CN217558634U

CN217558634U - Wind-guiding circle, fan and electrical equipment

Info

Publication number: CN217558634U
Application number: CN202220725311.4U
Authority: CN
Inventors: 辛博; 晁汐; 黄焕文
Original assignee: Huawei Technologies Co Ltd
Current assignee: Huawei Technologies Co Ltd
Priority date: 2022-03-30
Filing date: 2022-03-30
Publication date: 2022-10-11
Anticipated expiration: 2032-03-30

Abstract

The embodiment of the application provides a wind-guiding circle, fan and electrical equipment. The outer wall surface of the air guide ring is spirally provided with a plurality of air guide ribs, and the outlet end of the air guide ring is embedded into the air inlet of the impeller. When the impeller rotates, the air guide ribs rotate back to the backflow air flow in the gaps, the spiral outlet direction of the air guide ribs is consistent with the air inlet speed direction of the front edge of the blades of the impeller, the rotated air flow enters the impeller at a proper angle, the impact of the backflow air flow on the air inlet flow in the impeller is reduced, the air volume and the air static and dynamic pressure efficiency of the fan are improved, the refrigeration energy efficiency ratio is improved, the structural strength of the air guide ring is improved, the reliability, the service life and the mass production performance of the fan are not affected, and the problem that when the conventional air guide ring is adopted, the backflow air flow directly impacts the upper surfaces of the blades to cause large-scale separation flow is overcome. The fan with the air guide ring and the electrical equipment with the fan can improve the air quantity, the air dynamic and static pressure efficiency and the refrigeration energy efficiency ratio of the fan.

Description

Wind-guiding circle, fan and electrical equipment

Technical Field

The embodiment of the application relates to fan technical field, especially relates to a wind-guiding circle, fan and electrical equipment.

Background

Electric equipment with high power consumption (such as a data center) can generate a large amount of heat during working, and air cooling and heat dissipation can be performed by generating air flow through a fan. For example, a centrifugal fan as shown in fig. 1 is adopted, the centrifugal fan includes a wind guide ring 100', an impeller 200' and a motor 300', one end of the wind guide ring 100' is embedded into the wind inlet 211 'of the impeller 200', and a gap 115 'is formed between the wind guide ring 100' and the inner wall of the wind inlet 211 'of the impeller 200'. The motor 300 'is connected with the impeller 200' to drive the impeller 200 'to rotate, the rotating impeller 200' applies work to the gas, so that the external air smoothly enters the impeller 200 'through the air guide ring 100' and then is transmitted to the outside of the impeller 200', and the formed air inlet flow 1' cools and dissipates heat of the heating device. The gap 115 'between the wind guide ring 100' and the impeller 200 'has high-speed backflow airflow 2' with large influence, which can cause low fan air volume and air dynamic and static pressure efficiency, thereby making the refrigeration energy efficiency ratio difficult to improve.

SUMMERY OF THE UTILITY MODEL

The embodiment of the application provides a wind-guiding circle, fan and electrical equipment, has solved the wind-guiding circle in the current fan and has had the great high-speed backward flow of influence with the clearance of impeller, leads to the lower problem of fan amount of wind and pneumatic and static pressure efficiency.

In order to achieve the above purpose, the embodiment of the present application adopts the following technical solutions:

in a first aspect, the embodiment of the application provides an air guide ring, the air guide ring has an airflow channel, the airflow channel has an inlet end and an outlet end which are arranged oppositely, the outlet end is embedded into an air inlet of an impeller, a gap is formed between an outer wall surface of the outlet end and an inner wall surface of the air inlet of the impeller, the outer wall surface of the air guide ring is spirally provided with a plurality of air guide ribs along the circumferential direction, the air guide ribs are used for enabling backflow air flow returning to the impeller through the gap to rotate, and the spiral outlet direction of the air guide ribs is consistent with the air inlet speed direction of a blade front edge of the impeller.

According to the air guide ring provided by the embodiment of the application, the plurality of air guide ribs are spirally arranged on the outer wall surface of the air guide ring, and the outlet end of the air guide ring is embedded into the air inlet of the impeller. When the impeller rotates, the air guide ribs rotate back to the backflow air flow in the gaps, the spiral outlet direction of the air guide ribs is consistent with the air inlet speed direction of the front edge of the blades of the impeller, the rotated air flow enters the impeller at a proper angle, the impact of the backflow air flow on the air inlet flow in the impeller is reduced, the air volume and the air static and dynamic pressure efficiency of the fan are improved, the refrigeration energy efficiency ratio is improved, the structural strength of the air guide ring is improved, the reliability, the service life and the mass production performance of the fan are not affected, and the problem that when the conventional air guide ring is adopted, the backflow air flow directly impacts the upper surfaces of the blades to cause large-scale separation flow is overcome.

In an alternative implementation, each air guide rib has opposite first initial ends and first terminal ends, the first initial ends are arranged towards the inlet end, and the first terminal ends are arranged adjacent to or extend to the edge of the outlet end. The air guide ribs can guide the backflow airflow to flow along the direction from the first starting end to the first terminating end, and the backflow airflow enters the impeller through the gap at a certain prerotation speed.

In an alternative implementation, the thickness of the wind guide ribs ranges from 0.5 millimeters (mm) to 3mm. The structure is easy to form, and more air guide ribs are arranged in an effective space, so that the backflow airflow obtains a certain pre-rotation speed and is injected into the impeller through the gap, and the influence of the backflow airflow on the airflow inside the impeller is reduced.

In an alternative embodiment, the maximum radial height h of the wind guide ribs _o And the width g of the gap satisfy the following relationship: h is not less than 1mm _o Less than or equal to 2g. The air guide ribs are easy to form, the outlet end of the air guide ring is conveniently embedded and assembled at the air inlet of the impeller to form a certain gap, and the backflow air flow can obtain a certain prerotation speed and is injected into the impeller from the gap.

