Impeller, fan unit, booster fan, air conditioning system, thermal management system and vehicle

Abstract

The invention relates to the technical field of fans, and discloses an impeller, a fan unit, a booster fan, an air conditioning system, a heat management system and a vehicle. According to the impeller, a plurality of blades are unevenly distributed in the circumferential direction of an impeller hub, and the value of the phase included angle between every two adjacent blades is limited; therefore, on the premise that it is guaranteed that the size of the impeller is small and the air volume is large, the total noise, especially the order noise, generated by rotation of the impeller can be effectively reduced, and the sound quality and the NVH level of the booster fan are improved. The fan unit, the booster fan, the air conditioning system, the heat management system and the vehicle all comprise the impeller, the total noise, especially the order noise, generated by rotation of the impeller can be effectively reduced, and the sound quality and the NVH level of the booster fan are improved.

Description

Technical Field

[0001] The present invention relates to the technical field of fans, and in particular to an impeller, a fan unit, a booster fan, an air-conditioning system, a thermal management system and a vehicle. Background Art

[0002] Conventional automotive boost fans typically utilize a centrifugal design, resulting in large dimensions, significant space occupation, and inflexible placement, impacting both automakers and consumers. In terms of boosting capacity, centrifugal boost fans offer a simpler structure and higher boosting capabilities, making them the preferred choice for ducted boosting, provided space is not a concern.

[0003] Considering the current crowded component layout within vehicles, miniaturized booster fans have a broader market demand. Axial-flow impellers, with their axial inlet and outlet characteristics, fit directly into the air duct, avoiding significant airflow deflection, making them the optimal choice for miniaturized booster fans. Axial-flow impellers offer high air volume and low pressure, but their relatively small number of blades and high rotational speed often produce significant order noise, resulting in poor sound quality and severely limiting their application scenarios. Summary of the Invention

[0004] The object of the present invention is to propose an impeller, a fan unit, a booster fan, an air-conditioning system, a thermal management system and a vehicle, which can effectively reduce the total noise generated by the rotation of the impeller, especially the order noise, and improve the sound quality and NVH level of the booster fan.

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

[0006] Impeller, including:

[0007] impeller hub;

[0008] Multiple blades are arranged on the impeller hub at intervals along the circumference of the impeller hub, and the multiple blades are unevenly distributed along the circumference of the impeller hub; the phase angle between two adjacent blades ranges from 288° / N to 432° / N, where N is the number of blades.

[0009] As a preferred technical solution of the above-mentioned impeller, the plurality of blades include a first preset blade and a plurality of second preset blades, and the second preset blades located on both sides of the first preset blade are symmetrically arranged with respect to the first preset blade.

[0010] As a preferred technical solution of the above impeller, among two adjacent blades, the projection of the leading edge x1 of one blade on the preset plane does not intersect with the trailing edge y1 of the other blade;

[0011] The preset plane is perpendicular to the axial direction of the impeller hub.

[0012] As a preferred technical solution of the above-mentioned impeller, the number of the blades is 5 to 11.

[0013] As a preferred technical solution for the above-mentioned impeller, it also includes a blade crown, which is annular and is sleeved on the outside of the multiple blades. The ends of the multiple blades radially away from the impeller hub are fixedly connected to the blade crown.

[0014] In order to achieve the above object, the present invention further provides a fan unit, comprising:

[0015] an impeller housing, the impeller housing including a mounting cavity;

[0016] In the impeller as described in any of the above items, the impeller hub is rotatably disposed in the mounting cavity.

[0017] As a preferred technical solution for the fan unit, the impeller housing further includes a first opening and a second opening both communicating with the mounting cavity; the first opening and the second opening are sequentially arranged along the axial direction of the impeller hub.

[0018] As a preferred technical solution for the fan unit, a plurality of impellers are provided, and the plurality of impellers are arranged in sequence along the axial direction of the impeller hub.

[0019] As an optimal technical solution for the fan unit, the multiple impellers include a first impeller and a second impeller, the air inlet side of the first impeller faces the first opening, the air inlet side of the second impeller is arranged opposite to the air outlet side of the first impeller, and the air outlet side of the second impeller faces the second opening.

