A heat dissipation fan impeller and a heat dissipation fan assembly

Abstract

The utility model discloses a heat dissipation fan impeller and heat dissipation fan assembly, including central hub and a group of fan blade, along the radial use equidistance arc and resolve into several radius different fan blade airfoil section with fan blade, from inside to outside are S1, S2,..., S n Wherein n is natural number, the projection curve of fan blade leading edge in fan blade rotation plane is y 前 Wherein: y 前 =a1x 5 +b1x 4 +c1x 3 +d1x 2 +e1x+f1, fan blade mounting angle beta satisfies following polynomial function: beta=a2x 7 +b2x 6 +c2x 5 +d2x 4 +e2x 3 +f2x 2 +g2x+h2, fan blade chord length C satisfies following polynomial function: C=a3x 7 +b3x 6 +c3x 5 +d3x 4 +e3x 3 +f3x 2 +g3x+h3, this heat dissipation fan can be in the size under the outer ring diameter of pressure - preserving ring 346-450mm, further reduce noise while guaranteeing enough air volume.

Description

Technical Field

[0001] This utility model relates to the field of fan technology, and in particular to a cooling fan impeller and a cooling fan assembly. Background Technology

[0002] The cooling fan assembly is mainly used in the cooling system to dissipate heat. The cooling fan assembly includes a shroud, a drive motor, and a fan impeller. The shroud includes a housing and a motor mounting hub inside the housing. The motor mounting hub and the housing are connected by several stiffening plates. The drive motor is fixed to the motor mounting hub. The fan impeller mainly includes a central hub and a set of fan blades. The inner ends of the set of fan blades are fixed to the central hub, and pressure-holding rings are fixed to the outer ends of the set of fan blades. The central hub is fixed to the motor rotor. The high-speed rotation of the rotor drives the fan to rotate. The edge of the pressure-holding ring is folded outwards to form a folded edge. The shroud is provided with a folded edge. The current fan blades have a stepped fit with a clearance, and the outer end of the suction surface is flush with the surface of the pressure ring. As the fan impeller rotates, air is drawn in from the suction surface of the fan blades and flows out from the pressure surface. Because there is a gap between the pressure ring and the shroud, the air flowing out from the pressure surface of the fan blades will be drawn in again through the gap, flowing backwards, and then around the pressure ring before being drawn in again from the suction surface of the fan blades. At this time, the airflow will form a vortex on the inner side of the pressure ring. This vortex will generate a large resistance to the airflow, resulting in a reduction in air volume, an increase in static pressure on the pressure surface of the fan blades, and the presence of the vortex will also make the fan run unevenly, thus increasing the noise.

[0003] However, for fans with an outer diameter of 346-450mm for the pressure ring and an outer diameter of 135.6-155.6mm for the central hub, further reducing noise is a design challenge. Utility Model Content

[0004] The first technical problem to be solved by this utility model is to provide a cooling fan impeller that can further reduce noise while keeping the outer diameter of the pressure ring 346-450mm.

[0005] The second technical problem to be solved by this utility model is to provide a cooling fan assembly that not only reduces noise but also improves protection capabilities.

[0006] To solve the first technical problem mentioned above, the technical solution of this utility model is: a cooling fan impeller, comprising a central hub and a set of fan blades, wherein the inner end of the set of fan blades is fixed to the central hub, and a pressure-holding ring is fixed to the outer end of the set of fan blades. The number of fan blades is seven, nine, or eleven. The outer diameter of the central hub is 135.6-155.6 mm. Specifically, when the number of fan blades is seven, the outer diameter of the pressure-holding ring is 346-395 mm; when the number of fan blades is nine, the outer diameter of the pressure-holding ring is 385-405 mm; and when the number of fan blades is eleven, the outer diameter of the pressure-holding ring is 410-450 mm. The fan blades are decomposed radially into several airfoil sections with different radii using equally spaced circular arcs, numbered S1, S2, ..., S... from the inside out. n Where n is a natural number, the front point of each airfoil section is called the leading edge of the airfoil; the point with the greatest distance from the leading edge is called the trailing edge; the straight line connecting the leading and trailing edges is called the chord line of the airfoil section, the length of which is C, and the angle between the chord line and the plane of rotation is β; the windward side of the blade is the leading edge, the leeward side is the trailing edge, and the projection curve of the leading edge in the plane of rotation is y. 前 ,in: y 前 = a1×x 5 +b1×x 4 +c1×x 3 +d1×x 2 +e1×x+f1 In the above formula: a1 = 2.7503e -8 ±2.75e -9 b1 = -1.6216e -5 ±1.62e -6 c1=3.7723e -3 ±3.77e -4 d1=-4.2707e -1 ±4.27e -2 e1=2.2909e 1 ±2.29; f1=-4.5645e 2 ±45.6; Where x is the x-coordinate of the plane of rotation of the fan blade, y 前 The vertical coordinate of the plane of rotation of the fan blades; The fan blade installation angle β satisfies the following polynomial function: β=a2×r 7 +b2×r 6 +c2×r 5 +d2×r 4 +e2×r3 +f2×r 2 +g2×r+h2 In the above formula: a2 = 7.30042e -12 ±7.3e -13 b2 = -6.49315e -9 ±1e -10 c2=2.41521e -6 ±2.42e -7 ; d2=-0.000486617±0.0000487; e2=0.0573324±0.00573; f2=-3.949431172±0.395; g2=147.118±14.7; h2 = -2252.26288 ± 22.5; Where r is the radius of the fan blade airfoil section with the center of the central hub as the center, and the unit is mm; the fan blade mounting angle β is in degrees. The chord length C of the fan blade satisfies the following polynomial function: C = a3×r 7 +b3×r 6 +c3×r 5 +d3×r 4 +e3×r 3 +f3×r 2 +g3×r+h3 In the above formula: a3 = -7.80241e -12 ±7.8e -13 b3=6.93038e -9 ±6.93e -10 c3 = -2.58228e -6 ±2.58e -7 d3=5.23236e -4 ±5.23e -5 ;e3=-0.06225±0.00623; f3=4.349±0.435; g3=-165.3559±16.5; h3=2693.499±269; The unit for the fan blade chord length C is mm.