In an alternative embodiment, the inlet angle β of the wind guide ribs _o1 The range is-10 degrees to 10 degrees; outlet angle beta of wind-guiding rib _o2 The range is-15 to 45 degrees. The air guide ribs can enable backflow air flow passing through the gaps to rotate at proper angles and then enter the impeller, and the shadow of the backflow air flow on the air inlet flow near the blades and the impeller is reducedAnd (6) sounding.

In an optional implementation mode, in the direction from the outlet end to the inlet end, each air guide rib is provided with a first surface and a concave curved surface which are connected, the first surface and the inner wall surface of an air inlet of the impeller are oppositely arranged, the distance between the first surface and the inner wall surface of the air inlet of the impeller is larger than or equal to the width of the gap, and the concave curved surface and the outer wall surface of the air guide ring are sunken towards the same direction. The air guide ribs can not change the gap width between the air guide ring and the impeller, so that the assembly of the air guide ring and the impeller is facilitated. The top of the part of the air guide rib, which is far away from the outer side wall of the air guide ring, is set to be a concave curved surface, so that most of the area of the air guide rib can effectively guide the backflow air flow, and the backflow air flow obtains a certain pre-rotation speed.

In an optional implementation mode, the airflow rotated by the air guide ribs flows to the blade tips of the impeller, and the attack angle of the airflow at the blade tips of the impeller ranges from-5 degrees to 15 degrees. The influence of the backflow airflow on the intake flow in the impeller is favorably reduced, so that the air quantity and the aerodynamic pressure efficiency of the fan are improved.

In an alternative implementation, the inner wall surface of the outlet end is provided with a plurality of raised strips along the circumferential direction, each raised strip has a second starting end and a second terminating end which are opposite, the second starting end is arranged towards the inlet end, and the second terminating end is arranged adjacent to or extends to the edge of the outlet end. The plurality of protruding strips are arranged on the inner wall surface of the outlet end of the air guide ring, a certain flow direction vortex is generated, and the mixing effect of the boundary layer air flow of the inner wall surface near the outlet end of the air guide ring and the high kinetic energy air flow of the main flow is increased, so that the falling vortex influence near the outlet end of the air guide ring is reduced, the air volume and the aerodynamic pressure efficiency of the fan are improved, and the noise of the fan is reduced.

In an alternative implementation, the thickness of the raised strips ranges from 0.3mm to 1.5mm. A plurality of protruding strips are arranged in a local small area of the outer wall surface of the outlet end of the air guide ring, so that the air guide ring is easy to produce and manufacture, and extra aerodynamic resistance caused by the protruding strips and the groove structure with overlarge thickness is avoided.

In an alternative implementation, the axial height of the raised strips ranges from 1mm to 15mm. The axial height of the protruding strips is set according to the range, the production and the manufacture are easy, and extra aerodynamic resistance caused by the fact that the protruding strips with too large axial height are arranged is avoided.

In an alternative implementation, the spacing s of the edges of the second terminating end and the exit end _i The range is 0mm to 3mm. Certain flow direction vortexes are generated near the outlet end of the air guide ring, and the influence of the shedding vortexes near the outlet end of the air guide ring on the air inlet flow of the impeller is reduced.

In an optional implementation mode, the maximum normal distance range of the top contour line of the convex strip and the inner wall surface of the outlet end is 0.3-1 mm, the maximum height of the convex strip is set according to the range, the production and the manufacture are easy, and extra pneumatic resistance caused by the arrangement of the convex strip with an overlarge height is avoided.

In an alternative implementation, the inlet angle of the raised bars ranges from-10 to 10, and the outlet angle of the raised bars ranges from-10 to 10. The protruding strips can generate certain flow direction vortexes near the outlet end of the air guide ring, and the influence of the falling vortexes near the outlet end of the air guide ring on the air inlet flow of the impeller is reduced.

In an alternative implementation manner, the distance between the top contour line of the convex strip and the inner wall surface of the outlet end in the direction from the second starting end to the second terminating end is gradually increased and then gradually decreased. The protruding strips can generate certain flow direction vortexes near the outlet end of the air guide ring, and the influence of the falling vortexes near the outlet end of the air guide ring on the air inlet flow of the impeller is reduced.

In a second aspect, an embodiment of the present application provides a fan, including: the impeller is used for being connected with a driving device of the fan, and the outlet end of the air guide ring is embedded into an air inlet of the impeller. After the air guide ring is arranged, the air quantity and the air dynamic and static pressure efficiency of the fan are effectively improved.

In a third aspect, an embodiment of the present application provides an electrical apparatus, including the above-mentioned fan.

Drawings

FIG. 1 is a cross-sectional view of a conventional blower;

FIG. 2 is a perspective view of a conventional wind-guiding ring;

FIG. 3 is a perspective view and a partially enlarged view of an air guiding ring according to an embodiment of the present disclosure;

FIG. 4 is a perspective assembly view of the wind-guiding collar of FIG. 3 as applied to a wind turbine;

FIG. 5 is a perspective cross-sectional view of the blower of FIG. 4;

FIG. 6 is a partial cross-sectional view of the blower of FIG. 4;

FIG. 7 is another perspective assembly view of the blower of FIG. 4;

FIG. 8 is an enlarged view of a portion of the wind-guiding collar of FIG. 3;

fig. 9 (a) and (b) are a front view and a side view of the air guide rib, respectively;

FIG. 10 is a flow field simulation diagram of a fan using a conventional wind guide ring;

FIG. 11 is a flow field simulation using the blower of FIG. 4;

FIG. 12 is a perspective and enlarged view of a wind deflector ring according to another embodiment of the present disclosure;

FIG. 13 is an assembled perspective view of the wind deflector of FIG. 12 when applied to a fan;

FIG. 14 (a) and (b) are a front view and a side view of the projected strip, respectively;

FIG. 15 is a flow field simulation and a partial enlarged view of a fan using a conventional wind guide ring;

FIG. 16 is a simulation and partial enlarged view of the flow field of the blower of FIG. 13.