[0020] As a preferred technical solution of the fan unit, the blades of the first impeller are first blades, and the blades of the second impeller are second blades;

[0021] Along the rotation direction of the first impeller and with the rotation direction of the first impeller as a positive value, a first phase angle α is provided between the blade root and the blade tip of the trailing edge y1 of the first blade of the first impeller; and / or,

[0022] Along the rotation direction of the second impeller and taking the rotation direction of the second impeller as a 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 of the second impeller.

[0023] As a preferred technical solution of the fan unit, the blades of the first impeller are first blades, and the blades of the second impeller are second blades;

[0024] The number of the first blades of the first impeller is 9, and along the circumference of the first impeller, the phase angles between the first blades of two adjacent first impellers are 43.9°, 34.7°, 39.3°, 44.2°, 35.9°, 44.2°, 39.3°, 34.7° and 43.9° respectively; and / or,

[0025] The number of the second blades of the second impeller is 7. Along the circumference of the second impeller, the phase angles between the second blades of two adjacent second impellers are 50.4°, 52.4°, 53.7°, 47.1°, 53.7°, 52.4° and 50.4° respectively.

[0026] As a preferred technical solution of the fan unit, the first impeller and the second impeller rotate in opposite directions. As a preferred technical solution of the fan unit, the blades of the first impeller are first blades, and the blades of the second impeller are second blades;

[0027] The number of the first blades of the first impeller is not equal to the number of the second blades of the second impeller, and the numbers of the blades are both odd numbers.

[0028] As an optimal technical solution for the fan unit, the fan unit also includes an air guide member arranged corresponding to the impeller, and the air inlet side of the air guide member is arranged opposite to the air outlet side of the corresponding impeller; the air guide member includes an air guide hub and a plurality of guide vanes, and the air guide hub is fixed in the installation cavity; the plurality of guide vanes are arranged on the air guide hub at circumferential intervals along the air guide hub.

[0029] As a preferred technical solution of the fan unit, the plurality of guide vanes are unevenly distributed along the circumference of the guide hub.

[0030] As a preferred technical solution for the fan unit, ends of the plurality of guide vanes radially away from the guide hub are all fixedly connected to the impeller housing.

[0031] As a preferred technical solution of the fan unit, the plurality of guide vanes include a first preset guide vane and a plurality of second preset guide vanes, and the second preset guide vanes located on both sides of the first preset guide vane are symmetrically arranged with respect to the first preset guide vane.

[0032] In order to achieve the above object, the present invention further provides a booster fan, comprising a fan unit as described in any one of the above items.

[0033] As a preferred technical solution for the booster fan, a plurality of the fan units are provided, and the plurality of the fan units are arranged in a direction perpendicular to the impeller hub.

[0034] In order to achieve the above object, the present invention further provides an air conditioning system, comprising the booster fan as described in any one of the above items.

[0035] In order to achieve the above object, the present invention further provides a thermal management system, comprising the booster fan as described in any one of the above items or the air conditioning system as described above.

[0036] In order to achieve the above object, the present invention also provides a vehicle, comprising the above thermal management system or the above air conditioning system.

[0037] The present invention has at least the following beneficial effects:

[0038] The impeller provided by the present invention distributes multiple blades unevenly along the circumference of the impeller hub and limits the value of the phase angle between two adjacent blades. As a result, while ensuring a small impeller size and a large air volume, the total noise generated by the impeller rotation, especially the order noise, can be effectively reduced, thereby improving the sound quality and NVH level of the booster fan.

[0039] The fan unit, booster fan, air-conditioning system, thermal management system and vehicle provided by the present invention all include the above-mentioned impeller, which can effectively reduce the total noise generated by the impeller rotation, especially the order noise, and improve the sound quality and NVH level of the booster fan. BRIEF DESCRIPTION OF THE DRAWINGS

[0040] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following briefly introduces the drawings required for use in describing the embodiments of the present invention. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the contents of the embodiments of the present invention and these drawings without any creative work.

