Impeller assembly and fan

Abstract

The invention discloses an impeller assembly and a fan. The impeller assembly comprises a front disc, a rear disc, a hub and a plurality of blades. An impeller inlet is formed in the small-diameter end of the front disc, and the diameter of the impeller inlet is D0; the distances between the large-diameter end and the small-diameter end of the rear disc and the front disc are b and H respectively, an impeller outlet is formed between the rear disc and the large-diameter end of the front disc, and the diameter of the impeller outlet is D2; the hub is arranged on the rear disc, and the diameter of the hub is d; the blades are arranged around the outer surface of the hub at intervals, the torsion angle of each blade is omega, each blade forms a first contour and a second contour, a plane parallel to the axis of the hub is defined as a reference plane, the first contour and the second contour of each blade are projected on the reference plane, and installation angles beta 1A and beta 1B are formed. The included angle between the second contour extension line of the blade and the tangent line at the intersection point of the rear disc is a mounting angle beta 2. The problems that in the prior art, a draught fan is large in noise, low in efficiency and high in energy consumption are solved.

Description

Technical Field

[0001] The present invention relates to the technical field of centrifugal fans, and in particular to an impeller assembly and a fan. Background Art

[0002] The impeller assembly is the core energy transmission component of the fan. Its geometric parameters and flow channel design directly affect the equipment's efficiency, noise, and operational stability. For example: ① When the inlet and outlet diameters do not match, the flow velocity in the flow channel changes suddenly, which can easily generate vortices and flow separation, resulting in energy loss; ② When the blade installation angles do not match, localized backflow can occur, reducing efficiency and generating aerodynamic noise.

[0003] To this end, designing a fan with low noise level, high efficiency and good aerodynamic performance is more in line with market demand. Summary of the Invention

[0004] In view of the deficiencies in the prior art, the present invention aims to provide an impeller assembly and a fan to solve the problems of high noise, low efficiency and high energy consumption of the fan in the prior art.

[0005] To achieve the above object, the present invention adopts the following technical solutions:

[0006] Impeller assembly, including:

[0007] a front disc comprising a small diameter end and a large diameter end oppositely disposed, wherein the small diameter end of the front disc is provided with an impeller inlet having a diameter of D0, and the small diameter end of the front disc is connected to the large diameter end by an inclined connecting section having an inclination angle of θ1;

[0008] a rear disc spaced apart from the front disc and arranged close to the large diameter end thereof, wherein the distances between the rear disc and the large diameter end and the small diameter end of the front disc are b and H respectively, and an impeller outlet is formed between the rear disc and the large diameter end of the front disc, and the diameter of the impeller outlet is D2;

[0009] a hub, provided on the rear disc and extending toward the impeller inlet, with a diameter of d;

[0010] A plurality of blades are spaced apart around the outer surface of the hub, the blades have a torsion angle of ω and are formed with a first profile and a second profile, the first profile of the blade being fixed to the hub and the second profile extending toward the impeller outlet, a plane parallel to the hub axis being defined as a reference plane, the first profile and the second profile of the blade being projected onto the reference plane and forming installation angles β1A and β1B, and the angle between the extension line of the second profile of the blade and the tangent line at the intersection of the rear disc is defined as the installation angle β2;

[0011] Wherein, the impeller assembly satisfies one of the following relationships:

[0012] (1) D0=0.772D2, θ1=7.4°, b=0.212D2, H=0.370D2, d=0.120D2, ω=73.1°, β1A=29.6°, β1B=59.8°, β2=73.9°;

[0013] (2) D0 = 0.614D2, θ1 = 0.1°, b = 0.297D2, H = 0.373D2, d = 0 or d = 0.145D2,

[0014] ω=46.5°, β1A=35.1°, β1B=24.3°, β2=26.1°;

[0015] (3) D0 = 0.689D2, θ1 = 1.3°, b = 0.277D2, H = 0.358D2, d = 0 or d = 0.145D2,

[0016] ω=48.4°, β1A=20.4°, β1B=21.5°, β2=25.9°;

[0017] (4) D0=0.586D2, θ1=5.1°, b=0.127D2, H=0.323D2, d=0.131D2, ω=66.1°, β1A=42°, β1B=83.5°, β2=55.1°;

[0018] (5) D0=0.596D2, θ1=6.4°, b=0.127D2, H=0.368D2, d=0.131D2, ω=52.9°, β1A=26.8°, β1B=65.7°, β2=39.6°;

[0019] (6) D0=0.758D2, θ1=9.2°, b=0.175D2, H=0.384D2, d=0.147D2, ω=54.3°, β1A=34.9°, β1B=80.2°, β2=34.9°;

[0020] (7) D0=0.642D2, θ1=4.3°, b=0.17D2, H=0.312D2, d=0.149D2, ω=45.9°, β1A=35.9°, β1B=81.2°, β2=49.8°;

[0021] (8) D0=0.606D2, θ1=5.1°, b=0.197D2, H=0.386D2, d=0.137D2, ω=47.7°, β1A=β1B=39.3°, β2=44.8°;

[0022] (9) D0=0.457D2, θ1=1.2°, b=0.099D2, H=0.234D2, d=0.122D2, ω=13.6°, β1A=19.8°, β1B=64.7°, β2=151.4°;

[0023] (10) D0=0.493D2, θ1=9.2°, b=0.062D2, H=0.188D2, d=0.116D2, ω=71.8°, β1A=66.6°, β1B=28.9°, β2=42.4°.

[0024] Furthermore, the plurality of blades form a blade inlet, the diameter of the blade inlet is D1, and satisfies: D0=D1;

[0025] or

[0026] The diameter of the blade inlet is D1', which satisfies the following: D0<D1'.