Detailed Description

In order to make the technical problems, technical solutions and advantageous effects to be solved by the present application clearer, the present application is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of and not restrictive on the broad application. While the description of the present application will be presented in conjunction with certain embodiments, this is not intended to limit the features of this application to that embodiment. Rather, the embodiments are described as applications in order to cover other alternatives or modifications that may extend from the claims of the present application. In the following description, numerous specific details are included to provide a thorough understanding of the present application. The present application may be practiced without these particulars. Moreover, some of the specific details have been omitted from the description in order to avoid obscuring or obscuring the focus of the present application. It should be noted that, in the present application, the embodiments and features of the embodiments may be combined with each other without conflict.

It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or be indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or be indirectly connected to the other element.

It is to be understood that in the description of the embodiments of the present application, it is to be noted that the terms "mounted" and "connected" are to be construed broadly unless otherwise explicitly stated or limited, and for example, "connected" may or may not be detachably connected; may be directly connected or indirectly connected through an intermediate. The terms "length," "width," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like refer to an orientation or positional relationship that is based on the orientation or positional relationship shown in the drawings, merely for convenience in describing and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be taken as limiting the application.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or to implicitly indicate the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present application, "a plurality" means two or more unless specifically limited otherwise.

In the embodiment of the present application, "and/or" is only one kind of association relationship describing an association object, and indicates that three types of relationships may exist, for example, a and/or B may indicate: a exists alone, A and B exist simultaneously, and B exists alone. In addition, the character "/" herein generally indicates that the former and latter related objects are in an "or" relationship.

Reference throughout this specification to "one embodiment" or "some embodiments," or the like, means that a particular feature, structure, or characteristic described in connection with the embodiment is included in one or more embodiments of the present application. Thus, appearances of the phrases "in one embodiment," "in some embodiments," "in other embodiments," or the like, in various places throughout this specification are not necessarily all referring to the same embodiment, but rather mean "one or more but not all embodiments" unless specifically stated otherwise. The terms "comprising," "including," "having," and variations thereof mean "including, but not limited to," unless otherwise specifically stated.

In the conventional blower as shown in fig. 1 and 2, the wind guide ring 100 'is a stationary member, and the impeller 200' is a rotating member. One end of the wind guide ring 100' is embedded into the wind inlet 211' of the impeller 200', that is, a part where the wind guide ring 100' and the impeller 200' are axially overlapped exists, and a gap 115' exists in the radial direction, so that the impeller 200' can conveniently rotate.

When the impeller 200' rotates, the external air is sucked into the air guiding ring 100' to form an intake flow 1 passing through the impeller 200', and a "negative pressure" region 3 is formed at the air guiding ring 100' and the front thereof, and a "positive pressure" region 4 is formed outside the impeller 200 '. Under the action of the positive and negative pressure difference, the airflow outside the impeller 200 'will be injected into the impeller 200' from the gap 115 'between the wind guide ring 100' and the impeller 200', and a backflow airflow 2' is formed. The airflow passing through the gap 115 'may impact the airflow near the blades of the impeller 200' and in the impeller flow channel, which is a secondary flow generated by leakage in the fan, and may cause the fan air volume and the fan aerodynamic static pressure efficiency to be low, thereby making the refrigeration energy efficiency ratio difficult to be improved.

The fan aerodynamic static pressure efficiency is the ratio of the product of the air volume (Q) generated by the fan and the air pressure (P) generated by the air volume to the fan power (W), namely the fan aerodynamic static pressure efficiency eta = P × Q/W. The fan power is the shaft power required by the fan. The refrigeration energy efficiency ratio is a ratio of a rated cooling capacity to a rated power (power consumption) and is used for representing the energy conversion efficiency of the refrigeration system.

In order to solve the problem that the gap between the air guide ring and the impeller in the conventional fan has a large influence on high-speed backflow, which results in low air volume and low aerodynamic and static pressure efficiency of the fan, referring to fig. 3 to 6, an embodiment of the present application provides an air guide ring 100, where the air guide ring 100 has an air flow channel 110, the air flow channel 110 has an inlet end 111 and an outlet end 112 that are oppositely disposed, the outlet end 112 is embedded into an air inlet 211 of the impeller 200, a gap 115 is formed between an outer wall surface 113 of the outlet end 112 and an inner wall surface of the air inlet 211 of the impeller 200, a plurality of air guide ribs 120 are spirally disposed along a circumferential direction on an outer wall surface 113 of the air guide ring 100, and the air guide ribs 120 are used for rotating a backflow air flow 2 that returns to the impeller 200 through the gap 115, and, with reference to fig. 7, a spiral outlet direction of the air guide ribs 120 is consistent with a direction of a front edge 221 of a blade 220 of the air inlet impeller 200.

The wind guide ring 100 can be applied to a centrifugal fan and a mixed flow fan.

Referring to fig. 7, the impeller 200 includes a plurality of circumferentially distributed blades 220, each blade 220 having opposite leading and trailing

edges

221, 222 and opposite tip and

root

223, 224. The leading edge 221, the blade tip 223, the trailing edge 222 and the blade root 224 are connected in sequence, and are four edges of the blade 220. The blade tip 223 is a side near the wind-guiding ring 100. During rotation of the impeller 200, the airflow entering the impeller 200 flows from the leading edge 221 to the trailing edge 222 of the blades 220.

