CN215719781U - Centrifugal impeller and centrifugal fan - Google Patents

Abstract

The utility model discloses a centrifugal impeller and a centrifugal fan. The centrifugal impeller comprises a centrifugal impeller wheel cover, a wheel disc, a noise reduction structure and a plurality of main blades arranged between the wheel cover and the wheel disc, wherein the main blades are uniformly distributed along the circumferential direction of the wheel disc; the noise reduction structure and the main blades are arranged on two opposite sides of the wheel cover; the noise reduction structure comprises a plurality of noise reduction blades which are uniformly distributed along the circumferential direction of the wheel cover, and the noise reduction blades are of wing-shaped structures; the installation angles of the noise reduction blades and the main blades are both larger than 90 degrees or both smaller than 90 degrees. Through setting up the blade of making an uproar, can play the effect of making an uproar.

Description

Centrifugal impeller and centrifugal fan

Technical Field

The utility model relates to the technical field of fans, in particular to a centrifugal impeller and a centrifugal fan.

Background

The centrifugal fan is suitable for various ventilation and heat dissipation systems such as pipeline fans, heat dissipation fans, purification and ventilation systems and the like. The centrifugal fan comprises a centrifugal impeller and a motor driving the centrifugal impeller to rotate. Centrifugal impeller includes the wheel cap and sets up the blade in the downside of wheel cap, and the wheel cap is hollow structure, and this hollow structure forms the air intake, when the smooth surface entering air intake of wind process wheel cap, can produce the vortex noise, leads to centrifugal fan's noise great.

SUMMERY OF THE UTILITY MODEL

The technical problem to be solved by the embodiments of the present invention is to provide a centrifugal impeller and a centrifugal fan, aiming at the defect of high noise of the centrifugal impeller.

In order to solve the technical problem, an embodiment of the present invention provides a centrifugal impeller, including a shroud, a disk, a noise reduction structure, and a plurality of main blades arranged between the shroud and the disk, wherein the plurality of main blades are uniformly distributed along a circumferential direction of the disk;

the noise reduction structure and the main blade are arranged on two opposite sides of the wheel cover; the noise reduction structure comprises a plurality of noise reduction blades which are uniformly distributed along the circumferential direction of the wheel cover, and the noise reduction blades are of wing-shaped structures;

the installation angles of the noise reduction blades and the main blades are both larger than 90 degrees or both smaller than 90 degrees.

The absolute value range of the difference value between the installation angle of the noise reduction blade and the installation angle of the main blade is 3-7 degrees.

Wherein projections of any two adjacent noise reduction blades on an axial plane have an overlapping region; the axial plane is a plane passing through the axial lead of the wheel cover.

Wherein the wheel cover is of a hollow circular ring structure; the intersection line of the noise reduction blade and the wheel cover is an arc line, the arc line extends from the outer edge of the wheel cover to the inner edge of the wheel cover, and the minimum distance between the arc line and the inner edge of the wheel cover is larger than 0.

In the axial lead direction of the centrifugal impeller, the height of the wheel cover is gradually increased from the outer edge to the inner edge, and the height of the noise reduction blade is lower than that of the inner edge.

Wherein, in the extending direction from the outer edge of the wheel cover to the inner edge of the wheel cover, the height of the noise reduction blade on the wheel cover is gradually reduced.

An auxiliary blade is arranged between at least one group of adjacent two main blades, and the height of the auxiliary blade is smaller than that of the main blade; the mounting angles of the auxiliary blades and the main blades are both larger than 90 degrees or both smaller than 90 degrees; the auxiliary blade and the main blade are both wing-shaped structures;

the wheel disc is of a hollow circular ring structure, and the auxiliary blades are close to the outer periphery of the wheel disc and far away from the inner periphery of the wheel disc;

the minimum distance between the auxiliary blade and the inner periphery of the wheel disc is larger than the minimum distance between the main blade and the inner periphery of the wheel disc.

Wherein the ratio of the height of the auxiliary blade to the height of the main blade ranges from 40% to 60%;

the ratio of the surface area of the auxiliary blade to the surface area of the main blade ranges from 15% to 35%.

The number of the auxiliary blades is multiple, all the auxiliary blades are uniformly distributed along the circumferential direction of the wheel disc, and the number of the auxiliary blades is the same as that of the main blades;

the difference range of the installation angle of the auxiliary blade and the installation angle of the main blade is-3 degrees.

The embodiment of the utility model also provides a centrifugal fan which comprises a motor and the centrifugal impeller, wherein the motor is fixedly connected with the centrifugal impeller.

The embodiment of the utility model has the following beneficial effects: through setting up the blade of making an uproar that falls, block the wind that produces the vortex noise that gets into from the air intake of wheel cap, can play the effect of noise reduction.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.

Fig. 1 is a schematic structural view of an embodiment of a centrifugal impeller provided by the present invention.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

Fig. 1 is a schematic structural diagram of an embodiment of a centrifugal impeller according to the present invention.

