CN217354888U - Blade and fan - Google Patents

Abstract

The present disclosure relates to a blade and a fan. The blade (10) comprises: a low pressure side surface (12) and a high pressure side surface (14); a plurality of fluid passages (30) extending from the high-pressure side surface (14) to the low-pressure side surface (12) through the thickness of the blade (10); and a moving body (20) movably disposed in the blade (10) and adapted to move according to a rotation speed of the blade (10) during rotation of the blade (10) to change opening degrees of the plurality of fluid passages (30). According to the blade of the present disclosure, the performance of the fan can be significantly improved.

Description

Blade and fan

Technical Field

Embodiments of the present disclosure relate generally to fans and, in particular, to blades for fans.

Background

Fans are widely used in various apparatuses. The conventional fan has a fixed blade angle, which generates a loud noise and reduces efficiency when the fan is rotated at a high speed. It is desirable to provide fan efficiency and reduce fan noise.

Disclosure of Invention

Embodiments of the present disclosure provide a blade and a fan that aim to address one or more of the above problems, as well as other potential problems.

According to a first aspect of the present disclosure, a blade is provided. The blade includes: a low pressure side surface and a high pressure side surface; a plurality of fluid passages extending through a thickness of the vane from a high pressure side surface to the low pressure side surface; and a moving body movably disposed in the vane and adapted to move to change an opening degree of the plurality of fluid passages according to a rotation speed of the vane during rotation of the vane.

According to the blade of the embodiment of the present disclosure, by providing the fluid passages on the blade and moving by the moving body according to the rotation speed of the blade to adaptively change the opening degrees of the plurality of fluid passages, it is possible to significantly improve the performance of the fan, and in particular, it is possible to maintain the efficiency of the fan at a low speed while improving the fluid efficiency of the fan at a high speed and reducing noise.

In some embodiments, the blade comprises: a plurality of inlet grooves provided on the high pressure side surface at intervals from each other, a cavity communicating with the inlet grooves and receiving the moving body; and a plurality of outlet slots disposed spaced apart from each other on the low pressure side surface and communicating with the cavity, each inlet slot and each outlet slot being arranged in correspondence with each other to form a respective fluid passage.

In some embodiments, the plurality of inlet slots and the plurality of outlet slots are each aligned in a radial direction of the blade.

In some embodiments, each of the inlet slots communicates substantially perpendicularly to the cavity at the high pressure side surface.

In some embodiments, each of the outlet slots communicates to the cavity substantially parallel to the low pressure side surface.

In some embodiments, each of the outlet slots is disposed downstream in the direction of fluid flow relative to the inlet slot.

In some embodiments, the moving body includes a plurality of tuning channels spaced apart from each other, wherein each tuning channel is arranged in correspondence with each fluid channel, wherein the moving body blocks the fluid channel when the vane rotates at a first speed, and the tuning channels are aligned with the fluid channel when the vane rotates at a second speed higher than the first speed.

In some embodiments, each of the tuning channels includes an inlet side opening adjacent to the inlet slot, an outlet side opening adjacent to the outlet slot, and a channel portion connecting the inlet side opening and the outlet side opening, wherein a curvature of the inlet side opening is formed to match a curvature of the inlet slot, and the outlet side opening is substantially parallel to the low pressure side surface.

In some embodiments, the mover is resiliently loaded in the cavity, and the mover is movable under centrifugal force of rotation of the blades.

In some embodiments, the mobile body is loaded in the cavity via a radially biased spring, wherein the preload force of the spring is set such that: the moving body is held at a radially inner position and closes the plurality of fluid passages when the rotation speed of the blade is less than a predetermined threshold value; the movable body moves toward the radially outer position by a centrifugal force to increase the opening degrees of the plurality of fluid passages when the rotation speed of the vane exceeds a predetermined threshold value, and the opening degrees of the plurality of fluid passages are maximized when the movable body is at the radially outermost position.

In some embodiments, the plurality of fluid channels are formed in the blade at a location adjacent to where a fluid vortex is formed.

