CN116464666A - Centrifugal impeller and centrifugal fan - Google Patents

Centrifugal impeller and centrifugal fan Download PDF

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Publication number
CN116464666A
CN116464666A CN202210030674.0A CN202210030674A CN116464666A CN 116464666 A CN116464666 A CN 116464666A CN 202210030674 A CN202210030674 A CN 202210030674A CN 116464666 A CN116464666 A CN 116464666A
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CN
China
Prior art keywords
blade
centrifugal impeller
edge
top plate
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202210030674.0A
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Chinese (zh)
Inventor
辛博
黄焕文
晁汐
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Huawei Technologies Co Ltd
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Huawei Technologies Co Ltd
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Filing date
Publication date
Application filed by Huawei Technologies Co Ltd filed Critical Huawei Technologies Co Ltd
Priority to CN202210030674.0A priority Critical patent/CN116464666A/en
Priority to PCT/CN2022/137640 priority patent/WO2023134344A1/en
Publication of CN116464666A publication Critical patent/CN116464666A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
    • H05K7/00—Constructional details common to different types of electric apparatus
    • H05K7/20—Modifications to facilitate cooling, ventilating, or heating

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The application relates to the field of fan equipment, in particular to a centrifugal impeller and a centrifugal fan. The centrifugal impeller includes: the blade assembly comprises a bottom plate, a top plate and a plurality of blades which are uniformly arranged along the circumferential direction of the axes of the top plate and the bottom plate and are positioned between the bottom plate and the top plate; the blade is provided with a front edge, a blade root, a tail edge and a blade tip, wherein the front edge and the tail edge are oppositely arranged, and the blade root and the blade tip are oppositely arranged; the blade comprises a main flow area and a jet flow area from a blade root to a blade tip, wherein one part of a front edge is positioned in the main flow area, and the other part of the front edge is positioned in the jet flow area; the direction of the relative velocity of the air flow and the blades flowing into the centrifugal impeller and the rotational velocity of the leading edge at the main flow regionForm an entrance angle beta in the opposite direction of (a) 1 The direction of the relative velocity of the air flow and the blade forms an inlet angle beta with the opposite direction of the rotational velocity of the leading edge at the jet zone 2 Inlet angle beta during rotation of the centrifugal impeller 1 Gradually decrease, entrance angle beta 2 Gradually increasing. The centrifugal impeller in the application can improve the pneumatic efficiency of the fan.

Description

Centrifugal impeller and centrifugal fan
Technical Field
The application relates to the field of fan equipment, in particular to a centrifugal impeller and a centrifugal fan.
Background
Along with the continuous increase of the power consumption of the chip of the electronic equipment, the refrigerating demand for various temperature control systems is increased, and the energy consumption of the temperature control systems is also increased continuously. For example, the refrigerating capacity requirement of a single refrigerating machine in a temperature control system of various large, medium and small data centers has reached tens to hundreds of kilowatts, the energy consumption of the refrigerating machine almost reaches the same magnitude, and the improvement of the refrigerating capacity and the energy efficiency ratio has become the core requirement of the temperature control system. In temperature control systems of various data centers, large centrifugal fans (with diameters of 400-1000 mm and power consumption of kilowatt level) are common and core refrigeration components.
Therefore, how to increase the efficiency of the centrifugal fan is a core problem of the temperature control system.
Disclosure of Invention
The application provides a centrifugal impeller and centrifugal fan, this centrifugal impeller can improve the efficiency of fan, satisfies temperature control system's refrigeration demand.
In a first aspect, a centrifugal impeller herein may include a base plate, a top plate, and a plurality of vanes, which may be uniformly arranged along a circumference of an axis of the top plate and the base plate and each located between the base plate and the top plate; the blade may have a leading edge, a blade root, a trailing edge and a blade tip, the leading edge and the trailing edge being disposed opposite each other, the blade root and the blade tip being disposed opposite each other in a direction from the blade root to the blade tip, the blade comprising a main flow region and a jet region, a portion of the leading edge being located in the main flow region and another portion being located in the jet region; the direction of the relative velocity of the air flow flowing into the centrifugal impeller and the blades and the opposite direction of the rotational velocity of the leading edge at the main flow region form an inlet angle beta 1 The direction of the relative velocity of the air flow and the blade and the opposite direction of the rotational velocity of the leading edge at the jet zone form an inlet angle beta 2 During rotation of the centrifugal impeller, an inlet angle beta 1 Gradually decrease, entrance angle beta 2 Gradually increasing.