[0007] Preferably, the direction axis perpendicular to the blade chord is defined as the Z-axis. The curve connecting the midpoints of the upper and lower surfaces of the blade airfoil section parallel to the Z-axis is called the airfoil mid-curvature. The ratio of the maximum distance f between the airfoil mid-curvature and the blade chord to the chord length C is called the maximum camber F. The distance from the blade airfoil section S1 to the blade airfoil section S... nThe maximum camber F first gradually increases and then gradually decreases, from the airfoil section S1 to the airfoil section S... n The airfoil thickness h first gradually decreases and then gradually increases.

[0008] Preferably, n is 17, and the airfoil section S1 to airfoil section S 17 The F-values ​​are shown in the table below: <![CDATA[F2]]> 0.058±0.001 <![CDATA[F3]]> 0.060±0.001 <![CDATA[F4]]> 0.061±0.001 <![CDATA[F5]]> 0.061±0.001 <![CDATA[F6]]> 0.060±0.001 <![CDATA[F7]]> 0.059±0.001 <![CDATA[F8]]> 0.058±0.001 <![CDATA[F9]]> 0.058±0.001 <![CDATA[F 10 ]]> 0.056±0.001 <![CDATA[F 11 ]]> 0.054±0.001 <![CDATA[F 12 ]]> 0.052±0.001 <![CDATA[F 13 ]]> 0.048±0.001 <![CDATA[F 14 ]]> 0.044±0.001 <![CDATA[F 15 ]]> 0.036±0.001 <![CDATA[F 16 ]]> 0.029±0.001 <![CDATA[F 17 ]]> 0.020±0.001 .

[0009] Preferably, the airfoil section S1 to the airfoil section S n The ratio of the airfoil thickness h to the chord length C is called the relative airfoil thickness H, and the values ​​of H are shown in the table below: <![CDATA[H2]]> 6.6% <![CDATA[H3]]> 6.3% <![CDATA[H4]]> 6.1% <![CDATA[H5]]> 6.0% <![CDATA[H6]]> 5.9% <![CDATA[H7]]> 5.8% <![CDATA[H8]]> 5.8% <![CDATA[H9]]> 5.7% <![CDATA[H 10 ]]> 5.7% <![CDATA[H 11 ]]> 5.7% <![CDATA[H 12 ]]> 5.7% <![CDATA[H 13 ]]> 5.8% <![CDATA[H 14 ]]> 6.0% <![CDATA[H 15 ]]> 6.2% <![CDATA[H 16 ]]> 6.4% <![CDATA[H 17 ]]> 6.6% .

[0010] Preferably, in the nine-bladed fan, the included angles between adjacent blades are 42.01±0.01°, 38.48±0.01°, 40.67±0.01°, 40.67±0.01°, 38.48±0.01°, 42.01±0.01°, 37.15±0.01°, 43.38±0.01°, and 37.15±0.01°, respectively; when the number of blades is seven, the included angles between adjacent blades are 50.33±0.01°, 51.84±0.01°, 49.57±0.01°, and 55.2°, respectively. The included angles between adjacent blades are 1±0.01°, 48.48±0.01°, 51.37±0.01°, and 53.20±0.01°. When the number of fan blades is eleven, the included angles between adjacent blades are 37.32±0.01°, 27.49±0.01°, 35.00±0.01°, 34.99±0.01°, 27.49±0.01°, 37.32±0.01°, 31.95±0.01°, 29.15±0.01°, 38.19±0.01°, 29.15±0.01°, and 31.95±0.01°. Therefore, by changing the included angle between adjacent blades, the fan can produce lower piercing noise under load.

