Centrifugal fan wheel and air conditioner

Abstract

The application discloses a centrifugal fan wheel and an air conditioner, and relates to the technical field of air conditioners. The centrifugal fan wheel comprises a front disc of an impeller and a plurality of first fan blades. The plurality of first fan blades are arranged in an annular array in the front disc of the impeller. The first fan blades are oppositely provided with a concave flange side and a convex flange side. The cross section of the concave flange side comprises at least two circular arcs with different radii and connected in sequence. The cross section of the convex flange side is a fitting curve formed by three curves connected in sequence. Compared with the prior art, the centrifugal fan wheel provided by the application can improve the air outlet efficiency, increase the air outlet volume, reduce the generated noise and improve the comfort of users due to the adoption of the concave flange side composed of at least two circular arcs and the convex flange side arranged in a fitting curve.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and in particular to a centrifugal fan and an air conditioner. Background Technology

[0002] Currently, air conditioners typically use centrifugal fans to exchange heat between airflow and refrigerant in a heat exchanger to achieve cooling or heating. During this process, a large amount of airflow passes through the centrifugal impeller of the centrifugal fan, making the centrifugal impeller a major factor influencing noise generation in air conditioners.

[0003] Most centrifugal impellers nowadays adopt a multi-blade forward-curving design, with the blade profile of its cross-section consisting of a single circular arc. The blades have a uniform thickness or no variation along the chord length, which causes pressure fluctuations in the surrounding gas during operation. The air pressure acts on the volute components, generating noise and causing a certain amount of airflow loss, resulting in low air output efficiency and seriously affecting user comfort. Summary of the Invention

[0004] The problem solved by this invention is how to improve air output efficiency, increase air volume, reduce noise, and enhance user comfort.

[0005] To solve the above problems, the technical solution of the present invention is implemented as follows:

[0006] In a first aspect, the present invention provides a centrifugal impeller, comprising an impeller front disc and a plurality of first blades. The plurality of first blades are arranged in a ring array within the impeller front disc. The first blades are provided with concave flange sides and convex flange sides opposite to each other. The cross-section of the concave flange side includes at least two arc segments with different radii connected in sequence. The cross-section of the convex flange side is a fitting curve formed by connecting three curve segments in sequence. The functional relationship of the fitting curve is as follows:

[0007]

[0008] Where x is in millimeters, the x-axis is the direction along the line connecting the two ends of the arc of the first blade from the first blade to the impeller front plate, the y-axis is perpendicular to the x-axis from the concave flange side to the convex flange side, and the origin is the endpoint of the arc of the first blade away from the impeller front plate. Compared with the prior art, the centrifugal impeller provided by the present invention, due to the use of a concave flange side composed of at least two arc segments and a convex flange side arranged in a fitted curve, can improve air outlet efficiency, increase air volume, reduce noise, and improve user comfort.

[0009] Furthermore, when x = 4.45, the distance between the concave and convex flange sides is the largest, and the thickness of the first blade is the largest. The thickness of the first blade gradually increases and then gradually decreases in the x-axis direction, so that the airflow passing through the first blade first diffuses outward to both sides of the blade, and then approaches each other along the concave and convex flange sides, reducing air resistance and improving air outlet efficiency.

[0010] Furthermore, the cross-section of the concave flange side includes a first arc and a second arc connected in sequence. The first arc is connected to the impeller front disc through the second arc, and the ratio of the radius of the second arc to the radius of the first arc ranges from 1.52 to 1.7. A reasonable ratio of the radius of the second arc to the radius of the first arc can improve the airflow guiding effect, thereby increasing the air volume and improving the air outlet efficiency.

[0011] Furthermore, the central angle of the first arc ranges from 70 degrees to 83 degrees. A reasonable central angle of the first arc ensures that the arc has sufficient length to guide the airflow, thereby improving the airflow effect and reducing the noise generated.