[0041] Figure 1a A first structural schematic diagram of an impeller provided in an embodiment of the present invention;

[0042] Figure 1b A second structural schematic diagram of an impeller provided in an embodiment of the present invention;

[0043] Figure 1c A third structural schematic diagram of an impeller provided in an embodiment of the present invention;

[0044] Figure 1d A fourth structural schematic diagram of an impeller provided in an embodiment of the present invention;

[0045] Figure 2 A schematic structural diagram of a blade crown and an impeller housing provided in an embodiment of the present invention;

[0046] Figure 3 A first structural schematic diagram of a booster fan provided in an embodiment of the present invention;

[0047] Figure 4a A first structural schematic diagram of an air guide member provided in an embodiment of the present invention;

[0048] Figure 4b A second structural schematic diagram of the air guide member provided in an embodiment of the present invention;

[0049] Figure 5a A second structural schematic diagram of a booster fan provided in an embodiment of the present invention;

[0050] Figure 5b A second structural schematic diagram of a booster fan provided in an embodiment of the present invention;

[0051] Figure 5c A third structural schematic diagram of the booster fan provided in an embodiment of the present invention;

[0052] Figure 6 A schematic structural diagram of a first impeller provided in an embodiment of the present invention;

[0053] Figure 7 A schematic structural diagram of a second impeller provided in an embodiment of the present invention;

[0054] Figure 8 A schematic structural diagram of a first blade and a second blade provided in an embodiment of the present invention;

[0055] Figure 9 A cross-sectional view of an axial-flow booster fan provided by an embodiment of the present invention;

[0056] Figure 10 A first partial cross-sectional view of an axial-flow booster fan provided by an embodiment of the present invention;

[0057] Figure 11 A first structural schematic diagram of a first impeller of an axial-flow booster fan provided in an embodiment of the present invention;

[0058] Figure 12 A first structural schematic diagram of a second impeller of an axial-flow booster fan provided in an embodiment of the present invention;

[0059] Figure 13 A schematic structural diagram of a fan unit of an axial-flow booster fan provided in an embodiment of the present invention;

[0060] Figure 14 A second structural schematic diagram of the first impeller of the axial-flow booster fan provided in an embodiment of the present invention;

[0061] Figure 15 A second structural schematic diagram of a second impeller of the axial-flow booster fan provided in an embodiment of the present invention;

[0062] Figure 16 A schematic structural diagram of a first blade and a second blade of an axial-flow booster fan provided in an embodiment of the present invention;

[0063] Figure 17 A second partial cross-sectional view of the axial-flow booster fan provided by an embodiment of the present invention;

[0064] Figure 18 A third partial cross-sectional view of the axial-flow booster fan provided by an embodiment of the present invention;

[0065] Figure 19 A third structural schematic diagram of the first impeller of the axial-flow booster fan provided in an embodiment of the present invention;

[0066] Figure 20 A schematic structural diagram of an axial-flow booster fan (excluding the fan housing) provided in an embodiment of the present invention;

[0067] Figure 21 A schematic structural diagram of an axial-flow booster fan (including a fan housing) provided in an embodiment of the present invention;

[0068] Figure 22 A schematic structural diagram of an axial-flow booster fan provided in an embodiment of the present invention;

[0069] Figure 23 A schematic diagram of a fourth structure of a first impeller of an axial-flow booster fan provided by an embodiment of the present invention;

[0070] Figure 24 A schematic diagram of a fifth structure of the first impeller of the axial-flow booster fan provided by an embodiment of the present invention;

[0071] Figure 25 A schematic diagram of a third structure of the second impeller of the axial-flow booster fan provided by an embodiment of the present invention;

[0072] Figure 26 A schematic diagram of a fourth structure of a second impeller of an axial-flow booster fan provided by an embodiment of the present invention;

[0073] Figure 27 A schematic diagram of a first structure of a first air guide member of an axial-flow booster fan provided by an embodiment of the present invention;

[0074] Figure 28 A schematic diagram of a second structure of a first air guide member of an axial-flow booster fan provided in an embodiment of the present invention;

[0075] Figure 29 A schematic diagram of a first structure of a second air guide member of an axial-flow booster fan provided by an embodiment of the present invention;

[0076] Figure 30A schematic diagram of a second structure of a second air guide member of an axial-flow booster fan provided by an embodiment of the present invention;

[0077] Figure 31 A schematic structural diagram of a first thermal management system provided by an embodiment of the present invention;

[0078] Figure 32 A schematic structural diagram of a second thermal management system provided by an embodiment of the present invention;

[0079] Figure 33 A cross-sectional view of a thermal management system provided by an embodiment of the present invention.

