Blower unit, supercharging blower, air conditioning system, thermal management system, and vehicle

Abstract

The application relates to the technical field of fans, and discloses a fan unit, a supercharging fan, an air conditioning system, a thermal management system and a vehicle, wherein the fan unit is provided with a first phase angle alpha between the blade root and the blade top of the trailing edge y1 of the first blade in the first impeller rotating direction and taking the rotating direction of the first impeller as a positive value, so that the first blade adopts a curved angle design; the fan unit is provided with a second phase angle beta between the blade root and the blade top of the leading edge x2 of the second blade in the second impeller rotating direction and taking the rotating direction of the second impeller as a positive value, so that the second blade adopts a curved angle design; and by limiting the value range of alpha+beta, the phenomenon that the pressure fluctuation caused by the wake of the first blade at different radial heights impacts the leading edge x2 of the second blade in time can be dispersed, and then the pressure fluctuation is eliminated, so that the order noise and the total noise of the supercharging fan are reduced, and the difficulty of the first blade and the second blade in the die is reduced.

Description

Technical Field

[0001] This invention relates to the field of technology, and more particularly to a fan unit, a booster fan, an air conditioning system, a thermal management system, and a vehicle. Background Technology

[0002] Conventional automotive booster fans typically employ a centrifugal structure, resulting in a large size that significantly encroaches on interior space and lacks flexible placement, impacting both automakers' choices and consumer usage. In terms of boosting capacity, centrifugal booster fans offer a simpler structure and stronger boosting capability, making them the preferred choice for duct boosting if space constraints are not a primary concern.

[0003] Considering the current crowded component layout inside vehicles, miniaturized booster fans have a broader market demand. Axial flow fan blades, due to their axial airflow characteristics, can be directly matched with air ducts, avoiding significant airflow deflection, making them the best choice for miniaturized booster fans. Axial flow impellers are characterized by large air volume and low air pressure, but due to their fewer blades and relatively high rotational speed, they often generate noticeable first-order noise and poor sound quality, severely limiting their application scenarios. Summary of the Invention

[0004] The purpose of this invention is to provide a fan unit, a booster fan, an air conditioning system, a thermal management system, and a vehicle that can reduce the total noise and order noise of the booster fan.

[0005] To achieve this objective, the present invention adopts the following technical solution:

[0006] The fan unit includes:

[0007] The first impeller includes a first hub and a plurality of first blades, the plurality of first blades being spaced apart on the first hub along the circumferential direction of the first hub; along the rotation direction of the first impeller and with the rotation direction of the first impeller as positive, a first phase angle α is provided between the blade root and the blade tip of the trailing edge y1 of the first blade.

[0008] The second impeller has its air inlet side facing the air outlet side of the first impeller. The second impeller includes a second hub and a plurality of second blades, which are spaced apart circumferentially on the second hub. Along the rotation direction of the second impeller, with the rotation direction of the second impeller as the positive value, a second phase angle β is provided between the blade root and the blade tip of the leading edge x2 of the second blade.

[0009] The value of α+β ranges from 50%*360° / N1 to 150%*360° / N1; N1 is the number of the first leaf.

[0010] As a preferred technical solution for the wind turbine unit, the first impeller and the second impeller rotate in opposite directions.

[0011] As a preferred technical solution for the wind turbine unit, α≥20°; and / or, β≥20°.

[0012] As a preferred technical solution for the wind turbine unit, the first impeller includes nine first blades, α = 20°, β = 21°.

[0013] As a preferred technical solution for the wind turbine unit, multiple first blades are unevenly distributed along the circumference of the first hub; and / or,

[0014] Multiple second blades are unevenly distributed along the circumference of the second hub.

[0015] As a preferred technical solution for the wind turbine unit, the plurality of first blades include first preset blades and a plurality of second preset blades, wherein the second preset blades located on both sides of the first preset blades are symmetrically arranged with respect to the first preset blades; and / or,

[0016] The plurality of second blades include a third preset blade and a plurality of fourth preset blades, wherein the fourth preset blades located on both sides of the third preset blade are symmetrically arranged with respect to the third preset blade.

[0017] As a preferred technical solution for the fan unit, the fan unit further includes an impeller housing, wherein the first impeller and the second impeller are rotatably disposed within the mounting cavity of the impeller housing; the impeller housing includes a first opening and a second opening, both of which communicate with the mounting cavity, and the first opening and the second opening are arranged sequentially along the axial direction of the first hub; the air inlet side of the first impeller faces the first opening, and the air outlet side of the second impeller faces the second opening.

[0018] As a preferred technical solution for the wind turbine unit, the first impeller further includes a first blade crown, which is annular and sleeved on the outside of a plurality of first blades. The ends of the plurality of first blades radially away from the first hub are all connected to the first blade crown; and / or,

[0019] The first impeller also includes a second blade crown, which is annular and is sleeved on the outside of a plurality of second blades. The ends of the plurality of second blades that are radially away from the second hub are all connected to the second blade crown.

[0020] As a preferred technical solution for the fan unit, the fan unit further includes a first air guide component corresponding to the first impeller. The first air guide component includes a third hub and a plurality of first guide vanes. The third hub is fixed to the air outlet side of the first impeller, and the plurality of first guide vanes are spaced apart on the third hub circumferentially; and / or,

[0021] The fan unit further includes a second air guide component corresponding to the second impeller. The second air guide component includes a fourth hub and a plurality of second guide vanes. The fourth hub is fixed to the air outlet side of the second impeller, and the plurality of second guide vanes are arranged at intervals along the circumference of the fourth hub.

[0022] As a preferred technical solution for the wind turbine unit, a plurality of first guide vanes are unevenly distributed along the circumference of the third hub; and / or,

[0023] Multiple second guide vanes are unevenly distributed along the circumference of the fourth hub.

[0024] To achieve the above objectives, the present invention also provides a booster fan, including the fan unit as described in any of the preceding claims.

[0025] As a preferred technical solution for the aforementioned booster fan, the fan unit, or multiple fan units, is arranged in a direction perpendicular to the first hub.

[0026] To achieve the above objectives, the present invention also provides an air conditioning system, characterized in that it includes a booster fan as described in any of the preceding claims.

[0027] To achieve the above objectives, the present invention also provides a thermal management system, characterized in that it includes a booster fan as described in any of the preceding claims or an air conditioning system as described above.

[0028] To achieve the above objectives, the present invention also provides a vehicle, characterized in that it includes an air conditioning system as described above or a thermal management system as described above.

[0029] The present invention has at least the following beneficial effects:

[0030] The fan unit provided by this invention has a first phase angle α between the root and tip of the trailing edge y1 of the first blade, with the rotation direction of the first impeller as the positive value, so that the first blade adopts a curved design; and a second phase angle β between the root and tip of the leading edge x2 of the second blade, with the rotation direction of the second impeller as the positive value, so that the second blade adopts a curved design; and by limiting the range of values ​​of α+β, the phenomenon of pressure fluctuations generated by the trailing edge of the first blade at different radial heights impacting the leading edge x2 of the second blade can be discretized in time, thereby eliminating the pressure fluctuations, reducing the order noise and total noise of the booster fan, and reducing the demolding difficulty of the first and second blades.

[0031] The booster fan, air conditioning system, thermal management system, and vehicle provided by the present invention all include the aforementioned fan unit, which can reduce the total noise and order noise of the booster fan. Attached Figure Description

[0032] To more clearly illustrate the technical solutions in the embodiments of the present invention, the accompanying drawings used in the description of the embodiments of the present invention will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the content of the embodiments of the present invention and these drawings without creative effort.

[0033] Figure 1a This is a schematic diagram of the first structure of the impeller provided in an embodiment of the present invention;

[0034] Figure 1b This is a schematic diagram of the second structure of the impeller provided in an embodiment of the present invention;

[0035] Figure 1c A schematic diagram of the third structure of the impeller provided in an embodiment of the present invention;

[0036] Figure 1d A schematic diagram of the fourth structure of the impeller provided in an embodiment of the present invention;

[0037] Figure 2 This is a schematic diagram of the structure of the blade crown and impeller housing provided in an embodiment of the present invention;

[0038] Figure 3 This is a first structural schematic diagram of the booster fan provided in an embodiment of the present invention;

[0039] Figure 4a This is a first structural schematic diagram of the air guide provided in an embodiment of the present invention;

[0040] Figure 4b This is a schematic diagram of the second structure of the air guide provided in an embodiment of the present invention;

[0041] Figure 5a This is a schematic diagram of the second structure of the booster fan provided in an embodiment of the present invention;

[0042] Figure 5b This is a schematic diagram of the second structure of the booster fan provided in an embodiment of the present invention;

[0043] Figure 5c This is a schematic diagram of the third structure of the booster fan provided in an embodiment of the present invention;

[0044] Figure 6 This is a schematic diagram of the structure of the first impeller provided in an embodiment of the present invention;

[0045] Figure 7 This is a schematic diagram of the structure of the second impeller provided in an embodiment of the present invention;

[0046] Figure 8 This is a schematic diagram of the structure of the first blade and the second blade provided in an embodiment of the present invention;

[0047] Figure 9 A cross-sectional view of an axial flow booster fan provided in an embodiment of the present invention;

[0048] Figure 10 This is a first partial sectional view of an axial flow booster fan provided in an embodiment of the present invention;

[0049] Figure 11 This is a schematic diagram of the first structure of the first impeller of the axial flow booster fan provided in an embodiment of the present invention;

[0050] Figure 12 This is a schematic diagram of the first structure of the second impeller of the axial flow booster fan provided in an embodiment of the present invention;

[0051] Figure 13 This is a schematic diagram of the fan unit of the axial flow booster fan provided in an embodiment of the present invention;

[0052] Figure 14 This is a schematic diagram of the second structure of the first impeller of the axial flow booster fan provided in an embodiment of the present invention;

[0053] Figure 15 This is a schematic diagram of the second structure of the second impeller of the axial flow booster fan provided in an embodiment of the present invention;

[0054] Figure 16 This is a schematic diagram of the structure of the first and second blades of an axial flow booster fan provided in an embodiment of the present invention;

[0055] Figure 17 This is a second partial sectional view of an axial flow booster fan provided in an embodiment of the present invention;

[0056] Figure 18 This is a third partial sectional view of an axial flow booster fan provided in an embodiment of the present invention;

[0057] Figure 19 A schematic diagram of the third structure of the first impeller of the axial flow booster fan provided in an embodiment of the present invention;

[0058] Figure 20 This is a schematic diagram of the structure of an axial flow booster fan (excluding the fan housing) provided in an embodiment of the present invention;

[0059] Figure 21 A schematic diagram of the structure of an axial flow booster fan (including the fan housing) provided in an embodiment of the present invention;

[0060] Figure 22 This is a schematic diagram of the structure of an axial flow booster fan provided in an embodiment of the present invention;

[0061] Figure 23 A schematic diagram of the fourth structure of the first impeller of the axial flow booster fan provided in an embodiment of the present invention;

[0062] Figure 24 A schematic diagram of the fifth structure of the first impeller of the axial flow booster fan provided in an embodiment of the present invention;

[0063] Figure 25 A schematic diagram of the third structure of the second impeller of the axial flow booster fan provided in an embodiment of the present invention;

[0064] Figure 26 A schematic diagram of the fourth structure of the second impeller of the axial flow booster fan provided in an embodiment of the present invention;

[0065] Figure 27 A schematic diagram of the first structure of the first air guide component of the axial flow booster fan provided in an embodiment of the present invention;

[0066] Figure 28 A schematic diagram of the second structure of the first air guide component of the axial flow booster fan provided in an embodiment of the present invention;

[0067] Figure 29 A schematic diagram of the first structure of the second air guide of the axial flow booster fan provided in an embodiment of the present invention;

[0068] Figure 30 This is a schematic diagram of the second structure of the second air guide of the axial flow booster fan provided in an embodiment of the present invention;

[0069] Figure 31 This is a schematic diagram of the structure of a first thermal management system provided in an embodiment of the present invention;

[0070] Figure 32This is a schematic diagram of the structure of a second thermal management system provided in an embodiment of the present invention;

[0071] Figure 33 A cross-sectional view of a thermal management system provided in an embodiment of the present invention.

[0072] Figures 1a to 8 middle:

[0073] 10. Booster fan; 101. Fan unit;

[0074] 1′, Impeller; 1a′, First impeller; 1b′, Second impeller; 11′, Impeller hub; 12′, Blade; 13′, Blade crown;

[0075] 3a. Impeller housing; 31. Mounting cavity; 311. Reinforcing structure; 32. First opening; 33. Second opening;

[0076] 5′, air guide component; 5a′, first air guide component; 5b′, second air guide component; 51′, air guide hub; 52′, guide vane.

[0077] Figures 9 to 33 middle:

[0078] 10. Booster fan; 101. Fan unit;

[0079] 1. First impeller; 11. First hub; 12. First blade; 13. First blade crown;

[0080] 2. Second impeller; 21. Second hub; 22. Second blade; 23. Second blade crown;

[0081] 3a. Impeller housing; 31. Mounting cavity; 311. Reinforcing structure; 312. Support structure; 32. First opening; 33. Second opening; 3a1. First housing; 3a2. Second housing; 3b1. First locking element; 3b2. Second locking element; 3c. Fan housing; 3c1. First shell section; 3c2. Second shell section; 3d. Vibration damping structure;

[0082] 41. First driving component; 42. Second driving component;

[0083] 5. First air guide component; 51. Third hub; 52. First guide vane;

[0084] 6. Second air guide component; 61. Fourth hub; 62. Second guide vane;

[0085] 71. Hat cover; 72. Coccyx;

[0086] 20. Air conditioning unit; 201. Air conditioning outlet; 301. Connecting pipe; 302. Transition pipe. Detailed Implementation

[0087] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, and not all of the structures.