[0027] Furthermore, the height of the blade is h, and h satisfies one of the following relationships:

[0028] (1')h=0.357D2;

[0029] (2')h=0.328D2;

[0030] (3')h=0.306D2;

[0031] (4')h=0.303D2;

[0032] (5')h=0.347D2;

[0033] (6')h=0.368D2;

[0034] (7')h=0.297D2;

[0035] (8')h=0.367D2;

[0036] (9')h=0.205D2;

[0037] (10')h=0.168D2.

[0038] Furthermore, the number of the plurality of blades is defined as z, satisfying: z=8-21.

[0039] Furthermore, the first contour and the second contour of the blade are smoothly transitioned through a bridge section.

[0040] Furthermore, the bridge section of one of the two adjacent blades is twisted toward the other blade so as to be arranged toward the impeller inlet.

[0041] A fan, comprising: the impeller assembly described above.

[0042] Furthermore, the fan also includes a volute, which wraps the impeller assembly and forms a fan inlet and a fan outlet, which are used to be connected to the impeller inlet and the impeller outlet respectively.

[0043] Furthermore, the width of the fan outlet is B, and B satisfies one of the following relationships:

[0044] (1")B=0.584D2;

[0045] (2")B=0.871D2;

[0046] (3")B=0.866D2;

[0047] (4")B=0.667D2;

[0048] (5")B=0.518D2;

[0049] (6')B=0.672D2;

[0050] (7")B=0.52D2;

[0051] (8")B=0.676D2;

[0052] (9")B=0.25D2;

[0053] (10”)B=0.232D2.

[0054] Furthermore, the volute lines of the volute are R1, R2, R3 and R4, and the volute tongue angle is θ2, and the volute satisfies one of the following relationships:

[0055] (1”')R1=0.668D2, R2=0.786D2, R3=0.936D2, R4=1.066D2, θ2=35.7°;

[0056] (2”')R1=0.669D2, R2=0.850D2, R3=1.049D2, R4=1.227D2, θ2=35.4°;

[0057] (3"')R1=0.674D2, R2=0.832D2, R3=0.984D2, R4=1.158D2, θ2=37.4°;

[0058] (4"')R1=0.637D2, R2=0.745D2, R3=0.869D2, R4=0.995D2, θ2=32.1°;

[0059] (5"')R1=0.659D2, R2=0.758D2, R3=0.854D2, R4=0.947D2, θ2=33.2°;

[0060] (6"')R1=0.627D2, R2=0.802D2, R3=0.942D2, R4=1.075D2, θ2=19.1°;

[0061] (7"')R1=0.607D2, R2=0.73D2, R3=0.835D2, R4=0.941D2, θ2=29.4°;

[0062] (8"')R1=0.647D2, R2=0.777D2, R3=0.891D2, R4=1.015D2, θ2=31.8°;

[0063] (9"')R1=0.581D2, R2=0.649D2, R3=0.709D2, R4=0.792D2, θ2=23°;

[0064] (10"') R1=0.565D2, R2=0.664D2, R3=0.771D2, R4=0.880D2, θ2=12.1°.

[0065] Compared with the existing technology, the present invention has the following beneficial effects: by optimizing the impeller inlet and outlet diameters, the spacing between the front disc, rear disc, hub and blades, the blade installation angle, etc., the impeller assembly has lower noise, higher efficiency and lower energy consumption. BRIEF DESCRIPTION OF THE DRAWINGS

[0066] Figure 1 This is a schematic structural diagram of an impeller assembly according to an embodiment of the present invention;

[0067] Figure 2 is a cross-sectional view of an impeller assembly in one embodiment of the present invention;

[0068] Figure 3 is a front view of an impeller assembly in one embodiment of the present invention;

[0069] Figure 4 for Figure 3 Sectional view along line AA;

[0070] Figure 5 Schematic diagram of a portion of the structure of an impeller assembly in one embodiment of the present invention;

[0071] Figure 6 Schematic diagram of the structure when the first contour and the second contour are projected onto the reference plane in one embodiment of the present invention;

[0072] Figure 7 Schematic diagram of the structure of the volute in one embodiment of the present invention;

[0073] Figure 8 It is a side view of a volute in one embodiment of the present invention.

[0074] The reference numerals in the drawings of the specification include:

[0075] 1. Front disc; 101. Small diameter end; 102. Large diameter end; 103. Connecting section; 104. Blade inlet; 2. Impeller inlet; 3. Rear disc; 4. Impeller outlet; 5. Hub; 6. Blade; 601. First profile; 602. Second profile; 603. Bridging section; 7. Volute. DETAILED DESCRIPTION

[0076] The present invention will be further described in detail below through specific embodiments:

[0077] In the embodiment of the present invention, Figures 1-6 As shown, the impeller assembly includes: a front disc 1, a rear disc 3, a hub 5 and a plurality of blades 6; the front disc 1 includes a small diameter end 101 and a large diameter end 102 which are arranged opposite to each other, the small diameter end 101 of the front disc 1 is provided with an impeller inlet 2, the diameter of the impeller inlet 2 is D0, the small diameter end 101 of the front disc 1 and its large diameter end 102 are connected by an inclined connecting section 103, the inclination angle of the connecting section 103 is θ1; the rear disc 3 is spaced apart from the front disc 1 and arranged close to its large diameter end 102, the spacings between the rear disc 3 and the large diameter end 102 of the front disc 1 and the small diameter end 101 are b and H respectively, and an impeller outlet is configured between the rear disc 3 and the large diameter end 102 of the front disc 1 The impeller outlet 4 has a diameter of D2; the hub 5 is provided on the rear disc 3 and extends toward the impeller inlet 2, and has a diameter of d; a plurality of blades 6 are arranged at intervals around the outer surface of the hub 5, the blades 6 have a torsion angle of ω, and are formed with a first profile 601 and a second profile 602, the first profile 601 of the blade 6 is fixed to the hub 5, and the second profile 602 thereof extends toward the impeller outlet 4, a plane parallel to the axis of the hub 5 is defined as a reference plane, the first profile 601 and the second profile 602 of the blade 6 are projected onto the reference plane, and form installation angles β1A and β1B, and the angle between the extension line of the second profile 602 of the blade 6 and the tangent at the intersection of the rear disc 3 is the installation angle β2.