With reference to fig. 8, the spiral outlet direction of the air guide ribs 120 refers to the tangential direction of the center line of one end (i.e., the first terminating end 122 mentioned below) of the air guide ribs 120 close to the outlet end 112. Referring to fig. 7, the spiral outlet direction of the air guide rib 120 is the same as the air intake velocity direction of the leading edge 221 of the blade 220 of the impeller 200, and the two directions are not absolutely the same and may have a certain angular deviation, for example, from-10 ° to 10 °.

Referring to fig. 3 to 6, in the wind-guiding ring 100 according to the embodiment of the present application, a plurality of wind-guiding ribs 120 are spirally disposed on an outer wall surface 113 of the wind-guiding ring 100, and an outlet end 112 of the wind-guiding ring 100 is inserted into an air inlet 211 of the impeller 200. When the impeller 200 rotates, the return air flow 2 returned to the gap 115 is rotated by the air guide ribs 120, the spiral outlet direction of the air guide ribs 120 is consistent with the air inlet speed direction of the front edges 221 of the blades 220 of the impeller 200, the rotated air flow enters the impeller 200 at a proper angle, the impact of the return air flow 2 on the inlet air flow 1 in the impeller 200 is reduced, the air volume and air dynamic and static pressure efficiency of the fan is improved, the refrigeration energy efficiency ratio is improved, the structural strength of the air guide ring 100 is improved, the reliability, the service life and the mass production of the fan are not influenced, and the problem that when a conventional air guide ring is adopted, the return air flow directly impacts the upper surfaces of the blades to cause large-scale separation flow is overcome.

When the wind-guiding ring 100 is disposed, referring to fig. 6, the inner wall of the wind-guiding ring 100 may be disposed as a streamlined retractable airflow channel 110, and from the inlet end 111 to the outlet end 112, the inner diameter of the airflow channel 110 gradually decreases from large to small, and then gradually increases, and the inner diameter of the inlet end 111 is larger than the inner diameter of the outlet end 112. When the impeller 200 rotates, the air flow in front of the wind-guiding ring 100 can smoothly enter the impeller 200 through the air flow channel 110. Referring to fig. 3, the air guide ribs 120 may be uniformly arranged on the outer wall surface 113 of the air guide ring 100 to form a spiral structure. The wind guide ring 100 and the wind guide ribs 120 can be integrally formed, and are easy to process.

In providing impeller 200, referring to fig. 4, impeller 200 includes a top plate 210, a bottom plate 230, and a plurality of blades 220 disposed between top plate 210 and bottom plate 230. Referring to fig. 5 and 7, the tip 223 of the blade 220 is connected to the top plate 210, and the root 224 of the blade 220 is connected to the bottom plate 230. The air inlet 211 is disposed on the top plate 210, an impeller channel is formed between two adjacent blades 220, and an air outlet 201 is formed at an end of the impeller channel. Under the driving of the motor 300, the impeller 200 rotates and applies work to the air, so that the air is sucked into the air guide ring 100, enters the impeller 200, turns 90 degrees and flows out of the air outlet 201.

In some embodiments, referring to fig. 3 and 8, each wind guide rib 120 has a first starting end 121 and a first terminating end 122, the first starting end 121 is disposed toward the inlet end 111, and the first terminating end 122 is disposed adjacent to the edge of the outlet end 112 or extends to the edge of the outlet end 112. The air guide ribs 120 are disposed on the outer wall surface 113 of the outlet end 112 of the air guide ring 100, when the outlet end 112 of the air guide ring 100 is embedded into the air inlet 211 of the impeller 200, the first starting end 121 is located outside the air inlet 211 of the impeller 200, and the first terminating end 122 is located inside the air inlet 211 of the impeller 200, with reference to fig. 6, the air guide ribs 120 can guide the backflow air flow 2 to flow along the direction from the first starting end 121 to the first terminating end 122, and enter the impeller 200 through the gap 115 at a certain pre-rotation speed.

Referring to fig. 3 and 9 (a), the y direction is a radial direction of the wind guide ring, the z direction is an axial direction of the wind guide ring, and the z-direction positions of the first starting end 121 and the first terminating end 122 of the wind guide rib 120 on the yz plane are z respectively _o1 And z _o2 Then the axial height l of the wind guide rib 120 _o ＝z _o2 -z _o1 . First start end 121 position z of wind guide rib 120 _o1 Is not less than the z-direction position of the inlet end 111 of the wind guide ring 100 and the z-direction position of the first termination end 122 _o2 The z-direction position of the outlet end 112 of the wind guiding ring 100 is not exceeded, namely the axial height l of the wind guiding rib 120 _o Is smaller than the axial height of the wind guide ring 100.

In some embodiments, referring to fig. 9 (a), the thickness t of the air guide rib 120 _o The range is 0.5 millimeters (mm) to 3mm. Thickness t of the air guide rib 120 _o Taking values according to the above range, the structure is easy to form, more air guide ribs 120 are arranged in the effective space, and in combination with fig. 5, the backflow air flow 2 obtains a certain pre-rotation speed and is injected into the impeller 200 through the gap 115, so that the influence of the backflow air flow 2 on the air flow 1 in the impeller 200 is reduced. The thickness of the air guide ribs 120 is too small to facilitate molding, and the number of the air guide ribs 120 arranged in a limited space is too large.

Illustratively, the thickness t of the wind-guiding rib 120 _o And may be 0.5mm, 1mm, 1.5mm, 2mm, 2.5mm, 3mm, etc., as desired.

