CN116066402A - Centrifugal fan impeller and air conditioner - Google Patents

Centrifugal fan impeller and air conditioner Download PDF

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Publication number
CN116066402A
CN116066402A CN202111294399.5A CN202111294399A CN116066402A CN 116066402 A CN116066402 A CN 116066402A CN 202111294399 A CN202111294399 A CN 202111294399A CN 116066402 A CN116066402 A CN 116066402A
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China
Prior art keywords
edge side
centrifugal fan
degrees
fan impeller
air
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CN202111294399.5A
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Chinese (zh)
Inventor
李颖颖
柯得军
杜伟
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Aux Air Conditioning Co Ltd
Ningbo Aux Electric Co Ltd
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Aux Air Conditioning Co Ltd
Ningbo Aux Electric Co Ltd
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Priority to CN202111294399.5A priority Critical patent/CN116066402A/en
Publication of CN116066402A publication Critical patent/CN116066402A/en
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    • 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
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
    • 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
    • F04D29/66—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
    • F04D29/663—Sound attenuation
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0022—Centrifugal or radial fans

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention discloses a centrifugal fan impeller and an air conditioner, and relates to the technical field of air conditioners. The centrifugal fan impeller comprises a wheel disc and a plurality of fan blades. The plurality of fan blades are arranged in the wheel disc in an annular array, the fan blades are provided with a flange side, a front edge side, a concave edge side and a rear edge side which are connected end to end, the rear edge side is connected with the wheel disc, the cross section of the concave edge side is arc-shaped, and the cross section of the flange side is a fitting curve formed by sequentially connecting four sections of curves or straight lines. Compared with the prior art, the centrifugal fan impeller provided by the invention has the advantages that due to the adoption of the concave edge side arranged in the arc shape and the flange side arranged in the fitting curve, the generated noise can be reduced, the air quantity loss is reduced, the air outlet quantity is increased, the air outlet effect is improved, and the user experience is improved.

Description

Centrifugal fan impeller and air conditioner
Technical Field
The invention relates to the technical field of air conditioners, in particular to a centrifugal fan impeller and an air conditioner.
Background
At present, in the application of an air conditioner, a centrifugal fan is generally utilized to drive air to flow so as to form an air outlet flow, and then a heat exchanger is utilized to exchange heat for the air outlet flow so as to realize the heating or refrigerating function. Most of impellers in the conventional centrifugal fan adopt a multi-wing forward mode, and the blades have equal thickness or no change rule along the chord length direction, so that in the air outlet process of the centrifugal fan, the impellers rotate at high speed, ambient air pressure pulsation can be caused, air pressure acts on a volute part to form noise, certain air quantity loss can be caused, the air outlet quantity is reduced, the air outlet efficiency is reduced, and the user experience is influenced.
Disclosure of Invention
The invention solves the problems of reducing the generated noise, reducing the air quantity loss, increasing the air quantity, improving the air outlet effect and improving the user experience.
In order to solve the problems, the technical scheme of the invention is realized as follows:
in a first aspect, the invention provides a centrifugal fan impeller, comprising a wheel disc and a plurality of fan blades, wherein the fan blades are arranged in the wheel disc in a ring-shaped array, the fan blades are provided with a flange side, a front edge side, a concave edge side and a rear edge side which are connected end to end, the rear edge side is connected with the wheel disc, the cross section of the concave edge side is in an arc shape, the cross section of the flange side is a fitting curve formed by sequentially connecting four sections of curves or straight lines, and the function relation of the fitting curve is as follows:
Figure BDA0003335993130000011
the unit of x is millimeter, the x-axis direction is the direction from the front edge side to the rear edge side on the connecting line of the two ends of the mean camber line of the fan blade, the y-axis direction is the direction perpendicular to the x-axis and from the concave edge side to the flange side, and the origin is the intersection point of the mean camber line of the fan blade and the front edge side. Compared with the prior art, the centrifugal fan impeller provided by the invention has the advantages that due to the adoption of the concave edge side arranged in the arc shape and the flange side arranged in the fitting curve, the generated noise can be reduced, the air quantity loss is reduced, the air outlet quantity is increased, the air outlet effect is improved, and the user experience is improved.