[0078] The plurality of blades 6 form a blade inlet 104 , and the diameter of the blade inlet 104 is D1 .

[0079] The height of the blade 6 is h.

[0080] The number of the plurality of blades 6 is defined as z.

[0081] Example 1

[0082] In this embodiment, the diameter D0 of the impeller inlet 2, the inclination angle θ1 of the connecting section 103, the distance b between the rear disc 3 and the large diameter end 102 of the front disc 1, and the distance H between the small diameter end 101 thereof, the diameter D2 of the impeller outlet 4, the diameter d of the hub 5, the torsion angle ω of the blade 6, the installation angles β1A and β1B formed by the projection of the first profile 601 and the second profile 602 of the blade 6 on the reference plane, the installation angle β2 formed by the second profile 602, the diameter D1 of the blade inlet 104, the height h of the blade 6, and the number z of the blades 6 are shown in Table 1:

[0083]

[0084] Table 1

[0085] Wherein, D2 = 1000 mm, β1A and β1B are the installation angles of the blade inlet 104, and β2 is the installation angle of the blade outlet.

[0086] D0=D1=0.772D2. Since D0<D2, the diameter of the impeller inlet 2 is reduced, the inlet flow velocity is increased, the guiding effect on the fluid flow is enhanced, and the inlet turbulence loss is reduced. At the same time, D0 and D1 are consistent, ensuring that the fluid flow from the inlet to the blade 6 has no sudden change, avoiding local flow separation, and improving efficiency, thereby balancing the flow velocity and flow stability.

[0087] d = 0.120D2, setting a smaller hub 5 diameter increases the cross-sectional area of ​​the flow path at the root of the blades 6, reduces hub 5's resistance to the fluid, and increases flow rate. Simultaneously, the lightweight design reduces material costs and enables hub 5 to withstand the torque and centrifugal loads transmitted by the blades 6.

[0088] b = 0.212D². A smaller spacing can limit the width of the outlet flow channel, maintaining the outlet dynamic pressure level and preventing excessive dissipation of kinetic energy. Furthermore, H = 0.370D² can promote the conversion of kinetic energy into static pressure, improving static pressure recovery efficiency.

[0089] θ1 = 7.4°, which creates a smooth transition between the large-diameter end 101 and the small-diameter end 102 of the front disc 1 , reducing the risk of boundary layer separation caused by centrifugal force. This also allows the fluid to gradually accelerate along the front disc, reducing flow losses and improving energy transfer efficiency.

[0090] β1A = 29.6°, β1B = 59.8°, and β2 = 73.9°. The smaller inlet installation angle (at the hub 5) is used to adapt to low linear velocity areas and avoid inlet impact losses. The larger inlet installation angle (at the outer edge of blade 6) matches high linear velocity and improves the energy transfer efficiency of the outer edge of blade 6. At the same time, the outlet installation angle β2 can optimize the outlet flow direction, reduce eddy current losses, and improve static pressure recovery capability. In addition, combined with the height of blade 6 h = 0.357D2, the appropriate height can ensure sufficient flow area, avoid friction losses caused by excessive flow rate, balance flow requirements, ensure structural compactness, prevent vibration and strength issues caused by excessively tall blades 6, and reduce overall noise. Of course, selecting an appropriate number of blades 6 (z = 8) and equidistantly arranged on the circumference of the hub can improve energy transfer efficiency on the one hand, and avoid friction losses caused by too many blades 6 on the other hand, which can increase manufacturing costs.

[0091] This embodiment utilizes a combination of parameters to match flow velocity, flow channel, etc., which can maximize the energy conversion efficiency. At the same time, it adopts a smooth transition connection method to reduce flow separation, suppress turbulent pulsation, and then form an impeller assembly with low noise, high efficiency and low energy consumption.

[0092] Example 2

[0093] In this embodiment, the diameter D0 of the impeller inlet 2, the inclination angle θ1 of the connecting section 103, the distance b between the rear disc 3 and the large diameter end 102 of the front disc 1, and the distance H between the small diameter end 101 thereof, the diameter D2 of the impeller outlet 4, the diameter d of the hub 5, the torsion angle ω of the blade 6, the installation angles β1A and β1B formed by the projection of the first profile 601 and the second profile 602 of the blade 6 on the reference plane, the installation angle β2 formed by the second profile 602, the diameter D1 of the blade inlet 104, the height h of the blade 6, and the number z of the blades 6 are shown in Table 2:

[0094]

[0095] Table 2

[0096] Among them, D2=1000㎜.

[0097] Compared to the first embodiment, the diameter D0 of the impeller inlet 2 is reduced in this embodiment. A smaller inlet diameter significantly increases the inlet flow velocity and enhances the guidance of fluid flow. The larger hub 5 diameter d and the larger outlet width b not only withstand higher centrifugal loads but also reduce the outlet flow velocity, promoting the conversion of kinetic energy into static pressure. At the same time, the flow channel distance H remains essentially unchanged, maintaining the expansion trend of the axial flow channel. In this embodiment, the diameter d of the hub 5 can be selected to be 0 or 0.145D2. When d = 0, the impeller assembly does not include the hub 5, which is suitable for impeller assemblies in simulation tests, facilitating the optimization of the various blade parameter values ​​during the test. Conversely, when d = 0.145D2, it is suitable for the installation of blades 6, thereby securing blades 6 between the front disk 1 and the rear disk 3.