In some embodiments, the plurality of fluid channels are formed in a region 1/3-1/2 from a trailing edge of the blade in a fluid flow direction relative to a circumferential length of the blade.

According to a second aspect of the present disclosure, a fan is provided. The fan comprises a plurality of blades according to the first aspect.

Drawings

The above and other objects, features and advantages of the embodiments of the present disclosure will become readily apparent from the following detailed description read in conjunction with the accompanying drawings. In the drawings, several embodiments of the present disclosure are illustrated by way of example and not by way of limitation.

Fig. 1 shows an overall structural schematic diagram of a fan according to the present disclosure.

FIG. 2 shows a schematic structural view of a blade according to an embodiment of the present disclosure.

FIG. 3 illustrates a cross-sectional schematic view of a fluid passage disposed on a blade according to an embodiment of the present disclosure.

Fig. 4 illustrates an overall structural schematic diagram of a moving body according to an embodiment of the present disclosure.

Fig. 5 illustrates a schematic structure of a tuning channel of a moving body according to an embodiment of the present disclosure.

FIG. 6 illustrates a perspective view of a blade with a fluid passage in a closed state according to an embodiment of the present disclosure.

FIG. 7 illustrates a perspective view of a blade with a fluid passage in an open state according to an embodiment of the present disclosure.

Fig. 8 illustrates a fluid flow simulation effect diagram without a fluid channel according to an embodiment of the present disclosure.

Fig. 9 illustrates a fluid flow simulation effect diagram of providing a fluid channel according to an embodiment of the present disclosure.

Like or corresponding reference characters designate like or corresponding parts throughout the several views.

Detailed Description

Preferred embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. While the preferred embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.

The term "include" and variations thereof as used herein is meant to be inclusive in an open-ended manner, i.e., "including but not limited to". Unless specifically stated otherwise, the term "or" means "and/or". The term "based on" means "based at least in part on". The terms "one example embodiment" and "one embodiment" mean "at least one example embodiment". The term "another embodiment" means "at least one additional embodiment". The terms "upper," "lower," "front," "rear," and the like, refer to placement or positional relationships based on the orientation or positional relationship shown in the drawings, merely for convenience in describing the principles of the disclosure, and do not indicate or imply that the referenced elements must be in a particular orientation, constructed or operated in a particular orientation, and therefore should not be taken as limiting the disclosure.

As described above, the conventional fan generates a great noise when rotating at a high speed, and the operating efficiency of the fan is seriously affected. The inventors of the present application found out through a large number of experiments that the causes of these noises are as follows. Typically the blade angle of a fan is fixed and when the blade angle of attack is greater than the design point, fluid flow splits and vortices occur behind the blades. When the fan speed is above the design speed, the vortex flow and separated fluid flow create additional aerodynamic noise and the fan blade efficiency is far below the design point. In view of this, the inventors propose a method of improving the operating efficiency of the fan and reducing noise, and in particular, a method of improving the operating efficiency of the fan and reducing noise by improving the structure of the blades to reduce or prevent vortex formation. The inventive concepts according to embodiments of the present disclosure are described in detail below with reference to the accompanying drawings.

Fig. 1 shows a schematic structural diagram of a fan 100 capable of implementing an embodiment according to the present disclosure. As shown in fig. 1, the fan 100 includes a plurality of blades 10, the blades 10 being fixedly mounted to a hub of the fan and the blades 10 extending from a radially inner side toward a radially outer side.

The electric machine of the fan 100 operates to drive the blades 10 to rotate about the circumference and create a low pressure region and a high pressure region of fluid flow, from which the fluid flow will flow to the high pressure region. It is worth noting that although the axial flow fan is illustrated in the illustrated embodiment as an example to illustrate the inventive concept according to the embodiments of the present disclosure, the embodiments according to the present disclosure can be applied to other types of fans as well.