In particular from root to rootDirection of blade tip, inlet angle beta of main flow area 1 Trend of variation with entrance angle beta of jet zone 2 The change trend of the blade tip and the front edge are different, so that the area where the blade tip and the front edge are connected is upwarp, and jet flow can be guided to smoothly enter the airflow channel of the fan impeller, thereby reducing the influence of the jet flow on the main flow and improving the efficiency of the fan.
In order to improve the efficiency of the centrifugal impeller, the main flow area may include a plurality of subareas in the direction from the blade root to the blade tip, and the inlet angle and beta of the subareas adjacent to the jet flow area 2 The maximum difference between the blade tips and the front edge can be 5 to 35 degrees, so that the upwarp of the area where the blade tips are connected with the front edge is obvious.
In a possible embodiment, in order to further increase the efficiency of the centrifugal impeller, the inlet angle β is the direction from the blade root to the blade tip 1 Can be reduced from 40 DEG to 25 DEG, and the inlet angle beta 2 Can be increased from 25 ° to 50 °.
In one possible embodiment, in order to make the design of the blade more rational, the angle between the tangent line of the center line of the blade at the leading edge and the rotation speed direction of the tangent point in the direction from the leading edge to the trailing edge is beta 3 Wherein beta is 3 And beta 1 Beta 2 May be-10 to 10 deg..
In one possible embodiment, the camber of the blade tip is adapted to be adapted in order to smooth the transition of the centre line of the blade from the leading edge to the trailing edge, in particular a plane formed by the angle t of the centre line of the blade in the circumferential direction with the abscissa and m with the ordinate, wherein,
m represents the integral length of the projection of any midline of the blade on the meridian plane from the leading edge to the trailing edge; r represents the distance from any point on the centerline to the axis of rotation of the centrifugal impeller; in the projection of the blade (t, m), the length of the line connecting the centerline of the jet zone and the intersection of the leading edge and the trailing edge is c, the height of the line connecting the centerline of the jet zone (the line connecting the centerline of the jet zone and the intersection of the leading edge and the trailing edge) is y, and the value of |y|/c may be 0 to 0.2. To ensure a smoother blade direction from leading edge to trailing edge.
It should be noted that the value of y/c may be 0.05 to make the centerline of the jet region and the centerline of the main stream region smoother from the leading edge to the trailing edge.
In one possible embodiment, in order to smooth the transition of the midline of the blade from the leading edge to the trailing edge, the camber of the midline of the jet region is greater than the camber of the midline of any of said main flow regions in the (t, m) projection.
In one possible embodiment, when the blade is specifically arranged, in order to sweep the tip and root of the blade, the trailing edge assumes a C-shaped configuration, and each portion of the blade needs to meet the following conditions: in the direction from the top plate to the bottom plate, the connecting line between the end part of the blade and the axis and the connecting line between the connecting point of the front edge and the blade root and the axis are in an included angle ofThe included angle between the connecting line of the end part of the blade and the axis and the connecting line of the connecting part of the front edge and the blade tip and the axis is +.>The included angle between the connecting line of the end part of the blade and the axis and the connecting line of the tail edge nearest to the front edge and positioned on the axis is +.>The included angle between the connecting line of the end part of the blade and the axis and the connecting line of the connecting part of the blade root and the tail edge and the axis is +.>Connection of the blade tip to the trailing edgeThe included angle between the connecting line of the position and the axis is +.>
Wherein,,
more specifically, the method comprises the steps of,
in one possible embodiment, the trailing edge may be inverted C-shaped in order to reduce stress concentrations between the root and the baseplate and between the tip and the top of the blade. Specifically, an included angle between a tangent line of the blade root at the connection position of the blade root and the tail edge and a tangent line of the tail edge at the connection position of the tail edge and the blade root is alpha 1 The included angle between the tangent line of the connection part of the tail edge and the blade tip and the tangent line of the connection part of the blade tip and the tail edge is alpha 2 Wherein the alpha is 1 And alpha 2 More than 15 deg. and less than 60 deg..
It should be noted that α 1 May be 30 DEG alpha 2 May be 40 °.
In a second aspect, the application further provides a centrifugal fan, including a motor, a wind-guiding ring and a centrifugal impeller in any one of the first aspect, wherein the wind-guiding ring is located above the top plate, and the axial distance between the wind-guiding ring and the junction of the blade tip and the front edge is 0 to 10mm. Specifically, due to the change of the blades in the centrifugal impeller, the flow of the blade grid channels in the centrifugal fan can be obviously improved, so that the efficiency of the centrifugal fan is improved.