[0012] Furthermore, the end of the first blade furthest from the impeller front disk is provided with a leading edge side, and the concave edge side is connected to the convex edge side through the leading edge side. The cross-section of the leading edge side is a third circular arc, and the radius of the third circular arc ranges from 0.5 mm to 0.7 mm. A reasonable radius of the third circular arc can minimize air resistance while ensuring the air guiding effect.

[0013] Furthermore, an inlet installation angle is formed between the circle centered on the midpoint of the impeller front plate and the distance between the midpoint and the origin, and the arc of the first fan blade. The inlet installation angle ranges from 60 to 70 degrees. A reasonable inlet installation angle can effectively improve the static pressure ratio and isentropic efficiency of the first fan blade while ensuring the air volume.

[0014] Furthermore, the centrifugal impeller also includes a rear impeller disc and multiple second blades. The multiple second blades are arranged in a ring array within the rear impeller disc, which is coaxial with the front impeller disc. The front and rear impeller discs can rotate synchronously to drive the multiple first and second blades, thereby achieving the air outlet function and increasing the air volume.

[0015] Furthermore, the first and second fan blades are staggered. In the circumferential direction of the impeller front or rear disc, the ratio of the angle at which the first fan blade rotates to the position of the adjacent second fan blade to the angle at which the second fan blade rotates to the position of the adjacent first fan blade ranges from 0.5 to 0.7. A reasonable stagger ratio can effectively improve airflow efficiency and reduce wind noise.

[0016] Furthermore, the spacing between two adjacent first fan blades ranges from 9.5 mm to 10.5 mm. A reasonable spacing between two adjacent first fan blades can maximize the air volume while ensuring the air guiding effect.

[0017] Secondly, the present invention provides an air conditioner including the aforementioned centrifugal impeller. The centrifugal impeller includes an impeller front disc and a plurality of first fan blades arranged in a circular array within the impeller front disc. Each first fan blade has a concave flange side and a convex flange side opposite to each other. The cross-section of the concave flange side includes at least two arc segments of different radii connected sequentially. The cross-section of the convex flange side is a fitting curve formed by three sequentially connected curves. The functional relationship of the fitting curve is:

[0018]

[0019] Where x is in millimeters, the x-axis is the direction along the line connecting the two ends of the arc of the first fan blade, from the first fan blade to the front disc of the impeller, the y-axis is perpendicular to the x-axis, from the concave flange side to the convex flange side, and the origin is the endpoint of the arc of the first fan blade furthest from the front disc of the impeller. Air conditioners can improve airflow efficiency, increase air volume, reduce noise, and enhance user comfort. Attached Figure Description

[0020] Figure 1 This is an axonometric view of the centrifugal impeller according to the first embodiment of the present invention;

[0021] Figure 2 This is a schematic diagram of the connection between the impeller front disc and the first fan blade in the centrifugal fan according to the first embodiment of the present invention;

[0022] Figure 3 This is a mathematical model diagram of the connection between the impeller front disc and the first fan blade in the centrifugal fan according to the first embodiment of the present invention;

[0023] Figure 4 This is a mathematical model diagram of the flange side of the first blade in the centrifugal impeller according to the first embodiment of the present invention;

[0024] Figure 5 This is another mathematical model diagram showing the connection between the impeller front disc and the first fan blade in the centrifugal fan described in the first embodiment of the present invention;

[0025] Figure 6 This is a front view of the centrifugal impeller described in the first embodiment of the present invention.

[0026] Explanation of reference numerals in the attached figures:

[0027] 100 - Centrifugal impeller; 110 - Impeller front plate; 120 - Impeller rear plate; 130 - First impeller blade; 131 - Concave flange side; 132 - Convex flange side; 133 - Leading edge side; 140 - Second impeller blade. Detailed Implementation

[0028] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

[0029] First Embodiment

[0030] Please refer to Figure 1 This invention provides a centrifugal fan 100 for driving airflow. It can improve airflow efficiency, increase air volume, reduce noise, and enhance user comfort.