A schematic structural view of a blade 10 according to an embodiment of the present disclosure is described below with reference to fig. 2-3. As shown in FIG. 2, the blade 10 includes a low pressure side surface 12 and a high pressure side surface 14. The high pressure side surface 14 and the low pressure side surface 12 are opposing surfaces, in particular, the high pressure side surface 14 is the surface where the fluid flows into the blade where it hits the blade; the low pressure side surface 12 is the surface where the fluid exits the vane where it flows away from the vane. A plurality of fluid passages 30 extend through the thickness of the blade 10 from the high pressure side surface 14 to the low pressure side surface 12. The blade 10 may be mounted to the hub of the fan at a radially inner position R1; the blade 10 is free at a radially outer position R2. Also shown in FIG. 2 are the fluid flow direction leading edge P1 and the fluid flow direction trailing edge P2 of the blade 10. When the fan is operating, fluid flows from the leading edge P1 of the blade 10 toward the downstream trailing edge P2.

In some embodiments, a plurality of fluid passages 30 are formed in the blade 10 in the direction of fluid flow at or near a location in the blade where fluid vortices are prone to form. By providing the fluid passage 30 at a position where a vortex is easily formed, the formation of the vortex can be effectively prevented, thereby improving the flow efficiency of the fan and reducing the noise of the fan.

In some embodiments, the plurality of fluid passages 30 are formed in a region from the trailing edge 1/3-1/2 in the fluid flow direction of the blade 10 relative to the circumferential length of the blade 10. The inventors have found experimentally that these regions are effective in avoiding or reducing the formation of vortices and reducing the noise of the fan.

As shown in fig. 3, the blade 10 may further include a cavity 16, and the mover 20 is disposed in the cavity 16. The mover 20 is movably disposed in the cavity 16. The moving body 20 moves according to the rotation speed of the blade 10 during the rotation of the blade 10 to change the opening degrees of the plurality of fluid passages 30. For example, when the blade 10 rotates at a low speed, the moving body 20 may be held at the radially inner position R1 of the blade 10; when the blade 10 rotates at a high speed, the moving body 20 is moved from the radially inner position R1 toward the radially outer position R2 by the increased centrifugal force. Thereby, the opening degree of the fluid passage 30 can be adjusted by the position of the moving body.

In some embodiments, as shown in FIG. 3, a plurality of inlet slots 142 may be disposed on the high pressure side surface 14 spaced apart from one another. Each inlet slot 142 has a radially extending length and allows fluid to enter the cavity. A plurality of outlet grooves 122 are provided on the low pressure side surface 12 at intervals from each other. Similarly, each outlet slot 122 has a radially extending length and allows fluid to flow out of the cavity. Each inlet slot 142 and each outlet slot 122 are arranged in correspondence with each other to form a respective fluid channel 30. The cavity 16 may be disposed intermediate the walls of the blade and in communication with the inlet slot 142, the outlet slot 122. It is worth noting that although in the embodiment shown in fig. 2 and 3, the blade 10 may include a plurality of fluid passages 30; the number of the fluid passages 30 is not limited, and the number of the fluid passages 30 may be one or more.

In some embodiments, the arrangement of the plurality of inlet slots 142 and the plurality of outlet slots 122 is arranged in a manner that minimizes flow resistance. In this case, the influence of the arrangement of the inlet tank 142 and the outlet tank 122 on the fluid flow efficiency can be reduced as much as possible. In the embodiment shown in fig. 2 and 3, the plurality of inlet slots 142 and the plurality of outlet slots 122 are respectively aligned in a straight line along the radial direction of the blade 10. In this case, the inlet slots 142 and the outlet slots 122 may reduce slot-induced turbulence. Further, although in the illustrated embodiment, only one row of inlet and outlet slots 142, 122 is provided, it should be appreciated that this is merely exemplary and that in other embodiments, multiple rows of inlet and outlet slots 142, 122 may be provided and inventive concepts according to the present disclosure may be implemented.