In some embodiments, referring to fig. 6 and 9 (b), the maximum radial height h of the wind guide rib 120 _o And the width g of the gap 115 satisfy the following relationship: h is not less than 1mm _o Less than or equal to 2g. Maximum radial height h of air guide ribs 120 _o The air guide ribs 120 are arranged in the radial direction of the air guide ring 100Root 125 to crest 126. As shown in fig. 9 (b), the x direction is another radial direction of the wind guide ring, the z direction is the axial direction of the wind guide ring, and the maximum radial height h of the wind guide rib 120 on the xz plane is _o The maximum dimension of the air guide rib 120 in the x direction. Referring to fig. 6, width g of gap 115 is a distance between outer wall surface 113 of outlet end 112 of air-guiding ring 100 and inner wall surface of inlet 211 of impeller 200 in the radial direction of air-guiding ring 100. Maximum radial height h of the air guide ribs 120 _o The width g of the gap 115 is not more than 2 times, and the minimum is 1mm, so that the air guide rib 120 is easy to form, the outlet end 112 of the air guide ring 100 is embedded and assembled at the air inlet 211 of the impeller 200 to form a certain gap 115, and the backflow air flow 2 can obtain a certain pre-rotation speed and is injected into the impeller 200 from the gap 115. Maximum radial height h _o Too small an arrangement is inconvenient for molding and too large an arrangement is inconvenient for assembling the air guide ring 100 and the impeller 200.

Illustratively, the width g of the gap 115 ranges from 3mm to 10mm, as desired. When the width g of the gap 115 is 5mm, the maximum radial height h of the air guide rib 120 _o May be 1mm, 2mm, 5mm, 6mm, 8mm, 10mm, etc., as desired.

In some embodiments, referring to fig. 9 (a), the inlet angle β of the air guide rib 120 _o1 The range is-10 to 10 degrees; outlet angle beta of wind-guiding rib 120 _o2 The range is-15 to 45 degrees. Inlet angle β of the air guide ribs 120 _o1 The included angle between the tangential line of the starting point of the central line of the wind guide rib 120 (i.e. the position of the first starting end 121) and the axial direction of the wind guide ring (i.e. the z direction) is referred to. Outlet angle beta of the air guide ribs 120 _o2 The included angle between the tangential line of the center line terminal point (i.e. the position of the first terminal end 122) of the wind guide rib 120 and the axial direction of the wind guide ring is referred to. The outlet angle direction of the wind guide rib 120 is the spiral outlet direction of the wind guide rib 120. In this embodiment, referring to fig. 5, the air guide ribs 120 can rotate the backflow airflow passing through the gap 115 by a proper angle and then enter the impeller 200, so as to reduce the influence of the backflow airflow 2 on the inlet airflow 1 near the blades 220 and the impeller 200.

Exemplary, the inlet angle β of the wind guide ribs 120 _o1 Can be-10 deg. -5 deg. -1 deg. -0 deg. -1 deg. -5 deg., 5 deg. 10 deg., etc., and air-guiding ribsExit angle beta of strip 120 _o2 May be-15 °, -10 °, -5 °, -0 °, 10 °, 20 °, 30 °, 45 °, etc., as desired.

In some embodiments, referring to fig. 6 and 9 (b), in a direction from the outlet end 112 to the inlet end 111, each wind guide rib 120 has a first surface 123 and a concave curved surface 124 connected to each other, the first surface 123 is disposed opposite to an inner wall surface of the wind inlet 211 of the impeller 200, a distance between the first surface 123 and the inner wall surface of the wind inlet 211 of the impeller 200 is greater than or equal to a width g of the gap 115, and the concave curved surface 124 and the outer wall surface 113 of the wind guide ring 100 are concave towards the same direction. A part of the top 126 of the air guide rib 120 extending into the air inlet 211 of the impeller 200 is defined as a first surface 123, and the distance between the first surface 123 and the inner wall surface of the air inlet 211 of the impeller 200 is greater than or equal to the width g of the gap 115, so that the air guide rib 120 does not change the width g of the gap 115 between the air guide ring 100 and the impeller 200, and the assembly of the air guide ring 100 and the impeller 200 is facilitated. The outer diameter of the airflow channel 110 of the air guide ring 100 gradually decreases and then gradually increases, the air guide ribs 120 are designed according to the fluctuation degree of the outer wall surface 113 of the air guide ring 100, namely, the top 126 of the part, far away from the outer side wall of the air guide ring 100, of the air guide ribs 120 is set to be a concave curved surface 124, so that most areas of the air guide ribs 120 can effectively guide the backflow airflow, and the backflow airflow obtains a certain pre-rotation speed. The first surface 123 may be a plane or a curved surface.

In some embodiments, referring to fig. 5 and 7, the airflow rotating through the air guide ribs 120 flows to the blade tips 223 of the blades 220 of the impeller 200, and the angle of attack of the blade tips 223 of the blades 220 of the impeller 200 ranges from-5 ° to 15 °. The angle of attack of the airflow is defined as the angle between the tangential line of the camber line of the blade 220 at the location of the leading edge 221 and the direction of the incoming flow in the cross-section from the leading edge 221 to the trailing edge 222. Through setting up wind-guiding rib 120, make the air current angle of attack of blade 220 apex 223 satisfy above-mentioned angle range, be favorable to reducing the influence of backward flow air current 2 to inlet flow 1 in impeller 200 to promote fan amount of wind and aerodynamic pressure efficiency. Too large or too small angle of attack of the airflow can cause the backflow airflow 2 to directly impact the blades 220 of the impeller 200, so that large-scale separation flow is caused, and the air volume and the aerodynamic pressure efficiency of the fan are reduced.

Specifically, the airflow attack angle range of the blade tip 223 of the blade 220 of the impeller 200 is 0 to 10 degrees, and the airflow attack angle of the blade tip 223 is in the range by arranging the air guide rib 120, so that the influence of the backflow airflow 2 on the intake airflow 1 in the impeller 200 is further reduced. Illustratively, the angle of attack of the airflow at the tip 223 of the blade 220 of the impeller 200 may be 0 °, 1 °, 5 °, 9 °, 10 °, etc., as desired.