[0031] It should be noted that the centrifugal impeller 100 is used in a centrifugal fan (not shown in the figure), which includes a drive motor (not shown in the figure) and the centrifugal impeller 100. The drive motor is connected to the centrifugal impeller 100 for transmission, and the drive motor can drive the centrifugal impeller 100 to rotate, so that the centrifugal impeller 100 generates negative pressure, thereby driving airflow to generate an exhaust airflow.

[0032] The centrifugal impeller 100 includes a front impeller plate 110, a rear impeller plate 120, multiple first fan blades 130, and multiple second fan blades 140. The front impeller plate 110 and the rear impeller plate 120 are both annular and have the same diameter. The rear impeller plate 120 is coaxially arranged with the front impeller plate 110. The multiple first fan blades 130 and multiple second fan blades 140 are arranged between the front impeller plate 110 and the rear impeller plate 120. Specifically, the multiple first fan blades 130 are arranged in a ring array within the front impeller plate 110, and the multiple second fan blades 140 are arranged in a ring array within the rear impeller plate 120. During the rotation of the centrifugal impeller 100 driven by the drive motor, the front impeller plate 110 and the rear impeller plate 120 rotate synchronously, driving the multiple first fan blades 130 and multiple second fan blades 140 to move, thereby achieving the air outlet function and increasing the air volume.

[0033] Please refer to the reference. Figure 2 , Figure 3 and Figure 4 In this embodiment, the first fan blade 130 is bent to guide airflow, reduce air resistance, improve air outlet efficiency, and increase air volume. Specifically, the first fan blade 130 has a concave flange side 131 and a convex flange side 132 opposite to each other. The concave flange side 131 is the side of the first fan blade 130 that is recessed inward, and the convex flange side 132 is the side of the first fan blade 130 that is protruding outward. The cross-section of the concave flange side 131 includes at least two arc segments with different radii that are connected in sequence, and the cross-section of the convex flange side 132 is a fitted curve formed by connecting three curve segments in sequence.

[0034] It is worth noting that the cross-section of the concave flange side 131 includes a first arc and a second arc connected in sequence. The second arc is disposed between the first arc and the impeller front plate 110, and the first arc is connected to the impeller front plate 110 through the second arc. The centers of both the first and second arcs are located on the side of the concave flange side 131 away from the convex flange side 132. For ease of understanding, the first arc is represented as segment ab, and the second arc is represented as segment bc. During the rotation of the centrifugal impeller 100, the airflow flows from the first arc to the second arc on the concave flange side 131. However, this is not the only possibility. In other embodiments, the cross-section of the concave flange side 131 may include three or four arcs connected in sequence, and the number of arcs forming the concave flange side 131 is not specifically limited.

[0035] It should be noted that the ratio of the radius of the second arc to the radius of the first arc ranges from 1.52 to 1.7. A reasonable ratio of the radius of the second arc to the radius of the first arc can improve the airflow guiding effect, thereby increasing the air volume and improving the air outlet efficiency. For ease of understanding, the radius of the first arc is denoted as L, and the radius of the second arc is denoted as M. In this embodiment, the ratio of the radius of the second arc to the radius of the first arc is 1.6, but it is not limited to this. In other embodiments, the ratio of the radius of the second arc to the radius of the first arc can be 1.52 or 1.7, and the specific value of the ratio of the radius of the second arc to the radius of the first arc is not limited.

[0036] Furthermore, the central angle of the first arc ranges from 70 degrees to 83 degrees. A reasonable central angle of the first arc ensures that the arc has sufficient length to guide airflow, thereby improving the airflow effect and reducing noise. For ease of understanding, the central angle of the first arc is denoted as A. In this embodiment, the central angle of the first arc is 76 degrees, but it is not limited to this. In other embodiments, the central angle of the first arc can be 70 degrees or 83 degrees; the size of the central angle of the first arc is not specifically limited.