Further, when x=2.5, the distance between the concave edge side and the flange side is the largest, and the thickness of the fan blade is the largest. The thickness of the fan blade is gradually increased and then gradually reduced in the x-axis direction, so that the air flow flowing through the fan blade is outwards diffused towards the two sides of the fan blade, and then approaches to each other along the concave edge side and the flange side, the air resistance is reduced, and the air outlet efficiency is improved.
Further, the central angle of the arc formed by the concave edge side ranges from 90 degrees to 110 degrees. The central angle of reasonable concave edge side can guarantee to have sufficient arc length to lead air when being convenient for processing production to improve the wind-guiding effect, reduce the noise that produces.
Further, the number of the fan blades ranges from 42 to 45. The reasonable number of the fan blades can ensure the air output and simultaneously reduce the generated noise as much as possible.
Further, an inlet installation angle is formed between a circle taking the middle point of the wheel disc as the center and passing through the origin and the camber line of the fan blade, and the range of the inlet installation angle is 65-75 degrees. The reasonable inlet mounting angle can effectively improve the static pressure ratio and isentropic efficiency of the fan blade while guaranteeing the air output.
Further, an outlet installation angle is formed between a circle taking the middle point of the wheel disc as the center of a circle and passing through the intersection point of the fan blade mean camber line and the trailing edge side and the fan blade mean camber line, and the range of the outlet installation angle is 160-175 degrees. The reasonable outlet installation angle can effectively increase the air output, improve the air output efficiency and reduce the generated noise.
Further, the difference between the outlet mounting angle and the inlet mounting angle ranges from 90 degrees to 105 degrees. The reasonable difference between the outlet installation angle and the inlet installation angle can reduce the generated noise as much as possible while guaranteeing the air outlet effect, and is convenient for the processing of the centrifugal fan impeller.
Further, the cross section of the front edge side is arc-shaped, and the radius of the arc of the front edge side ranges from 0.5 mm to 0.7 mm. The reasonable radius of the arc on the front edge side can ensure the air guiding effect and reduce the air resistance to the maximum extent.
Further, the ratio of the diameter of the circle centered at the midpoint of the wheel disc and passing through the origin to the outer diameter of the wheel disc ranges from 0.78 to 0.85. The reasonable wheel diameter ratio can increase the air output, improve the air output efficiency and reduce the generated noise.
In a second aspect, the invention provides an air conditioner, including the centrifugal fan impeller, where the centrifugal fan impeller includes a wheel disc and a plurality of fan blades, the plurality of fan blades are arranged in the wheel disc in a ring array, the fan blades are provided with a flange side, a front edge side, a concave edge side and a rear edge side, the rear edge side is connected with the wheel disc, the cross section of the concave edge side is in a circular arc shape, the cross section of the flange side is a fitting curve formed by sequentially connecting four sections of curves or straight lines, and the function relationship of the fitting curve is:
Figure BDA0003335993130000031
the unit of x is millimeter, the x-axis direction is the direction from the front edge side to the rear edge side on the connecting line of the two ends of the mean camber line of the fan blade, the y-axis direction is the direction perpendicular to the x-axis and from the concave edge side to the flange side, and the origin is the intersection point of the mean camber line of the fan blade and the front edge side. The air conditioner can reduce the noise that produces, reduces the amount of wind loss, increases the air output, improves the air-out effect, promotes user experience.