[0011] After adopting the above technical solution, the effect of this utility model is that: compared with a fan of the same size, the projection curve of the leading edge of the fan blade in the plane of rotation of the fan blade is y 前When the fan blade installation angle β and the fan blade chord length C satisfy the specific polynomials mentioned above, the leading edge of the entire fan blade has a larger curvature. This makes the transition between the fan blade and the pressure-holding ring smoother, which helps to suppress or delay the occurrence of turbulence, reduce turbulence noise, and ensure sufficient airflow. Compared with similarly sized fans currently on the market, it reduces noise, ensures sufficient airflow, and improves efficiency. This cooling fan impeller can be widely used in various fields, such as vehicle cooling systems, digital center or energy storage cooling systems.

[0012] Furthermore, since the direction axis perpendicular to the blade chord is defined as the Z-axis, the curve connecting the midpoints of the upper and lower surfaces of the blade airfoil section parallel to the Z-axis is called the airfoil mid-curvature. The ratio of the maximum distance f between the airfoil mid-curvature and the blade chord to the chord length C is called the maximum camber F. The distance from the blade airfoil section S1 to the blade airfoil section S... n The maximum camber F first gradually increases and then gradually decreases, from the airfoil section S1 to the airfoil section S... n The airfoil thickness h first gradually decreases and then gradually increases. Therefore, by optimizing the airfoil section of the fan blade, the air pressure and air volume of the fan can be further increased.

[0013] To solve the second technical problem mentioned above, the technical solution of this utility model is: a cooling fan assembly, including a shroud and a drive motor. The cooling fan assembly also includes the cooling fan impeller. The shroud includes a cover and a motor mounting hub inside the cover. The motor mounting hub and the cover are connected by a plurality of radially extending radial stiffeners. The drive motor is mounted on the motor mounting hub. The radial stiffeners are provided with a plurality of annular reinforcing ribs.

[0014] After adopting the above technical solution, the effect of this utility model is that the cooling fan assembly uses the above-mentioned cooling fan, which can ensure airflow while reducing noise. At the same time, the radial stiffeners and annular reinforcing ribs can improve the protection level of the entire cooling fan. Attached Figure Description

[0015] The present invention will be further described below with reference to the accompanying drawings and embodiments.

[0016] Figure 1 This is a schematic diagram of the cooling fan structure of Embodiment 1 of this utility model; Figure 2 This is a perspective view of the cooling fan structure of Embodiment 1 of this utility model; Figure 3 This is a schematic diagram of the airfoil section division; Figure 4 This is a schematic diagram of the airfoil cross-section; Figure 5 This is a schematic diagram of the airfoil parameters coordinates; Figure 6 It is a projection curve of the leading edge and trailing edge of the fan blade; Figure 7 This is a diagram showing the positional relationship between the installation angle β, chord length C, and blade radius r; Figure 8 The waveform diagrams show simulated noise from the new and old 385mm nine-blade fan blades. Figure 9 The waveform diagrams show simulated noise from the new and old 405mm nine-blade fan blades. Figure 10 This is a three-dimensional structural view of the cooling fan assembly in Example 2; Figure 11 This is a three-dimensional view of the back of the cooling fan assembly in Example 2; Figure 12 This is a waveform diagram of the simulated noise of the new and old 346m seven-blade fan blades in Example 3; Figure 13 These are waveform diagrams of simulated noise from the new and old seven-blade fan blades of the 355m fan in Example 3; Figure 14 This is a waveform diagram of the simulated noise of the new and old 11-blade fan blades in Example 4; In the attached diagram: 1. Central hub; 2. Pressure holding ring; 3. Fan blade; 301. Leading edge of fan blade; 302. Trailing edge of fan blade; 303. Airfoil mid-curve; 304. Fan blade chord line; 4. Wind shield; 41. Cover body; 42. Motor mounting hub; 43. Radial stiffener; 44. Annular reinforcing rib. Detailed Implementation

[0017] The present invention will be further described in detail below through specific embodiments. Example 1

[0018] like Figures 1 to 4 As shown, a cooling fan impeller includes a central hub and a set of fan blades. The inner end of the set of fan blades is fixed to the central hub, and a pressure-holding ring is fixed to the outer end of the set of fan blades. The outer diameter of the pressure-holding ring is 385~405mm, the outer diameter of the central hub is 135.6-155.6mm, and the number of fan blades is nine.

[0019] In this embodiment, the outer diameter of the pressure-holding ring is 385 mm, and the outer diameter of the central hub is 145.6 mm. The polynomial in this embodiment is applicable to outer diameters of 346-450 mm and outer diameters of the central hub of 135.6-155.6 mm.