[0088] In the description of this invention, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "fixed" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0089] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0090] In the description of this embodiment, the terms "upper," "lower," "right," etc., refer to the orientation or positional relationship shown in the accompanying drawings. They are used only for ease of description and simplification of operation, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the present invention. In addition, the terms "first" and "second" are used only for distinction in description and have no special meaning.

[0091] In this embodiment, the phase angle between two adjacent blades is the circumferential angle difference between the leading edges of the two adjacent blades. The phase angle between two adjacent guide vanes is the circumferential angle difference between the leading edges of the two adjacent guide vanes.

[0092] Example 1

[0093] like Figures 1a to 8As shown, an embodiment of the present invention provides a blade crown, a guide vane, an impeller, a fan unit, and a booster fan. The booster fan 10 includes a fan unit 101, which includes an impeller 1' and an impeller housing 3a. The impeller housing 3a includes a mounting cavity 31 and a first opening 32 and a second opening 33, both of which are connected to the mounting cavity 31. The impeller 1' is rotatably disposed in the mounting cavity 31, with the air inlet side of the impeller 1' facing the first opening 32 and the air outlet side of the impeller 1' facing the second opening 33.

[0094] like Figure 1a and Figure 1b As shown, the impeller 1′ includes an impeller hub 11′ and multiple blades 12′. The multiple blades 12′ are arranged at intervals along the circumference of the impeller hub 11′, and the multiple blades 12′ are unevenly distributed along the circumference of the impeller hub 11′. The phase angle between two adjacent blades 12′ ranges from 288° / N to 432° / N, where N is the number of blades 12′.

[0095] The blade 12′ adopts the above configuration, which can effectively reduce the total noise generated by the rotation of the impeller 1′ while ensuring the dynamic and static balance of the booster fan 10. At the same time, it solves the problems of high first-order noise, poor sound quality and low NVH level of the booster fan 10, so that the booster fan 10 can provide the required air volume and air pressure while meeting the requirements of low noise and good sound quality.

[0096] Specifically, the first opening 32 and the second opening 33 are arranged sequentially along the axial direction of the impeller hub 11′.

[0097] In some embodiments, such as Figure 1c As shown, in two adjacent blades 12', the projection of the leading edge x1 of one blade 12' onto a preset plane does not intersect with the trailing edge y1 of the other blade 12'. The preset plane is perpendicular to the axial direction of the impeller hub 11'. This configuration further improves the convenience of industrial mold making and the airflow and pressure performance of the booster fan.

[0098] In some embodiments, the plurality of blades 12′ include a first preset blade and a plurality of second preset blades. The second preset blades located on both sides of the first preset blade are symmetrically arranged about the first preset blade, which is beneficial to better reduce order noise.

[0099] In some embodiments, the number of blades 12′ is 5 to 11. By limiting the number of blades 12′ as described above, the convenience of industrial mold making can be ensured, and the air volume and air pressure performance of the booster fan 10 can be maintained.

[0100] The impeller 1′ also includes a blade crown 13′, which is annular and is fitted on the outside of multiple blades 12′. The ends of the multiple blades 12′ that are radially away from the impeller hub 11′ are all fixedly connected to the blade crown 13′.

[0101] By wrapping multiple blades 12' with the blade crown 13', the airflow on the pressure and suction surfaces at the tips of the blades 12' is isolated, and fluid leakage on the pressure and suction surfaces at the tips of the blades 12' is prevented. This prevents the generation of large vortex structures in the tip region of the blades 12', thereby avoiding noise caused by the vortex and eliminating an important cause of order noise. This achieves the purpose of reducing the total noise and order noise amplitude of the booster fan 10 and improving the sound quality of the booster fan 10.

[0102] In some embodiments, along the axial direction of the impeller hub 11′, the variation law of the outer diameter of the blade crown 13′ is the same as the variation law of the inner diameter of the impeller housing 3a corresponding to the blade crown 13′, so as to ensure the smooth axial flow of airflow.

[0103] Specifically, when the inner wall of the impeller housing 3a corresponding to the blade crown 13′ is a cylindrical surface, the outer circumferential surface of the blade crown 13′ is also a cylindrical surface. When the inner wall of the impeller housing 3a corresponding to the blade crown 13′ is a gradually expanding or contracting conical surface, the blade crown 13′ is also a gradually expanding or contracting conical surface.

[0104] In some embodiments, such as Figure 2 As shown, a first gap a is provided between the blade crown 13′ and the inner wall of the impeller housing 3a, thereby preventing radial runout of the impeller 1′ from causing friction and scratching between the blade crown 13′ and the inner wall of the impeller housing 3a.

[0105] In some embodiments, the value of the first gap a ranges from 0.5 mm to 2 mm, which ensures that the blade crown 13′ and the inner wall of the impeller housing 3a will not rub against each other, while also helping to reduce the size of the booster fan 10.

[0106] For example, the first gap a can be any value between 0.5mm and 2mm, such as 0.5mm, 1mm, 1.5mm or 2mm.

[0107] In some embodiments, the thickness b of the blade crown 13' is in the range of 0.5 mm to 1.5 mm along the radial direction of the impeller hub 11', thereby ensuring the structural strength of the blade crown 13' and enabling the blade crown 13' to better isolate the airflow between the pressure surface and the suction surface of the blade 12'.

[0108] For example, the thickness b of the leaf crown 13′ can be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0109] In some embodiments, along the axial direction of the impeller hub 11′, the length of the blade crown 13′ is not less than the length of the blade tip of the blade 12′, and the length of the blade crown 13′ is not greater than the length of the impeller hub 11′.

[0110] For ease of understanding, such as Figure 1d As shown, along the axial direction of the impeller hub 11′, the length of the blade crown 13′ is denoted as d, the length of the blade tip of the blade 12′ is denoted as e, and the length of the impeller hub 11′ is denoted as f, where e≤d≤f.

[0111] It should be noted that, whether along the axial direction of the impeller hub 11′ or along the circumference of the impeller hub 11′, the blade crown 13′ can completely cover multiple blades 12′, thereby completely isolating the airflow on the pressure surface and suction surface of the blades 12′, resulting in better noise reduction.

[0112] In some embodiments, such as Figure 2 As shown, the inner wall of the impeller housing 3a is provided with a reinforcing structure 311; along the axial direction of the impeller hub 11′, a third gap c is provided between the blade crown 13′ and the reinforcing structure 311, which can prevent the impeller 1′ from moving axially and causing the blade crown 13′ to collide with the impeller housing 3a, so as to ensure the normal operation of the impeller 1′.

[0113] In some embodiments, the value of the third gap c ranges from 3mm to 8mm, which ensures that the blade crown 13′ and the impeller housing 3a will not have axial impact, while also helping to reduce the size of the booster fan 10.

[0114] For example, the third gap c can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0115] In some embodiments, the reinforcing structure 311 is provided on the air outlet side of the impeller 1'. The inner diameter of the blade crown 13' on the air outlet side of the impeller 1' is equal to the inner diameter of the impeller housing 3a where the reinforcing structure 311 is provided. This ensures that the blade crown 13' can isolate the airflow from the pressure surface and suction surface of the blade 12' without affecting the axial flow of the airflow.

[0116] In some other embodiments, the reinforcing structure 311 may also be provided on the air inlet side of the impeller 1'. The inner diameter of the blade crown 13' on the air inlet side of the impeller 1' is equal to the inner diameter of the impeller housing 3a where the reinforcing structure 311 is provided. This ensures that the blade crown 13' can isolate the airflow on the pressure surface and suction surface of the blade 12' without affecting the axial flow of the airflow.

[0117] like Figure 3As shown, the fan unit 101 also includes an air guide 5', which is fixed in the mounting cavity 31. The air inlet side of the impeller 1' faces the first opening 32, and the air outlet side of the impeller 1' is opposite to the air inlet side of the air guide 5'. The air outlet side of the air guide 5' faces the second opening 33. The air guide 5' is used to deflect the airflow generated by the impeller 1' to the axial direction of the impeller 1'.

[0118] In some embodiments, a fifth gap is provided between the blade crown 13' and the air guide 5' along the axial direction of the impeller hub 11', thereby preventing the axial movement of the impeller 1' from causing axial impact between the blade crown 13' and the air guide 5'.

[0119] In some embodiments, the fifth gap ranges from 3mm to 8mm, which ensures that the blade crown 13′ and the air guide 5′ will not have axial impact, while also helping to reduce the size of the booster fan 10.

[0120] For example, the fifth gap can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0121] like Figure 4a and Figure 4b As shown, the air guide 5′ includes an air guide hub 51′ and multiple guide vanes 52′. The air guide hub 51′ is fixed in the mounting cavity 31, and the multiple guide vanes 52′ are arranged at intervals along the circumference of the air guide hub 51′.

[0122] Since the impeller 1' rotates and does work, the airflow has a certain vortex. The aforementioned air guide 5' can deflect the airflow with a certain vortex to the axial direction of the impeller hub 11' of the impeller 1', converting part of the dynamic pressure into static pressure, achieving deswirl, and improving the pressurization effect.

[0123] In this embodiment, the axis of the guide hub 51′ coincides with the axis of the impeller hub 11′ of the impeller 1′.

[0124] It should be noted that the noise generated by the airflow produced by the rotation of impeller 1′ and the interference of the air guide 5′ is the main source of noise, especially the order noise, which is the most obvious and can easily form a very sharp sound, causing discomfort to the ears of drivers and passengers.

[0125] In some embodiments, multiple guide vanes 52′ are unevenly distributed along the circumference of the guide hub 51′, thereby effectively preventing the airflow generated by the rotation of the impeller 1′ from continuously striking the guide vanes 52′ at frequencies related to the rotational speed of the impeller 1′ (including frequencies several times the rotational speed of the impeller 1′) and generating some fixed frequency noise, thereby avoiding causing discomfort to the ears of drivers and passengers.

[0126] The phase angle between two adjacent guide vanes 52′ ranges from 180° / n1 to 540° / n1, where n1 is the number of guide vanes 52′. This setting helps to further improve the noise reduction effect.

[0127] It should be noted that since the guide vane 52′ is a stationary structural component and does not rotate, the multiple guide vanes 52′ of the air guide component 5′ can allow for a greater degree of uneven arrangement compared to the multiple blades 12′ of the impeller 1′.

[0128] In some embodiments, the ends of multiple guide vanes 52′ that are radially away from the wind guide hub 51′ are all fixedly connected to the impeller housing 3a. Thus, the multiple guide vanes 52′ can support and fix the wind guide hub 51′, and improve the installation stability of the guide vanes 52′. This not only has a simple structure, but also improves the wind guiding effect and noise reduction effect.

[0129] In some embodiments, the bending angle of the guide vane 52′ is in the range of 30° to 50°, and the bending angle of the guide vane 52′ gradually increases from the root to the tip of the vane, thereby improving the despinning effect.

[0130] For example, the bending angle of the guide vane 52′ can be any value between 30° and 50°, such as 30°, 35°, 40°, 45° or 50°.

[0131] In some embodiments, the geometric outlet angle of the guide vane 52′ is in the range of 80° to 100°, which can improve the deswirl effect.

[0132] For example, the geometric outlet angle of the guide vane 52′ can be any value between 80° and 100°, such as 80°, 85°, 90°, 95° or 100°.

[0133] In some embodiments, the plurality of guide vanes 52' include a first preset guide vane and a plurality of second preset guide vanes, wherein the second preset guide vanes located on both sides of the first preset guide vane are symmetrically arranged about the first preset guide vane.

[0134] The aforementioned guide vane 52′ configuration can better eliminate the order noise generated by the interference between the impeller 1′ and the air guide 5′.

[0135] It should be noted that in some other embodiments, the second preset guide vanes located on both sides of the first preset guide vane can be asymmetrically arranged with respect to the first preset guide vane, which can also achieve the effect of noise reduction.

[0136] In some embodiments, in two adjacent guide vanes 52', the projection of the leading edge of one guide vane 52' onto a preset plane does not intersect with the trailing edge of the other guide vane 52', thereby improving the convenience of industrial mold making. The preset plane is perpendicular to the axial direction of the third hub.

[0137] It should be noted that the drive component used to drive the impeller 1′ to rotate can be installed on the wind guide hub 51′ so that the wind guide hub 51′ can be supported by the guide vane 52′, thereby improving the installation stability of the drive component.

[0138] In some embodiments, the number of guide vanes 52′ is 9 to 15. Compared to the impeller 1′, the guide vanes 52′ are smaller in size, so a larger number can be set, which is beneficial to improving the support stability of the guide vanes 52′ for the drive component.

[0139] In some embodiments, multiple impellers 1′ are provided, and the multiple impellers 1′ are arranged sequentially along the axial direction of the impeller hub 11′.