The centrifugal impeller comprises a wheel cover 1, a wheel disc 2, a noise reduction structure and a plurality of main blades 3 arranged between the wheel cover 1 and the wheel disc 2, wherein the plurality of main blades 3 are uniformly distributed along the circumferential direction of the wheel disc; the noise reduction structure and the main blades 3 are arranged on two opposite sides of the wheel cover; the noise reduction structure comprises a plurality of noise reduction blades 5 which are uniformly distributed along the circumferential direction of the wheel cover, and the noise reduction blades 5 are of wing-shaped structures; the installation angles of the noise reduction blades 5 and the main blades 3 are both larger than 90 degrees or both smaller than 90 degrees.

The installation angle refers to an included angle between an outer side extension line of the blade and a tangent line of the rotation direction of the point of the blade in the opposite direction when viewed from the radial section of the wind wheel. The impeller with the mounting angle larger than 90 degrees is a forward-inclined impeller, and the impeller with the mounting angle smaller than 90 degrees is a backward-inclined impeller. The embodiment of the utility model can preferably select the installation angles of the noise reduction blades 5 and the main blades 3 to be less than 90 degrees.

According to the embodiment of the utility model, the noise reduction blade is arranged to block the wind which enters from the air inlet of the wheel cover and generates the turbulent flow noise, so that the noise reduction effect can be achieved.

In order to reduce noise better, the absolute value range of the difference value between the installation angle of the noise reduction blade 5 and the installation angle of the main blade 3 is 3-7 degrees.

Preferably, the projections of any two adjacent noise reduction blades 5 on the axial plane have an overlapping region; the axial plane is a plane passing through the axial center line of the wheel cover 1. This prevents a gap from being formed between two adjacent noise reduction blades 5, which would cause airflow to enter the intake opening through the gap, resulting in increased noise.

Preferably, the wheel cover 1 is a hollow circular ring structure; the connecting line of the noise reduction blades 5 and the wheel cover 1 is an arc line, the arc line extends from the outer edge 11 of the wheel cover 1 to the inner edge 12 of the wheel cover 1, and the minimum distance between the arc line and the inner edge 12 of the wheel cover 1 is larger than 0.

Preferably, the height of the shroud 1 is gradually increased from the outer edge 11 to the inner edge 12 in the axial direction of the centrifugal impeller, and the height of the noise reduction blades 5 is lower than the height of the inner edge 12. Such as the noise reduction blades 5 having a height greater than the height of the inner edge 12, may have an impact on the installation of other components of the centrifugal motor.

Further, since the height of the shroud 1 gradually increases from the outer edge 11 to the inner edge 12, the height of the noise reduction blades 5 protruding from the shroud 1 in the extending direction from the outer edge 11 of the shroud 1 to the inner edge 12 of the shroud 1 may be gradually reduced for the sake of beauty and reduction in material cost. In the axial lead direction of the centrifugal impeller, the protrusion height specifically refers to the distance between the top of the noise reduction blade 5 and the connecting line of the noise reduction blade and the shroud 1.

In addition, as a more preferable embodiment, an auxiliary blade 4 is arranged between at least one group of two adjacent main blades 3, and the height of the auxiliary blade 4 is smaller than that of the main blades 3; the installation angles of the auxiliary blades 4 and the main blades 3 are both larger than 90 degrees or both smaller than 90 degrees; the auxiliary blades 4 and the main blades 3 are both wing-shaped structures; the disk 2 is a hollow circular ring structure, and the auxiliary blades 4 are close to the outer periphery 21 of the disk 2 and far away from the inner periphery 22 of the disk 2. The embodiment of the present invention may preferably set the installation angles of the auxiliary blade 4 and the main blade 3 to be less than 90 degrees. The auxiliary blade 4 is arranged between two adjacent main blades 3, so that the wind pressure at the radial outlet of the centrifugal impeller can be increased; meanwhile, the height of the auxiliary blade 4 is smaller than that of the main blade 3, the auxiliary blade 4 is close to the outer periphery 21 of the wheel disc 2, the inner periphery 22 far away from the wheel disc 2 can reduce the blocking effect of the auxiliary blade 4 on the wind of the air outlet, the increased wind pressure and the increased wind volume can be released outwards smoothly through the air outlet, and finally the wind pressure and the wind volume outside the air outlet are increased.

Preferably, the minimum distance between the auxiliary blades 4 to the inner periphery 22 of the disk 2 is greater than the minimum distance between the primary blades 3 to the inner periphery 22 of the disk 2. In this case, the blocking effect of the auxiliary blade 4 to the wind of the wind outlet can be further reduced.