In some embodiments, the manner of opening of inlet slot 142 is provided in a manner that minimizes flow resistance. In the embodiment shown in FIG. 3, the inlet slot 142 communicates substantially perpendicular to the high pressure side surface 14 to the cavity 16. It is worth mentioning that the term "substantially vertical" should be understood as meaning that the inlet direction of the inlet slot is as vertical or approximately vertical as possible with respect to the high pressure side surface. For example, in some embodiments, the normal to the opening direction of the inlet slot is in the range of 70 ° to 110 °, more preferably in the range of 80 ° to 100 °, with respect to the high pressure side surface.

In some embodiments, the manner of opening of the outlet slot 122 is arranged in a manner that minimizes flow resistance. In the embodiment shown in FIG. 3, the outlet slot 122 communicates with the cavity 16 substantially parallel to the low pressure side surface 12. It is worth noting that the term "substantially parallel" should be understood to mean that the outlet direction of the outlet slot 122 is as parallel or approximately parallel as possible to the low pressure side surface 12. For example, in some embodiments, the outlet direction of the outlet slot 122 is at an angle in the range of 0 to 20, and more preferably in the range of 0 to 15, relative to the low pressure side surface.

In some embodiments, as shown in FIG. 3, outlet slot 122 is disposed downstream in the direction of fluid flow relative to inlet slot 142. Thereby, flow resistance between the inlet tank 142 and the outlet tank 122 may be minimized. The circumferential spacing between the inlet and outlet slots 142, 122 may be determined in relation to the optimum operating performance of the fan. For example, the appropriate circumferential spacing between the inlet and outlet slots 142, 122 may be set based on the designed operating rotational speed of the fan.

Fig. 4 and 5 illustrate structural details of the moving body 20 according to an embodiment of the present disclosure. Mobile body 20 may include a plurality of tuning channels 22 spaced apart from one another. The tuning channel 22 has a radial extension. The tuning channels 22 are arranged in correspondence with the respective fluid channels 30. Thus, when the mover 20 is disposed in the chamber 16, the degree of opening of the tuning passage 22 to communicate with the inlet tank 142 and the outlet tank 122 is adjusted by changing the position of the mover 20. In some embodiments, the mobile body 20 may be configured to move radially based on the centrifugal force to vary the degree of opening in the radial direction of the inlet and outlet slots 142, 122. For example, when the blade 10 rotates at a first speed, the moving body 20 completely blocks the inlet groove 142 and the outlet groove 122, and thus the fluid passage 30, and when the blade 10 rotates at a second speed higher than the first speed, the moving body 20 moves from the radially inner side toward the radially outer side, whereby the area of the tuning passage 22 communicating with the inlet groove 142 and the outlet groove 122 increases, thereby increasing the opening degree of the fluid passage 30.

In some embodiments, tuning passage 22 is configured in a manner to minimize flow resistance to minimize the effect of tuning passage 22 on fluid flow efficiency. In the embodiment shown in fig. 5, tuning passage 22 includes an inlet side opening 224 adjacent inlet slot 142, an outlet side opening 222 adjacent outlet slot 122, and a passage portion 226 connecting inlet side opening 224 and outlet side opening 222. The channel portion 226 may be formed as a smooth transition between the inflow side opening 224 and the outflow side opening 222. In some embodiments, the inflow side opening 224 is formed with a curvature matching that of the inlet groove 142, and the outflow side opening 222 is substantially parallel to the low pressure side surface 12.

In some embodiments, the mobile body 20 may be elastically loaded in the cavity 16 and is movable under the centrifugal force of the rotation of the blade 10 in a radially inner first position and a radially outer second position. The moving body can be elastically loaded in the cavity in various ways. In some embodiments, as shown in fig. 6, the mobile body 20 may be loaded in the cavity 16 via a radially biased spring 40. It is worth mentioning that this is only exemplary and any other suitable elastic means may be used to implement the inventive concept according to embodiments of the present disclosure.