[0140] In specific embodiments of the present invention, such as Figure 5a and 5b As shown, there are two impellers 1′. For ease of description, the two impellers 1′ are referred to as the first impeller 1a′ and the second impeller 1b′, respectively. The air inlet side of the second impeller 1b′ is arranged opposite to the air outlet side of the first impeller 1a′.

[0141] It should be noted that, as Figure 5a As shown, in the case of a series axial flow booster fan, the first impeller 1a′ and the second impeller 1b′ rotate in the same direction. By connecting the first impeller 1a′ and the second impeller 1b′ in series, the air is pressurized in combination, thereby achieving a higher boosting capacity.

[0142] Furthermore, each impeller 1' is correspondingly arranged with a guide vane 5'. In other words, the guide vane 5' is located on the outlet side of the corresponding impeller 1'. The guide vane 5' can deflect the airflow generated by the corresponding impeller 1' to the axial direction of the impeller hub 11' of that impeller 1' to ensure the pressurization effect. Specifically, there are two guide vanes 5'. For ease of description, the guide vane 5' corresponding to the first impeller 1a' is referred to as the first guide vane 5a', and the guide vane 5' corresponding to the second impeller 1b' is referred to as the second guide vane 5b'.

[0143] In some embodiments, the number of first guide vanes of the first air guide 5a' is not equal to the number of second guide vanes of the second air guide 5b'. This avoids interference between the first impeller 1a' and the first air guide 5a', as well as the order noise derived from interference between the second impeller 1b' and the second air guide 5b'. It also prevents the main orders of the first impeller 1a' and the second impeller 1b' from overlapping, which could lead to noise amplification at certain frequencies (e.g., 450Hz–800Hz), thus improving the noise reduction effect. Preferably, the number of first guide vanes of the first air guide 5a' is less than the number of second guide vanes of the second air guide 5b', resulting in a better noise reduction effect.

[0144] In a specific embodiment of the present invention, the first air guide 5a′ has 11 first guide vanes, and the phase angle between two adjacent first guide vanes in the first air guide 5a′ ranges from 17.1° to 49.1° (i.e., 180° / 11 to 540° / 11). For example, in the first air guide 5a′, the phase angles between two adjacent first guide vanes are successively 36.5°, 35.3°, 33.3°, 31.1°, 29.4°, 28.8°, 29.4°, 31.1°, 33.3°, 35.3°, and 36.5°. The second air guide 5b′ has 13 second guide vanes, and the phase angle between two adjacent second guide vanes in the second air guide 5b′ ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, in the second air guide 5b′, the phase angles between two adjacent second guide vanes are 35.1°, 33.4°, 30.4°, 26.8°, 23.3°, 20.9°, 20.0°, 20.9°, 23.3°, 26.8°, 30.4°, 33.4° and 35.1° respectively.

[0145] In some embodiments, the phase angle between two adjacent first guide vanes of the first guide vane 5a′ is not equal to the phase angle between two adjacent second guide vanes of the second guide vane 5b′, thereby making the uneven distribution of the multiple first guide vanes of the first guide vane 5a′ different from the uneven distribution of the multiple second guide vanes of the second guide vane 5b′. This further reduces the order noise derived from the mutual interference between the first impeller 1a′ and the first guide vane 5a′, and the mutual interference between the second impeller 1b′ and the second guide vane 5b′, and avoids the overlap of the main orders of the first impeller 1a′ and the second impeller 1b′, which would lead to noise amplification at certain frequencies (e.g., 450Hz to 800Hz), thus further improving the noise reduction effect.

[0146] It should be noted that in some other embodiments, the number of first guide vanes of the first guide element 5a' can be equal to the number of second guide vanes of the second guide element 5b'. Furthermore, the phase angle between two adjacent first guide vanes of the first guide element 5a' can be unequal to the phase angle between two adjacent second guide vanes of the second guide element 5b'. When it is not possible to design the number of first guide vanes of the first guide element 5a' and the number of second guide vanes of the second guide element 5b' to be unequal, the phase angle between two adjacent first guide vanes of the first guide element 5a' can be unequal to the phase angle between two adjacent second guide vanes of the second guide element 5b'. This further reduces the order noise generated by the interference between the first impeller 1a' and the first guide element 5a', and the interference between the second impeller 1b' and the second guide element 5b', thereby achieving noise reduction.

[0147] In a specific embodiment of the present invention, the first guide vane of the first guide element 5a′ is 13 in number, and the phase angle between two adjacent first guide vanes of the first guide element 5a′ ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, the phase angles between two adjacent first guide vanes of the first guide element 5a′ are successively 31.4°, 30.6°, 29.1°, 27.2°, 25.5°, 24.3°, 23.9°, 24.3°, 25.5°, 27.2°, 29.1°, 30.6°, and 31.4°. The second guide vane of the second guide element 5b′ is 13 in number, and the phase angle between two adjacent second guide vanes of the second guide element 5b′ ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, the phase angles between two adjacent second guide vanes of the second guide element 5b′ are 35.1°, 33.4°, 30.4°, 26.8°, 23.3°, 20.9°, 20.0°, 20.9°, 23.3°, 26.8°, 30.4°, 33.4° and 35.1° respectively.

[0148] like Figure 5b As shown, for the counter-rotating axial flow booster fan, the first impeller 1a′ and the second impeller 1b′ rotate in opposite directions. During operation, the first impeller 1a′ and the second impeller 1b′ rotate in opposite directions to combine and boost the air, thereby achieving a higher boosting capacity.

[0149] In a specific embodiment of the present invention, the first impeller 1a′ has nine first blades, and the phase angle between two adjacent first blades ranges from 32° to 48° (288° / 9 to 432° / 9). Exemplarily, the phase angles between two adjacent first blades are 43.9°, 34.7°, 39.3°, 44.2°, 35.9°, 44.2°, 39.3°, 34.7°, and 43.9°, respectively, and these values ​​ensure that the first blades of the first impeller 1a′ do not overlap along the axial direction of the first impeller 1a′. Further, the second impeller 1b′ has seven second blades, and the phase angle between two adjacent second blades ranges from 41.1° to 61.7° (288° / 7 to 432° / 7). For example, the phase angles between two adjacent second blades are 50.4°, 52.4°, 53.7°, 47.1°, 53.7°, 52.4° and 50.4° respectively, and can satisfy that the second blades of the second impeller 1b′ do not overlap each other along the axial direction of the second impeller 1b′.

[0150] In some embodiments, along the rotation direction of the impeller 1′ and with the rotation direction of the impeller 1′ as the positive value, the trailing edge y1 of the blade 12′ has a phase angle α between the blade root and the blade tip. In other words, the blade 12′ adopts a curved design.

[0151] The above configuration can discretize the phenomenon of pressure fluctuations generated by the wakes of blades 12′ at different radial heights impacting other structures of the downstream booster fan 10 in time. In other words, it can distribute the phenomenon of pressure fluctuations generated by the wakes of blades 12′ at different radial heights impacting other structures of the downstream booster fan 10 at different times, thereby eliminating the pressure fluctuations. This can significantly reduce the order noise problem of the booster fan 10 and slightly reduce the total noise of the booster fan 10.

[0152] In specific embodiments of the present invention, such as Figures 6 to 8 As shown, along the rotation direction of the first impeller 1a′ and with the rotation direction of the first impeller 1a′ as the positive value, a first phase angle α is provided between the root and tip of the trailing edge y1 of the first blade of the first impeller 1a′; along the rotation direction of the second impeller 1b′ and with the rotation direction of the second impeller 1b′ as the positive value, a second phase angle β is provided between the root and tip of the leading edge x2 of the second blade of the second impeller 1b′.

[0153] This configuration allows for the time-discretion of the phenomenon where pressure fluctuations generated by the wakes of the first blades of the first impeller 1a′ at different radial heights impact the leading edge x2 of the second blades of the second impeller 1b′. In other words, it enables the phenomenon of pressure fluctuations generated by the wakes of the first blades of the first impeller 1a′ at different radial heights impacting the leading edge x2 of the second blades of the second impeller 1b′ to be distributed at different times, thereby eliminating the pressure fluctuations. This not only significantly reduces the order noise problem of the booster fan 10 but also slightly reduces the total noise of the booster fan 10.

[0154] In some embodiments, the value of α+β ranges from 50%*360° / N1 to 150%*360° / N1, and both α and β are not less than 20°; N1 is the number of the first blades of the first impeller 1a′. α+β being greater than 50%*360° / N1 allows the impacts at different radial heights to be dispersed at different times when the trailing edge x2 of the first blade of the first impeller 1a′ interferes with the leading edge x2 of the second blade of the second impeller 1b′ during rotation. This avoids noise amplification caused by simultaneous or short-term impacts, thus preventing the formation of prominent order noise. If α+β is less than 150%*360° / N1, the demolding difficulties caused by excessive bending of the first blade of the first impeller 1a′ and the second blade of the second impeller 1b′ can be avoided. If α+β exceeds 360° / N1, the effect of improving the order noise by the bending angle of the second blade of the first impeller 1a′ and the second impeller 1b′ will be weakened. Therefore, it is not necessary to excessively bend the second blade of the first impeller 1a′ and the second impeller 1b′.

[0155] In a specific embodiment of the present invention, the first impeller 1a′ has 9 first blades, α is 20°, β is 21°, α+β=41°, which satisfies the range of 20°~60° (50%*360° / 9~150%*360° / 9).

[0156] In some embodiments, such as Figure 5c As shown, multiple first impellers 1a′ and second impellers 1b′ are provided. One first impeller 1a′ and a second impeller 1b′ disposed opposite to the air outlet side of the first impeller 1a′ form a fan unit 101. In other words, in this embodiment, the booster fan 10 includes multiple fan units 101, which are arranged along an axial direction perpendicular to the impeller hub 11′. This arrangement allows multiple fan units 101 to correspond to different areas within the vehicle cabin, enabling independent adjustment of airflow and speed in different areas of the cabin, thereby improving the comfort of the driver and passengers.

[0157] In a specific embodiment of the present invention, two fan units 101 may be provided. Of course, one, three, four, or even more fan units 101 may also be provided, which is not limited here.

[0158] The booster fan 10 in this embodiment has the advantages of low total noise, low order noise, and friendly sound quality while meeting the air volume and air pressure requirements. It has a high NVH level and can solve the problems of large size and difficult layout of existing booster fans. In this way, it can greatly free up the storage space in the vehicle, improve the usability of the product in the vehicle, and bring greater improvement to the vehicle product competitiveness.

[0159] Example 2

[0160] In existing technologies, axial flow booster fans, due to their axial airflow characteristics, can be directly matched with air ducts, avoiding significant airflow deflection, making them the best choice for miniaturization. Axial flow booster fans are characterized by large air volume and low air pressure. However, due to their fewer blades and relatively high rotational speed, the blade wakes or vortices generated by the blades continuously strike downstream structures at frequencies related to or several times the impeller's rotational speed, producing noise at certain fixed frequencies, especially order noise. This sound is easily distinguishable by the human ear, leading to auditory discomfort and poor sound quality, severely limiting their application scenarios.

[0161] To solve this problem, such as Figure 9 and Figure 10 As shown, an embodiment of the present invention also provides a booster fan. In this embodiment, the booster fan 10 is a counter-rotating axial flow booster fan. The booster fan 10 includes a fan unit 101, which includes a first impeller 1, a second impeller 2, and an impeller housing 3a.

[0162] The impeller housing 3a includes a mounting cavity 31 and a first opening 32 and a second opening 33, both of which communicate with the mounting cavity 31. The first impeller 1 and the second impeller 2 are rotatably disposed within the mounting cavity 31. The air inlet side of the first impeller 1 faces the first opening 32, and the air outlet side of the second impeller 2 faces the second opening 33. In this embodiment, the first opening 32 and the second opening 33 are sequentially arranged along the axial direction of the first hub 11.

[0163] The first impeller 1 and the second impeller 2 rotate in opposite directions. During operation, the first blade 12 and the second impeller 2 rotate in opposite directions to combine and pressurize the air, thereby achieving a high pressurization capacity.

[0164] like Figure 11 As shown, the first impeller 1 includes a first hub 11 and a plurality of first blades 12. The plurality of first blades 12 are arranged at intervals along the circumference of the first hub 11, and the plurality of first blades 12 are unevenly distributed along the circumference of the first hub 11. The phase angle between two adjacent first blades 12 ranges from 288° / N1 to 432° / N1, where N1 is the number of first blades 12.

[0165] like Figure 12As shown, the air inlet side of the second impeller 2 is arranged opposite to the air outlet side of the first impeller 1; the second impeller 2 includes a second hub 21 and a plurality of second blades 22, the plurality of second blades 22 are arranged at intervals along the circumference of the second hub 21, and the plurality of second blades 22 are unevenly distributed along the circumference of the second hub 21; the phase angle between two adjacent second blades 22 ranges from 288° / N2 to 432° / N2, where N2 is the number of second blades 22.

[0166] The first blade 12 and the second blade 22 are configured as described above. Under the premise of ensuring the dynamic and static balance of the axial flow booster fan, the total noise generated by the rotation of the first impeller 1 and the second impeller 2 can be effectively reduced. At the same time, the problems of high first-order noise, poor sound quality and low NVH level of the axial flow booster fan 10 are solved. Under the premise that the axial flow booster fan 10 can provide the required air volume and air pressure, it can also meet the requirements of low noise and good sound quality.