[0020] The fan blade is divided into several airfoil sections with different radii along the radial direction using equally spaced circular arcs, numbered S1, S2, ..., S... from the inside out. n Where n is a natural number, such as Figure 3 As shown, in this embodiment, n is preferably 17, where the diameter of S1 is equal to the diameter of the central hub, S 17 The diameter of the airfoil is equal to the inner diameter of the pressure-holding ring, thus the fan blade is divided into 17 airfoil sections. When the fan rotates, the airflow direction is parallel to the fan axis. However, since the fan blades are rotating, the direction of the airflow relative to the fan blades is the incoming flow direction. Different airfoil sections have different incoming airflow angles. Each airfoil section needs to be adjusted to the most suitable fan blade installation angle β and chord length C to achieve optimal operating conditions.

[0021] The front point of each airfoil section is called the leading edge of the airfoil; the point with the greatest distance from the leading edge is called the trailing edge; the straight line connecting the leading and trailing edges is called the chord line of the airfoil section, the length of which is C, and the angle between the chord line and the plane of rotation is the blade installation angle β; the windward side of the blade is the leading edge, the leeward side is the trailing edge, and the projection curve of the leading edge in the plane of rotation is y. 前 ,in: y 前 = a1×x 5 +b1×x 4 +c1×x 3 +d1×x 2 +e1×x+f1 In the above formula: a1 = 2.7503e -8 ±2.75e -9 b1 = -1.6216e -5 ±1.62e -6 c1=3.7723e -3 ±3.77e -4 d1=-4.2707e -1 ±4.27e -2 e1=2.2909e 1 ±2.29; f1=-4.5645e 2 ±45.6; Where x is the x-coordinate of the plane of rotation of the fan blade, y 前 The vertical coordinate of the plane of rotation of the fan blades; The specific values ​​are shown in the table below: 70 5.31 135 -18.72 75 3.08 140 -18.93 80 0.35 145 -18.89 85 -2.56 150 -18.50 90 -5.43 155 -17.64 95 -8.12 160 -16.08 100 -10.52 165 -13.55 105 -12.59 170 -9.67 110 -14.32 175 -3.97 115 -15.72 180 4.13 120 -16.83 185 15.31 like Figure 6 As shown, Figure 6The text describes the projection curve of the leading edge of the fan blade onto the plane of rotation of the fan blade, with the specific polynomial being y. 前 = 2.7503e -8 ×x 5 -1.6216e -5 ×x 4 +3.7723e -3 ×x 3 -4.2707e -1 ×x 2 +2.2909e 1 ×x-4.5645e 2 Where e is a natural constant; since the curve of the leading edge of the blade is uniquely determined by a polynomial, and the blade mounting angle β and chord length C can also be uniquely determined by a polynomial function, then the projection curve y of the trailing edge of the blade in the blade rotation plane is... 后 This corresponds to and is uniquely determined, therefore no additional determination of y is needed. 后 The polynomial is being redefined.

[0022] The fan blade installation angle β satisfies the following polynomial function: β=a2×r 7 +b2×r 6 +c2×r 5 +d2×r 4 +e2×r 3 +f2×r 2 +g2×r+h2 In the above formula: a2 = 7.30042e -12 ±7.3e -13 b2 = -6.49315e -9 ±1e -10 c2=2.41521e -6 ±2.42e -7 ; d2=-0.000486617±0.0000487; e2=0.0573324±0.00573; f2=-3.949431172±0.395; g2=147.118±14.7; h2 = -2252.26288 ± 22.5; Where r is the radius of the fan blade airfoil section with the center of the central hub as the center, and the unit is mm; the fan blade mounting angle β is in degrees. The chord length C of the fan blade satisfies the following polynomial function: C = a3×r 7 +b3×r 6 +c3×r 5+d3×r 4 +e3×r 3 +f3×r 2 +g3×r+h3 In the above formula: a3 = -7.80241e -12 ±7.8e -13 b3=6.93038e -9 ±6.93e -10 c3 = -2.58228e -6 ±2.58e -7 d3=5.23236e -4 ±5.23e -5 ;e3=-0.06225±0.00623; f3=4.349±0.435; g3=-165.3559±16.5; h3=2693.499±269; The unit for the fan blade chord length C is mm.

[0023] After applying the polynomials described above, the projection curve of the leading edge of the fan blade onto the plane of rotation of the fan blade can be determined as y. 前、 Given that the blade chord length C and the blade installation angle β are fixed, the projection curve of the blade trailing edge onto the blade rotation plane is y. 后 This corresponds to a unique determination.