[0080] Figures 1a to 8 middle:

[0081] 10. Booster fan; 101. Fan unit;

[0082] 1′, impeller; 1a′, first impeller; 1b′, second impeller; 11′, impeller hub; 12′, blades; 13′, blade crown;

[0083] 3a, impeller housing; 31, mounting cavity; 311, reinforcement structure; 32, first opening; 33, second opening;

[0084] 5′, air guide member; 5a′, first air guide member; 5b′, second air guide member; 51′, air guide hub; 52′, guide vane.

[0085] Figures 9 to 33 middle:

[0086] 10. Booster fan; 101. Fan unit;

[0087] 1. First impeller; 11. First hub; 12. First blade; 13. First blade crown;

[0088] 2. Second impeller; 21. Second hub; 22. Second blade; 23. Second blade crown;

[0089] 3a, impeller housing; 31, mounting cavity; 311, reinforcement structure; 312, support structure; 32, first opening; 33, second opening; 3a1, first housing; 3a2, second housing; 3b1, first locking member; 3b2, second locking member; 3c, fan housing; 3c1, first housing portion; 3c2, second housing portion; 3d, vibration damping structure;

[0090] 41. First driving member; 42. Second driving member;

[0091] 5. First air guide; 51. Third hub; 52. First guide vane;

[0092] 6. Second air guide; 61. Fourth hub; 62. Second guide vane;

[0093] 71. hood; 72. coccyx;

[0094] 20. Air conditioning box; 201. Air conditioning outlet; 301. Connecting pipe; 302. Transition pipe. DETAILED DESCRIPTION

[0095] The present invention will be further described in detail below with reference to the accompanying drawings and examples. It will be understood that the specific embodiments described herein are intended only to illustrate the present invention and are not intended to limit the present invention. It should also be noted that, for ease of description, the accompanying drawings only illustrate portions relevant to the present invention, not all structures.

[0096] In the description of the present invention, unless otherwise expressly specified or limited, the terms "connected," "connected," and "fixed" should be understood in a broad sense. For example, they may refer to fixed connections, detachable connections, or integration; mechanical connections or electrical connections; direct connections or indirect connections through an intermediate medium; and internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention in specific circumstances.

[0097] In the present invention, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Furthermore, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly below or obliquely below the second feature, or may simply mean that the first feature is lower in level than the second feature.

[0098] In the description of this embodiment, the terms "upper," "lower," "right," and other orientations or positional relationships are based on the orientations or positional relationships shown in the accompanying drawings and are intended solely for ease of description and simplified operation. They do not indicate or imply that the devices or components referred to must have, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limitations on the present invention. Furthermore, the terms "first" and "second" are used solely for descriptive purposes and have no special meanings.

[0099] In this embodiment, the phase angle between two adjacent blades is the circumferential angle difference between the leading edge roots of the two adjacent blades. The phase angle between two adjacent guide vanes is the circumferential angle difference between the leading edge roots of the two adjacent guide vanes.

[0100] Example 1

[0101] like Figures 1a to 8 As shown, an embodiment of the present invention provides a blade crown, an air guide, an impeller, a fan unit and a booster fan, the booster fan 10 includes a fan unit 101, the fan unit 101 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 connected to the mounting cavity 31, the impeller 1′ is rotatably arranged 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′ faces the second opening 33.

[0102] like Figure 1a and Figure 1b As shown, the impeller 1′ includes an impeller hub 11′ and a plurality of blades 12′. The plurality of blades 12′ are arranged at intervals along the circumference of the impeller hub 11′, and the plurality of 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′.