[0037] It is worth noting that the functional relationship of the fitting curve formed by the cross-section of flange side 132 is as follows:

[0038]

[0039] Where x is in millimeters, the x-axis is the direction along the line connecting the two ends of the arc of the first fan blade 130 and extending from the first fan blade 130 to the impeller front plate 110, the y-axis is perpendicular to the x-axis and extends from the concave flange side 131 to the convex flange side 132, and the origin is the endpoint of the arc of the first fan blade 130 away from the impeller front plate 110. For ease of understanding, the origin is represented as point O.

[0040] Specifically, as shown by the above functional relationship, the cross-section of the flange side 132 includes a first curved segment, a second curved segment, and a third curved segment connected in sequence. The first curved segment is positioned away from the impeller front plate 110, while the third curved segment is positioned close to the impeller front plate 110. The entire cross-section of the flange side 132 has a parabolic shape, which better adapts to changes in the flow field and reduces air resistance. For ease of understanding, the first curved segment is denoted as de, the second curved segment as ef, and the third curved segment as fg. During the airflow process of the centrifugal impeller 100, the airflow on the flange side 132 flows from the first curved segment along the second curved segment and towards the third curved segment, resulting in a better velocity distribution on the surface of the flange side 132. This improves the separation and development of the air adsorption layer on the surface of the first impeller 130, effectively reduces air resistance, increases airflow efficiency, and reduces vortex noise within the volute component, making the flow field distribution more uniform.

[0041] In this embodiment, both the concave flange side 131 and the convex flange side 132 are eccentric structures. The first curved segment and a portion of the second curved segment correspond to the first arc, and the third curved segment and another portion of the second curved segment correspond to the second arc. Specifically, the thickness of the first fan blade 130 gradually increases and then gradually decreases in the x-axis direction, so that the airflow passing through the first fan blade 130 first diffuses outward to both sides of the fan blade, and then approaches each other along the concave flange side 131 and the convex flange side 132, reducing air resistance and improving air outlet efficiency. When x = 4.45, the distance between the concave flange side 131 and the convex flange side 132 is the largest, and the thickness of the first fan blade 130 is the largest.

[0042] It should be noted that the first fan blade 130 has a leading edge side 133 at the end away from the impeller front plate 110. The concave flange side 131 is connected to the convex flange side 132 through the leading edge side 133. The cross-section of the leading edge side 133 is a third circular arc, which facilitates the guidance of airflow to the concave flange side 131 and the convex flange side 132 respectively, reducing air resistance and improving the air guiding effect. It can be understood that the third circular arc represents segment ad, which is the profile of the part where the concave flange side 131 and the convex flange side 132 connect at the end away from the impeller front plate 110.

[0043] Furthermore, the radius of the third arc ranges from 0.5 mm to 0.7 mm. A reasonable radius of the third arc can minimize air resistance while ensuring the air guiding effect. For ease of understanding, the radius of the third arc is denoted as N. In this embodiment, the radius of the third arc is 0.6 mm, but it is not limited to this. In other embodiments, the radius of the third arc can be 0.5 mm or 0.7 mm, and the size of the radius of the third arc is not specifically limited.

[0044] It is worth noting that the inlet installation angle is formed between the circle with the midpoint of the impeller front plate 110 as the center and the distance between the midpoint of the impeller front plate 110 and the origin as the radius, and the arc of the first fan blade 130. That is, the inlet installation angle is formed between the circle with the midpoint of the impeller front plate 110 as the center and passing through the origin and the arc of the first fan blade 130. The inlet installation angle is formed between the tangent of this circle at the origin and the tangent of the arc of the first fan blade 130 at the origin.

[0045] Please refer to Figure 5 Furthermore, the inlet installation angle ranges from 60 degrees to 70 degrees. A reasonable inlet installation angle can effectively improve the static pressure ratio and isentropic efficiency of the first fan blade 130 while ensuring the air volume. For ease of understanding, the inlet installation angle is denoted as B. In this embodiment, the inlet installation angle is 65 degrees, but it is not limited to this. In other embodiments, the inlet installation angle can be 60 degrees or 70 degrees, and the size of the inlet installation angle is not specifically limited.