It should be noted that, in order to improve the efficiency of the centrifugal fan, the axial distance between the wind guiding ring and the connection position of the blade tip and the front edge may be 4mm.
In a possible embodiment, the axis of the base plate is provided with a mounting hole for mounting the motor, and the head of the motor is arranged on the base plateThe motor head is provided with a guide surface which is positioned in the circumferential direction of the platform, and the diameter of the platform is D 1 The diameter of one side of the bottom plate far away from the top plate is D 2 ，D 1 /D 2 < 0.2; the side of the bottom plate facing the top plate and the guide surface form a continuous curved surface, and the curvature radius rho of any point on the curved surface is more than 10mm. In the setting mode, the vortex flow at the junction of the motor and the bottom plate can disappear, so that the efficiency of the centrifugal fan is improved, a wind scooper is not required to be arranged, the assembly process of the device is simplified, and the use of materials can be reduced, so that the cost is saved.
In order to make the centrifugal fan more efficient, D 1 Can be 45mm, D 2 May be 600mm and ρ may be 22.5mm.
Drawings
FIG. 1 is a schematic diagram of a centrifugal fan in the prior art;
FIG. 2a is a front view of FIG. 1;
FIG. 2b is a partial side view of FIG. 1;
fig. 3 is a schematic structural view of a blade in a centrifugal wind wheel according to an embodiment of the present disclosure;
FIG. 4 is a partial side view of a centrifugal wind wheel provided with a wind guide ring according to an embodiment of the present application;
fig. 5 is a schematic structural diagram of a centrifugal wind wheel according to an embodiment of the present disclosure;
fig. 6 is a schematic structural diagram of a centrifugal wind wheel according to an embodiment of the present disclosure;
FIG. 7a is a simulated view of a blade in a centrifugal wind wheel provided in an embodiment of the present application;
FIG. 7b is a schematic view of a midline of a main flow region and a jet region of a blade provided by an embodiment of the present application;
FIG. 8 is a schematic view of a projection of a blade on a two-dimensional plane provided by an embodiment of the present application;
fig. 9 is a top view of a centrifugal wind wheel provided in an embodiment of the present application from a top plate to a bottom plate;
FIG. 10 is a schematic view of a centrifugal wind wheel according to an embodiment of the present disclosure showing a blade;
FIG. 11a is a simulation of stress concentration for a prior art centrifugal wind wheel;
FIG. 11b is a simulation diagram of stress concentration of a centrifugal wind wheel provided by an embodiment of the present application;
FIG. 12a is a schematic view of a prior art centrifugal wind wheel with 95% blade height and adjacent flow field stretched projection on a plane;
FIG. 12b is a schematic view of a prior art centrifugal wind wheel with 99% blade height and an adjacent flow field stretched projection on a plane;
FIG. 12c is a schematic view of a centrifugal wind wheel with 95% blade height and an adjacent flow field stretched projection on a plane according to an embodiment of the present application;
FIG. 12d is a schematic view of a centrifugal wind wheel with 99% blade height and an adjacent flow field stretched projection on a plane according to an embodiment of the present application;
FIG. 13 is a schematic diagram of a centrifugal fan efficiency detection structure according to an embodiment of the present disclosure;
fig. 14 is a schematic diagram of the motor and the bottom plate in the centrifugal fan provided in the embodiment of the application;
FIG. 15a is a schematic illustration of a prior art centrifugal fan in which the motor is swirling at the interface with the base plate;
FIG. 15b is a schematic diagram of vortex flow at the interface between the motor and the bottom plate in the centrifugal fan according to the embodiment of the present application;
fig. 16 is a schematic diagram of a centrifugal fan efficiency detection structure according to an embodiment of the present disclosure.
Reference numerals:
1-an air guide ring; 2-top plate; 3-a bottom plate; 4-leaf blades; 5-a motor;
10-leaf blade; 11-leading edge; 12-blade root; 120-root midline; 13-trailing edge; 14-blade tips; 140-tip midline; 20-top plate; 30-a bottom plate; 40-wind guiding ring; 50-an electric motor; 51-platform.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the present application more apparent, the present application will be described in further detail with reference to the accompanying drawings.