Drawings
FIG. 1 is an isometric view of a centrifugal fan wheel according to a first embodiment of the present invention;
FIG. 2 is a front view of a centrifugal fan wheel according to a first embodiment of the invention;
FIG. 3 is a schematic view of a centrifugal fan impeller according to a first embodiment of the present invention, in which a wheel disc is connected to a fan blade;
FIG. 4 is a diagram of a mathematical model of the connection of a disk to a blade in a centrifugal fan impeller according to a first embodiment of the invention;
FIG. 5 is a mathematical model of the flange side of a fan blade in a centrifugal fan wheel according to a first embodiment of the invention;
FIG. 6 is another mathematical model of the connection of the disk to the blade in the centrifugal fan wheel according to the first embodiment of the invention;
FIG. 7 is a mathematical model of a centrifugal fan wheel according to a first embodiment of the invention;
FIG. 8 is a top view of a centrifugal fan wheel according to a first embodiment of the invention;
fig. 9 is a schematic structural view of a centrifugal fan impeller according to a first embodiment of the present invention, in which a first fan blade and a second fan blade are arranged in a staggered manner.
Reference numerals illustrate:
100-centrifugal fan impeller; 110-a wheel disc; 111-a first wheel disc; 112-a second wheel disc; 120-fan blades; 121-flange side; 122-leading edge side; 123-concave edge side; 124-trailing edge side; 125-a first fan blade; 126-second fan blade.
Detailed Description
In order that the above objects, features and advantages of the invention will be readily understood, a more particular description of the invention will be rendered by reference to specific embodiments thereof which are illustrated in the appended drawings.
First embodiment
Referring to fig. 1 and 2 in combination, an embodiment of the present invention provides a centrifugal fan impeller 100 for generating negative pressure to drive air flow to form an air-out airflow. The novel air conditioner can reduce the generated noise, reduce the air quantity loss, increase the air outlet quantity, improve the air outlet effect and improve the user experience.
The centrifugal fan impeller 100 is applied to a centrifugal fan (not shown), and the centrifugal fan includes a driving motor (not shown) and the centrifugal fan impeller 100. The driving motor is in transmission connection with the centrifugal fan impeller 100, and the driving motor can drive the centrifugal fan impeller 100 to rotate so as to enable the centrifugal fan impeller 100 to generate negative pressure and drive air to flow to form air-out air flow.
Referring to fig. 3, 4 and 5, the centrifugal fan impeller 100 includes a disk 110 and a plurality of blades 120. The wheel disc 110 is annularly arranged, the plurality of fan blades 120 are annularly arranged in the wheel disc 110 in an array, and the plurality of fan blades 120 jointly act to drive air to flow to form air-out air flow. The fan blades 120 are bent to guide air, reduce air resistance and improve air outlet efficiency. Specifically, the fan blade 120 is provided with a flange side 121, a front edge side 122, a concave edge side 123 and a rear edge side 124, which are connected end to end, the rear edge side 124 is connected with the wheel disc 110, the concave edge side 123 is a side of the fan blade 120 which is concave inwards, the flange side 121 is a side of the fan blade 120 which is convex outwards, and the front edge side 122 is a side of the fan blade 120 which is far away from the wheel disc 110. The cross section of the concave edge side 123 is arc-shaped, and the cross section of the flange side 121 is a fitting curve formed by sequentially connecting four curves or straight lines.
It is worth noting that the central angle of the arc formed by the concave edge side 123 ranges from 90 degrees to 110 degrees, and the reasonable central angle of the concave edge side 123 can ensure that the concave edge side 123 has enough arc length to guide air while being convenient for processing and production, thereby improving the air guiding effect and reducing the generated noise. For ease of understanding, the arc of the concave edge side 123 is denoted as ab-segment, and the central angle of the arc of the concave edge side 123 is denoted as a. In the present embodiment, the central angle of the arc formed by the concave edge 123 is 100 degrees, but the present invention is not limited thereto, and in other embodiments, the central angle of the arc formed by the concave edge 123 may be 90 degrees or 110 degrees, and the size of the central angle of the arc formed by the concave edge 123 is not particularly limited.