[0167] In some embodiments, the booster fan 10 includes a plurality of fan units 101, which are arranged in a direction perpendicular to the axial direction of the first hub 11. This arrangement allows the plurality of fan units 101 to correspond to different areas within the vehicle cabin, enabling independent adjustment of the airflow and speed in different areas of the vehicle cabin, thereby improving the comfort of the driver and passengers.

[0168] In specific embodiments of the present invention, such as Figure 13 As shown, two fan units 101 are provided. Of course, one, three, four, or even more fan units 101 can be provided, which is not limited here.

[0169] It should be noted that in the same fan unit 101, the axis of the second hub 21 coincides with the axis of the first hub 11. In other words, the second hub 21 and the first hub 11 are coaxially arranged.

[0170] In some embodiments, such as Figure 9 As shown, the booster fan 10 also includes a first drive member 41 corresponding to the first impeller 1 and a second drive member 42 corresponding to the second impeller 2. The first drive member 41 is connected to the corresponding first impeller 1 to drive the corresponding first impeller 1 to rotate; the second drive member 42 is connected to the corresponding second blade 22 to drive the corresponding second impeller 2 to rotate.

[0171] Specifically, the first driving component 41 includes a first motor, and the second driving component 42 includes a second motor. The output shaft of the first motor is connected to the first hub 11 of the corresponding first impeller 1, and the output shaft of the second motor is connected to the second hub 21 of the corresponding second impeller 2. Thus, by controlling the first motor and the second motor respectively, the rotational speed of the first impeller 1 and the second impeller 2 can be controlled.

[0172] For example, the output shaft of the first motor is connected to the first hub 11 of the corresponding first impeller 1, and the output shaft of the second motor is connected to the second hub 21 of the corresponding second impeller 2 via connecting flanges.

[0173] In some other embodiments, the booster fan 10 includes a drive mechanism corresponding to each of the multiple fan units 101. A drive mechanism drives the first impeller 1 and the second impeller 2 of the same fan unit 101 to rotate. For example, the drive mechanism includes a drive element and a reversing assembly. The first impeller 1 is directly connected to the output shaft of the drive element, and the second impeller 2 is connected to the output shaft of the drive element through the reversing assembly, thereby causing the first impeller 1 and the second impeller 2 to rotate in opposite directions. Specifically, the drive element is a motor, and the reversing assembly is a gear set. Of course, the reversing assembly can also be other reversing structures in the prior art, which are not limited here.

[0174] In some embodiments, the number of first blades 12 is 5 to 11. By limiting the number of first blades 12 as described above, the convenience of industrial mold opening can be ensured, and the air volume and air pressure performance of the axial flow booster fan can be maintained.

[0175] In some embodiments, the number of second blades 22 is 5 to 11. By limiting the number of second blades 22 as described above, the convenience of industrial mold opening can be ensured, and the air volume and air pressure performance of the axial flow booster fan can be maintained.

[0176] In some embodiments, such as Figure 14 As shown, in two adjacent first blades 12, the projection of the leading edge x1 of one first blade 12 onto a preset plane does not intersect with the trailing edge y1 of the other first blade 12. The preset plane is perpendicular to the axial direction of the first hub 11. This configuration further improves the convenience of industrial mold making and the airflow and pressure performance of the axial flow booster fan.

[0177] In some embodiments, such as Figure 15 As shown, in two adjacent second blades 22, the projection of the leading edge x2 of one second blade 22 onto a preset plane does not intersect with the trailing edge y2 of the other second blade 22. This arrangement further improves the convenience of industrial mold making and the airflow and pressure performance of the axial flow booster fan.

[0178] In some embodiments, the number of the first blade 12 and the second blade 22 are not equal, which helps to improve the order noise of the counter-rotating axial flow booster fan and avoid the order noise caused by airflow interference between the first impeller 1 and the second impeller 2.

[0179] In some embodiments, the number of first blades 12 is greater than the number of second blades 22, which helps to further improve the order noise of the counter-rotating axial flow booster fan and further avoid the order noise caused by airflow interference between the first impeller 1 and the second impeller 2.

[0180] In some embodiments, the plurality of first blades 12 include a first preset blade and a plurality of second preset blades, wherein the second preset blades located on both sides of the first preset blade are symmetrically arranged about the first preset blade, which is beneficial to better reduce order noise.

[0181] In some embodiments, the plurality of second blades 22 include a third preset blade and a plurality of fourth preset blades, wherein the fourth preset blades located on both sides of the third preset blade are symmetrically arranged about the third preset blade, thereby helping to better reduce order noise.

[0182] It should be noted that in some other embodiments, the second preset blades located on both sides of the first preset blade can be asymmetrically arranged, and the fourth preset blades located on both sides of the third preset blade can also be asymmetrically arranged, which can also achieve the purpose of improving the noise reduction effect.

[0183] In a specific embodiment of the present invention, there are nine first blades 12, and the phase angles between two adjacent first blades 12 are 43.9°, 34.7°, 39.3°, 44.2°, 35.9°, 44.2°, 39.3°, 34.7°, and 43.9°, respectively. There are seven second blades 22, and the phase angles between two adjacent second blades 22 are 50.4°, 52.4°, 53.7°, 47.1°, 53.7°, 52.4°, and 50.4°, respectively.

[0184] In some embodiments, such as Figure 16 As shown, along the rotation direction of the first impeller 1 and with the rotation direction of the first impeller 1 as the positive value, the first blade 12 has a first phase angle α between the blade root and the blade tip at the trailing edge y1. In other words, the first blade 12 adopts a curved design.

[0185] In some embodiments, along the rotation direction of the second impeller 2 and with the rotation direction of the second impeller 2 as the positive value, a second phase angle β is provided between the blade root and the blade tip of the leading edge x2 of the second blade 22. In other words, the second blade 22 adopts a curved design.

[0186] This configuration allows for the time-discretion of the phenomenon where pressure fluctuations generated by the wake of the first blade 12 at different radial heights impact the leading edge x2 of the second blade 22. In other words, it enables the phenomenon of pressure fluctuations generated by the wake of the first blade 12 at different radial heights impacting the leading edge x2 of the second blade 22 to be distributed at different times, thereby eliminating the pressure fluctuations. This not only significantly reduces the order noise problem of the counter-rotating axial flow booster fan, but also slightly reduces the total noise of the counter-rotating axial flow booster fan.

[0187] In some embodiments, the value of α+β ranges from 50%*360° / N1 to 150%*360° / N1, and both α and β are not less than 20°. When α+β is greater than 50%*360° / N1, it allows the impacts at different radial heights to be dispersed at different times when the wake of the first blade 12 interferes with the leading edge x2 of the second blade 22 during the rotation of the first impeller 1 and the second impeller 2. This avoids noise amplification caused by simultaneous or short-term impacts, thus preventing the formation of convex order noise. When α+β is less than 150%*360° / N1, it avoids demolding difficulties caused by excessive bending of the first blade 12 and the second blade 22. Furthermore, if α+β exceeds 360° / N1, the effect of improving order noise through the bending angle of the first blade 12 and the second blade 22 will be weakened; therefore, excessive bending of the first blade 12 and the second blade 22 is unnecessary.

[0188] In a specific embodiment of the present invention, the number of first blades 12 is 9, the first phase angle α is 20°, and the second phase angle β is 21°. This can not only significantly reduce the order noise problem of the counter-rotating axial flow booster fan, but also facilitate the demolding of the first blades 12 and the second blades 22, reducing the processing difficulty of the first blades 12 and the second blades 22.

[0189] In some embodiments, the first impeller 1 further includes a first blade crown 13, which is annular and sleeved on the outside of a plurality of first blades 12. The ends of the plurality of first blades 12 that are radially away from the first hub 11 are all fixedly connected to the first blade crown 13.

[0190] By wrapping multiple first blades 12 with the first blade crown 13, the airflow on the pressure surface and suction surface at the top of the first blade 12 is isolated. This can prevent the airflow leakage on the pressure surface and suction surface at the top of the first blade 12 from generating a large vortex, thereby avoiding noise caused by the vortex. This achieves the purpose of reducing the total noise of the booster fan 10, improving the order noise level, and enhancing the sound quality of the booster fan 10.

[0191] In some embodiments, the second impeller 2 further includes a second blade crown 23, which is annular and is sleeved on the outside of a plurality of second blades 22. The ends of the plurality of second blades 22 that are radially away from the second hub 21 are all fixedly connected to the second blade crown 23.

[0192] By wrapping multiple second blades 22 with the aforementioned second blade crown 23, the airflow on the pressure surface and suction surface at the top of the second blades 22 is isolated. This can prevent airflow leakage on the pressure surface and suction surface at the top of the second blades 22, thus preventing the generation of large vortices. This avoids noise caused by the vortices, thereby reducing the total noise of the booster fan 10, improving the order noise level, and enhancing the sound quality of the booster fan 10.

[0193] In some embodiments, such as Figure 17 As shown, a first gap a1 is provided between the first blade crown 13 and the inner wall of the impeller housing 3a along the radial direction of the first hub 11, thereby preventing the first impeller 1 from radially jumping and causing friction and scratching between the first blade crown 13 and the inner wall of the impeller housing 3a.

[0194] In some embodiments, the value of the first gap a1 ranges from 0.5mm to 2mm. This ensures that the first blade crown 13 does not rub against the inner wall of the impeller housing 3a, while also reducing the size of the booster fan 10.

[0195] For example, the first gap a1 can be any value between 0.5mm and 2mm, such as 0.5mm, 1mm, 1.5mm or 2mm.

[0196] In some embodiments, such as Figure 18 As shown, along the radial direction of the second hub 21, a second gap a2 is provided between the second blade crown 23 and the inner wall of the impeller housing 3a, thereby preventing the radial runout of the second impeller 2 from causing friction and scratching between the second blade crown 23 and the inner wall of the impeller housing 3a.

[0197] In some embodiments, the value of the second gap a2 is in the range of 0.5mm to 2mm. While ensuring that the second blade crown 23 does not rub against the inner wall of the impeller housing 3a, it also helps to reduce the size of the booster fan 10.

[0198] For example, the second gap a2 can be any value between 0.5mm and 2mm, such as 0.5mm, 1mm, 1.5mm or 2mm.

[0199] It should be noted that the values ​​of the first gap a1 between the first blade crown 13 and the inner wall of the impeller housing 3a and the second gap a2 between the second blade crown 23 and the inner wall of the impeller housing 3a can be equal or unequal, and are not limited here.

[0200] In some embodiments, such as Figure 17 As shown, along the radial direction of the first hub 11, the thickness b1 of the first blade crown 13 ranges from 0.5mm to 1.5mm, which ensures the structural strength of the first blade crown 13 and enables the first blade crown 13 to better isolate the airflow between the pressure surface and the suction surface of the first blade 12.

[0201] For example, the thickness b1 of the first leaf crown 13 can be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0202] In some embodiments, such as Figure 18 As shown, along the radial direction of the second hub 21, the thickness b2 of the second blade crown 23 ranges from 0.5mm to 1.5mm, which ensures the structural strength of the second blade crown 23 and enables the second blade crown 23 to better isolate the airflow between the pressure surface and the suction surface of the second blade 22.

[0203] For example, the thickness b2 of the second leaf crown 23 can be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0204] It should be noted that the thickness b1 of the first leaf crown 13 and the thickness b2 of the second leaf crown 23 can be equal or unequal, and no limitation is made here.

[0205] In some embodiments, the inner wall of the impeller housing 3a is provided with a reinforcing structure 311. Along the axial direction of the first hub 11, the reinforcing structure 311 is located between the first impeller 1 and the second impeller 2, so as to increase the structural strength of the impeller housing 3a and extend its service life.

[0206] Furthermore, the impeller housing 3a is also provided with a support structure 312 for supporting the first driving member 41 and the second driving member 42. The support structure 312 is fixedly connected to the reinforcing structure 311 to improve the installation stability of the first driving member 41 and the second driving member 42. It should be noted that one support structure 312 can be provided to simultaneously support the first driving member 41 and the second driving member 42. Two support structures 312 can also be provided to support the first driving member 41 and the second driving member 42 respectively. Of course, more support structures 312 can be provided so that the first driving member 41 and the second driving member 42 are supported by multiple support structures 312 respectively.

[0207] For example, both the reinforcing structure 311 and the supporting structure 312 are protruding ribs protruding from the inner wall of the impeller housing 3a.

[0208] In some embodiments, such as Figure 17As shown, along the axial direction of the first hub 11, a third gap c1 is provided between the reinforcing structure 311 and the first blade crown 13, which can prevent the first impeller 1 from axially moving and causing the first blade crown 13 to collide with the impeller housing 3a.

[0209] In some embodiments, the value of the third gap c1 is in the range of 3mm to 8mm, which ensures that the first blade crown 13 and the impeller housing 3a will not have axial impact, and also helps to reduce the volume of the booster fan 10.

[0210] For example, the third gap c1 can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0211] In some embodiments, such as Figure 18 As shown, along the axial direction of the second hub 21, a fourth gap c2 is provided between the reinforcing structure 311 and the second blade crown 23, which can prevent the second impeller 2 from axially moving and causing the second blade crown 23 to collide with the impeller housing 3a.