In the prior art, a centrifugal fan is a core refrigeration component of a data center, as shown in fig. 1, the centrifugal fan comprises a wind guide ring 1, an impeller and a motor 5, wherein the wind guide ring 1 is a static piece, the wind guide ring 1 is arranged at an impeller inlet and has a certain overlapping length with the impeller inlet in the axial direction and has a smaller distance with the impeller inlet in the radial direction, and the main function of the wind guide ring 1 is to guide air flow to smoothly enter the fan impeller; the impeller is a rotating piece and comprises a top plate 2, a bottom plate 3 and a plurality of blades 4 arranged between the top plate 2 and the bottom plate 3; the motor 5 is a power component, the motor 5 is directly connected with the impeller, the impeller rotates and does work on gas under the driving of the motor 5, so that air is sucked into the air guide ring and then enters the impeller, and then is thrown to the outside after turning by about 90 degrees, and the air flow is formed to dissipate heat of the refrigeration equipment.
However, the following factors will generally have a significant impact on the efficiency of the centrifugal fan shown in fig. 1, and are described below in conjunction with fig. 2a and 2b, respectively:
1. influence of the air guide ring 1 and impeller gap: the wind-guiding ring 1 and the impeller are respectively static and rotating parts, a gap is necessarily formed between the static and rotating parts, air is sucked into the wind-guiding ring, so that the wind-guiding ring and the front area thereof are a negative pressure area (A area), and conversely, the outside of the impeller is a positive pressure area (B area), under the action of positive and negative pressure differences, air flow is 'shot' into the impeller air flow channel from the gap, and the air flow near the blades and in the impeller air flow channel is impacted, so that the air quantity and efficiency of the fan are reduced.
2. Influence of the matching molded line of the head part of the motor 5 and the impeller bottom plate 3: the motor 5 and the impeller are usually designed separately, the volume of the motor 5 is larger, the motor 5 protrudes out of the impeller bottom plate 3, and the molded lines are discontinuous, so that after the airflow enters the impeller, strong vortex flow is generated near the boundary between the motor 5 and the impeller due to the blocking effect of the outer contour of the motor 5, the flow can block the channel and can continuously dissipate kinetic energy into heat energy, and finally the air quantity and the pneumatic efficiency of the fan are reduced.
In order to solve the problems, the application provides a centrifugal impeller and a centrifugal fan.
The terminology used in the following embodiments is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. As used in the specification and the appended claims, the singular forms "a," "an," "the," and "the" are intended to include, for example, "one or more" such forms of expression, unless the context clearly indicates to the contrary.
Reference in the 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 application. Thus, appearances of the phrases "in one embodiment," "in some embodiments," "in other embodiments," and the like in the specification are not necessarily all referring to the same embodiment, but mean "one or more but not all embodiments" unless expressly specified otherwise. The terms "comprising," "including," "having," and variations thereof mean "including but not limited to," unless expressly specified otherwise.
For ease of understanding the present application, the chord, span and meridian planes of the blade are described below, with reference to FIG. 3, the blade 10 may be subdivided into a blade leading edge 11, a blade body and a trailing edge 13, with the connection of the blade 10 to the base plate being referred to as the blade root 12 and the connection of the blade 10 to the top plate being referred to as the blade tip 14. The direction from the leading edge 11 to the trailing edge 13 is referred to as chordwise and the direction from the root 12 to the tip 14 is referred to as spanwise. The center line of the blade is the connecting line of the middle points of the vertical heights of the upper surface and the lower surface of the blade, the mean camber lines of all the spanwise sections of the blade 10 form the center plane of the blade, for convenience of subsequent description, the chord direction and the spanwise position are defined herein, the mean camber line length of a certain spanwise section is l, the spanwise height of a certain chordwise section is h, the chordwise 10% position refers to a certain spanwise section, the center plane moves from the front edge 11 to the tail edge 13, and the 10% spanwise height refers to a certain chordwise section moving from the blade root 12 to the blade tip 14 for 0.1h.
The meridian plane is a plane passing through the rotation axis of the centrifugal fan, referring to fig. 4, the meridian plane flow path of the centrifugal fan refers to the intersection line of the bottom plate 30 and the top plate 20 with the meridian plane, and the meridian plane flow path further includes the projection of the fan blades 10 on the meridian plane along the circumferential direction, that is, the front edge 11 and the tail edge 13 of the blades shown in the meridian plane rotate around the axis of the centrifugal fan, and the formed curved surface just can include the leading edge 11 molded line and the tail edge 13 molded line of all the blades 10 of the centrifugal fan.