The cross section of the flange side 121 forms a fitted curve as a function of:
Figure BDA0003335993130000051
the unit of x is millimeter, the x-axis direction is the direction from the front edge side 122 to the rear edge side 124 on the connection line of the two ends of the mean camber line of the fan blade 120, the y-axis direction is the direction perpendicular to the x-axis and from the concave edge side 123 to the flange side 121, and the origin is the intersection point of the mean camber line of the fan blade 120 and the front edge side 122. For ease of understanding, the origin is denoted as o-point.
Specifically, as can be seen from the above functional relationship, the cross section of the flange side 121 includes a first curve segment, a second curve segment, a third curve segment and a straight line segment that are sequentially connected, where the first curve segment is disposed away from the wheel disc 110, the straight line segment is disposed close to the wheel disc 110, and the cross section of the entire flange side 121 is in a parabolic shape, so that the cross section can better adapt to the flow field variation, and the air resistance is smaller. For ease of understanding, the first curve segment is denoted as cd segment, the second curve segment as de segment, the third curve segment as ef segment, and the straight line segment as fg segment. In the process of air-out of the centrifugal fan impeller 100, air flows on the flange side 121 sequentially along the second curve section and the third curve section from the first curve section and flows towards the direction of the straight line section, so that the surface of the flange side 121 has good flow velocity distribution, the separation and development of an air separation layer on the surface of the fan blade 120 are improved, the air resistance is effectively reduced, the air-out efficiency is improved, the vortex noise in the volute component is reduced, and the flow field distribution is more uniform.
In this embodiment, the flange side 121 is an eccentric structure, and the thickness of the fan blade 120 is gradually increased and then gradually decreased in the x-axis direction, so that the air flow flowing through the fan blade 120 is firstly spread outwards towards two sides of the fan blade 120, and then approaches each other along the concave edge side 123 and the flange side 121, thereby reducing air resistance and improving air outlet efficiency. When x=2.5, the distance between the concave edge side 123 and the flange side 121 is the largest, and the thickness of the fan blade 120 is the largest; when x=5, the value of y is the largest, and the distance between the flange side 121 and the connecting line of the two ends of the camber line in the fan blade 120 is the largest.
In this embodiment, the cross section of the front edge 122 is arc-shaped, so that the air flow is guided to the concave edge 123 and the flange 121, respectively, to reduce air resistance and improve air guiding effect. It will be appreciated that the arc of the leading edge side 122 is represented as an ac segment, which is the partial line of the concave edge side 123 and the flange side 121 that are connected to each other at the end remote from the wheel disc 110; the trailing edge side 124 is curved as shown in bg, which is the portion of the line where the concave edge side 123 and the flange side 121 join each other near the end of the wheel disc 110.
Further, the radius of the arc of the leading edge 122 ranges from 0.5 mm to 0.7 mm, and the reasonable radius of the arc of the leading edge 122 can reduce the air resistance to the maximum extent while ensuring the air guiding effect. For ease of understanding, the radius of the arc of the leading edge side 122 is denoted as R. In the present embodiment, the radius of the arc formed by the leading edge 122 is 0.6 mm, but the present invention is not limited thereto, and in other embodiments, the radius of the arc formed by the leading edge 122 may be 0.5 mm or 0.7 mm, and the radius of the arc formed by the leading edge 122 is not particularly limited.
It should be noted that, the number of the fan blades 120 ranges from 42 to 45, and the reasonable number of the fan blades 120 can reduce the generated noise as much as possible while guaranteeing the air output. In the present embodiment, the number of the fan blades 120 is 43, but is not limited thereto, and in other embodiments, the number of the fan blades 120 may be 42 or 45, and the number of the fan blades 120 is not particularly limited.
Referring to fig. 6, it is noted that an inlet installation angle is formed between a circle passing through the origin and the center line of the wheel disc 110, that is, a tangent line of the circle at the origin and a tangent line of the center line of the fan blade 120 at the origin. Specifically, the range of the inlet installation angle is 65-75 degrees, and the reasonable inlet installation angle can effectively improve the static pressure ratio and isentropic efficiency of the fan blade 120 while guaranteeing the air output. For ease of understanding, the inlet mounting angle is denoted B. In the present embodiment, the inlet mounting angle is 90 degrees, but the present invention is not limited thereto, and in other embodiments, the inlet mounting angle may be 65 degrees or 75 degrees, and the size of the inlet mounting angle is not particularly limited.