[0098] θ1=0.1°, so that the sizes of the large diameter end 102 and the small diameter end 101 of the front disc 1 are infinitely close, that is, the connecting section 103 is almost not tilted, so that the front disc 1 is constructed into a straight cylinder structure, so that the axial flow of the fluid is dominant and the centrifugal force is reduced.

[0099] Furthermore, h = 0.328D2 and ω = 46.5° create a shallower flow channel. This, combined with the blade twist angle, allows for a smaller twist angle suitable for flow conditions with low linear velocity differences. Simultaneously, the combination of β1A, β1B, and β2 results in a steeper inlet angle of attack for blade 6, bringing the outlet flow direction closer to the axial direction.

[0100] Therefore, by reducing the inlet diameter, increasing the number of blades 6, and lowering the installation angle and torsion angle, the axial flow is made more suitable for a low-resistance, high-flow environment; at the same time, constraining the various parameter values ​​of blades 6 can not only match the low linear velocity difference, but also utilize a uniform flow velocity distribution to reduce the noise caused by turbulent pulsation.

[0101] Example 3

[0102] In this embodiment, the diameter D0 of the impeller inlet 2, the inclination angle θ1 of the connecting section 103, the distance b between the rear disc 3 and the large diameter end 102 of the front disc 1, and the distance H between the small diameter end 101 thereof, the diameter D2 of the impeller outlet 4, the diameter d of the hub 5, the torsion angle ω of the blade 6, the installation angles β1A and β1B formed by the projection of the first profile 601 and the second profile 602 of the blade 6 on the reference plane, the installation angle β2 formed by the second profile 602, the diameter D1 of the blade inlet 104, the height h of the blade 6, and the number z of the blades 6 are shown in Table 3:

[0103]

[0104]

[0105] Table 3

[0106] Among them, D2=1000㎜.

[0107] The D0 value in this embodiment is between that of the first and second embodiments, that is, D0=0.689D2. On the one hand, it can avoid turbulent loss of high-speed flow, and on the other hand, it also reduces the risk of flow separation caused by low speed; it is suitable for medium flow application environment.

[0108] The diameter d of the hub 5 remains the same as that of the second embodiment. A larger hub 5 can enhance the centrifugal load capacity and is suitable for high-speed applications. Meanwhile, this value can also be 0 or 0.145D2. The purpose is the same as that of the second embodiment and will not be described in detail here.

[0109] At the same time, due to the limitation of D0 in this embodiment, the values ​​of b and H are also between implementations one and two, appropriately reducing the outlet flow velocity to balance the dynamic pressure and static pressure conversion efficiency; shortening the flow channel extension length, reducing flow friction loss, and forming a compact structure.

[0110] Furthermore, the coordination of ω and various mounting angles not only matches flow conditions with low linear velocity differentials, suitable for low to medium specific speeds, but also reduces secondary flow losses and localized turbulence. Thus, a balance between centrifugal and axial flows is achieved through the low front disc inclination and mounting angle. A large hub 5 diameter and a moderate number of blades 6 ensure reliability at high speeds, while the combined outlet mounting angle and width reduce kinetic energy dissipation and noise.

[0111] Example 4

[0112] In this embodiment, the diameter D0 of the impeller inlet 2, the inclination angle θ1 of the connecting section 103, the distance b between the rear disc 3 and the large diameter end 102 of the front disc 1, and the distance H between the small diameter end 101 thereof, the diameter D2 of the impeller outlet 4, the diameter d of the hub 5, the torsion angle ω of the blade 6, the installation angles β1A and β1B formed by the projection of the first profile 601 and the second profile 602 of the blade 6 on the reference plane, the installation angle β2 formed by the second profile 602, the diameter D1 of the blade inlet 104, the height h of the blade 6, and the number z of the blades 6 are shown in Table 4:

[0113]

[0114] Table 4

[0115] Among them, D2=1000㎜.

[0116] D0=D1=0.586D2, a smaller inlet diameter can increase the inlet flow velocity, enhance the guiding effect on the flow, and reduce the risk of flow separation. At the same time, the diameter of the impeller inlet 2 is consistent with the diameter of the blade inlet 104, ensuring a smooth transition of the fluid from the inlet to the blade 6, avoiding local flow velocity mutations, and reducing turbulent losses. The outlet width b can limit the outlet flow channel width, maintain a high outlet dynamic pressure, and is suitable for application scenarios that require high kinetic energy output. At the same time, the shortening of the axial spacing H can reduce flow friction losses, improve structural compactness, and form a high-speed impeller assembly. In addition, a moderate inclination angle avoids boundary layer separation caused by large angles, while guiding the fluid to accelerate and improve energy transfer efficiency.

[0117] In addition, a larger twist angle matches the hub 5 and the outer edge of the blade 6 to reduce secondary flow losses, adapting to high-speed impeller assemblies and improving power transfer efficiency. A larger mounting angle β1A is also adapted to the hub 5 in this embodiment, reducing inlet impact losses and improving efficiency. Mounting angle β1B is used to adapt to high-pressure scenarios; and β2 can reduce outlet vortex losses while maintaining high static pressure recovery. The blade 6 height h is adjusted to be between shallow flow channels and high flow rates, balancing flow velocity uniformity and flow requirements to reduce the risk of flow separation while adapting to high-speed operations.