The preload force of the spring may be selectively set and an appropriate spring may be selected to meet the moving performance requirements of the moving body 20. In some embodiments, the spring 40 may be disposed at a radially inner side or a radially outer side, and the position of the moving body 20 may be adjusted by an elastic force of the spring and an action of a centrifugal force during rotation of the fan. In some embodiments, the preload force of the spring is set by: when the rotation speed of the blade 10 is less than the predetermined threshold value, the moving body 20 is maintained at the radially inner first position and closes the plurality of fluid passages 30. When the rotation speed of the vanes 10 exceeds a predetermined threshold value, the moving body 20 moves toward the radially outer position by the centrifugal force to increase the opening degrees of the plurality of fluid passages 30. In particular, when the moving body 20 is at the outermost side in the radial direction, the opening degrees of the plurality of fluid passages 30 are the largest.

Fig. 6 and 7 show schematic views of the working principle of a blade according to an embodiment of the present disclosure. As shown in fig. 6, at the time of low-speed rotation of the fan, the moving body 20 is located near the radially inner position R1. Mobile body 20 blocks inlet channel 142 and outlet channel 122, thereby closing fluid passageway 30. Since the moving body 20 completely closes the fluid passage 30, the fan efficiency is not affected.

As the fan speed increases, the centrifugal force acting on the moving body 20 will increase; under the action of the increased centrifugal force, the moving body 20 will move from the radially inner position R1 toward the radially outer position R2 against the action of the spring 30. Tuning passage 22 on mobile body 20 begins to communicate with inlet channel 142 and outlet channel 122. The fluid stream striking the high pressure side surface 14 will enter the inlet slot 142 and exit through the tuning passage 22, the outlet slot 122. Thus, fluid flow impinging on the high pressure side surface 14 flows through the fluid passage 30. Thereby, formation of a vortex and a diversion of the fluid flow can be prevented, and fluid efficiency is improved.

As the fan speed increases, the centrifugal force will continue to increase, further pushing the moving body 20 towards the radially outer position R2, thereby further increasing the opening of the fluid passage 30. When the fan reaches maximum speed, as shown in FIG. 7, the tuning passage 22 is fully aligned with the inlet slot 142 and the outlet slot 122, and the opening of the fluid passage 30 is maximized. Thereby, formation of a vortex and diversion of the fluid flow can be further prevented, and fluid efficiency is improved.

According to the blade of the embodiment of the disclosure, the performance of the fan is improved by controlling the size of the slot through the movement of the moving body. Eliminating or weakening eddy current at high speed, reducing noise and improving efficiency; and the effective action area of the fan blades is increased at low speed, and the efficiency of the fan is improved.

Fig. 8 and 9 show fluid flow simulation effect diagrams without and with fluid channels according to embodiments of the present disclosure. As shown in fig. 8, with respect to the blade not provided with the structure according to the embodiment of the present disclosure, when the blade rotates at a high speed, a large amount of vortex and fluid diversion exists at a position near the lower edge of the blade. These vortices and fluid shunting will destroy the flow efficiency of the fluid and increase the noise of the fan. As shown in fig. 9, with the blade provided with the structure according to the embodiment of the present disclosure, even when the blade rotates at a high speed, there is substantially no vortex flow and fluid diversion at a position near the lower edge of the blade. Compared with the traditional fan, the fan provided by the embodiment of the disclosure has the advantages that the efficiency of the fan is obviously improved, and the noise is reduced.

While operations are depicted in a particular order, this should be understood as requiring that such operations be performed in the particular order shown or in sequential order, or that all illustrated operations be performed, to achieve desirable results. Under certain circumstances, multitasking and parallel processing may be advantageous. Likewise, while several specific implementation details are included in the above discussion, these should not be construed as limitations on the scope of the disclosure. Certain features that are described in the context of separate embodiments can also be implemented in combination in a single implementation. Conversely, various features that are described in the context of a single implementation can also be implemented in multiple implementations separately or in any suitable subcombination.

Although the subject matter has been described in language specific to structural features and/or methodological acts, it is to be understood that the subject matter defined in the appended claims is not necessarily limited to the specific features or acts described above. Rather, the specific features and acts described above are disclosed as example forms of implementing the claims.