[0212] In some embodiments, the value of the fourth gap c2 is in the range of 3mm to 8mm, which ensures that the second blade crown 23 and the impeller housing 3a will not have axial impact, and also helps to reduce the volume of the booster fan 10.

[0213] For example, the fourth gap c2 can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0214] It should be noted that the values ​​of the third gap c1 between the reinforcing structure 311 and the first impeller 1 and the fourth gap c2 between the reinforcing structure 311 and the second impeller 2 along the axial direction of the first hub 11 can be equal or unequal, and are not limited here.

[0215] In some embodiments, the inner diameter of the first blade crown 13 on the air outlet side of the first impeller 1 is equal to the inner diameter of the impeller housing 3a at the location where the reinforcing structure 311 is provided.

[0216] In some embodiments, the inner diameter of the second blade crown 23 on the air inlet side of the second impeller 2 is equal to the inner diameter of the impeller housing 3a at the location where the reinforcing structure 311 is provided.

[0217] This configuration ensures that the first blade crown 13 can isolate the airflow on the pressure surface and suction surface of the first blade 12, and the second blade crown 23 can isolate the airflow on the pressure surface and suction surface of the second blade 22, without affecting the axial flow of the airflow.

[0218] In some embodiments, along the axial direction of the first hub 11, the length of the first blade crown 13 is not less than the length of the tip of the first blade 12, and the length of the first blade crown 13 is not greater than the length of the first hub 11.

[0219] For ease of understanding, such as Figure 19 As shown, the length of the first leaf crown 13 is denoted as d, the length of the tip of the first blade 12 is denoted as e, and the length of the first hub 11 is denoted as f, where e≤d≤f.

[0220] In some embodiments, along the axial direction of the second hub 21, the length of the second blade crown 23 is not less than the length of the blade tip of the second blade 22, and the length of the second blade crown 23 is not greater than the length of the second hub 21.

[0221] It should be noted that the lengths of the first blade crown 13 and the second blade crown 23 along the axial direction of the first hub 11 can be equal or unequal, and no limitation is made here.

[0222] For example, in a specific embodiment of the present invention, the first gap a1 is 1 mm. The thickness b1 of the first blade crown 13 is 1 mm. The third gap c1 is 5.5 mm. The second gap a2 is 1 mm. The thickness b2 of the second blade crown 23 is 1 mm. The fourth gap c2 is 5.5 mm. Along the axial direction of the first hub 11, the length of the first blade crown 13 is 26 mm. Along the axial direction of the second hub 21, the length of the second blade crown 23 is 21 mm. This configuration improves the structural strength of the first impeller 1 and the second impeller 2, as well as the smoothness of the axial flow of airflow, and also enhances the noise reduction effect.

[0223] It should be noted that, whether along the axial direction or the circumferential direction of the first hub 11, the first blade crown 13 can completely cover the multiple first blades 12, thereby completely isolating the airflow on the pressure surface and suction surface of the first blades 12. Similarly, the second blade crown 23 can completely cover the multiple second blades 22, thereby completely isolating the airflow on the pressure surface and suction surface of the second blades 22, resulting in better noise reduction.

[0224] In some embodiments, such as Figure 17 As shown, along the axial direction of the first hub 11, the variation law of the outer diameter of the first blade crown 13 is the same as the variation law of the inner diameter of the impeller housing 3a corresponding to the first blade crown 13.

[0225] In some embodiments, such as Figure 18 As shown, along the axial direction of the second hub 21, the variation law of the outer diameter of the second blade crown 23 is the same as the variation law of the inner diameter of the impeller housing 3a corresponding to the second blade crown 23.

[0226] It should be noted that the shape of the outer peripheral surface of the first blade crown 13 is the same as the shape of the inner wall of the impeller housing 3a corresponding to the first blade crown 13, and the shape of the outer peripheral surface of the second blade crown 23 is the same as the shape of the inner wall of the impeller housing 3a corresponding to the second blade crown 23, which is conducive to further improving the smoothness of the axial flow of air.

[0227] Specifically, when the inner wall of the impeller housing 3a corresponding to the first blade crown 13 and the inner wall of the impeller housing 3a corresponding to the second blade crown 23 are both cylindrical surfaces, the outer peripheral surface of the first blade crown 13 and the outer peripheral surface of the second blade crown 23 are also cylindrical surfaces; when the inner wall of the impeller housing 3a corresponding to the first blade crown 13 and the inner wall of the impeller housing 3a corresponding to the second blade crown 23 are both conical surfaces that gradually expand or contract from the first impeller 1 to the second impeller 2, the outer peripheral surface of the first blade crown 13 and the outer peripheral surface of the second blade crown 23 are also conical surfaces that gradually expand or contract from the first impeller 1 to the second impeller 2.

[0228] In some embodiments, such as Figure 9 As shown, the fan unit 101 also includes a cap 71 and a tail cone 72. The cap 71 is located at the end of the first impeller 1 away from the second impeller 2, and the tail cone 72 is located at the end of the second impeller 2 away from the first impeller 1. By providing the cap 71 and the tail cone 72, the noise generated by the airflow can be reduced.

[0229] Specifically, the cap 71 is fixedly connected to the first wheel hub 11, and the tail cone 72 is fixedly connected to the second wheel hub 21.

[0230] In some embodiments, such as Figure 20 As shown, the impeller housing 3a includes a first housing 3a1 and a second housing 3a2. The first housing 3a1 and the second housing 3a2 are detachably connected by a first locking member 3b1 such as a first bolt. The first impeller 1 and the first driving member 41 are both located in the first housing 3a1, and the second impeller 2 and the second driving member 42 are both located in the second housing 3a2, thereby improving the convenience of assembly.

[0231] It should be noted that when there are multiple fan units 101, the first housings 3a1 of the multiple fan units 101 are fixedly connected or integrally formed into a first integrated housing, and the second housings 3a2 of the multiple fan units 101 are fixedly connected or integrally formed into a second integrated housing, thereby reducing the mold opening cost and simplifying the assembly.

[0232] In some embodiments, such as Figure 21 As shown, the booster fan 10 also includes a fan housing 3c. The first housing 3a1 and the second housing 3a2 are both fixed inside the fan housing 3c. A vibration damping structure 3d is provided between the first housing 3a1 and the fan housing 3c, and between the second housing 3a2 and the fan housing 3c, in order to achieve the purpose of vibration reduction and noise reduction.

[0233] For example, the fan housing 3c includes a first housing portion 3c1 and a second housing portion 3c2. The first housing portion 3c1 and the second housing portion 3c2 are detachably connected by a second locking member 3b2 such as a second bolt, which facilitates the assembly of the booster fan 10.

[0234] Specifically, the first shell portion 3c1 and the second shell portion 3c2 are arranged opposite each other along the radial direction of the first hub 11. Of course, the first shell portion 3c1 and the second shell portion 3c2 can also be arranged opposite each other along the axial direction of the first hub 11.

[0235] The booster fan 10 in this embodiment, while meeting the air volume and air pressure requirements, has the advantages of low total noise, low order noise, and friendly sound quality. It has a high NVH level and can solve the problems of large size and difficult layout of existing booster fans. In this way, it can greatly free up the storage space in the vehicle, improve the usability of the product in the vehicle, realize the miniaturization of the booster fan 10, and bring greater improvement to the vehicle product competitiveness.

[0236] Example 3

[0237] In existing technologies, axial flow booster fans, due to their axial inlet and outlet characteristics, can be directly matched with air ducts, avoiding significant airflow deflection, making them the best choice for miniaturization of booster fans. Axial flow booster fans are characterized by large air volume and low air pressure. However, due to their fewer blades and relatively high rotational speed, the blade wakes or vortices generated by the blades continuously strike the downstream structure at frequencies related to or several times the impeller's rotational speed, producing noise at certain fixed frequencies, especially order noise. This sound is easily distinguishable by the human ear, leading to auditory discomfort and poor sound quality, severely limiting their application scenarios.

[0238] To solve this problem, such as Figure 22 As shown, an embodiment of the present invention also provides a booster fan. In this embodiment, the booster fan 10 is a series axial flow booster fan. The booster fan 10 includes a fan unit 101, which includes a first impeller 1, a second impeller 2, and an impeller housing 3a.

[0239] The impeller housing 3a includes a mounting cavity 31 and a first opening 32 and a second opening 33, both of which communicate with the mounting cavity 31. The first impeller 1 and the second impeller 2 are rotatably disposed within the mounting cavity 31. The air inlet side of the first impeller 1 faces the first opening 32, and the air outlet side of the second impeller 2 faces the second opening 33. In this embodiment, the first opening 32 and the second opening 33 are sequentially arranged along the axial direction of the first hub 11.

[0240] The first impeller 1 and the second impeller 2 rotate in the same direction. In other words, the first impeller 1 and the second impeller 2 are coaxially connected in series. Under the premise of ensuring the dynamic and static balance of the axial flow booster fan, the noise reduction purpose is achieved. At the same time, the problems of high noise and poor sound quality of the axial flow booster fan are solved. This allows the axial flow booster fan to provide the required air volume and air pressure while meeting the requirements of low noise and good sound quality.

[0241] like Figure 23 and Figure 24 As shown, the first impeller 1 includes a first hub 11 and a plurality of first blades 12. The plurality of first blades 12 are arranged at intervals along the circumference of the first hub 11, and the plurality of first blades 12 are unevenly distributed along the circumference of the first hub 11. The phase angle between two adjacent first blades 12 ranges from 288° / N1 to 432° / N1, where N1 is the number of first blades 12.

[0242] like Figure 25 and Figure 26 As shown, the air inlet side of the second impeller 2 is arranged opposite to the air outlet side of the first impeller 1; the second impeller 2 includes a second hub 21 and a plurality of second blades 22, the plurality of second blades 22 are arranged at intervals along the circumference of the second hub 21, and the plurality of second blades 22 are unevenly distributed along the circumference of the second hub 21; the phase angle between two adjacent second blades 22 ranges from 288° / N2 to 432° / N2, where N2 is the number of second blades 22.

[0243] The first blade 12 and the second blade 22 are configured as described above. Under the premise of ensuring the dynamic and static balance of the axial flow booster fan, the total noise generated by the rotation of the first impeller 1 and the second impeller 2 can be effectively reduced. At the same time, the problems of high order noise, poor sound quality and low NVH level of the axial flow booster fan are solved. Under the premise of providing the required air volume and air pressure of the axial flow booster fan, it can meet the requirements of low noise and good sound quality.

[0244] In some embodiments, the booster fan 10 includes a plurality of fan units 101, which are arranged in a direction perpendicular to the axial direction of the first hub 11. This arrangement allows the plurality of fan units 101 to correspond to different areas within the vehicle cabin, enabling independent adjustment of the airflow and speed in different areas of the vehicle cabin, thereby improving the comfort of the driver and passengers.

[0245] In a specific embodiment of the present invention, two fan units 101 may be provided. Of course, one, three, four, or even more fan units 101 may also be provided, which is not limited here.

[0246] It should be noted that in the same fan unit 101, the axis of the second hub 21 coincides with the axis of the first hub 11. In other words, the second hub 21 and the first hub 11 are coaxially arranged.

[0247] In some embodiments, the booster fan 10 further includes a first driving member corresponding to the first impeller 1 and a second driving member corresponding to the second impeller 2. The first driving member is driven to the corresponding first impeller 1 to drive the corresponding first impeller 1 to rotate; the second driving member is driven to the corresponding second blade 22 to drive the corresponding second impeller 2 to rotate.

[0248] Specifically, the first driving component includes a first motor, and the second driving component includes a second motor. The output shaft of the first motor is connected to the first hub 11 of the corresponding first impeller 1, and the output shaft of the second motor is connected to the second hub 21 of the corresponding second impeller 2. Thus, by controlling the first motor and the second motor respectively, the rotational speeds of the first impeller 1 and the second impeller 2 can be controlled.

[0249] For example, the output shaft of the first motor is connected to the first hub 11 of the corresponding first impeller 1, and the output shaft of the second motor is connected to the second hub 21 of the corresponding second impeller 2 via connecting flanges.

[0250] In other embodiments, the first impeller 1 and the second impeller 2 can be driven to rotate by a driving mechanism. For example, the driving mechanism includes a driving element and a reversing assembly. The first impeller 1 is directly connected to the output shaft of the driving element, and the second impeller 2 is connected to the output shaft of the driving element through the reversing assembly, thereby making the rotation directions of the first impeller 1 and the second impeller 2 opposite. Specifically, the driving element is a motor, and the reversing assembly is a gear set. Of course, the reversing assembly can also be other reversing structures in the prior art, which are not limited here.

[0251] In some embodiments, the number of first blades 12 is 5 to 11. By limiting the number of first blades 12 as described above, the convenience of industrial mold making can be ensured, and the air volume and air pressure performance of the axial flow booster fan can be maintained.

[0252] In some embodiments, the number of second blades 22 is 5 to 11. By limiting the number of second blades 22 as described above, the convenience of industrial mold making can be ensured, and the air volume and air pressure performance of the axial flow booster fan can be maintained.

[0253] In some embodiments, such as Figure 14As shown, in two adjacent first blades 12, the projection of the leading edge x1 of one first blade 12 onto a preset plane does not intersect with the trailing edge y1 of the other first blade 12. The preset plane is perpendicular to the axial direction of the first hub 11. This configuration further improves the convenience of industrial mold making and the airflow and pressure performance of the axial flow booster fan.