[0118] Therefore, the impeller assembly in this embodiment is suitable for application environments with high static pressure, and the lightweight hub 5 and the high torsion angle can match high-speed power transmission and improve efficiency.

[0119] Example 5

[0120] In this embodiment, the diameter D0 of the impeller inlet 2, the inclination angle θ1 of the connecting section 103, the distance b between the rear disc 3 and the large diameter end 102 of the front disc 1, and the distance H between the small diameter end 101 thereof, the diameter D2 of the impeller outlet 4, the diameter d of the hub 5, the torsion angle ω of the blade 6, the installation angles β1A and β1B formed by the projection of the first profile 601 and the second profile 602 of the blade 6 on the reference plane, the installation angle β2 formed by the second profile 602, the diameter D1 of the blade inlet 104, the height h of the blade 6, and the number z of the blades 6 are shown in Table 5:

[0121]

[0122]

[0123] Table 5

[0124] Among them, D2=1000㎜.

[0125] The diameter of the blade inlet 104 is smaller than the diameter of the impeller outlet 4, i.e., D0 = 0.596D2. This increases the inlet flow velocity to enhance flow guidance while avoiding turbulent losses caused by excessive flow velocity. Furthermore, D0 = D1, ensuring a continuous flow path from the inlet to the blade 6, reduces flow separation and local vortices, and improves efficiency.

[0126] Constraining the b and H values ​​adjusts the outlet kinetic energy and static pressure recovery capabilities, maintaining high outlet dynamic pressure, balancing the static pressure recovery effect of flow channel expansion with friction losses, and improving energy conversion efficiency. Combined with the hub diameter d, the flow channel cross-sectional area can be optimized, increasing flow capacity and being suitable for medium to high flow rates.

[0127] For the blade ω, β1A, β1B and β2 values, they are not only used to adapt the above parameter values ​​to adapt to the flow conditions of medium and high linear velocity differences, but also to grade the flow attack angle to match the linear velocity of different areas. Specifically, β1A = 26.8° at the hub inlet, which reduces the inlet impact of the low linear velocity area at the hub 5 through a lower installation angle, suppresses turbulence generation, and improves efficiency. β1B = 65.7° at the outer edge of the blade, which strengthens the centrifugal effect and increases static pressure through a high installation angle, and is suitable for high-pressure scenarios. β2 = 39.6° at the outlet, which balances the conversion between dynamic pressure and static pressure through a medium tangential angle, reduces outlet vortex losses, and maintains a high static pressure recovery efficiency. Based on the above, using a blade 6 height of h = 0.303D2 can improve the uniformity of the flow velocity distribution, reduce the risk of flow separation, and improve the control ability of high-viscosity fluids.

[0128] Example 6

[0129] In this embodiment, the diameter D0 of the impeller inlet 2, the inclination angle θ1 of the connecting section 103, the distance b between the rear disc 3 and the large diameter end 102 of the front disc 1, and the distance H between the small diameter end 101 thereof, the diameter D2 of the impeller outlet 4, the diameter d of the hub 5, the torsion angle ω of the blade 6, the installation angles β1A and β1B formed by the projection of the first profile 601 and the second profile 602 of the blade 6 on the reference plane, the installation angle β2 formed by the second profile 602, the diameter D1 of the blade inlet 104, the height h of the blade 6, and the number z of the blades 6 are shown in Table 6:

[0130]

[0131]

[0132] Table 6

[0133] Among them, D2=1000㎜.

[0134] A larger inlet diameter can reduce inlet flow velocity and turbulent losses, making it suitable for low-viscosity fluids. At the same time, D0 = D1, ensuring that the fluid enters the flow passage of blade 6 without sudden changes, suppressing flow separation and improving efficiency. The outlet width b balances the conversion between dynamic and static pressures, reducing outlet kinetic energy dissipation and adapting to high-pressure systems. The axial spacing H promotes the conversion of kinetic energy to static pressure and improves static pressure recovery. Combined with the larger hub 5 diameter d, it enhances resistance to centrifugal loads and adapts to high speeds. Combined with the coordination of blades ω, β1A, β1B, and β2, a balance between high pressure head and reasonable flow rate is achieved, making it suitable for high-speed applications.

[0135] Example 7

[0136] In this embodiment, the diameter D0 of the impeller inlet 2, the inclination angle θ1 of the connecting section 103, the distance b between the rear disc 3 and the large diameter end 102 of the front disc 1, and the distance H between the small diameter end 101 thereof, the diameter D2 of the impeller outlet 4, the diameter d of the hub 5, the torsion angle ω of the blade 6, the installation angles β1A and β1B formed by the projection of the first profile 601 and the second profile 602 of the blade 6 on the reference plane, the installation angle β2 formed by the second profile 602, the diameter D1 of the blade inlet 104, the height h of the blade 6, and the number z of the blades 6 are shown in Table 7:

[0137]

[0138]

[0139] Table 7

[0140] Among them, D2=1000㎜.

[0141] Since D0 = D1 = 0.642D2, on the one hand, it can ensure a smooth transition of the inlet flow channel and reduce the inlet impact loss. On the other hand, it can increase the inlet flow velocity by reducing the inlet cross-sectional area, enhance the fluid acceleration ability, and suppress cavitation. In order to match the flow demand, the b value is constrained to suppress the proportion of outlet kinetic energy and improve the static pressure conversion efficiency. At the same time, the H value is reasonably allocated to balance the centrifugal effect and friction loss, enhance the flow field stability, and reduce turbulent pulsation. In addition, the matching of the hub 5 and the blade 6 can optimize the stress distribution at the root of the blade, improve structural reliability, reduce the interference of the hub 5 on the blade 6, improve efficiency, and reduce noise.