Referring to fig. 3 to 5, the present application provides a centrifugal impeller including a base plate 30, a top plate 20, and a plurality of blades 10, wherein the plurality of blades 10 are uniformly arranged along a circumferential direction of an axis of the top plate 20 and the base plate 30, and the plurality of blades 10 are located between the base plate 30 and the top plate 20; the blade 10 has a leading edge 11, a blade root 12, a trailing edge 13 and a blade tip 14, the leading edge 11 and the trailing edge 13 being disposed opposite each other, the blade root 12 and the blade tip 14 being disposed opposite each other; from the blade root 12 to the blade tip 14, the blade 10 comprises a main flow region in which a part of the leading edge 11 is located and a jet region in which another part is located; the direction of the relative velocity of the air flow flowing into the centrifugal impeller and the blades 10 forms an inlet angle beta with the opposite direction of the rotational velocity of the leading edge 11 in the main flow region 1 The direction of the relative velocity of the air flow and the blade 10 forms an inlet angle beta with the opposite direction of the rotational velocity of the leading edge 11 at the jet zone 2 Inlet angle beta during rotation of the centrifugal impeller 1 Gradually decrease, entrance angle beta 2 Gradually increasing.
Specifically, for the sake of clearer expression of beta 1 And beta 2 With continued reference to FIG. 6,W, which shows the direction of the relative velocity of the airflow and the blade 10, U shows the direction of the rotational velocity of the leading edge 11, C shows the absolute velocity of the airflow, β 1 Beta 2 Is the included angle between the reverse directions of W and U; wherein the jet area can be represented as the area between the line near the blade tip 14 and the blade tip 14 in fig. 7a (it can be understood that the direction from the blade root 12 to the blade tip 14 is more than 95% of the area is the jet area, wherein the position of the jet area can be adjusted according to the actual situation), due to the inlet angle beta of the main flow area 1 Trend of variation with entrance angle beta of jet zone 2 The change trend of the blade tip 14 and the front edge 11 is different, so that the blade tip 14 and the front edge 11 can be tilted upwards and guidedThe jet flow smoothly enters the airflow channel of the impeller of the centrifugal fan, so that the influence of the jet flow on the main flow is reduced, and the efficiency of the fan is improved.
For greater fan efficiency, the main flow region may include a plurality of sub-regions, the inlet angle and beta of the sub-regions adjacent the jet region, in the direction from the blade root 12 to the blade tip 14 2 The maximum difference between them is 5 to 35 DEG, and the entrance angle and beta of the sub-region adjacent to the jet region 2 The difference between the two is 5-35 degrees, so that the region where the blade tip 14 and the front edge 11 are connected has obvious upturned, the jet flow is guided to smoothly enter the airflow channel of the centrifugal fan impeller, and the influence of the jet flow on the main flow is reduced.
It should be noted that, in order to more clearly show that there is a significant upturned connection between the blade tip 14 and the leading edge 11, reference may be made to fig. 7b, in which fig. 7b, the first line may be defined as the blade root centerline 120, the last line may be defined as the blade tip centerline 140, and as can be seen from fig. 7a and 7b, the lines between the blade tip centerline 140 and the blade root centerline 120, and between the blade tip centerline 140 and the blade root centerline 120, have a significant upturned front edge of the blade tip centerline 140.
In one possible embodiment, in order to make the design of the blade more rational, the tangential line of the midline of the blade 10 at the leading edge 11 in the direction of the leading edge 11 to the trailing edge 13 is at an angle beta to the rotational speed direction of the tangent point 3 Wherein beta is 3 And beta 1 Beta 2 May be-10 to 10 deg..
In one possible embodiment, in order to smooth the transition of the centre line of the blade from the leading edge to the trailing edge, the camber of the blade tip needs to be adapted, in particular, with reference to fig. 8, the angle t in the circumferential direction of the centre line of the blade is an abscissa, a plane formed by m is an ordinate, wherein,
m represents the integral length of the projection of any central line of the blade on the meridian plane from the leading edge to the trailing edge; r represents the distance from any point on the midline to the axis of the base plate; in the projection of (t, m), the length of the line connecting the centerline of the jet region with the intersection of the leading edge 11 and the trailing edge 13 is c, the height between the centerline of the jet region and the line connecting the centerline of the jet region with the intersection of the leading edge 11 and the trailing edge 13 is y, and the value of y/c may be 0 to 0.2.