[0254] In some embodiments, such as Figure 15 As shown, in two adjacent second blades 22, the projection of the leading edge x2 of one second blade 22 onto a preset plane does not intersect with the trailing edge y2 of the other second blade 22. This arrangement further improves the convenience of industrial mold making and the airflow and pressure performance of the axial flow booster fan.

[0255] In some embodiments, the plurality of first blades 12 include a first preset blade and a plurality of second preset blades, wherein the second preset blades located on both sides of the first preset blade are symmetrically arranged about the first preset blade, which is beneficial to better reduce order noise.

[0256] In some embodiments, the plurality of second blades 22 include a third preset blade and a plurality of fourth preset blades, wherein the fourth preset blades located on both sides of the third preset blade are symmetrically arranged about the third preset blade, thereby helping to better reduce order noise.

[0257] It should be noted that in some other embodiments, the second preset blades located on both sides of the first preset blade can be asymmetrically arranged, and the fourth preset blades located on both sides of the third preset blade can also be asymmetrically arranged, which can also achieve the purpose of improving the noise reduction effect.

[0258] In some embodiments, the number of first blades 12 and the number of second blades 22 are both odd numbers.

[0259] In some embodiments, the number of first blades 12 is not equal to the number of second blades 22.

[0260] This configuration helps to further improve the order noise of the series axial flow booster fan and avoid the order noise caused by airflow interference between the first impeller 1 and the second impeller 2.

[0261] In some embodiments, the number of first blades 12 is greater than the number of second blades 22, which helps to further improve the order noise of the series axial flow booster fan and further avoid the order noise caused by airflow interference between the first impeller 1 and the second impeller 2.

[0262] In a specific embodiment of the present invention, there are nine first blades 12, and the phase angle between two adjacent first blades 12 ranges from 32° to 48° (i.e., 288° / 9 to 432° / 9). For example, the phase angles between two adjacent first blades 12 or between two adjacent second blades 22 are 45.8°, 32.1°, 38.9°, 46.3°, 33.8°, 46.3°, 38.9°, 32.1°, and 45.8°, respectively. There are nine second blades 22, and the phase angle between two adjacent second blades 22 ranges from 32° to 48° (i.e., 288° / 9 to 432° / 9). For example, the phase angles between two adjacent second blades 22 are 45.8°, 32.1°, 38.9°, 46.3°, 33.8°, 46.3°, 38.9°, 32.1° and 45.8° respectively.

[0263] In another specific embodiment of the present invention, the number of first blades 12 is 11, and the phase angle between two adjacent first blades 12 ranges from 26° to 39° (i.e., 288° / 11 to 432° / 11). Exemplarily, the phase angles between two adjacent first blades 12 or between two adjacent second blades 22 are 28.7°, 35.3°, 33.3°, 38.9°, 29.4°, 28.8°, 29.4°, 38.9°, 33.3°, 35.3°, and 28.7°, respectively. The number of second blades 22 is 11, and the phase angle between two adjacent second blades 22 ranges from 26° to 39° (i.e., 288° / 11 to 432° / 11). For example, the phase angles between two adjacent second blades 22 are 28.7°, 35.3°, 33.3°, 38.9°, 29.4°, 28.8°, 29.4°, 38.9°, 33.3°, 35.3° and 28.7° respectively.

[0264] In some embodiments, such as Figure 16 As shown, along the rotation direction of the first impeller 1 and with the rotation direction of the first impeller 1 as the positive value, the first blade 12 has a first phase angle α between the blade root and the blade tip at the trailing edge y1. In other words, the first blade 12 adopts a curved design.

[0265] In some embodiments, along the rotation direction of the second impeller 2 and with the rotation direction of the second impeller 2 as the positive value, a second phase angle β is provided between the blade root and the blade tip of the leading edge x2 of the second blade 22. In other words, the second blade 22 adopts a curved design.

[0266] This configuration allows for the time-discretion of the phenomenon where pressure fluctuations generated by the wake of the first blade 12 at different radial heights impact the leading edge x2 of the second blade 22. In other words, it enables the phenomenon of pressure fluctuations generated by the wake of the first blade 12 at different radial heights impacting the leading edge x2 of the second blade 22 to be distributed at different times, thereby eliminating the pressure fluctuations. This not only significantly reduces the order noise problem of the series axial flow booster fan, but also slightly reduces the total noise of the series axial flow booster fan.

[0267] In some embodiments, the value of α+β ranges from 50%*360° / N1 to 150%*360° / N1, and both α and β are not less than 20°. When α+β is greater than 50%*360° / N1, it allows the impacts at different radial heights to be dispersed at different times when the wake of the first blade 12 interferes with the leading edge x2 of the second blade 22 during the rotation of the first impeller 1 and the second impeller 2. This avoids noise amplification caused by simultaneous or short-term impacts, thus preventing the formation of convex order noise. When α+β is less than 150%*360° / N1, it avoids demolding difficulties caused by excessive bending of the first blade 12 and the second blade 22. Furthermore, if α+β exceeds 360° / N1, the effect of improving order noise through the bending angle of the first blade 12 and the second blade 22 will be weakened; therefore, excessive bending of the first blade 12 and the second blade 22 is unnecessary.

[0268] In a specific embodiment of the present invention, the number of first blades 12 is 9, the first phase angle α is 20°, and the second phase angle β is 21°. This can not only significantly reduce the order noise problem of the series axial flow booster fan, but also facilitate the demolding of the first blades 12 and the second blades 22, reducing the processing difficulty of the first blades 12 and the second blades 22.

[0269] In some embodiments, the first impeller 1 further includes a first blade crown 13, which is annular and sleeved on the outside of a plurality of first blades 12. The ends of the plurality of first blades 12 that are radially away from the first hub 11 are all fixedly connected to the first blade crown 13.

[0270] By wrapping multiple first blades 12 with the first blade crown 13, the airflow on the pressure surface and suction surface at the top of the first blade 12 is isolated. This can prevent the airflow leakage on the pressure surface and suction surface at the top of the first blade 12 from generating a large vortex, thereby avoiding noise caused by the vortex. This achieves the purpose of reducing the total noise of the booster fan 10, improving the order noise level, and enhancing the sound quality of the booster fan 10.

[0271] In some embodiments, the second impeller 2 further includes a second blade crown 23, which is annular and is sleeved on the outside of a plurality of second blades 22. The ends of the plurality of second blades 22 that are radially away from the second hub 21 are all fixedly connected to the second blade crown 23.

[0272] By wrapping multiple second blades 22 with the aforementioned second blade crown 23, the airflow on the pressure surface and suction surface at the top of the second blades 22 is isolated. This can prevent airflow leakage on the pressure surface and suction surface at the top of the second blades 22, thus preventing the generation of large vortices. This avoids noise caused by the vortices, thereby reducing the total noise of the booster fan 10, improving the order noise level, and enhancing the sound quality of the booster fan 10.

[0273] In some embodiments, such as Figure 17 As shown, a first gap a1 is provided between the first blade crown 13 and the inner wall of the impeller housing 3a along the radial direction of the first hub 11, thereby preventing the first impeller 1 from radially jumping and causing friction and scratching between the first blade crown 13 and the inner wall of the impeller housing 3a.

[0274] In some embodiments, the value of the first gap a1 ranges from 0.5mm to 2mm. This ensures that the first blade crown 13 does not rub against the inner wall of the impeller housing 3a, while also reducing the size of the booster fan 10.

[0275] For example, the first gap a1 can be any value between 0.5mm and 2mm, such as 0.5mm, 1mm, 1.5mm or 2mm.

[0276] In some embodiments, such as Figure 18 As shown, along the radial direction of the second hub 21, a second gap a2 is provided between the second blade crown 23 and the inner wall of the impeller housing 3a, thereby preventing the radial runout of the second impeller 2 from causing friction and scratching between the second blade crown 23 and the inner wall of the impeller housing 3a.

[0277] In some embodiments, the value of the second gap a2 is in the range of 0.5mm to 2mm. While ensuring that the second blade crown 23 does not rub against the inner wall of the impeller housing 3a, it also helps to reduce the size of the booster fan 10.

[0278] For example, the second gap a2 can be any value between 0.5mm and 2mm, such as 0.5mm, 1mm, 1.5mm or 2mm.

[0279] It should be noted that the values ​​of the first gap a1 between the first blade crown 13 and the inner wall of the impeller housing 3a and the second gap a2 between the second blade crown 23 and the inner wall of the impeller housing 3a can be equal or unequal, and are not limited here.

[0280] In some embodiments, such as Figure 17 As shown, along the radial direction of the first hub 11, the thickness b1 of the first blade crown 13 ranges from 0.5mm to 1.5mm, which ensures the structural strength of the first blade crown 13 and enables the first blade crown 13 to better isolate the airflow between the pressure surface and the suction surface of the first blade 12.

[0281] For example, the thickness b1 of the first leaf crown 13 can be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0282] In some embodiments, such as Figure 18 As shown, along the radial direction of the second hub 21, the thickness b2 of the second blade crown 23 ranges from 0.5mm to 1.5mm, which ensures the structural strength of the second blade crown 23 and enables the second blade crown 23 to better isolate the airflow between the pressure surface and the suction surface of the second blade 22.

[0283] For example, the thickness b2 of the second leaf crown 23 can be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0284] It should be noted that the thickness b1 of the first leaf crown 13 and the thickness b2 of the second leaf crown 23 can be equal or unequal, and no limitation is made here.

[0285] In some embodiments, the inner wall of the impeller housing 3a is provided with a reinforcing structure 311. Along the axial direction of the first hub 11, the reinforcing structure 311 is located between the first impeller 1 and the second impeller 2, so as to increase the structural strength of the impeller housing 3a and extend its service life.

[0286] Furthermore, the impeller housing 3a is also provided with a support structure 312 for supporting the first driving component and the second driving component. The support structure 312 is fixedly connected to the reinforcing structure 311 to improve the installation stability of the first driving component and the second driving component. It should be noted that one support structure 312 can be provided to simultaneously support the first driving component and the second driving component. Two support structures 312 can also be provided to support the first driving component and the second driving component respectively. Of course, more support structures 312 can be provided so that the first driving component and the second driving component are supported by multiple support structures 312 respectively.

[0287] For example, both the reinforcing structure 311 and the supporting structure 312 are protruding ribs protruding from the inner wall of the impeller housing 3a.

[0288] In some embodiments, such as Figure 17As shown, along the axial direction of the first hub 11, a third gap c1 is provided between the reinforcing structure 311 and the first blade crown 13, which can prevent the first impeller 1 from axially moving and causing the first blade crown 13 to collide with the impeller housing 3a.

[0289] In some embodiments, the value of the third gap c1 is in the range of 3mm to 8mm, which ensures that the first blade crown 13 and the impeller housing 3a will not have axial impact, and also helps to reduce the volume of the booster fan 10.

[0290] For example, the third gap c1 can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0291] In some embodiments, such as Figure 18 As shown, along the axial direction of the second hub 21, a fourth gap c2 is provided between the reinforcing structure 311 and the second blade crown 23, which can prevent the second impeller 2 from axially moving and causing the second blade crown 23 to collide with the impeller housing 3a.

[0292] In some embodiments, the value of the fourth gap c2 is in the range of 3mm to 8mm, which ensures that the second blade crown 23 and the impeller housing 3a will not have axial impact, and also helps to reduce the volume of the booster fan 10.

[0293] For example, the fourth gap c2 can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0294] It should be noted that the values ​​of the third gap c1 between the reinforcing structure 311 and the first impeller 1 and the fourth gap c2 between the reinforcing structure 311 and the second impeller 2 along the axial direction of the first hub 11 can be equal or unequal, and are not limited here.

[0295] In some embodiments, the inner diameter of the first blade crown 13 on the air outlet side of the first impeller 1 is equal to the inner diameter of the impeller housing 3a at the location where the reinforcing structure 311 is provided.

[0296] In some embodiments, the inner diameter of the second blade crown 23 on the air inlet side of the second impeller 2 is equal to the inner diameter of the impeller housing 3a at the location where the reinforcing structure 311 is provided.

[0297] This configuration ensures that the first blade crown 13 can isolate the airflow on the pressure surface and suction surface of the first blade 12, and the second blade crown 23 can isolate the airflow on the pressure surface and suction surface of the second blade 22, without affecting the axial flow of the airflow.

[0298] In some embodiments, along the axial direction of the first hub 11, the length of the first blade crown 13 is not less than the length of the tip of the first blade 12, and the length of the first blade crown 13 is not greater than the length of the first hub 11.

[0299] For ease of understanding, such as Figure 19 As shown, the length of the first leaf crown 13 is denoted as d, the length of the tip of the first blade 12 is denoted as e, and the length of the first hub 11 is denoted as f, where e≤d≤f.

[0300] In some embodiments, along the axial direction of the second hub 21, the length of the second blade crown 23 is not less than the length of the blade tip of the second blade 22, and the length of the second blade crown 23 is not greater than the length of the second hub 21.

[0301] It should be noted that the lengths of the first blade crown 13 and the second blade crown 23 along the axial direction of the first hub 11 can be equal or unequal, and no limitation is made here.