Further, an outlet installation angle is formed between a circle taking the midpoint of the wheel disc 110 as the center and passing through the intersection point of the mean camber line of the fan blade 120 and the trailing edge side 124 and the mean camber line of the fan blade 120, that is, an outlet installation angle is formed between a tangent line of the circle at the intersection point and a tangent line of the mean camber line of the fan blade 120 at the intersection point. Specifically, the range of export installation angle is 160 degrees to 175 degrees, and reasonable export installation angle can effectively increase the air-out volume, improves air-out efficiency to reduce the noise that produces. For ease of understanding, the outlet mounting angle is denoted as C. In the present embodiment, the outlet mounting angle is 168 degrees, but the present invention is not limited thereto, and in other embodiments, the outlet mounting angle may be 160 degrees or 175 degrees, and the size of the outlet mounting angle is not particularly limited.
It should be noted that, the difference between the outlet mounting angle and the inlet mounting angle ranges from 90 degrees to 105 degrees, and the reasonable difference between the outlet mounting angle and the inlet mounting angle can reduce the generated noise as much as possible while ensuring the air outlet effect, and is convenient for processing the centrifugal fan impeller 100. In this embodiment, the difference between the outlet mounting angle and the inlet mounting angle is 98 degrees, but the difference between the outlet mounting angle and the inlet mounting angle may be 90 degrees or 105 degrees in other embodiments, and the difference between the outlet mounting angle and the inlet mounting angle is not particularly limited.
Referring to fig. 7, it is noted that the ratio of the diameter of the circle passing through the origin with the center point of the wheel disc 110 is in the range of 0.78 to 0.85, that is, the ratio of the diameter of the centrifugal fan impeller 100 is in the range of 0.78 to 0.85, so that the reasonable ratio can increase the air output, improve the air output efficiency, and reduce the generated noise. For ease of understanding, the diameter of a circle centered at the midpoint of the wheel disc 110 and passing through the origin is denoted D, and the outer diameter of the wheel disc 110 is denoted E. In the present embodiment, the ratio of the diameter of the centrifugal fan impeller 100 is 0.82, but the ratio of the diameter of the centrifugal fan impeller 100 may be 0.78 or 0.85 in other embodiments, and the size of the ratio of the diameter of the centrifugal fan impeller 100 is not particularly limited.
Referring to fig. 8 and 9 in combination, the fan blade 120 includes a first fan blade 125 and a second fan blade 126. The number of the first fan blades 125 and the second fan blades 126 is plural, and the first fan blades 125 and the second fan blades 126 are disposed in the wheel disc 110. Specifically, the shapes of the first fan blade 125 and the second fan blade 126 are the same, the first fan blade 125 and the second fan blade 126 are arranged in a staggered manner, and the first fan blade 125 and the second fan blade 126 arranged in a staggered manner can effectively improve the air outlet efficiency of the centrifugal fan impeller 100 and increase the air outlet quantity.
The wheel 110 includes a first wheel 111 and a second wheel 112 coaxially disposed. The diameters of the first wheel disc 111 and the second wheel disc 112 are equal, a plurality of first fan blades 125 are arranged in the first wheel disc 111 in an annular array, and a plurality of second fan blades 126 are arranged in the second wheel disc 112 in an annular array. In the process that the driving motor drives the centrifugal fan impeller 100 to rotate, the first wheel disc 111 and the second wheel disc 112 synchronously rotate to drive the first fan blade 125 and the second fan blade 126 to move, so that the wind function is realized.