It should be noted that the value of y/c may be 0.05 to make the center line of the blade smoother from the leading edge 11 to the trailing edge 13, wherein the value of y/c may also be 0.03, 0.1, 0.16, etc. In addition, it can be seen from fig. 8 that the projection of the midline of the jet region is different from the projection of the midline of the blade spanwise 90% (main flow region), i.e. the projection of the midline of the jet region has a curvature greater than the projected curvature of the midline of the main flow region.
Referring to fig. 9, in particular, when the blade is provided, in order for the trailing edge 13 of the blade to be of an inverted C-shape, each portion of the blade needs to satisfy the following conditions: in the direction from the top plate to the bottom plate 30 and in the clockwise direction, the line between the end of the blade and the axis of the bottom plate 30 and the top plate (the horizontal projection is the center of the top plate) is defined as a straight line a, the line between the junction of the front edge 11 and the blade root 12 and the axis is defined as a straight line b, the line between the junction of the front edge 11 and the blade tip 14 and the axis is defined as a straight line c, the line between the tail edge 13 closest to the front edge 11 and the axis is defined as a straight line d, the line between the junction of the blade root 12 and the tail edge 13 and the axis is defined as a straight line e, and the line between the junction of the blade tip 14 and the tail edge 13 and the axis is defined as a straight line f, wherein the included angle between the straight line a and the straight line b isThe angle between the straight line a and the straight line c is +.>The angle between the line a and the line d is +.>The angle between the line a and the line e is +.>The included angle between the straight line a and the straight line f is +.>Wherein,,more specifically, the ∈> The arrangement mode can reduce stress concentration at the joint of the blade root 12 and the bottom plate 30, and also can reduce stress concentration at the joint of the blade tip 14 and the top plate, thereby improving the aerodynamic efficiency of the centrifugal fan.
Referring to fig. 9 and 10, in a specific arrangementAnd->When (I)>Can be 3 DEG, or>Can be 30 DEG,/DEG>Can be 50 DEG, ">Can be 65 DEG%>May be 76 °; at this time, the included angle α between the tangent line of the blade root 12 at the junction of the blade root 12 and the trailing edge 13 and the tangent line of the trailing edge 13 at the junction of the trailing edge 13 and the blade root 12 1 ，α 1 May be 30 DEG, and the included angle alpha between the tangent line of the trailing edge 13 at the junction of the trailing edge 13 and the blade tip 14 and the tangent line of the blade tip 14 at the junction of the blade tip 14 and the trailing edge 13 2 ，α 2 May be 40 deg., where, due to alpha 1 And alpha 2 The value of (2) may be greater than 15 ° and less than 60 °, stress concentrations between the blade root 12 and the bottom plate 30, and between the blade tip 14 and the top plate 20 on the blade 10 may be reduced, and aerodynamic efficiency of the centrifugal fan may be improved.
More specifically, to illustrate the effect of a centrifugal fan that may have an inverted-C-shaped trailing edge, referring to fig. 11a and 11b, the local stress concentration of a centrifugal fan having an inverted-C-shaped trailing edge may be reduced from 220MPa to 140MPa, and the aerodynamic efficiency of a centrifugal fan having a C-shaped trailing edge may be improved by 0.5% in the present application, compared to a centrifugal fan having an inverted-C-shaped trailing edge and a centrifugal fan having no C-shaped trailing edge.
When the centrifugal impeller as described above with reference to fig. 3 to 6 is applied to a centrifugal fan, the centrifugal fan may include a motor 50, a wind guide ring 40 and the centrifugal impeller as described above, the wind guide ring 40 is located above a top plate 20 of the centrifugal impeller, and an axial distance between the wind guide ring 40 and a junction between a tip 14 of a blade 10 and a leading edge 11 of the centrifugal impeller is 0 to 10mm.
Specifically, the axial distance between the tip 14 and the leading edge 11 of the blade 10 may be 4mm, and the area from the root 12 to 95% of the blade height in the spanwise direction may be the main flow area, where the inlet angle β is 1 Slowly decreasing from 40 ° to 25 °, the entry angle β in the jet zone 2 From 25 to 50, and y/c may be 0.05 to make the midline of the blade 10 smoother from the leading edge 11 to the trailing edge 13. FIG. 12a is a schematic view of a prior art centrifugal wind wheel with 95% blade height and adjacent flow field stretched projection on a plane; FIG. 12b is a schematic view of a prior art centrifugal wind wheel with 99% blade height and an adjacent flow field stretched projection on a plane; referring to fig. 12a, 12b, 12c and 12d, stretching projection of all blades with 95% and 99% spanwise blade heights and adjacent flow fields onto a plane can show that the impeller in the prior art has locally obvious vortex or separation flow, and the fluidity of the blade grid channels of the impeller in the application is obviously improved. Further, referring to the actual measurement result of FIG. 13Where P represents the fan operating backpressure (Pa), Q represents the fan flow (CMH), the test standard is AMCA 210-07, the right vertical axis represents the aerostatic efficiency of the fan, and the maximum aerostatic efficiency of the centrifugal fan in the present application is improved by about 3% relative to the existing centrifugal fan.