[0302] For example, in a specific embodiment of the present invention, the first gap a1 is 1 mm. The thickness b1 of the first blade crown 13 is 1 mm. The third gap c1 is 5.5 mm. The second gap a2 is 1 mm. The thickness b2 of the second blade crown 23 is 1 mm. The fourth gap c2 is 5.5 mm. Along the axial direction of the first hub 11, the length of the first blade crown 13 is 26 mm. Along the axial direction of the second hub 21, the length of the second blade crown 23 is 21 mm. This configuration improves the structural strength of the first impeller 1 and the second impeller 2, as well as the smoothness of the axial flow of airflow, and also enhances the noise reduction effect.

[0303] It should be noted that, whether along the axial direction or the circumferential direction of the first hub 11, the first blade crown 13 can completely cover the multiple first blades 12, thereby completely isolating the airflow on the pressure surface and suction surface of the first blades 12. Similarly, the second blade crown 23 can completely cover the multiple second blades 22, thereby completely isolating the airflow on the pressure surface and suction surface of the second blades 22, resulting in better noise reduction.

[0304] In some embodiments, such as Figure 17 As shown, along the axial direction of the first hub 11, the variation law of the outer diameter of the first blade crown 13 is the same as the variation law of the inner diameter of the impeller housing 3a corresponding to the first blade crown 13.

[0305] In some embodiments, such as Figure 18 As shown, along the axial direction of the second hub 21, the variation law of the outer diameter of the second blade crown 23 is the same as the variation law of the inner diameter of the impeller housing 3a corresponding to the second blade crown 23.

[0306] It should be noted that the shape of the outer peripheral surface of the first blade crown 13 is the same as the shape of the inner wall of the impeller housing 3a corresponding to the first blade crown 13, and the shape of the outer peripheral surface of the second blade crown 23 is the same as the shape of the inner wall of the impeller housing 3a corresponding to the second blade crown 23, which is conducive to further improving the smoothness of the axial flow of air.

[0307] Specifically, when the inner walls of the impeller housing 3a corresponding to the first blade crown 13 and the inner walls of the impeller housing 3a corresponding to the second blade crown 23 are both cylindrical surfaces, the outer peripheral surfaces of the first blade crown 13 and the second blade crown 23 are also cylindrical surfaces; when the inner walls of the impeller housing 3a corresponding to the first blade crown 13 and the inner walls of the impeller housing 3a corresponding to the second blade crown 23 are both conical surfaces that gradually expand or contract from the first impeller 1 to the second impeller 2, the outer peripheral surfaces of the first blade crown 13 and the second blade crown 23 are also conical surfaces that gradually expand or contract from the first impeller 1 to the second impeller 2.

[0308] In some embodiments, such as Figure 22 as well as Figures 27 to 28 As shown, the series axial flow booster fan also includes a first air guide 5 corresponding to the first impeller 1. The first air guide 5 is located on the air outlet side of the first impeller 1. The first air guide 5 includes a third hub 51 and a plurality of first guide vanes 52. The third hub 51 is fixed in the mounting cavity 31. The plurality of first guide vanes 52 are arranged at intervals along the circumference of the third hub 51. The ends of the plurality of first guide vanes 52 that are radially away from the third hub 51 are all fixedly connected to the impeller housing 3a.

[0309] Because the rotation of the first impeller 1 imparts a certain degree of vortex to the airflow, the first air guide 5 can deflect the vortex-bearing airflow to the axial direction of the first hub 11, converting some of the dynamic pressure into static pressure, thus eliminating vortex and improving the pressurization effect. Simultaneously, the first drive component used to drive the rotation of the first impeller 1 can be installed on the third hub 51, so that the first guide vane 52 can support the third hub 51, improving the installation stability of the first drive component.

[0310] In some embodiments, such as Figure 22 as well as Figures 29 to 30 As shown, the series axial flow booster fan also includes a second air guide 6 corresponding to the second impeller 2. The second air guide 6 is located on the air outlet side of the second impeller 2. The second air guide 6 includes a fourth hub 61 and a plurality of second guide vanes 62. The fourth hub 61 is fixedly installed in the mounting cavity 31. The plurality of second guide vanes 62 are spaced apart on the fourth hub 61 along the circumference of the fourth hub 61. The ends of the plurality of second guide vanes 62 that are radially away from the fourth hub 61 are all fixedly connected to the impeller housing 3a.

[0311] Because the rotation of the second impeller 2 imparts a certain degree of vortex to the airflow, the aforementioned second air guide 6 can deflect the vortex-bearing airflow to the axial direction of the second hub 21, converting some of the dynamic pressure into static pressure, thus achieving devortexing and improving the pressurization effect. Simultaneously, the second drive component used to drive the rotation of the second impeller 2 is installed on the fourth hub 61, so that the second guide vane 62 provides support to the fourth hub 61, improving the installation stability of the second drive component.

[0312] Specifically, the air inlet side of the first air guide 5 is arranged opposite to the air outlet side of the first impeller 1, and the air inlet side of the second impeller 2 is arranged opposite to the air outlet side of the first air guide 5; the first air guide 5 is used to deflect the airflow generated by the first impeller 1 to the axial direction of the first impeller 1; the air inlet side of the second air guide 6 is arranged opposite to the air outlet side of the second impeller 2, and the air outlet side of the second air guide 6 faces the second opening 33; the second air guide 6 is used to deflect the airflow generated by the second impeller 2 to the axial direction of the second impeller 2.

[0313] It should be noted that the axis of the third hub 51 coincides with the axis of the first hub 11, and the axis of the fourth hub 61 coincides with the axis of the second hub 21. Since the axis of the second hub 21 coincides with the axis of the first hub 11, it means that the second hub 21, the third hub 51, and the fourth hub 61 are all coaxially set with the first hub 11.

[0314] The main sources of noise in a series axial flow booster fan are the interference between the airflow generated by the rotation of the first impeller 1 and the first air guide 5, and the noise generated by the interference between the airflow generated by the rotation of the second impeller 2 and the second air guide 6. In particular, the order noise is the most obvious and can easily form a very sharp sound, causing discomfort to the ears of drivers and passengers.

[0315] To address this issue, in embodiments of the present invention, a plurality of first guide vanes 52 are unevenly distributed along the circumference of the third hub 51, and a plurality of second guide vanes 62 are unevenly distributed along the circumference of the fourth hub 61.

[0316] The aforementioned first guide vane 52 and second guide vane 62 can effectively prevent the airflow generated by the rotation of the first impeller 1 and the second impeller 2 from continuously striking the first guide vane 52 and the second guide vane 62 at frequencies related to the rotational speed of the first impeller 1 (including frequencies several times the rotational speed of the first impeller 1) and frequencies related to the rotational speed of the second impeller 2 (including frequencies several times the rotational speed of the second impeller 2), thereby avoiding discomfort to the ears of the driver and passengers.

[0317] In some embodiments, the phase angle between two adjacent first guide vanes 52 ranges from 180° / n1 to 540° / n1, where n1 is the number of first guide vanes 52. The phase angle between two adjacent second guide vanes 62 ranges from 180° / n2 to 540° / n2, where n2 is the number of second guide vanes 62. This arrangement helps to further improve the noise reduction effect. Since both the first guide vanes 52 and the second guide vanes 62 are stationary structural components and do not rotate, the multiple first guide vanes 52 of the first air guide 5 can be arranged with a greater degree of non-uniformity compared to the multiple first blades 12 of the first impeller 1; similarly, the multiple second guide vanes 62 of the second air guide 6 can be arranged with a greater degree of non-uniformity compared to the multiple second blades 22 of the second impeller 2.

[0318] In some embodiments, the number of first guide vanes 52 is 9 to 15. Compared to the first blade 12, the first guide vanes 52 are smaller in size, so a larger number can be provided, which is beneficial to improving the support stability of the first guide vanes 52 for the first drive member.

[0319] In some embodiments, the number of second guide vanes 62 is 9 to 15. Compared to the second blade 22, the second guide vanes 62 are smaller in size, so a larger number can be provided, which is beneficial to improving the support stability of the second guide vanes 62 for the second drive member.

[0320] In some embodiments, the bending angle of the first guide vane 52 is in the range of 30° to 50°, and the bending angle of the first guide vane 52 gradually increases from the root to the tip of the first guide vane 52, thereby improving the despinning effect.

[0321] For example, the bending angle of the first guide vane 52 can be any value between 30° and 50°, such as 30°, 35°, 40°, 45° or 50°.

[0322] In some embodiments, the bending angle of the second guide vane 62 is in the range of 30° to 50°, and the bending angle of the second guide vane 62 gradually increases from the root to the tip, thereby improving the despinning effect.

[0323] For example, the bending angle of the second guide vane 62 can be any value between 30° and 50°, such as 30°, 35°, 40°, 45° or 50°.

[0324] In some embodiments, the geometric outlet angle of the first guide vane 52 is in the range of 80° to 100°, thereby improving the deswirl effect.

[0325] For example, the geometric outlet angle of the first guide vane 52 can be any value between 80° and 100°, such as 80°, 85°, 90°, 95° or 100°.

[0326] In some embodiments, the geometric outlet angle of the second guide vane 62 is in the range of 80° to 100°, thereby improving the deswirl effect.

[0327] For example, the geometric outlet angle of the second guide vane 62 can be any value between 80° and 100°, such as 80°, 85°, 90°, 95° or 100°.

[0328] In some embodiments, the plurality of first guide vanes 52 include a first preset guide vane and a plurality of second preset guide vanes. The second preset guide vanes located on both sides of the first preset guide vane are symmetrically arranged about the first preset guide vane, thereby better eliminating the order noise generated by the mutual interference between the first impeller 1 and the first air guide 5.

[0329] In some embodiments, the plurality of second guide vanes 62 include a third preset guide vane and a plurality of fourth preset guide vanes. The fourth preset guide vanes located on both sides of the third preset guide vane are symmetrically arranged about the third preset guide vane, thereby better eliminating the order noise generated by the mutual interference between the second impeller 2 and the second air guide 6.

[0330] It should be noted that in some other embodiments, the second preset guide vanes located on both sides of the first preset guide vane can be asymmetrically arranged with respect to the first preset guide vane, and the fourth preset guide vanes located on both sides of the third preset guide vane can also be asymmetrically arranged with respect to the first preset guide vane, which can also achieve the effect of noise reduction.

[0331] In some embodiments, the number of first guide vanes 52 is not equal to the number of second guide vanes 62, thereby avoiding the order noise derived from the mutual interference between the first impeller 1 and the first air guide 5, and the mutual interference between the second impeller 2 and the second air guide 6, so as to avoid the main order overlap of the first impeller 1 and the second impeller 2, which would lead to the amplification of noise at certain frequencies (such as 450Hz to 800Hz), and improve the noise reduction effect.

[0332] In a specific embodiment of the present invention, the number of first guide vanes 52 is 11, and the phase angle between two adjacent first guide vanes 52 ranges from 17.1° to 49.1° (i.e., 180° / 11 to 540° / 11). For example, the phase angle between two adjacent first guide vanes 52 is 36.5°, 35.3°, 33.3°, 31.1°, 29.4°, 28.8°, 29.4°, 31.1°, 33.3°, 35.3° and 36.5° respectively. The number of second guide vanes 62 is 13, and the phase angle between two adjacent second guide vanes 62 ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, the phase angles between two adjacent second guide vanes 62 are 35.1°, 33.4°, 30.4°, 26.8°, 23.3°, 20.9°, 20.0°, 20.9°, 23.3°, 26.8°, 30.4°, 33.4° and 35.1° respectively.

[0333] In some embodiments, the phase angle between two adjacent first guide vanes 52 is not equal to the phase angle between two adjacent second guide vanes 62, thereby making the uneven distribution of the multiple first guide vanes 52 of the first air guide 5 different from the uneven distribution of the multiple second guide vanes 62 of the second air guide 6, so as to further reduce the order noise derived from the mutual interference between the first impeller 1 and the first air guide 5, and the mutual interference between the second impeller 2 and the second air guide 6, and avoid the main order overlap of the first impeller 1 and the second impeller 2, which would lead to the amplification of noise at certain frequencies (such as 450Hz to 800Hz), and further improve the noise reduction effect.

[0334] It should be noted that in some other embodiments, the number of first guide vanes 52 can be equal to the number of second guide vanes 62. Furthermore, the phase angle between two adjacent first guide vanes 52 is not equal to the phase angle between two adjacent second guide vanes 62. When it is not possible to design the number of first guide vanes 52 and the number of second guide vanes 62 to be unequal, the phase angle between two adjacent first guide vanes 52 can be made unequal to the phase angle between two adjacent second guide vanes 62, thereby further reducing the order noise generated by the interference between the first impeller 1 and the first air guide 5, and the second impeller 2 and the second air guide 6, to achieve the purpose of noise reduction.

[0335] In a specific embodiment of the present invention, there are 13 first guide vanes 52, and the phase angle between two adjacent first guide vanes 52 ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, the phase angles between two adjacent first guide vanes 52 are 31.4°, 30.6°, 29.1°, 27.2°, 25.5°, 24.3°, 23.9°, 24.3°, 25.5°, 27.2°, 29.1°, 30.6°, and 31.4° respectively. There are also 13 second guide vanes 62, and the phase angle between two adjacent second guide vanes 62 ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, the phase angles between two adjacent second guide vanes 62 are 35.1°, 33.4°, 30.4°, 26.8°, 23.3°, 20.9°, 20.0°, 20.9°, 23.3°, 26.8°, 30.4°, 33.4° and 35.1° respectively.