In order to verify that the air guide ring 100 of the embodiment of the present application can reduce the influence of backflow airflow on intake airflow in the impeller, a simulation experiment is performed on a fan that adopts a conventional air guide ring as shown in fig. 1 and a fan that adopts the air guide ring 100 of the present application as shown in fig. 4.

Both fans meet the following characteristics, namely, a centrifugal fan adopting an Electronic Commutation (EC) motor. The parameters of the fan are as follows: the diameter of the impeller is 660mm, the rotating speed is 1800 revolutions per minute (rpm), the integral axial height of the air guide ring is 80mm, the depth of the outlet end of the air guide ring embedded into the air inlet of the impeller is 15mm, and the gap width between the air guide ring and the impeller is 5mm.

The fan adopting the wind guide ring 100 of the present application further satisfies the following characteristics, referring to (a) and (b) in fig. 3 and 9, that 36 wind guide ribs 120 are uniformly arranged in the circumferential direction on the outer wall surface 113 of the wind guide ring 100, and the thickness t of the wind guide ribs 120 _o Is 1mm, maximum radial height h _o 5.3mm, axial height l _o 61mm, the first terminal end 122 coincides with the edge of the outlet end 112 of the wind-guiding ring 100. Inlet angle beta of wind guide rib 120 _o1 Is 0 DEG, exit angle beta _o2 Is 45 deg..

According to simulation experiment, compare in the fan of conventional wind-guiding circle, the aerodynamic static pressure efficiency of the fan that has this application wind-guiding circle promotes 1%. Fig. 10 and 11 show the swirl and swirl core position of a conventional fan and a fan of the present application, respectively, in the recirculation zone, with the direction and length of the arrows indicating the direction and magnitude of the airflow, respectively. When the impeller 200 of the fan rotates, under the pressure difference between the outside of the impeller 200 and the inside of the wind guide ring 100, the airflow outside the impeller 200 will return to the gap 115 and be injected into the inside of the impeller 200.

Referring to fig. 10, in the fan of the conventional wind guide ring 100', the vortex core position in the backflow region is relatively close to the outside, that is, the distance between the vortex core position and the axis of the wind guide ring 100' is relatively large, the influence range of the vortex on the intake flow of the impeller is relatively large, and the aerodynamic static pressure efficiency is relatively low.

Compared with a fan with a conventional air guide ring 100', after the air guide ring 100 in the fan is additionally provided with the plurality of air guide ribs 120, referring to fig. 11, the core position of the vortex in the backflow area is closer to the axis of the air guide ring 100, the influence range of the vortex on the air inlet flow of the impeller 200 is smaller, the flow of the air inlet flow of the impeller 200 can be improved, and therefore the aerodynamic static pressure efficiency is improved.

In the conventional blower as shown in fig. 1, one end of the wind-guiding ring 100' is protruded into the wind inlet 211' of the impeller 200 '. The wind guiding ring 100' extends into the flow field near the end break of the impeller 200', and is influenced by the non-uniformity of the upstream incoming flow and the internal airflow of the impeller 200 '. The wind guide ring 100' extends into the vicinity of the end part of the impeller 200' to generate a certain shedding vortex (or separation vortex), and the shedding vortex can influence the flow of the inlet flow 1' of the impeller 200' to a certain extent after entering the impeller 200', so that the air volume and the aerodynamic pressure efficiency of the fan are reduced, and the noise of the fan can be increased.

Referring to fig. 12 and 13, in the wind deflector 100 provided in the embodiment of the present application, the inner wall surface 114 of the outlet end 112 is circumferentially provided with a plurality of protruding strips 130, each protruding strip 130 has a second starting end 131 and a second terminating end 132, the second starting end 131 is disposed toward the inlet end 111, and the second terminating end 132 is disposed adjacent to or extends to the edge of the outlet end 112.

The plurality of convex strips 130 are arranged on the inner wall surface 114 of the outlet end 112 of the air guide ring 100, so that a certain flow direction vortex is generated, the mixing effect of the boundary layer airflow of the inner wall surface 114 near the outlet end 112 of the air guide ring 100 and the main flow high kinetic energy airflow is increased, the falling vortex influence near the outlet end 112 of the air guide ring 100 is reduced, the air volume and the air dynamic and static pressure efficiency of the fan are improved, and the noise of the fan is reduced. When the flow field has a predominant flow direction, the fluid vortex having a vortex direction parallel to this flow direction is called a flow vortex.

When the convex strip 130 is provided, the plurality of convex strips 130 may be uniformly arranged on the inner wall surface 114 of the outlet end 112 of the wind-guiding ring 100. The protruding strips 130 can be sized to be much smaller than the air guide ribs 120, so as to improve the air flow characteristics near the outlet end 112 of the air guide ring 100, without providing excessive size of the protruding strips 130 to cause extra aerodynamic resistance. The air guide ring 100 and the protruding strips 130 can be of an integrally formed structure and are easy to process.

In some embodiments, referring to (a) of fig. 14, the thickness t of the raised bars 130 _i The range is 0.3mm to 1.5mm. The y direction is the radial direction of the wind guide ring, the z direction is the axial direction of the wind guide ring, and the thickness t of the convex strip 130 _i Is the distance of two parallel outer contours in the yz plane. Thickness t of the projecting strip 130 _i According to the arrangement in the range, the plurality of convex strips 130 are arranged only in a local small area of the outer wall surface 113 of the outlet end 112 of the wind guide ring 100, so that the production and the manufacture are easy, and the extra aerodynamic resistance caused by the arrangement of the convex strips and the groove structure with overlarge thickness is avoided. Illustratively, the thickness t of the raised bars 130 _i And may be 0.3mm, 0.5mm, 1mm, 1.2mm, 1.5mm, etc., as desired.