[0024] like Figure 7 As shown, Figure 7 The diagram illustrates the relationship between the blade chord length C, the blade mounting angle β, and the radius r. The specific coordinates are shown in the table below: 72.00 30.18 51.85 80.40 28.26 50.64 88.80 26.60 49.30 97.20 25.24 47.94 105.59 24.07 46.50 113.99 22.51 45.34 122.39 20.84 44.60 129.67 19.22 44.12 136.39 17.77 43.78 143.11 17.48 43.60 150.39 17.82 43.38 157.67 18.36 43.45 164.38 18.79 44.69 171.10 18.54 47.65 178.38 17.47 52.87 185.66 15.97 59.91 193.50 14.21 67.80 in Figure 7 In the diagram, the horizontal axis represents the radius r, the left vertical axis represents the installation angle, and the right vertical axis represents the chord length.

[0025] In this embodiment, the leading edge of the entire fan blade has a larger curvature, which makes the transition between the fan blade and the pressure-holding ring smoother. This helps to suppress or delay the occurrence of turbulence and reduce turbulence noise to some extent. Because the leading edge of the fan blade has a larger curvature, the airflow and efficiency of the fan are ensured by optimizing the blade chord length C and the blade mounting angle β.

[0026] Preferably, the direction axis perpendicular to the blade chord is defined as the Z-axis. The curve connecting the midpoints of the upper and lower surfaces of the blade airfoil section parallel to the Z-axis is called the airfoil mid-curvature. The ratio of the maximum distance f between the airfoil mid-curvature and the blade chord to the chord length C is called the maximum camber F. The distance from the blade airfoil section S1 to the blade airfoil section S... n The maximum camber F first gradually increases and then gradually decreases, from the airfoil section S1 to the airfoil section S...n The airfoil thickness h first gradually decreases and then gradually increases.

[0027] Preferably, the airfoil section S1 to the airfoil section S 17 The F-values ​​are shown in the table below: <![CDATA[F2]]> 0.058±0.001 <![CDATA[F3]]> 0.060±0.001 <![CDATA[F4]]> 0.061±0.001 <![CDATA[F5]]> 0.061±0.001 <![CDATA[F6]]> 0.060±0.001 <![CDATA[F7]]> 0.059±0.001 <![CDATA[F8]]> 0.058±0.001 <![CDATA[F9]]> 0.058±0.001 <![CDATA[F 10 ]]> 0.056±0.001 <![CDATA[F 11 ]]> 0.054±0.001 <![CDATA[F 12 ]]> 0.052±0.001 <![CDATA[F 13 ]]> 0.048±0.001 <![CDATA[F 14 ]]> 0.044±0.001 <![CDATA[F 15 ]]> 0.036±0.001 <![CDATA[F 16 ]]> 0.029±0.001 <![CDATA[F 17 ]]> 0.020±0.001 .

[0028] Preferably, the airfoil section S1 to the airfoil section S n The ratio of the airfoil thickness h to the chord length C is called the relative airfoil thickness H, and the values ​​of H are shown in the table below: <![CDATA[H2]]> 6.6% <![CDATA[H3]]> 6.3% <![CDATA[H4]]> 6.1% <![CDATA[H5]]> 6.0% <![CDATA[H6]]> 5.9% <![CDATA[H7]]> 5.8% <![CDATA[H8]]> 5.8% <![CDATA[H9]]> 5.7% <![CDATA[H 10 ]]> 5.7% <![CDATA[H 11 ]]> 5.7% <![CDATA[H 12 ]]> 5.7% <![CDATA[H 13 ]]> 5.8% <![CDATA[H 14 ]]> 6.0% <![CDATA[H 15 ]]> 6.2% <![CDATA[H 16 ]]> 6.4% <![CDATA[H 17 ]]> 6.6% .

[0029] like Figure 5 As shown, Figure 5 The diagram illustrates the parameters of the airfoil section in the XZ coordinate system; where the X direction is the horizontal direction and the Z direction is the vertical direction. Figure 5 The data in the image has been normalized in both the X and Z directions, with the horizontal length of the airfoil section scaled to 1. The airfoil section shows that the maximum camber F first gradually increases and then gradually decreases, while the airfoil thickness h first gradually decreases and then gradually increases. In actual production, it is only necessary to adjust the data based on the actual blade length. Figure 5 Simply multiply the base value by the corresponding coefficient.

[0030] In this embodiment, the circumferential angles between adjacent fan blades are not evenly distributed. Preferably, in the nine-blade fan, the circumferential angles between adjacent fan blades are 42.01±0.01°, 38.48±0.01°, 40.67±0.01°, 40.67±0.01°, 38.48±0.01°, 42.01±0.01°, 37.15±0.01°, 43.38±0.01°, and 37.15±0.01°. Therefore, by changing the circumferential angles between adjacent fan blades, the fan's sharp noise under load is reduced.