With continued reference to fig. 14, when a motor to be engaged with the centrifugal impeller is specifically provided, an assembly hole may be provided at the axis of the bottom plate 30, and a motor head is provided in the assembly hole, wherein a platform 51 is provided on a side of the motor head facing the top plate, the motor head is further provided with a guide surface located in the circumferential direction of the platform, and the diameter of the platform 51 is D 1 The side of the bottom plate 30 remote from the top plate has a diameter D 2 Wherein D is 1 /D 2 < 0.2; the side of the bottom plate 30 facing the top plate and the guide surface form a continuous curved surface, and the curvature radius rho of any point on the curved surface is more than 10mm. In the arrangement mode, vortex flow caused by discontinuity of the connection part of the impeller and the motor can be eliminated without using a guide cover, so that the pneumatic efficiency of the centrifugal fan is improved, in addition, structural parts of the centrifugal fan can be reduced, the installation and production cost is reduced, and the heat dissipation requirement of the high-power motor cannot be influenced.
More specifically, D 1 Can be 45mm, D 2 The plane of the bottom plate 30 facing the top plate is protruded to the position where the top plate is located, the connection part of the bottom plate and the platform 51 of the motor is a curved surface, the curvature radius of the connection part is minimum, and the minimum curvature radius ρ can be 22.5mm. At this time, referring to fig. 15a and 15b, it can be seen that the swirl flow at the boundary between the motor and the bottom plate in the present application disappears by comparing the centrifugal fan of the related art and the centrifugal fan in the present application. Referring to the actual measurement result of fig. 16, the pneumatic efficiency of the centrifugal fan is improved by 2.1%, and it is further explained that the vortex flow can be eliminated without using the wind scooper, thereby achieving the purpose of improving the pneumatic efficiency of the centrifugal fan.
The foregoing is merely specific embodiments of the present application, but the scope of the present application is not limited thereto, and any person skilled in the art can easily think about changes or substitutions within the technical scope of the present application, and the changes or substitutions are intended to 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 (16)

1. A centrifugal impeller, comprising: a bottom plate, a top plate, and a plurality of vanes that are uniformly arranged along a circumferential direction of an axis of the top plate and the bottom plate, and that are each located between the bottom plate and the top plate;
each blade has a leading edge, a blade root, a trailing edge, and a blade tip, the leading edge and the trailing edge being disposed opposite each other, the blade root and the blade tip being disposed opposite each other;
a direction from the blade root to the blade tip, the blade comprising a main flow region and a jet region, a portion of the leading edge being located in the main flow region and another portion being located in the jet region;
the direction of the relative velocity of the air flow flowing into the centrifugal impeller and the blades forms an inlet angle beta with the opposite direction of the rotational velocity of the leading edge at the main flow region 1 The direction of the relative velocity of the air flow and the blade, and the opposite direction of the rotational velocity of the leading edge at the jet zone, form an inlet angle beta 2 ；
During rotation of the centrifugal impeller, the inlet angle beta 1 Gradually decrease, the inlet angle beta 2 Gradually increasing.
2. The centrifugal impeller of claim 1, wherein the main flow region includes a plurality of sub-regions from the blade root to the blade tip, the inlet angle and β of the sub-regions adjacent to the jet region 2 The maximum difference between them is 5 to 35.
3. Centrifugal impeller according to claim 1 or 2, wherein the inlet angle β is the direction from the blade root to the blade tip 1 From 40 ° to 25 °, said entry angle β 2 Increasing from 25 ° to 50 °.
4. A centrifugal impeller according to any one of claims 1-3, wherein the tangential line of the centre line of the blade at the leading edge in the direction from the leading edge to the trailing edge forms an angle β with the direction of the rotational speed of the tangent point 3 Wherein beta is 3 And beta 1 Beta 2 Is-10 to 10 deg..