[0336] In some embodiments, in two adjacent first guide vanes 52, the projection of the leading edge of one first guide vane 52 onto a preset plane does not intersect with the trailing edge of the other first guide vane 52, thereby improving the convenience of industrial mold making.

[0337] In some embodiments, in two adjacent second guide vanes 62, the projection of the leading edge of one second guide vane 62 onto a preset plane does not intersect with the trailing edge of the other second guide vane 62, thereby improving the convenience of industrial mold making.

[0338] In some embodiments, a fifth gap is provided between the first blade crown 13 and the first air guide 5 along the axial direction of the first hub 11, thereby preventing the first impeller 1 from axially moving and causing the first blade crown 13 and the first air guide 5 to collide axially.

[0339] In some embodiments, the fifth gap ranges from 3mm to 8mm, which ensures that the first blade crown 13 and the first air guide 5 will not have axial impact, while also helping to reduce the size of the booster fan 10.

[0340] For example, the fifth gap can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0341] In some embodiments, a sixth gap is provided between the second blade crown 23 and the second air guide 6 along the axial direction of the second hub 21, thereby preventing the second impeller 2 from axially moving and causing the second blade crown 23 to collide with the first air guide 5.

[0342] In some embodiments, the sixth gap ranges from 3mm to 8mm, which ensures that the first blade crown 13 and the first air guide 5 will not have axial impact, while also helping to reduce the size of the booster fan 10.

[0343] For example, the sixth gap can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0344] It should be noted that the values ​​of the fifth gap between the first blade crown 13 and the first air guide 5 and the sixth gap between the second blade crown 23 and the second air guide 6 along the axial direction of the first hub 11 can be the same or different, and are not limited here.

[0345] In some embodiments, such as Figure 22 As shown, the fan unit 101 also includes a cap 71 and a tail cone 72. The cap 71 is located at the end of the first impeller 1 away from the second impeller 2, and the tail cone 72 is located at the end of the second impeller 2 away from the first impeller 1. By providing the cap 71 and the tail cone 72, the noise generated by the airflow can be reduced.

[0346] Specifically, the cap 71 is fixedly connected to the first wheel hub 11, and the tail cone 72 is fixedly connected to the second wheel hub 21.

[0347] In some embodiments, such as Figure 20 As shown, the impeller housing 3a includes a first housing 3a1 and a second housing 3a2. The first housing 3a1 and the second housing 3a2 are detachably connected by a first locking member 3b1, such as a first bolt. The first impeller 1, the first air guide 5 and the first drive member are all located in the first housing 3a1, and the second impeller 2, the second air guide 6 and the second drive member are all located in the second housing 3a2, thereby improving the convenience of assembly.

[0348] It should be noted that when there are multiple fan units 101, the first housings 3a1 of the multiple fan units 101 can be fixedly connected or integrally formed into a first integrated housing, and the second housings 3a2 of the multiple fan units 101 can be fixedly connected or integrally formed into a second integrated housing, thereby reducing the mold opening cost and simplifying the assembly.

[0349] In some embodiments, such as Figure 21 As shown, the booster fan 10 also includes a fan housing 3c. The first housing 3a1 and the second housing 3a2 are both fixed inside the fan housing 3c. A vibration damping structure 3d is provided between the first housing 3a1 and the fan housing 3c, and between the second housing 3a2 and the fan housing 3c, in order to achieve the purpose of vibration reduction and noise reduction.

[0350] For example, the fan housing 3c includes a first housing portion 3c1 and a second housing portion 3c2. The first housing portion 3c1 and the second housing portion 3c2 are detachably connected by a second locking member 3b2 such as a second bolt, which facilitates the assembly of the booster fan 10.

[0351] Specifically, the first shell portion 3c1 and the second shell portion 3c2 are arranged opposite each other along the radial direction of the first hub 11. Of course, the first shell portion 3c1 and the second shell portion 3c2 can also be arranged opposite each other along the axial direction of the first hub 11.

[0352] The booster fan 10 in this embodiment, while meeting the air volume and air pressure requirements, has the advantages of low total noise, low order noise, and friendly sound quality. It has a high NVH level and can solve the problems of large size and difficult layout of existing booster fans. In this way, it can greatly free up the storage space in the vehicle, improve the usability of the product in the vehicle, realize the miniaturization of the booster fan 10, and bring greater improvement to the vehicle product competitiveness.

[0353] Example 4

[0354] like Figures 31 to 33 As shown, embodiments of the present invention also provide an air conditioning system, a thermal management system, and a vehicle. The vehicle includes a cabin and a thermal management system. The thermal management system includes an air conditioning system for supplying air to the space inside the cabin.

[0355] The air conditioning system includes an air conditioning unit 20 and any of the above-mentioned booster fans 10 (for example, the booster fan 10 can be a counter-rotating axial flow booster fan or a series axial flow booster fan according to the above embodiments of the present invention). The air conditioning unit 20 includes an air conditioning outlet 201 (specifically, it can be a front-blowing air outlet, such as a rear-blowing air outlet). The booster fan 10 is located at the air conditioning outlet 201. The air inlet of the booster fan 10 is connected to the air conditioning outlet 201 so that the booster fan 10 draws air from the air conditioning outlet 201 and pressurizes it.

[0356] It should be noted that traditional automotive air conditioning units and booster fans 10 are set up independently, and traditional booster fans 10 are relatively large in size, making it difficult to integrate them behind the air conditioning outlet 201 of the automotive air conditioning unit, and requiring a large amount of installation space.

[0357] The thermal management system in this embodiment integrates the booster fan 10 with the air conditioning outlet 201 of the air conditioning unit 20, which can significantly reduce the space occupied by the air conditioning system while ensuring that the air volume and air pressure provided by the air conditioning system meet the requirements, thus achieving a compact design of the air conditioning system.

[0358] In this embodiment, the air outlet of the booster fan 10 is connected to the vehicle cabin, thereby enabling the booster fan 10 to adjust the air volume and speed delivered into the vehicle cabin while significantly reducing the space required for the air conditioning system.

[0359] The air conditioning system, thermal management system, and vehicle of the present invention, by applying the above-mentioned booster fan 10, can achieve a compact design of the thermal management system, while matching the NVH requirements of the vehicle, enhancing the usability of the compact thermal management system in the vehicle, and improving the product competitiveness of the vehicle.

[0360] When the booster fan 10 includes multiple fan units 101, the multiple fan units 101 are arranged along the air outlet direction perpendicular to the air outlet 201.

[0361] Specifically, such as Figure 31 and Figure 32 As shown, the air outlet of the booster fan 10 can be directly connected to the vehicle cabin, or it can be connected via a connecting pipe 301. Of course, one or more connecting pipes 301 can be provided; in other words, each connecting pipe 301 corresponds to one of the fan units 101. Specifically, the connecting pipe 301 connects the air outlet (i.e., the aforementioned second opening 33) of the corresponding fan unit 101 to the vehicle cabin. The air inlet of the booster fan 10 can be directly connected to the air conditioning outlet 201, or it can be connected via a transition pipe 302, thus adapting to different layout spaces and increasing its versatility. Furthermore, the booster fan 10 is connected to the air conditioning outlet 201 via a connecting structure.

[0362] For example, the connection structure can be a plug-in structure or a snap-fit ​​structure.

[0363] Specifically, the connection structure includes a first connecting part located at the air inlet of the booster fan and a second connecting part located at the air outlet of the air conditioner. The first connecting part and the second connecting part are plugged in or snapped together. For example, one end of the air inlet of the booster fan 10 is provided with a buckle, and the air outlet 201 is provided with a slot. The buckle and the slot are snapped together to connect the booster fan 10 and the air outlet 201.

[0364] In some embodiments, a sealing element, such as foam, is provided between the air inlet of the booster fan 10 and the air outlet 201 of the air conditioner to improve the sealing performance between the air inlet of the booster fan 10 and the air outlet 201 of the air conditioner.

[0365] In specific embodiments of the present invention, such as Figure 33As shown, there are two fan units 101, referred to as the first fan unit and the second fan unit. The first fan unit is connected to the left side of the vehicle cabin to supply air to the left side of the cabin, and the second fan unit is connected to the right side of the vehicle cabin to supply air to the right side of the cabin. For example, a connecting pipe 301 connects the first fan unit to the left side of the cabin, and another connecting pipe 301 connects the second fan unit to the right side of the cabin. By adjusting the speeds of the first and second motors corresponding to the left side, the airflow speed and volume in the left side can be adjusted; similarly, by adjusting the speeds of the first and second motors corresponding to the right side, the airflow speed and volume in the right side can be adjusted, achieving independent zoned airflow control. Alternatively, both the first and second motors corresponding to the left side can be stopped, thus supplying air only to the right side; conversely, both the first and second motors corresponding to the right side can be stopped, thus supplying air only to the left side.

[0366] Furthermore, the above description is merely a preferred embodiment of the present invention and the technical principles employed. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein, and various obvious changes, readjustments, and substitutions can be made without departing from the scope of protection of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments, and may include many other equivalent embodiments without departing from the concept of the present invention, the scope of which is determined by the scope of the appended claims.

Claims

1. A fan unit characterized by, Comprising: a first impeller comprising a first hub and a plurality of first blades, the plurality of first blades being arranged along a circumference of the first hub; a first phase angle a being arranged between a hub root and a hub top of a trailing edge y1 of the first blade in a rotation direction of the first impeller and being positive in the rotation direction of the first impeller; a second impeller, an air inlet side of the second impeller being arranged opposite to an air outlet side of the first impeller; the second impeller comprising a second hub and a plurality of second blades, the plurality of second blades being arranged along a circumference of the second hub; a second phase angle β being arranged between a hub root and a hub top of a leading edge x2 of the second blade in a rotation direction of the second impeller and being positive in the rotation direction of the second impeller; a value range of a+β being 50%*360° / N1~150%*360° / N1; N1 being a number of the first blades.

2. The fan unit according to claim 1, characterized in that The rotation directions of the first impeller and the second impeller are opposite.

3. The fan unit of claim 1, wherein, α≥20°; and / or, β≥20°.

4. The fan unit of claim 1, wherein The first impeller comprises nine first blades, α=20°, and β=21°.

5. The fan unit of claim 1, wherein The plurality of first blades are unevenly distributed along the circumference of the first hub; and / or, The plurality of second blades are unevenly distributed along the circumference of the second hub.

6. The fan unit of claim 1, wherein The plurality of first blades comprise a first preset blade and a plurality of second preset blades, the second preset blades on both sides of the first preset blade being symmetrically arranged about the first preset blade; and / or, The plurality of second blades comprise a third preset blade and a plurality of fourth preset blades, the fourth preset blades on both sides of the third preset blade being symmetrically arranged about the third preset blade. The fan unit further comprises an impeller shell, the first impeller and the second impeller are rotatably arranged in a mounting cavity of the impeller shell; the impeller shell comprises a first opening and a second opening, both of which are in communication with the mounting cavity, the first opening and the second opening are sequentially arranged along an axial direction of the first hub; an air inlet side of the first impeller faces the first opening, and an air outlet side of the second impeller faces the second opening.

7. The fan unit according to any one of claims 1-6, characterized in that The first impeller further comprises a first shroud, the first shroud is annular, the first shroud is sleeved on an outer side of the plurality of first blades, and an end of the plurality of first blades away from the first hub in a radial direction of the first hub is connected with the first shroud; and / or, 8. The fan unit according to any one of claims 1-6, characterized in that The second impeller further comprises a second shroud, the second shroud is annular, the second shroud is sleeved on an outer side of the plurality of second blades, and an end of the plurality of second blades away from the second hub in a radial direction of the second hub is connected with the second shroud. The fan unit further comprises a first air guide corresponding to the first impeller, the first air guide comprises a third hub and a plurality of first vanes, the third hub is fixedly arranged on an air outlet side of the first impeller, and the plurality of first vanes are arranged along a circumference of the third hub; and / or, 9. The fan unit according to any one of claims 1-6, characterized in that ​ The fan unit further comprises a second air guide corresponding to the second impeller, the second air guide comprising a fourth hub and a plurality of second guide vanes, the fourth hub being fixedly arranged at an air outlet side of the second impeller, and the plurality of second guide vanes being arranged at the fourth hub in a circumferential direction of the fourth hub.

10. The fan unit of claim 9, wherein, The plurality of first guide vanes are unevenly distributed along the circumferential direction of the third hub; and / or, The plurality of second guide vanes are unevenly distributed along the circumferential direction of the fourth hub.

11. A forced air fan characterized by, The air conditioning system comprises the fan unit as claimed in any one of claims 1-10.

12. The supercharger of claim 11, wherein, A plurality of the fan units are arranged in a direction perpendicular to the first hub.

13. An air conditioning system characterised by The supercharging fan comprises the fan unit as claimed in any one of claims 11-12.

14. A thermal management system characterized by, The supercharging fan comprises the fan unit as claimed in any one of claims 11-12 or the air conditioning system as claimed in claim 13.

15. Vehicle, characterized in that The air conditioning system comprises the air conditioning system as claimed in claim 13 or the thermal management system as claimed in claim 14.

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