[0142] Example 8

[0143] In this embodiment, the diameter D0 of the impeller inlet 2, the inclination angle θ1 of the connecting section 103, the distance b between the rear disc 3 and the large diameter end 102 of the front disc 1, and the distance H between the small diameter end 101 thereof, the diameter D2 of the impeller outlet 4, the diameter d of the hub 5, the torsion angle ω of the blade 6, the installation angles β1A and β1B formed by the projection of the first profile 601 and the second profile 602 of the blade 6 on the reference plane, the installation angle β2 formed by the second profile 602, the diameter D1 of the blade inlet 104, the height h of the blade 6, and the number z of the blades 6 are shown in Table 8:

[0144]

[0145]

[0146] Table 8

[0147] Among them, D2=1000㎜.

[0148] Compared with the seventh embodiment, the inlet diameter in this embodiment is smaller, which can increase the initial flow velocity of the fluid and maintain D0=D1, ensuring seamless connection between the blade inlet and the flow channel, and reducing turbulence caused by the fluid impacting the blade 6.

[0149] The increased outlet width allows for a higher volume flow rate and reduces the circumferential component of the outlet velocity, promoting efficient conversion of kinetic energy to static pressure. Furthermore, the expanded outlet width disperses wake energy, reducing turbulence intensity at the outlet and minimizing vibration and noise.

[0150] Longer flow channels provide ample space for the fluid to achieve gradient evolution of velocity and pressure, reducing flow distortion. By optimizing the flow channel value, overall efficiency is improved.

[0151] The smaller hub 5 further reduces flow blockage, increases effective flow area, and is suitable for high specific speeds. Combined with the shaping of blade parameters, the more strongly twisted blades 6 adapt to radial-axial velocity gradients, eliminating secondary flow and reducing flow losses. Furthermore, the consistent installation angle reduces inlet shock asymmetry, improves flow consistency, and balances angle of attack and diffusion requirements.

[0152] Embodiment 9

[0153] In this embodiment, the diameter D0 of the impeller inlet 2, the inclination angle θ1 of the connecting section 103, the distance b between the rear disc 3 and the large diameter end 102 of the front disc 1, and the distance H between the small diameter end 101 thereof, the diameter D2 of the impeller outlet 4, the diameter d of the hub 5, the torsion angle ω of the blade 6, the installation angles β1A and β1B formed by the projection of the first profile 601 and the second profile 602 of the blade 6 on the reference plane, the installation angle β2 formed by the second profile 602, the diameter D1 of the blade inlet 104, the height h of the blade 6, and the number z of the blades 6 are shown in Table 9:

[0154]

[0155]

[0156] Table 9

[0157] Among them, D2=1000㎜.

[0158] The extremely small inlet cross-sectional area can increase the inlet flow rate and reduce the duration of local low-pressure areas through high-speed flow. The compact H spacing can reduce the fluid residence time by utilizing a short flow channel, avoiding flow instability at high speeds, while also reducing the flow channel length to reduce wall friction losses. In addition, the coordination of the hub 5 and the blades 6 can reduce the interference of the hub 5 on the blades 6, improve efficiency, and reduce noise. This improves the efficiency of the impeller and reduces noise by controlling the flow velocity and pressure distribution within the impeller assembly, reducing fluid flow separation losses and impact losses, and controlling secondary flow losses and wake losses.

[0159] Example 10

[0160] In this embodiment, the diameter D0 of the impeller inlet 2, the inclination angle θ1 of the connecting section 103, the distance b between the rear disc 3 and the large diameter end 102 of the front disc 1, and the distance H between the small diameter end 101 thereof, the diameter D2 of the impeller outlet 4, the diameter d of the hub 5, the torsion angle ω of the blade 6, the installation angles β1A and β1B formed by the projection of the first profile 601 and the second profile 602 of the blade 6 on the reference plane, the installation angle β2 formed by the second profile 602, the diameter D1 of the blade inlet 104, the height h of the blade 6, and the number z of the blades 6 are shown in Table 10:

[0161]

[0162]

[0163] Table 10

[0164] Among them, D2=1000㎜.

[0165] The extremely small inlet cross-sectional area is used to increase the inlet flow velocity, and the flow channel with a compact structure is used to cooperate with the micro hub 5 and the blades 6 to reduce noise and improve efficiency.

[0166] In this embodiment of the present invention, the first profile 601 and the second profile 602 of the blade 6 are smoothly transitioned via a bridge section 603. The formation of the bridge section 603 not only enhances the overall structural strength and stability of the blade 6, but also reduces noise generated by the blade 6, thereby improving efficiency. Preferably, the bridge section 603 of one of two adjacent blades 6 is twisted toward the other blade 6, for placement toward the impeller inlet 2. This not only allows precise alignment with various installation angles but also reduces impact losses.

[0167] This embodiment further provides a fan including the impeller assembly described above. The specific structure of the impeller assembly is similar to that of the above embodiments. Since this fan utilizes all of the technical solutions of the above embodiments, it at least has all of the beneficial effects brought about by the technical solutions of the above embodiments, and therefore will not be described in detail here. The fan includes: the impeller assembly described above.

[0168] like Figure 7 、 Figure 8 As shown, the fan further includes a volute 7, which wraps the impeller assembly and forms a fan inlet and a fan outlet, which are used to be connected to the impeller inlet and the impeller outlet respectively.

[0169] In the above embodiment 1, in order to adapt to the impeller assembly, the fan outlet B of this fan is 0.584D2, the volute lines R1 = 0.668D2, R2 = 0.786D2, R3 = 0.936D2, R4 = 1.066D2 and the volute tongue angle θ2 = 35.7°.