Having described embodiments of the present disclosure, the foregoing description is intended to be exemplary, not exhaustive, and not limited to the disclosed embodiments. Many modifications and variations will be apparent to those of ordinary skill in the art without departing from the scope and spirit of the described embodiments. The terminology used herein is chosen in order to best explain the principles of the embodiments, the practical application, or improvements made to the technology in the marketplace, or to enable others of ordinary skill in the art to understand the embodiments disclosed herein.

Claims (13)

1. A blade (10), comprising:

a low pressure side surface (12) and a high pressure side surface (14);

a plurality of fluid passages (30) extending through the thickness of the blade (10) from a high pressure side surface (14) to the low pressure side surface (12); and

a moving body (20) movably disposed in the blade (10) and adapted to move according to a rotation speed of the blade (10) during rotation of the blade (10) to change an opening degree of the plurality of fluid passages (30).

2. Blade (10) according to claim 1, characterized in that the blade (10) comprises:

a plurality of inlet slots (142) disposed on the high pressure side surface (14) at intervals from each other,

-a cavity (16) communicating with said inlet slot (142) and intended to receive said mobile body (20); and

a plurality of outlet slots (122) disposed spaced apart from one another on the low pressure side surface (12) and in communication with the cavity (16), each inlet slot (142) and each outlet slot (122) being arranged in correspondence with one another to form a respective fluid passage (30).

3. Blade (10) according to claim 2, characterized in that said inlet slots (142) and outlet slots (122) are respectively aligned in a straight line along the radial direction of the blade (10).

4. Blade (10) according to claim 2, characterized in that each inlet slot (142) communicates to the cavity (16) substantially perpendicularly to the high pressure side surface (14).

5. Blade (10) according to claim 4, characterized in that each outlet slot (122) communicates to the cavity (16) substantially parallel to the low pressure side surface (12).

6. Blade (10) according to claim 2, characterized in that each outlet slot (122) is arranged downstream with respect to the inlet slot (142) in the fluid flow direction.

7. Blade (10) according to claim 2, characterized in that the mobile body (20) comprises a plurality of tuning channels (22) spaced apart from each other, wherein each tuning channel (22) is arranged in correspondence with each fluid channel (30), wherein the mobile body (20) blocks the fluid channel (30) when the blade (10) rotates at a first speed, and the tuning channels (22) are aligned with the fluid channel (30) when the blade (10) rotates at a second speed higher than the first speed.

8. Blade (10) according to claim 7, characterized in that each tuning channel (22) comprises an inflow side opening (224) adjacent to the inlet slot (142), an outflow side opening (222) adjacent to the outlet slot (122) and a channel portion (226) connecting the inflow side opening (224) and the outflow side opening (222), wherein the curvature of the inflow side opening (224) is formed matching the curvature of the inlet slot (142), the outflow side opening (222) being substantially parallel to the low pressure side surface (12).

9. Blade (10) according to any of claims 2 to 8, characterized in that the mobile body (20) is elastically loaded in the cavity (16) and is movable under the effect of the centrifugal force of rotation of the blade (10).

10. Blade (10) according to claim 9, characterized in that the moving body (20) is loaded in the cavity (16) via a radially biased spring (40), wherein the preload force of the spring is arranged such that: -when the rotation speed of the blade (10) is less than a predetermined threshold value, the mobile body (20) remains in a radially inner position and closes the plurality of fluid passages (30); when the rotational speed of the blade (10) exceeds a predetermined threshold value, the moving body (20) moves radially outward by centrifugal force to increase the opening degrees of the plurality of fluid passages (30), and when the moving body (20) is at the radially outermost position, the opening degrees of the plurality of fluid passages (30) are the largest.

11. The blade (10) of any of claims 1-8 and 10, wherein the plurality of fluid passages (30) are formed in the blade (10) at locations adjacent to fluid vortex formation.

12. The blade (10) of any of claims 1-8 and 10 wherein the plurality of fluid channels (30) are formed in a region from a trailing edge 1/3-1/2 of the blade (10) in a fluid flow direction relative to a circumferential length of the blade (10).

13. A fan, characterized in that it comprises a plurality of blades (10) according to any one of claims 1-12.

Images