5. The centrifugal impeller according to any one of claims 1 to 4, wherein a plane is formed with an angle t in the circumferential direction of the center line of the blade as an abscissa and m as an ordinate, wherein,
m represents the integral length of the projection of any midline of the blade on a meridian plane from the leading edge to the trailing edge;
r represents the distance from any point on the midline to the rotation axis of the centrifugal impeller;
in the projection of (t, m), the length of the line connecting the points of intersection of the leading edge and the trailing edge with the centerline of the jet zone is c, the height between the centerline of the jet zone and the line is y, and the |y|/c=0 to 0.2.
6. The centrifugal impeller of claim 5, wherein the camber of the centerline of the jet region is greater than the camber of the centerline of any of the main flow regions in the projection of (t, m).
7. The centrifugal impeller of claim 5, wherein y/c = 0.05.
8. The centrifugal impeller according to any one of claims 1-7, wherein the trailing edge is inverted-C-shaped.
9. A centrifugal impeller according to any one of claims 1 to 8, wherein the top plate is provided with an air inlet, the top plate is spaced from the bottom plate, and the axes of the top plate and the bottom plate are coincident.
10. The centrifugal impeller of claim 9, wherein the connection between the ends of the blades and the axis in the clockwise direction in the direction of the top plate toward the bottom plate is at an angle to the connection between the front edge and the blade root and the axis ofThe included angle between the connecting line of the end part of the blade and the axis and the connecting line of the connecting part of the front edge and the blade tip and the axis is +.>The included angle between the connecting line of the end part of the blade and the axis and the connecting line of the tail edge nearest to the front edge and positioned on the axis is +.>The included angle between the connecting line of the end part of the blade and the axis and the connecting line of the connecting part of the blade root and the tail edge and the axis is +.>The included angle between the connecting line of the end part of the blade and the axis and the connecting line of the connecting part of the blade tip and the tail edge and the axis is +.>
Wherein,,
11. the centrifugal impeller according to claim 10, whereinIn that the method is characterized in that,
12. the centrifugal impeller of claim 11, wherein the angle α between a tangent to the blade root at the junction of the blade root and the trailing edge and a tangent to the trailing edge at the junction of the trailing edge and the blade root is 1 The included angle between the tangent line of the connection part of the tail edge and the blade tip and the tangent line of the connection part of the blade tip and the tail edge is alpha 2 Wherein the alpha is 1 And alpha 2 More than 15 deg. and less than 60 deg..
13. The centrifugal impeller according to claim 12, wherein the α 1 30 DEG, said alpha 2 40 deg..
14. A centrifugal fan comprising a motor, a wind-guiding ring and a centrifugal impeller according to any one of claims 1 to 13;
the wind guide ring is positioned above the top plate, and the axial distance between the wind guide ring and the junction of the blade tip and the front edge is 0-10 mm.
15. The centrifugal fan according to claim 14, wherein an assembly hole for mounting the motor is provided at an axis of the bottom plate, a head of the motor is provided at the assembly hole, a side of the motor head facing the top plate has a platform with a diameter D 1 The diameter of the side of the bottom plate far away from the top plate is D 2 ，D 1 /D 2 ＜0.2；
The head of the motor is also provided with a guide surface, the guide surface is arranged in the circumferential direction of the platform, a continuous curved surface is formed on one side of the guide surface, which faces the top plate, of the bottom plate, and the curvature radius rho of any point on the curved surface is more than 10mm.
16. The centrifugal fan of claim 15, wherein D 1 =45 mm, said D 2 =600 mm, said ρ=22.5 mm.
CN202210030674.0A 2022-01-12 2022-01-12 Centrifugal impeller and centrifugal fan Pending CN116464666A (en)

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RU2550370C2 (en) * 2011-05-11 2015-05-10 Альстом Текнолоджи Лтд Centrifugal nozzle with projecting parts
CN102837383A (en) * 2012-08-08 2012-12-26 苏州工业园区协利塑胶有限公司 Centrifugation fan mould
CN111577655B (en) * 2020-04-14 2021-11-05 约克广州空调冷冻设备有限公司 Blade and axial flow impeller using same
CN111878455A (en) * 2020-09-17 2020-11-03 珠海格力电器股份有限公司 Centrifugal impeller, centrifugal fan and refrigeration equipment
CN113202789B (en) * 2021-06-09 2022-09-30 清华大学 Impeller for centrifugal compressor and centrifugal compressor
CN113738694B (en) * 2021-08-25 2024-04-05 哈尔滨工业大学 High-performance centrifugal impeller of breathing machine with round head-shaped front edge blade profile

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