. The utility model provides a runner centrifugal fan is protected to efficient, includes centrifugal impeller (1), spiral case (3) and front shroud (4), and inside centrifugal impeller (1) was located spiral case (3) and front shroud (4), characterized by: the surface of a blade (11) of the centrifugal impeller (1) is provided with a raised flow protection sheet (2), and the flow protection sheet (2) is positioned on the windward side.
2. The flow channel protection centrifugal fan of claim 1, wherein: the flow channel protection sheets (2) are arranged at equal intervals along the height of the blades (11), and the number N1 is 1-5.
3. The flow channel protection centrifugal fan of claim 2, wherein: the ratio of the thickness T1 of the flow channel protection sheet (2) to the thickness T2 of the blade (11) is 0.3 to 3.0; the ratio of the length L1 of the flow channel protection sheet (2) to the length L2 of the blade (11) is 0.1 to 0.4; the ratio of the width W1 of the flow channel protection sheet (2) to the height W2 of the blade (11) is 0.1 to 0.3.
4. The flow channel protection centrifugal fan of claim 2, wherein: the ratio of the installation distance D1 of the flow-protection sheet (2) to the length L2 of the blade (11) is 0.0 to 0.25.
5. The flow channel protection centrifugal fan of claim 1, wherein: the volute (3) is internally provided with a volute flow channel surrounding the centrifugal impeller (1), and the volute flow channel is divided into a section gradual change section AC and a section approximate section AB.
6. The flow channel protection centrifugal fan of claim 5, wherein: the section approximate section AB adopts a flow passage with similar sectional area between the section A and the outlet section B, and the ratio of the area R2 of any section in the section approximate section AB to the area R1 of the section A is 0.95 to 1.05.
7. The flow channel protection centrifugal fan of claim 5, wherein: the connecting line of the center of the minimum section C in the section transition section AC and the axis center is a straight line PO, and the connecting line of the center of the section A and the axis center is a straight line QO; the angle formed by line PO and line QO POQ is 60-180 deg.
8. The flow channel protection centrifugal fan of claim 7, wherein: the connecting line of the center of the outlet section B in the section approximate section AB and the axis center is a straight line SO; the included angle SOP formed by the straight line SO and the straight line PO is 5-30 degrees.
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| CN201920408415.0U CN209943142U (en) | 2019-03-28 | 2019-03-28 | Efficient flow-protecting channel centrifugal fan |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109989926A (en) * | 2019-03-28 | 2019-07-09 | 宁波纽新克电机股份有限公司 | A high-efficiency flow-preserving centrifugal fan |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109989926A (en) * | 2019-03-28 | 2019-07-09 | 宁波纽新克电机股份有限公司 | A high-efficiency flow-preserving centrifugal fan |
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