[0046] Please refer to Figure 6 It should be noted that the first fan blade 130 and the second fan blade 140 are staggered. This staggered arrangement effectively improves the air outlet efficiency of the centrifugal impeller 100 and increases the air volume. Specifically, in the circumferential direction of the impeller front plate 110 or impeller rear plate 120, the ratio of the angle at which the first fan blade 130 rotates to the position of an adjacent second fan blade 140 to the angle at which the second fan blade 140 rotates to the position of an adjacent first fan blade 130 ranges from 0.5 to 0.7. That is, on the cross-section of the centrifugal impeller 100, a second fan blade 140 is located between two adjacent first fan blades 130, wherein the ratio of the angle between the first first fan blade 130 and the second fan blade 140 to the angle between the second fan blade 140 and the second first fan blade 130 ranges from 0.5 to 0.7. Specifically, this angle ratio is called the tooth offset ratio of the centrifugal impeller 100. A reasonable tooth offset ratio can effectively improve the air output efficiency and reduce wind noise. For ease of understanding, the angle at which the first blade 130 rotates to the position of the adjacent second blade 140 is denoted as C, and the angle at which the second blade 140 rotates to the position of the adjacent first blade 130 is denoted as D.

[0047] In this embodiment, the misalignment ratio is 0.6, that is, in the circumferential direction of the impeller front plate 110 or the impeller rear plate 120, the ratio of the angle at which the first fan blade 130 rotates to the position of the adjacent second fan blade 140 to the angle at which the second fan blade 140 rotates to the position of the adjacent first fan blade 130 is 0.6. However, it is not limited to this. In other embodiments, the misalignment ratio can be 0.5 or 0.7. The size of the misalignment ratio is not specifically limited.

[0048] Furthermore, the spacing between two adjacent first fan blades 130 ranges from 9.5 mm to 10.5 mm. A reasonable spacing between two adjacent first fan blades 130 can maximize the airflow while ensuring the air guiding effect. For ease of understanding, the spacing between two adjacent first fan blades 130 is denoted as H. In this embodiment, the spacing between two adjacent first fan blades 130 is 9.9 mm, but it is not limited to this. In other embodiments, the spacing between two adjacent first fan blades 130 can be 9.5 mm or 10.5 mm. The size of the spacing between two adjacent first fan blades 130 is not specifically limited.

[0049] In this embodiment, the number of second wind blades 140 is equal to the number of first wind blades 130, and the specific structure of the second wind blades 140 is the same as that of the first wind blades 130, which will not be described again here.

[0050] In the centrifugal impeller 100 of this embodiment, a plurality of first blades 130 are arranged in a ring array within the impeller front disk 110. Each first blade 130 has a concave flange side 131 and a convex flange side 132 opposite to each other. The cross-section of the concave flange side 131 includes at least two arc segments with different radii connected sequentially. The cross-section of the convex flange side 132 is a fitted curve formed by three sequentially connected curves. The functional relationship of the fitted curve is as follows:

[0051]

[0052] Where x is in millimeters, the x-axis is the direction from the first fan blade 130 to the impeller front plate 110, located on the line connecting the two ends of the arc of the first fan blade 130. The y-axis is perpendicular to the x-axis and runs from the concave flange side 131 to the convex flange side 132. The origin is the endpoint of the arc of the first fan blade 130 away from the impeller front plate 110. Compared with the prior art, the centrifugal impeller 100 provided by the present invention, due to the use of a concave flange side 131 composed of at least two arc segments and a convex flange side 132 arranged in a fitted curve, can improve air outlet efficiency, increase air volume, reduce noise, and improve user comfort.

[0053] Second Embodiment

[0054] This invention provides an air conditioner (not shown) for regulating indoor temperature. The air conditioner includes a heat exchanger (not shown) and a centrifugal fan. The centrifugal fan includes a drive motor and a centrifugal impeller 100, with the drive motor connected to the centrifugal impeller 100. The basic structure, principle, and technical effects of the centrifugal impeller 100 are the same as in the first embodiment. For brevity, any parts not mentioned in this embodiment can be referred to the corresponding content in the first embodiment.