In some embodiments, referring to FIG. 14 (a), the axial height l of the raised bars 130 _i The range is 1mm to 15mm. In the yz plane, the z-position of the second starting end 131 and the second terminating end 132 of the raised strip 130 is z _i1 And z _i2 Then the axial height l of the raised bars 130 _i ＝z _i2 -z _i1 . Axial height l of the raised strip 130 _i According to the range setting, the pneumatic brake is easy to produce and manufacture, and extra aerodynamic resistance caused by the arrangement of the protruding strips with too large axial height is avoided. Illustratively, the axial height l of the raised bars 130 _i And may be 1mm, 3mm, 5mm, 7mm, 10mm, 12mm, 15mm, etc., as desired.

In some embodiments, referring to (a) and (b) of FIG. 14, the spacing s of the edges of the second terminating end 132 and the outlet end 112 _i The range is 0mm to 3mm. By adopting the scheme, certain flow direction vortex can be generated near the outlet end 112 of the air guide ring 100, and the influence of the shedding vortex near the outlet end 112 of the air guide ring 100 on the impeller air inflow is reduced.

In some embodiments, referring to FIG. 14 (b), the top contour 133 of the raised bar 130 and the interior of the outlet end 112Maximum normal distance h of wall 114 _i The range is 0.3mm to 1mm. The x direction is the other radial direction of the wind guide ring, the z direction is the axial direction of the wind guide ring, and on the xz plane, the top contour line 133 of the convex strip 130 is a side line of the convex strip 130 far away from the inner wall surface 114. Maximum normal distance h _i The maximum distance between the inner wall surface 114 and the top contour 133 of the protrusion 130 in a direction normal to the inner wall surface 114 of the outlet end 112 is the maximum height of the protrusion 130 in a direction normal to the inner wall surface 114. The maximum height of the raised strips 130 is set according to the above range, so that the production and the manufacture are easy, and the extra aerodynamic resistance caused by setting the raised strips 130 with too large height is avoided. Exemplary, maximum normal distance h _i And may be 0.3mm, 0.5mm, 0.7mm, 0.9mm, 1mm, etc., as desired.

In some embodiments, referring to fig. 14 (a), the entry angle β of the raised strip 130 _i1 The range is-10 to 10 degrees, and the exit angle beta of the convex strip 130 _i2 The range is-10 to 10 degrees. Entry angle β of the raised strip 130 _i1 Refers to the angle between the tangential line of the starting point of the center line of the raised strip 130 (i.e. the position of the second starting end 131) and the axial direction of the wind-guiding ring 100. Exit angle beta of the raised strip 130 _i2 The included angle between the tangential line of the center line terminal point (i.e. the position of the second terminal end 132) of the raised strip 130 and the axial direction of the wind guiding ring 100 is referred to. In this embodiment, referring to fig. 13, the protruding strips 130 can generate a certain flow vortex near the outlet end 112 of the air guide ring 100, so as to reduce the influence of the dropped vortex near the outlet end 112 of the air guide ring 100 on the impeller intake air flow.

Illustratively, the entry angle β of the raised bars 130 _i1 Can be-10 °, -5 °, -1 °, 0 °, -1 °, 5 °, 10 °, etc., the exit angle β of the raised strip 130 _i2 Can be-10 degrees, -5 degrees, -1 degrees, -0 degrees, -1 degrees, -5 degrees, 10 degrees, etc., as required.

In some embodiments, referring to fig. 14 (b), the distance between the top contour line 133 of the protruding strip 130 and the inner wall surface 114 of the outlet end 112 becomes larger and smaller in the direction from the second starting end 131 to the second terminating end 132. The raised strips 130 may be arranged in a generally triangular shape, or in a trapezoidal shape with one corner removed from the triangular shape, etc. With reference to fig. 13, the raised strips 130 can generate a certain flow vortex near the outlet end 112 of the wind-guiding ring 100, so as to reduce the influence of the dropped vortex near the outlet end 112 of the wind-guiding ring 100 on the intake airflow of the impeller.

In order to verify that the wind-guiding ring 100 of the embodiment of the present application can reduce the influence of the vortex shedding near the outlet end 112 of the wind-guiding ring 100, a simulation experiment is performed on the fan using the conventional wind-guiding ring 100' as shown in fig. 1 and the fan using the wind-guiding ring 100 of the present application as shown in fig. 13.

Both fans meet the following characteristics, a centrifugal fan using an Electronically Commutated (EC) motor. The fan parameters are as follows: the diameter of the impeller is 660mm, the rotating speed is 1800 revolutions per minute (rpm), the integral axial height of the air guide ring is 80mm, the depth of the outlet end of the air guide ring embedded into the air inlet of the impeller is 15mm, and the gap width between the air guide ring and the impeller is 5mm.

The fan using the wind-guiding ring 100 of the present application further satisfies the following characteristics, referring to (a) and (b) in fig. 12 and 14, that 36 protruding strips 130 are uniformly arranged on the inner wall surface 114 near the outlet end 112 of the wind-guiding ring 100 in the circumferential direction, and the thickness t of the protruding strips 130 _i 1.2mm, the second terminal end 132 and the edge of the outlet end 112 _i 2.5mm, axial height l of the projecting strip 130 _i 13.5mm, the maximum normal distance h between the top contour 133 of the raised strip 130 and the inner wall surface 114 of the outlet end 112 _i 1mm, inlet angle beta of the raised strip 130 _i1 And the exit angle beta of the raised strip 130 _i2 Are all 0 degrees.

According to simulation experiments, compared with a fan adopting a conventional wind guide ring 100', the fan adopting the wind guide ring 100 of the application can improve the pneumatic static pressure efficiency by about 0.6%. Fig. 15 and 16 show flow field simulation diagrams of a fan adopting the conventional wind guide ring and a fan adopting the wind guide ring of the present application, respectively.