[0031] like Figure 8 As shown, Figure 8The horizontal axis represents the frequency of the noise; the vertical axis represents the decibel value of the noise at different frequencies. The waveform in the graph represents the noise value after passing through A-weighted measurement. A-weighted measurement is a standard weighted curve used for audio measurement to reflect the response characteristics of the human ear. Sound pressure level is derived from A-weighting and is represented in dB(A), or simply A-weighted dB level. A-weighting is a widely used single-value evaluation index for noise and can be measured using a sound level meter. Since noise measurement must reflect the perceived loudness by the human ear, the auditory characteristics of the human ear must be fully considered. The human ear's sensitivity to changes in sound frequencies varies; too high or too low a sensitivity indicates decreased sensitivity, resembling the letter A, hence the name A-weighted. The A-weighting standard was established by the American Standards Institute (ASI) in the 1940s to describe the human ear's sensitivity to changes in sound frequencies. Figure 8 The diagram illustrates the simulated noise waveform. The fan being tested has an outer diameter of 385mm for the pressure ring and an outer diameter of 145.6mm for the central hub. The test standard is in accordance with national standards. The distance between the microphone and the center of the fan is 1m + 0.005m, and the distance between the center of the fan, the microphone, and the ground is 1.5m + 0.005m.

[0032] Figure 8 In the waveform diagram, the blue waveform is the noise waveform of the new fan impeller in this embodiment; the green waveform is the noise waveform of the old fan impeller of the same specification. It can be seen from the waveform diagram that the noise of the new fan impeller is 74.91 dB(A), while the noise of the old fan impeller is 77.09 dB(A). The fan impeller of this embodiment has lower noise.

[0033] The test parameters for the fan in this embodiment and the old model are shown in Tables 1 and 2 below:

[0034] Table 1

[0035] Table 2 The test comparisons in Tables 1 and 2 show that, under the same voltage and static pressure settings, the fan speeds in this embodiment and the older model are essentially the same. However, there are differences in standard airflow and static pressure efficiency. For example, with a static pressure of 270.0 Pa, the static pressure efficiency of the fan in this embodiment is 39.4%, while that of the older model is 38%. The standard airflow in this embodiment is 3058.8 m³ / s. 3 / h, the standard airflow of the older model fan is 2716.4 m³ / h. 3 / h. At other static pressure values, the fan in this embodiment is still superior to the older fan in terms of standard airflow and static pressure efficiency.

[0036] Tables 3 and 4 below show the specific test parameters for a nine-bladed fan impeller with a pressure-holding ring diameter of 405 mm.

[0037]

[0038] Table 3

[0039] Table 4 As can be seen from Tables 3 and 4, taking a static pressure of 270.0 Pa as an example, the static pressure efficiency of the fan in this embodiment is 39.3%, while the static pressure efficiency of the older fan is 38.9%. The standard airflow of this embodiment is 3082.2 m³ / s. 3 / h, the standard airflow of the older model fan is 2961.2 m³ / h. 3 / h.

[0040] like Figure 9 As shown, Figure 9 The document records the noise waveforms of the 405mm fan impeller in this embodiment and the older fan impeller. Figure 9 It can be observed that the noise level of the new fan impeller in this embodiment is 74.90 dB(A), while the noise level of the old fan impeller is 75.32 dB(A). The fan impeller in this embodiment has lower noise.

[0041] Example 2 This embodiment discloses a cooling fan assembly, including a shroud and a drive motor. The cooling fan assembly also includes the aforementioned cooling fan impeller. The shroud includes a housing and a motor mounting hub located within the housing. The motor mounting hub and the housing are connected by several radially extending radial stiffeners. The drive motor is mounted on the motor mounting hub, and the radial stiffeners are provided with several annular reinforcing ribs. Figure 10 and Figure 11 As shown, the cooling fan assembly uses the aforementioned cooling fan, which can ensure airflow while reducing noise. At the same time, the radial stiffeners and annular reinforcing ribs can improve the overall protection level of the cooling fan.

[0042] Example 3 This embodiment is basically the same as the scheme in Embodiment 1, except that the number of fan blades is seven. At this time, the outer diameter of the pressure holding ring is 346~395mm. When the number of fan blades is seven, the circumferential included angles between adjacent fan blades are 50.33±0.01°, 51.84±0.01°, 49.57±0.01°, 55.21±0.01°, 48.48±0.01°, 51.37±0.01°, and 53.20±0.01°, respectively.

[0043] The test parameters for the fan and the old fan when the pressure ring diameter is 346mm in Example 3 are shown in Tables 5 and 6 below:

[0044] Table 5

[0045] Table 6 A comparison of Tables 5 and 6 reveals that, under the same static pressure setting, the static pressure efficiency and airflow of the fan impeller in this embodiment are superior to those of the older fan impeller.