[0103] The blades 12′ are arranged as described above. Under the premise of ensuring the dynamic balance and static balance of the booster fan 10, the total noise generated by the rotation of the impeller 1′ can be effectively reduced, and the problems of high-order noise, poor sound quality and low NVH level of the booster fan 10 can be solved. Under the premise of the booster fan 10 providing the required air volume and pressure, the requirements of low noise and good sound quality can be met at the same time.

[0104] Specifically, the first opening 32 and the second opening 33 are sequentially arranged along the axial direction of the impeller hub 11 ′.

[0105] In some embodiments, as Figure 1c As shown, the projection of the leading edge x1 of one of the two adjacent blades 12′ onto a predetermined plane does not intersect with the trailing edge y1 of the other blade 12′. The predetermined plane is perpendicular to the axial direction of the impeller hub 11′. This arrangement further improves the convenience of industrial mold making and the air volume and pressure performance of the booster fan.

[0106] In some embodiments, the plurality of blades 12 ′ includes 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 with respect to the first preset blade, which is conducive to better reducing order noise.

[0107] 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 while maintaining the air volume and pressure performance of the booster fan 10 .

[0108] The impeller 1' further comprises a blade crown 13' which is annular and sleeved on the outside of the plurality of blades 12'. The ends of the plurality of blades 12' away from the impeller hub 11' in the radial direction are fixedly connected to the blade crown 13'.

[0109] The multiple blades 12′ are wrapped by the blade crown 13′ to isolate the airflow on the pressure surface and suction surface of the top of the blade 12′, hinder the leakage of fluid on the pressure surface and suction surface of the top of the blade 12′, and thus no blade tip leakage flow is generated, avoiding the generation of a large vortex structure in the top area of ​​the blade 12′, thereby avoiding the vortex from causing noise, and eliminating the important cause of order noise, thereby achieving 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.

[0110] In some embodiments, along the axial direction of the impeller hub 11 ′, the variation pattern of the outer diameter of the blade crown 13 ′ is the same as the variation pattern of the inner diameter of the impeller housing 3 a corresponding to the blade crown 13 ′, so as to ensure smooth axial flow of the airflow.

[0111] Specifically, when the inner wall of the impeller housing 3a corresponding to the blade crown 13' is a cylindrical surface, the outer peripheral 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.

[0112] In some embodiments, as Figure 2 As shown, a first gap a is provided between the blade crown 13 ′ and the inner wall of the impeller housing 3 a , thereby preventing the radial runout of the impeller 1 ′ from causing friction and scratching between the blade crown 13 ′ and the inner wall of the impeller housing 3 a .

[0113] In some embodiments, the first gap a has a value ranging from 0.5 mm to 2 mm, which not only ensures that there is no friction or scratching between the blade crown 13 ′ and the inner wall of the impeller housing 3 a , but also helps to reduce the volume of the booster fan 10 .

[0114] Exemplarily, the first gap a may be any value between 0.5 mm and 2 mm, such as 0.5 mm, 1 mm, 1.5 mm or 2 mm.

[0115] In some embodiments, along the radial direction of the impeller hub 11 ′, the thickness b of the blade crown 13 ′ ranges from 0.5 mm to 1.5 mm, thereby ensuring the structural strength of the blade crown 13 ′ and enabling the blade crown 13 ′ to better isolate the airflow on the pressure side and the suction side of the blade 12 ′.

[0116] Illustratively, the thickness b of the blade shroud 13 ′ may be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0117] In some embodiments, along the axial direction of the impeller hub 11 ′, the length of the blade shroud 13 ′ is not less than the length of the blade tip of the blade 12 ′, and the length of the blade shroud 13 ′ is not greater than the length of the impeller hub 11 ′.

[0118] For ease of understanding, Figure 1d As shown, the length of the blade crown 13' along the axial direction of the impeller hub 11' is recorded as d, the length of the blade tip of the blade 12' is recorded as e, and the length of the impeller hub 11' is recorded as f, where e≤d≤f.