[0170] In the above-mentioned second embodiment, in order to adapt to the impeller assembly, the fan outlet B of the fan is 0.871D2, the volute lines R1 = 0.669D2, R2 = 0.850D2, R3 = 1.049D2, R4 = 1.227D2 and the volute tongue angle θ2 = 35.4°.

[0171] In the above-mentioned third embodiment, in order to adapt to the impeller assembly, the fan outlet B of the fan is 0.866D2, the volute lines R1 are 0.674D2, R2 are 0.832D2, R3 are 0.984D2, R4 are 1.158D2 and the volute tongue angle θ2 is 37.4°.

[0172] In the fourth embodiment, in order to adapt to the impeller assembly, the fan outlet B of the fan is 0.667D2, the volute lines R1 = 0.637D2, R2 = 0.745D2, R3 = 0.869D2, R4 = 0.995D2 and the volute tongue angle θ2 = 32.1°.

[0173] In the fifth embodiment, in order to adapt to the impeller assembly, the fan outlet B of the fan is 0.518D2, the volute lines R1 = 0.659D2, R2 = 0.758D2, R3 = 0.854D2, R4 = 0.947D2 and the volute tongue angle θ2 = 33.2°.

[0174] In the sixth embodiment, in order to adapt to the impeller assembly, the fan outlet B of the fan is 0.672D2, the volute lines R1 = 0.627D2, R2 = 0.802D2, R3 = 0.942D2, R4 = 1.075D2 and the volute tongue angle θ2 = 19.1°.

[0175] In the above-mentioned embodiment seven, in order to adapt to the impeller assembly, the fan outlet B of this fan is 0.52D2, the volute lines R1 = 0.607D2, R2 = 0.73D2, R3 = 0.835D2, R4 = 0.941D2 and the volute tongue angle θ2 = 29.4°.

[0176] In the eighth embodiment, in order to adapt to the impeller assembly, the fan outlet B of the fan is 0.676D2, the volute lines R1 = 0.647D2, R2 = 0.777D2, R3 = 0.891D2, R4 = 1.015D2 and the volute tongue angle θ2 = 31.8°.

[0177] In the above-mentioned ninth embodiment, in order to adapt to the impeller assembly, the fan outlet B of the fan is 0.25D2, the volute lines R1 = 0.581D2, R2 = 0.649D2, R3 = 0.709D2, R4 = 0.792D2 and the volute tongue angle θ2 = 23°.

[0178] In the above-mentioned embodiment 10, in order to adapt to the impeller assembly, the fan outlet B of the fan is 0.232D2, the volute lines R1 are 0.565D2, R2 are 0.664D2, R3 are 0.771D2, R4 are 0.880D2 and the volute tongue angle θ2 is 12.1°.

[0179] Specifically, according to the size of the outlet width B, it can be divided into a narrow outlet group (B < 0.55D2), a medium-width outlet group (B between 0.58-0.68D2), and a wide outlet group (B > 0.86D2). The narrow outlet group can improve the outlet flow rate and static pressure recovery efficiency, and suppress outlet backflow. The medium-width outlet group can achieve the best balance between kinetic energy and static pressure conversion and reduce noise. The wide outlet group can reduce friction loss and make the outlet flow field uniform, suitable for high-flow application environments.

[0180] A four-stage gradual curvature design (i.e., R1, R2, R3, and R4) is adopted to keep the static pressure gradient in the volute 7 constant within the rated range, thus avoiding the sudden loss of the traditional single arc volute. In addition, according to the size of the spiral line R4, it can be divided into a compact type (R4 / R1=1.36), a standard type (R4 / R1 is between 1.45-1.56), and an extended type (R4 / R1>1.7). For the compact type, it can accelerate the circumferential flow in the volute 7, shorten the airflow path, and improve its transient response. The standard type can reduce pressure pulsation and improve its efficiency. The extended type can reduce the diffusion loss, reduce the separation zone area to the flow channel, and improve the anti-clogging ability.

[0181] Based on the nonlinear setting of the θ2 angle, the optimal volute tongue gap is automatically maintained when the speed changes to avoid gap whistling. In addition, according to the size of the volute tongue angle θ2, it can be divided into a small angle group (θ2 = 12.1 / 19.1° / 23°), a medium angle group (θ2 = 29.4° / 31.8° / 32.1° / 33.2°) and a large angle group (θ2 = 35.7° / 35.4° / 37.4°). For the small angle group, the flow velocity in the volute tongue gap can be reduced, reducing its noise. The medium angle group can attenuate the dynamic and static interference noise and redistribute the broadband noise energy. The large angle group can reduce the wake turbulence and reduce noise.

[0182] For example: the impeller assembly in the above-mentioned embodiment nine is matched with the corresponding parameters of the fan in Table 19, so that the fan pressure resistance reaches 2.5MPa and the micro-flow control accuracy is ±0.5%, thereby forming a fan with lower noise, higher efficiency and lower energy consumption.

[0183] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not limiting. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solutions of the present invention may be modified or replaced by equivalents without departing from the purpose and scope of the technical solutions of the present invention, which should all be included in the scope of the claims of the present invention.