[0046] like Figure 12 As shown, Figure 12 The document describes the noise waveforms of the fan impeller in this embodiment and the comparative fan impeller. Figure 12 It can be observed that the noise level of the new fan impeller in this embodiment is 75.83 dB(A), while the noise level of the old fan impeller is 76.65 dB(A). The fan impeller in this embodiment has lower noise.

[0047] The test parameters for the fan with a pressure-holding ring diameter of 355mm and the old fan are shown in Tables 7 and 8 below:

[0048] Table 7

[0049] Table 8 A comparison of Tables 7 and 8 reveals that, under the same static pressure setting, the static pressure efficiency and airflow of the fan impeller in this embodiment are superior to those of the older fan impeller.

[0050] like Figure 13 As shown, Figure 13 The document describes the noise waveforms of the fan impeller with a pressure-holding ring diameter of 355mm in this embodiment and the comparative fan impeller. Figure 13 It can be observed that the noise level of the new fan impeller in this embodiment is 75.65 dB(A), while the noise level of the old fan impeller is 77.06 dB(A). The fan impeller in this embodiment has lower noise. Example 4

[0051] The fan impeller in this embodiment is the same as that in Embodiment 1, except that the number of fan blades is eleven. When the number of fan blades is eleven, the outer diameter of the pressure-holding ring is 410~450mm, and the circumferential included angles between adjacent fan blades are 37.32±0.01°, 27.49±0.01°, 35.00±0.01°, 34.99±0.01°, 27.49±0.01°, 37.32±0.01°, 31.95±0.01°, 29.15±0.01°, 38.19±0.01°, 29.15±0.01°, and 31.95±0.01°.

[0052] The test parameters for the eleven-blade fan and the old fan of the same size when the pressure ring diameter of Example 4 is 450mm are shown in Tables 9 and 10 below:

[0053] Table 9

[0054] Table 10 A comparison of Tables 9 and 10 reveals that, under the same static pressure setting, the static pressure efficiency and airflow of the fan impeller in this embodiment are superior to those of the older fan impeller.

[0055] like Figure 14 As shown, Figure 14 The document records the noise waveform lines of the eleven-page fan impeller in this embodiment and the comparative fan impeller, from... Figure 14 It can be observed that the noise level of the new fan impeller in this embodiment is 77.65 dB(A), while the noise level of the old fan impeller is 81.94 dB(A). The fan impeller in this embodiment has lower noise.

[0056] The cooling fan impeller and cooling fan assembly in this embodiment are widely used and can be applied in thermal management systems of passenger cars, commercial vehicles, off-road vehicles, digital centers, and energy storage equipment. The above-described embodiments are merely descriptions of preferred embodiments of this utility model and are not intended to limit the scope of this utility model. Various modifications and alterations to the technical solution of this utility model without departing from its design spirit should fall within the protection scope defined by the claims of this utility model.

Claims

1. A cooling fan impeller, comprising a central hub and a set of fan blades, wherein the inner ends of the set of fan blades are fixed to the central hub, and the outer ends of the set of fan blades are fixed with pressure-holding rings, the number of fan blades being seven, nine, or eleven, and the outer diameter of the central hub being 135.6-155.6 mm, wherein... When the number of fan blades is seven, the outer diameter of the pressure-holding ring is 346~395mm; when the number of fan blades is nine, the outer diameter of the pressure-holding ring is 385~405mm; and when the number of fan blades is eleven, the outer diameter of the pressure-holding ring is 410~450mm. The fan blades are decomposed radially into several airfoil sections with different radii using equally spaced circular arcs, numbered S1, S2, ..., S... from the inside out. n Where n is a natural number, the front point of each airfoil section is called the leading edge of the airfoil; the point with the largest distance from the leading edge of the airfoil is called the trailing edge of the airfoil; the straight line connecting the leading edge and the trailing edge of the airfoil is called the chord line of the airfoil section, the length of the chord line is the chord length C, and the angle between the chord line and the plane of rotation of the airfoil is the airfoil mounting angle β of the airfoil section; the windward side of the airfoil is the leading edge side, and the leeward side is the trailing edge side. The characteristic feature is that the projection curve of the leading edge side of the airfoil in the plane of rotation of the airfoil is y. 前 ,in: y 前 = a1×x 5 +b1×x 4 +c1×x 3 +d1×x 2 +e1×x+f1 In the above formula: a1 = 2.7503e -8 ±2.75e -9 b1 = -1.6216e -5 ±1.62e -6 c1=3.7723e -3 ±3.77e -4 d1=-4.2707e -1 ±4.27e -2 e1=2.2909e 1 ±2.29; f1=-4.5645e 2 ±45.6; Where x is the x-coordinate of the plane of rotation of the fan blade, y 前 The vertical coordinate of the plane of rotation of the fan blades; The fan blade installation angle β satisfies the following polynomial function: β=a2×r 7 +b2×r 6 +c2×r 5 +d2×r 4 +e2×r 3 +f2×r 2 +g2×r+h2 In the above formula: a2 = 7.30042e -12 ±7.3e -13 b2 = -6.49315e -9 ±1e -10 c2=2.41521e -6 ±2.42e -7 ; d2=-0.000486617±0.0000487; e2=0.0573324±0.00573; f2=-3.949431172±0.395; g2=147.118±14.7; h2=-2252.26288±22.5； Where r is the radius of the fan blade airfoil section with the center of the central hub as the center, and the unit is mm; the fan blade mounting angle β is in degrees. The chord length C of the fan blade satisfies the following polynomial function: C = a3×r 7 +b3×r 6 +c3×r 5 +d3×r 4 +e3×r 3 +f3×r 2 +g3×r+h3 In the above formula: a3=-7.80241e -12 ±7.8e -13 ; b3=6.93038e -9 ±6.93e -10 ; c3=-2.58228e -6 ±2.58e -7 ; d3=5.23236e -4 ±5.23e -5 ; e3=-0.06225±0.00623; f3=4.349±0.435; g3=-165.3559±16.5; h3=2693.499±269; The unit for the fan blade chord length C is mm.