Further, in the circumferential direction of the wheel disc 110, the ratio of the angle at which the first fan blade 125 rotates to the position of the adjacent one of the second fan blades 126 to the angle at which the second fan blade 126 rotates to the position of the adjacent one of the first fan blades 125 ranges from 0.5 to 0.7, that is, on the cross section of the centrifugal fan impeller 100, one of the second fan blades 126 is located between the adjacent two first fan blades 125, wherein the ratio of the included angle between the first fan blade 125 and the second fan blade 126 to the included angle between the second fan blade 126 and the second first fan blade 125 ranges from 0.5 to 0.7. Specifically, the included angle ratio is referred to as a staggered gear ratio of the centrifugal fan impeller 100, and a reasonable staggered gear ratio can effectively improve air outlet efficiency and reduce wind noise. For ease of understanding, the angle at which the first fan blade 125 rotates to the position adjacent to one second fan blade 126 is denoted as F, and the angle at which the second fan blade 126 rotates to the position adjacent to one first fan blade 125 is denoted as G.
In this embodiment, the ratio of the dislocation ratio is 0.6, that is, the ratio of the angle at which the first fan blade 125 rotates to the position of the adjacent one of the second fan blades 126 to the angle at which the second fan blade 126 rotates to the position of the adjacent one of the first fan blades 125 in the circumferential direction of the wheel disc 110 is 0.6, but the present invention is not limited thereto, and in other embodiments, the dislocation ratio may be 0.5 or 0.7, and the size of the dislocation ratio is not particularly limited thereto.
In this embodiment, the distance between two adjacent first fan blades 125 is equal to the distance between two adjacent second fan blades 126, i.e. the number of first fan blades 125 in the first wheel disc 111 is equal to the number of second fan blades 126 in the second wheel disc 112. Specifically, the distance between two adjacent first fan blades 125 ranges from 9.5 mm to 10.5 mm, and the reasonable distance between two adjacent first fan blades 125 can increase the air output as much as possible while guaranteeing the air guiding effect. For ease of understanding, the spacing between adjacent two first blades 125 is denoted as H. In the present embodiment, the distance between two adjacent first fan blades 125 is 9.9 mm, but not limited thereto, and in other embodiments, the distance between two adjacent first fan blades 125 may be 9.5 mm or 10.5 mm, and the distance between two adjacent first fan blades 125 is not particularly limited.
In the centrifugal fan impeller 100 according to the embodiment of the present invention, a plurality of fan blades 120 are disposed in a circular array in a wheel disc 110, the fan blades 120 are provided with a flange side 121, a front edge side 122, a concave edge side 123 and a rear edge side 124 which are connected end to end, the rear edge side 124 is connected with the wheel disc 110, the cross section of the concave edge side 123 is in a circular arc shape, the cross section of the flange side 121 is a fitting curve formed by sequentially connecting four sections of curves or straight lines, and the function relationship of the fitting curve is:
Figure BDA0003335993130000091
the unit of x is millimeter, the x-axis direction is the direction from the front edge side 122 to the rear edge side 124 on the connection line of the two ends of the mean camber line of the fan blade 120, the y-axis direction is the direction perpendicular to the x-axis and from the concave edge side 123 to the flange side 121, and the origin is the intersection point of the mean camber line of the fan blade 120 and the front edge side 122. Compared with the prior art, the centrifugal fan impeller 100 provided by the invention has the advantages that due to the adoption of the concave edge side 123 arranged in the arc shape and the flange side 121 arranged in the fitting curve, the generated noise can be reduced, the air quantity loss is reduced, the air quantity is increased, the air outlet effect is improved, and the user experience is improved.
Second embodiment
The present invention provides an air conditioner (not shown) for controlling indoor air temperature. The air conditioner includes a heat exchanger (not shown) and a centrifugal fan including a driving motor and a centrifugal fan impeller 100, the driving motor being connected to the centrifugal fan impeller 100. The basic structure and principle of the centrifugal fan impeller 100 and the technical effects thereof are the same as those of the first embodiment, and for brevity, reference is made to the corresponding contents of the first embodiment where the description of the embodiment is not mentioned.