[0055] In this embodiment, the position of the heat exchanger corresponds to the position of the centrifugal fan. When the air conditioner is running, the drive motor can drive the centrifugal fan 100 to rotate, thereby generating negative pressure and driving airflow to form an outlet airflow. This outlet airflow can pass through the heat exchanger and be blown into the room. During this process, the heat exchanger can heat or cool the outlet airflow to achieve the function of regulating the indoor temperature.

[0056] The beneficial effects of the air conditioner described in this embodiment are the same as those of the first embodiment, and will not be repeated here.

[0057] While the present invention has been disclosed above, it is not limited thereto. Any person skilled in the art can make various modifications and alterations without departing from the spirit and scope of the invention; therefore, the scope of protection of the present invention should be determined by the scope defined in the claims.

Claims

1. A centrifugal impeller, characterized in that, The impeller includes a front impeller disc (110) and multiple first fan blades (130). The multiple first fan blades (130) are arranged in a ring array within the front impeller disc (110). Each first fan blade (130) has a concave flange side (131) and a convex flange side (132) opposite to each other. The cross-section of the concave flange side (131) includes at least two arc segments with different radii connected in sequence. The cross-section of the convex flange side (132) is a fitting curve formed by three curve segments connected in sequence. The functional relationship of the fitting curve is: Where x is in millimeters, the x-axis is the direction from the first fan blade (130) to the impeller front plate (110) along the line connecting the two ends of the arc of the first fan blade (130), the y-axis is perpendicular to the x-axis and runs from the concave flange side (131) to the convex flange side (132), and the origin is the endpoint of the arc of the first fan blade (130) away from the impeller front plate (110).

2. The centrifugal impeller according to claim 1, characterized in that, When x = 4.45, the distance between the concave side (131) and the convex side (132) is the largest, and the thickness of the first fan blade (130) is the largest.

3. The centrifugal impeller according to claim 1, characterized in that, The cross-section of the concave flange side (131) includes a first arc and a second arc connected in sequence. The first arc is connected to the impeller front disc (110) through the second arc. The ratio of the radius of the second arc to the radius of the first arc is in the range of 1.52 to 1.

7.

4. The centrifugal impeller according to claim 3, characterized in that, The central angle of the first arc ranges from 70 degrees to 83 degrees.

5. The centrifugal impeller according to claim 1, characterized in that, The first blade (130) has a leading edge side (133) at the end away from the impeller front plate (110). The concave edge side (131) is connected to the convex edge side (132) through the leading edge side (133). The cross-section of the leading edge side (133) is a third arc, and the radius of the third arc is in the range of 0.5 mm to 0.7 mm.

6. The centrifugal impeller according to claim 1, characterized in that, An inlet installation angle is formed between the circle with the midpoint of the impeller front plate (110) as the center and the distance between the midpoint of the impeller front plate (110) and the origin as the radius, and the arc of the first fan blade (130). The range of the inlet installation angle is 60 degrees to 70 degrees.

7. The centrifugal impeller according to claim 1, characterized in that, The centrifugal impeller also includes an impeller rear plate (120) and a plurality of second blades (140). The plurality of second blades (140) are arranged in a ring array within the impeller rear plate (120). The impeller rear plate (120) is coaxially arranged with the impeller front plate (110).

8. The centrifugal impeller according to claim 7, characterized in that, The first fan blade (130) and the second fan blade (140) are staggered. In the circumferential direction of the impeller front plate (110) or the impeller rear plate (120), the ratio of the angle at which the first fan blade (130) rotates to the position of the adjacent second fan blade (140) to the angle at which the second fan blade (140) rotates to the position of the adjacent first fan blade (130) is between 0.5 and 0.

7.

9. The centrifugal impeller according to claim 1, characterized in that, The spacing between two adjacent first blades (130) ranges from 9.5 mm to 10.5 mm.

10. An air conditioner, characterized in that, Includes the centrifugal fan as described in any one of claims 1 to 9.

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