2. The cooling fan impeller as described in claim 1, characterized in that: Define the direction axis perpendicular to the blade chord line as the Z-axis. The curve connecting the midpoints of the upper and lower surfaces of the airfoil section parallel to the Z-axis is called the airfoil mid-curvature. The ratio of the maximum distance f between the airfoil mid-curvature and the blade chord line to the chord length C is called the maximum camber F. The distance from airfoil section S1 to airfoil section S... n The maximum camber F first gradually increases and then gradually decreases, from the airfoil section S1 to the airfoil section S... n The airfoil thickness h first gradually decreases and then gradually increases.

3. A cooling fan impeller as described in claim 2, characterized in that: Where n is 17, the airfoil section S1 to airfoil section S 17 The F values ​​are as follows: F1 is 0.056±0.001; F2 is 0.058±0.001; F3 is 0.060±0.001; F4 is 0.061±0.001; F5 is 0.061±0.001; F6 is 0.060±0.001; F7 is 0.059±0.001; F8 is 0.058±0.001; F9 is 0.058±0.001; F 10 It is 0.056±0.001; F 11 It is 0.054±0.001; F 12 It is 0.052 ± 0.001; F 13 It is 0.048±0.001; F 14 It is 0.044±0.001; F 15 It is 0.036±0.001; F 16 It is 0.029±0.001; F 17 It is 0.020±0.

001.

4. A cooling fan impeller as described in claim 3, characterized in that: The fan blade airfoil section S1 to the fan blade airfoil section S n The ratio of airfoil thickness h to chord length C is called the relative airfoil thickness H. The H values ​​are shown in the table below: H1 = 6.9%; H2 = 6.6%; H3 = 6.3%; H4 = 6.1%; H5 = 6.0%; H6 = 5.9%; H7 = 5.8%; H8 = 5.8%; H9 = 5.7%; H... 10 It is 5.7%; H 11 It is 5.7%; H 12 It is 5.7%; H 13 It is 5.8%; H 14 It was 6.0%; H 15 It is 6.2%; H 16 It is 6.4%; H 17 It is 6.6%.

5. A cooling fan impeller as described in claim 4, characterized in that: In the nine-bladed fan, the included angles between adjacent blades are 42.01±0.01°, 38.48±0.01°, 40.67±0.01°, 40.67±0.01°, 38.48±0.01°, 42.01±0.01°, 37.15±0.01°, 43.38±0.01°, and 37.15±0.01°, respectively; when the number of blades is seven, the included angles between adjacent blades are 50.33±0.01°, 51.84±0.01°, 49.57±0.01°, and 55.21±0.01°, respectively. 0.01°, 48.48±0.01°, 51.37±0.01°, 53.20±0.01°; when the number of fan blades is eleven, the included angles between adjacent fan blades are 37.32±0.01°, 27.49±0.01°, 35.00±0.01°, 34.99±0.01°, 27.49±0.01°, 37.32±0.01°, 31.95±0.01°, 29.15±0.01°, 38.19±0.01°, 29.15±0.01°, 31.95±0.01°.

6. A cooling fan assembly, comprising a shroud and a drive motor, characterized in that: The cooling fan assembly also includes the cooling fan impeller as described in claim 1, the shroud includes a shroud body and a motor mounting hub located within the shroud body, the motor mounting hub and the shroud body are connected by a plurality of radially extending radial stiffeners, the drive motor is mounted on the motor mounting hub, and the radial stiffeners are provided with a plurality of annular reinforcing ribs.

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