In this embodiment, the position of the heat exchanger corresponds to the position of the centrifugal fan. When the air conditioner is operated, the driving motor can drive the centrifugal fan impeller 100 to rotate so as to generate negative pressure and drive air to flow so as to form air-out air flow, and the air-out air flow can pass through the heat exchanger and blow into a room, and in the process, the heat exchanger can heat or refrigerate the air-out air flow so as to realize the function of regulating and controlling the indoor air temperature.
The beneficial effects of the air conditioner according to the embodiment of the present invention are the same as those of the first embodiment, and will not be described in detail herein.
Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be made by one skilled in the art without departing from the spirit and scope of the invention, and the scope of the invention should be assessed accordingly to that of the appended claims.

Claims (10)

1. The utility model provides a centrifugal fan impeller, its characterized in that includes rim plate (110) and a plurality of fan blade (120), a plurality of fan blade (120) be annular array ground set up in rim plate (110), fan blade (120) are provided with flange side (121), leading edge side (122), concave edge side (123) and trailing edge side (124) that end to end, trailing edge side (124) with rim plate (110) are connected, the transversal arc of concave edge side (123) is personally submitted, the cross section of flange side (121) is four sections curves or straight line and connects gradually the fitting curve that forms, the functional relation of fitting curve is:
Figure FDA0003335993120000011
the unit of x is millimeter, the x-axis direction is the direction from the front edge side (122) to the rear edge side (124) which is positioned on the connecting line of the two ends of the mean camber line of the fan blade (120), the y-axis direction is the direction perpendicular to the x-axis and from the concave edge side (123) to the flange side (121), and the origin is the intersection point of the mean camber line of the fan blade (120) and the front edge side (122).
2. Centrifugal fan impeller according to claim 1, wherein the distance between the concave edge side (123) and the flange side (121) is greatest and the thickness of the fan blade (120) is greatest when x = 2.5.
3. The centrifugal fan impeller according to claim 1, wherein the central angle of the arc of the concave edge side (123) ranges from 90 degrees to 110 degrees.
4. Centrifugal fan impeller according to claim 1, wherein the number of blades (120) ranges from 42 to 45.
5. The centrifugal fan impeller according to claim 1, wherein an inlet mounting angle is formed between a circle centered on a midpoint of the disk (110) and passing through the origin and a camber line of the fan blade (120), the inlet mounting angle being in a range of 65 degrees to 75 degrees.
6. The centrifugal fan wheel according to claim 5, wherein an outlet mounting angle is formed between a circle centered at a midpoint of the wheel disc (110) and passing through an intersection of the mean camber line of the blade (120) and the trailing-edge side (124) and the mean camber line of the blade (120), the outlet mounting angle being in a range of 160 degrees to 175 degrees.
7. The centrifugal fan impeller of claim 6, wherein the outlet mounting angle differs from the inlet mounting angle by a range of 90 degrees to 105 degrees.
8. The centrifugal fan impeller according to claim 1, wherein the cross section of the leading edge side (122) is circular arc-shaped, and the radius of the circular arc of the leading edge side (122) ranges from 0.5 mm to 0.7 mm.
9. The centrifugal fan impeller according to claim 1, wherein the ratio of the diameter of a circle centered on the midpoint of the disk (110) and passing through the origin to the outer diameter of the disk (110) ranges from 0.78 to 0.85.
10. An air conditioner comprising a centrifugal fan impeller according to any one of claims 1 to 9.
CN202111294399.5A 2021-11-03 2021-11-03 Centrifugal fan impeller and air conditioner Pending CN116066402A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202111294399.5A CN116066402A (en) 2021-11-03 2021-11-03 Centrifugal fan impeller and air conditioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202111294399.5A CN116066402A (en) 2021-11-03 2021-11-03 Centrifugal fan impeller and air conditioner

Publications (1)

Publication Number Publication Date
CN116066402A true CN116066402A (en) 2023-05-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202111294399.5A Pending CN116066402A (en) 2021-11-03 2021-11-03 Centrifugal fan impeller and air conditioner

Country Status (1)

Country Link
CN (1) CN116066402A (en)

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