Preferably, the ratio of the height of the auxiliary blade 4 to the height of the main blade 3 ranges from 40% to 60%; the ratio of the surface area of the auxiliary blade 4 to the surface area of the main blade 3 ranges from 15% to 35%. The inventor verifies that the two ratio ranges can enable the wind pressure and the wind volume outside the air outlet between the two main blades 3 to reach the maximum range. Wherein, the optimal ratio range of the height of the auxiliary blade 4 to the height of the main blade 3 is 45-55%. The optimal ratio of the surface area of the auxiliary blade 4 to the surface area of the main blade 3 is in the range of 20% to 30%.

Preferably, the number of the auxiliary blades 4 is plural, and all the auxiliary blades 4 are uniformly distributed along the circumferential direction of the disk 2, and the number of the auxiliary blades 4 is the same as that of the main blades 3. Thus, an auxiliary blade 4 is disposed between any two adjacent main blades 3. The number of the auxiliary blades 4 and the main blades 3 can be 7, and 175 impellers are formed. The auxiliary blades 4 are uniformly distributed along the circumferential direction of the wheel disc 2, so that the air output and the air pressure of each air outlet are uniform, and the vibration of the centrifugal impeller caused by the non-uniform air output and the air pressure of each air outlet is avoided.

Preferably, the difference between the installation angle of the auxiliary blade 4 and the installation angle of the main blade 3 is-3 to 3 degrees. The inventor verifies that the absolute value of the difference between the installation angle of the auxiliary blade 4 and the installation angle of the main blade 3 exceeds 3, so that the wind resistance is overlarge, and a larger air output can be achieved when the difference is in a range of-3 to 3 degrees.

Preferably, the auxiliary blades 4 are integrally formed with the disk 2, and the main blades 3 are integrally formed with the shroud 1; the wheel disc 2 and the wheel cover 1 can be fixedly connected through ultrasonic riveting.

While the utility model has been described with reference to a preferred embodiment, it will be understood by those skilled in the art that various changes in form and detail may be made therein without departing from the spirit and scope of the utility model.

Claims (10)

1. The centrifugal impeller is characterized by comprising an impeller cover, a wheel disc, a noise reduction structure and a plurality of main blades arranged between the impeller cover and the wheel disc, wherein the main blades are uniformly distributed along the circumferential direction of the wheel disc;

the noise reduction structure and the main blade are arranged on two opposite sides of the wheel cover; the noise reduction structure comprises a plurality of noise reduction blades which are uniformly distributed along the circumferential direction of the wheel cover, and the noise reduction blades are of wing-shaped structures;

the installation angles of the noise reduction blades and the main blades are both larger than 90 degrees or both smaller than 90 degrees.

2. The centrifugal impeller as recited in claim 1, wherein the absolute value of the difference between the stagger angle of the noise reduction blades and the stagger angle of the main blades is in the range of 3-7 degrees.

3. The centrifugal impeller according to claim 1, wherein projections of any two adjacent noise reduction blades on an axial plane have an overlapping region; the axial plane is a plane passing through the axial lead of the wheel cover.

4. The centrifugal impeller of claim 1, wherein said shroud is a hollow annular structure; the intersection line of the noise reduction blade and the wheel cover is an arc line, the arc line extends from the outer edge of the wheel cover to the inner edge of the wheel cover, and the minimum distance between the arc line and the inner edge of the wheel cover is larger than 0.

5. The centrifugal impeller according to claim 1, wherein the height of the shroud is gradually increased from the outer edge of the shroud toward the inner edge of the shroud in the axial direction of the centrifugal impeller, and the height of the noise reduction blades is lower than the height of the inner edge.

6. The centrifugal impeller according to claim 5, wherein the noise reduction blades have a gradually decreasing height of projection on the shroud in a direction extending from the outer edge of the shroud toward the inner edge of the shroud.

7. The centrifugal impeller as recited in claim 1, wherein an auxiliary vane is disposed between at least one adjacent set of two of the main vanes, the auxiliary vane having a height less than a height of the main vanes; the mounting angles of the auxiliary blades and the main blades are both larger than 90 degrees or both smaller than 90 degrees; the auxiliary blade and the main blade are both wing-shaped structures;

the wheel disc is of a hollow circular ring structure, and the auxiliary blades are close to the outer periphery of the wheel disc and far away from the inner periphery of the wheel disc;

the minimum distance between the auxiliary blade and the inner periphery of the wheel disc is larger than the minimum distance between the main blade and the inner periphery of the wheel disc.

8. The centrifugal impeller of claim 7, wherein the ratio of the height of said auxiliary vanes to the height of said main vanes ranges from 40% to 60%;

the ratio of the surface area of the auxiliary blade to the surface area of the main blade ranges from 15% to 35%.

9. The centrifugal impeller according to claim 7, wherein the number of the auxiliary blades is plural, and all the auxiliary blades are uniformly distributed in the circumferential direction of the disk, and the number of the auxiliary blades is the same as that of the main blades;

the difference range of the installation angle of the auxiliary blade and the installation angle of the main blade is-3 degrees.

10. A centrifugal fan comprising a motor and a centrifugal impeller according to any one of claims 1-9, the motor being fixedly connected to the centrifugal impeller.

Images