Claims

1. Impeller assembly, characterized in that, include: a front disc comprising a small diameter end and a large diameter end oppositely disposed, wherein the small diameter end of the front disc is provided with an impeller inlet having a diameter of D0, and the small diameter end of the front disc is connected to the large diameter end by an inclined connecting section having an inclination angle of θ1; a rear disc spaced apart from the front disc and arranged close to the large diameter end thereof, wherein the distances between the rear disc and the large diameter end and the small diameter end of the front disc are b and H respectively, and an impeller outlet is formed between the rear disc and the large diameter end of the front disc, and the diameter of the impeller outlet is D2; a hub, provided on the rear disc and extending toward the impeller inlet, with a diameter of d; A plurality of blades are spaced apart around the outer surface of the hub, the blades have a torsion angle of ω and are formed with a first profile and a second profile, the first profile of the blade being fixed to the hub and the second profile extending toward the impeller outlet, a plane parallel to the hub axis being defined as a reference plane, the first profile and the second profile of the blade being projected onto the reference plane and forming installation angles β1A and β1B, and the angle between the extension line of the second profile of the blade and the tangent line at the intersection of the rear disc is defined as the installation angle β2; Wherein, the impeller assembly satisfies one of the following relationships: (1) D0=0.772D2, θ1=7.4°, b=0.212D2, H=0.370D2, d=0.120D2, ω=73.1°, β1A=29.6°, β1B=59.8°, β2=73.9°; (2) D0=0.614D2, θ1=0.1°, b=0.297D2, H=0.373D2, d=0 or d=0.145D2, ω=46.5°, β1A=35.1°, β1B=24.3°, β2=26.1°; (3) D0=0.689D2, θ1=1.3°, b=0.277D2, H=0.358D2, d=0 or d=0.145D2, ω=48.4°, β1A=20.4°, β1B=21.5°, β2=25.9°; (4) D0=0.586D2, θ1=5.1°, b=0.127D2, H=0.323D2, d=0.131D2, ω=66.1°, β1A=42°, β1B=83.5°, β2=55.1°; (5) D0=0.596D2, θ1=6.4°, b=0.127D2, H=0.368D2, d=0.131D2, ω=52.9°, β1A=26.8°, β1B=65.7°, β2=39.6°; (6) D0=0.758D2, θ1=9.2°, b=0.175D2, H=0.384D2, d=0.147D2, ω=54.3°, β1A=34.9°, β1B=80.2°, β2=34.9°; (7) D0=0.642D2, θ1=4.3°, b=0.17D2, H=0.312D2, d=0.149D2, ω=45.9°, β1A=35.9°, β1B=81.2°, β2=49.8°; (8) D0=0.606D2, θ1=5.1°, b=0.197D2, H=0.386D2, d=0.137D2, ω=47.7°, β1A=β1B=39.3°, β2=44.8°; (9) D0=0.457D2, θ1=1.2°, b=0.099D2, H=0.234D2, d=0.122D2, ω=13.6°, β1A=19.8°, β1B=64.7°, β2=151.4°; (10) D0=0.493D2, θ1=9.2°, b=0.062D2, H=0.188D2, d=0.116D2, ω=71.8°, β1A=66.6°, β1B=28.9°, β2=42.4°.

2. The impeller assembly according to claim 1, wherein: The plurality of blades form a blade inlet, the diameter of the blade inlet is D1, and satisfies: D0=D1; or The diameter of the blade inlet is D1', which satisfies the following: D0<D1'.

3. The impeller assembly according to claim 1, wherein: The height of the blade is h, which satisfies one of the following relationships: (1')h=0.357D2; (2')h=0.328D2; (3')h=0.306D2; (4')h=0.303D2; (5')h=0.347D2; (6')h=0.368D2; (7')h=0.297D2; (8')h=0.367D2; (9')h=0.205D2; (10')h=0.168D2.

4. The impeller assembly according to any one of claims 1 to 3, characterized in that: The number of the plurality of blades is defined as z, satisfying: z=8-21.

5. The impeller assembly according to claim 1, wherein: The first contour and the second contour of the blade are smoothly transitioned through the bridge section.

6. The impeller assembly according to claim 5, wherein: The bridge section of one of the two adjacent blades is twisted toward the other blade so as to be arranged toward the impeller inlet.

7. A fan, characterized in that include: The impeller assembly according to any one of claims 1 to 6.

8. The fan according to claim 7, characterized in that The fan further includes a volute, which wraps the impeller assembly and forms a fan inlet and a fan outlet, which are used to be connected to the impeller inlet and the impeller outlet respectively.

9. The fan according to claim 8, characterized in that The width of the fan outlet is B, and B satisfies one of the following relationships: (1")B=0.584D2; (2")B=0.871D2; (3")B=0.866D2; (4")B=0.667D2; (5")B=0.518D2; (6')B=0.672D2; (7")B=0.52D2; (8")B=0.676D2; (9")B=0.25D2; (10”)B=0.232D2.

10. The fan according to any one of claims 7 to 9, characterized in that: The volute lines of the volute are R1, R2, R3 and R4, and the volute tongue angle is θ2. The volute satisfies one of the following relationships: (1”')R1=0.668D2,R2=0.786D2,R3=0.936D2,R4=1.066D2,θ2=35.7°; (2”')R1=0.669D2,R2=0.850D2,R3=1.049D2,R4=1.227D2,θ2=35.4°; (3”')R1=0.674D2,R2=0.832D2,R3=0.984D2,R4=1.158D2,θ2=37.4°; (4”')R1=0.637D2,R2=0.745D2,R3=0.869D2,R4=0.995D2,θ2=32.1°; (5”')R1=0.659D2,R2=0.758D2,R3=0.854D2,R4=0.947D2,θ2=33.2°; (6”')R1=0.627D2, R2=0.802D2, R3=0.942D2, R4=1.075D2, θ2=19.1°;(7”')R1=0.607D2, R2=0.73D2, R3=0.835D2, R4=0.941D2, θ2=29.4°;(8”')R1=0.647D2, R2=0.777D2, R3 =0.891D2, R4=1.015D2, θ2=31.8°;(9”')R1=0.581D2, R2=0.649D2, R3=0.709D2, R4=0.792D2, θ2=23°;(10”')R1=0.565D2, R2=0.664D2, R3=0.771D2, R4=0.880D2, θ2=12.1°.

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