Referring to fig. 15, in the fan of the conventional wind guiding ring 100', a certain shedding vortex is generated near the end of the wind guiding ring 100' extending into the impeller 200', and the air flow in the region appears to be relatively turbulent, so that the aerodynamic static pressure efficiency of the fan is low, and the noise is large.

Referring to fig. 13 and 16, after the plurality of protruding strips 130 are added on the inner wall surface 114 of the outlet end 112 of the wind-guiding ring 100, the airflow near the outlet end 112 of the wind-guiding ring 100 is obviously improved, the airflow in the area becomes smoother, the aerodynamic static pressure efficiency of the fan is improved, and the noise is smaller.

Referring to fig. 4 to 6, an embodiment of the present application provides a fan, including: impeller 200 and above-mentioned wind-guiding circle 100, impeller 200 is used for connecting with the drive arrangement of fan, and the exit end 112 of wind-guiding circle 100 imbeds in the income wind gap 211 of impeller 200. The fan can be a centrifugal fan, a mixed flow fan, a wind driven generator and the like, and after the wind guide ring 100 of the embodiment is arranged, the air volume and the pneumatic and static pressure efficiency of the fan are effectively improved.

Because this fan has adopted all technical scheme of above-mentioned all embodiments, consequently all beneficial effects that have the technical scheme of above-mentioned embodiment brought again have, and the repeated description is no longer repeated herein.

Illustratively, the driving device may be a motor 300, and an output shaft of the motor 300 is directly connected to the impeller 200 or indirectly connected through a transmission mechanism to drive the impeller 200 to rotate. The drive device may also be a hydraulic motor or another rotary drive.

Referring to fig. 4 to 6, an electrical apparatus including the blower is provided in the embodiment of the present application. The electrical equipment can be a data center, a communication base station, an electrical cabinet, an air conditioner and other scenes which can adopt air cooling and heat dissipation. Exemplarily, electrical equipment is a data center, the data center is provided with a large number of high-power-consumption devices such as chips, the chips can generate a lot of heat during working, and the fan can cool and dissipate the high-power-consumption devices in air.

Since the electrical equipment adopts all the technical solutions of all the embodiments, all the beneficial effects brought by the technical solutions of the embodiments are also achieved, and are not described in detail herein.

Finally, it should be noted that: the above description is only an embodiment of the present application, but the scope of the present application is not limited thereto, and any changes or substitutions within the technical scope of the present disclosure should be covered by the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.

Claims

1. The air guide ring is characterized by comprising an air flow channel, wherein the air flow channel is provided with an inlet end and an outlet end which are arranged oppositely, the outlet end is embedded into an air inlet of an impeller, a gap is formed between the outer wall surface of the outlet end and the inner wall surface of the air inlet of the impeller, a plurality of air guide ribs are spirally arranged on the outer wall surface of the air guide ring along the circumferential direction, the air guide ribs are used for rotating backflow air which returns into the impeller through the gap, and the spiral outlet direction of the air guide ribs is consistent with the air inlet speed direction of the front edge of the blade of the impeller.

2. The wind-guiding collar of claim 1, wherein each wind-guiding rib has a first start end and a first end opposite to each other, the first start end being disposed toward the inlet end, and the first end being disposed adjacent to or extending to an edge of the outlet end.

3. The wind guide ring according to claim 1 or 2, wherein the thickness of the wind guide ribs ranges from 0.5mm to 3mm;

and/or the maximum radial height h of the wind guide ribs _o And the width g of the gap satisfies the following relationship: h is not less than 1mm _o ≤2g；

And/or the inlet angle range of the air guide ribs is-10 degrees to 10 degrees; the outlet angle range of the air guide ribs is-15-45 degrees.

4. The wind-guiding ring according to any one of claims 1 to 3, wherein each wind-guiding rib has a first surface and a concave curved surface connected to each other in a direction from the outlet end to the inlet end, the first surface is disposed opposite to an inner wall surface of the wind inlet of the impeller, a distance between the first surface and the inner wall surface of the wind inlet of the impeller is greater than or equal to a width of the gap, and the concave curved surface and an outer wall surface of the wind-guiding ring are recessed in the same direction.

5. The wind-guiding ring according to any one of claims 1 to 4, wherein the airflow rotating through the wind-guiding ribs flows to the blade tips of the impeller, and the angle of attack of the airflow at the blade tips of the impeller is in the range of-5 ° to 15 °.

6. The wind-guiding ring according to any one of claims 1 to 5, wherein the inner wall surface of the outlet end is provided with a plurality of protruding strips along the circumferential direction, each protruding strip has a second starting end and a second terminating end which are opposite, the second starting end is arranged towards the inlet end, and the second terminating end is arranged adjacent to the edge of the outlet end or extends to the edge of the outlet end.

7. The wind-guiding ring according to claim 6, wherein the thickness of the protruding strip ranges from 0.3mm to 1.5mm;

and/or the axial height range of the convex strips is 1 mm-15 mm;

and/or the distance between the second terminating end and the edge of the outlet end is 0 mm-3 mm;

and/or the maximum normal distance range between the top contour line of the convex strip and the inner wall surface of the outlet end is 0.3-1 mm;

and/or the inlet angle range of the raised strips is-10 to 10 degrees; the outlet angle range of the convex strip is-10 degrees to 10 degrees.

8. The wind-guiding ring according to claim 6 or 7, wherein, in the direction from the second starting end to the second terminating end, the distance between the top contour line of the convex strip and the inner wall surface of the outlet end gradually increases and then gradually decreases.

9. A fan, comprising: the air guide ring comprises an impeller and the air guide ring as claimed in any one of claims 1 to 8, wherein the impeller is used for being connected with a driving device of the fan, and the outlet end of the air guide ring is embedded into an air inlet of the impeller.

10. An electrical apparatus, characterized in that it comprises a fan as claimed in claim 9.