[0119] It should be noted that, whether along the axial direction of the impeller hub 11 ′ or along the circumferential direction of the impeller hub 11 ′, the blade crown 13 ′ can completely cover the multiple blades 12 ′, thereby enabling the blade crown 13 ′ to completely isolate the airflow on the pressure side and the suction side of the blade 12 ′, thereby achieving a better noise reduction effect.

[0120] In some embodiments, as Figure 2 As shown, the inner wall of the impeller housing 3a is provided with a reinforcement structure 311; along the axial direction of the impeller hub 11', a third gap c is provided between the blade crown 13' and the reinforcement structure 311, thereby preventing the axial movement of the impeller 1' and causing the blade crown 13' to collide axially with the impeller housing 3a, thereby ensuring the normal operation of the impeller 1'.

[0121] In some embodiments, the third gap c has a value ranging from 3 mm to 8 mm, which not only ensures that the blade crown 13 ′ and the impeller housing 3 a do not collide axially, but also helps to reduce the volume of the booster fan 10 .

[0122] Exemplarily, the third gap c may be any value between 3 mm and 8 mm, such as 3 mm, 4 mm, 5 mm, 6 mm, 7 mm or 8 mm.

[0123] In some embodiments, the reinforcement structure 311 is provided on the air outlet side of the impeller 1′, and 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 casing 3a where the reinforcement structure 311 is provided, which can ensure that the blade crown 13′ can isolate the airflow on the pressure side and the suction side of the blade 12′ without affecting the axial flow of the airflow.

[0124] In some other embodiments, the reinforcement structure 311 can also be provided on the air inlet side of the impeller 1′, and 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 casing 3a where the reinforcement structure 311 is provided, which can ensure that the blade crown 13′ can isolate the airflow on the pressure side and the suction side of the blade 12′ without affecting the axial flow of the airflow.

[0125] like Figure 3As shown, the fan unit 101 also includes an air guide 5′, which is fixed in the mounting cavity 31, with the air inlet side of the impeller 1′ facing the first opening 32, the air outlet side of the impeller 1′ being arranged opposite to the air inlet side of the air guide 5′, and the air outlet side of the air guide 5′ facing 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′.

[0126] 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 impeller 1 ′ from axially moving and causing an axial collision between the blade crown 13 ′ and the air guide 5 ′.

[0127] In some embodiments, the fifth gap is in the range of 3 mm to 8 mm, which ensures that the blade crown 13 ′ and the air guide 5 ′ do not collide axially and is also beneficial to reducing the volume of the booster fan 10.

[0128] Illustratively, the fifth gap may be any value between 3 mm and 8 mm, such as 3 mm, 4 mm, 5 mm, 6 mm, 7 mm or 8 mm.

[0129] like Figure 4a and Figure 4b As shown, the air guide member 5 ′ includes an air guide hub 51 ′ and a plurality of guide vanes 52 ′. The air guide hub 51 ′ is fixed in the installation cavity 31 , and the plurality of guide vanes 52 ′ are spaced apart on the air guide hub 51 ′ along the circumference of the air guide hub 51 ′.

[0130] Since the impeller 1′ rotates and does work, the airflow has a certain rotation. The above-mentioned air guide member 5′ can deflect the airflow with a certain rotation to the axial direction of the impeller hub 11′ of the impeller 1′, converting part of the dynamic pressure into static pressure, achieving de-rotation and improving the supercharging effect.

[0131] In this embodiment, the axis of the guide hub 51 ′ coincides with the axis of the impeller hub 11 ′ of the impeller 1 ′.

[0132] It should be noted that the noise generated by the interference of the airflow generated by the rotation of the impeller 1' and the air guide 5' is the main source of noise, especially the order noise is the most obvious, which can easily form a very sharp sound and cause discomfort to the ears of drivers and passengers.

[0133] 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 hitting the guide vanes 52′ at a frequency related to the rotation speed of the impeller 1′ (including a frequency several times the rotation speed of the impeller 1′) to generate some fixed-frequency noise, thereby avoiding causing discomfort to the ears of the driver and passengers.

[0134] 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 arrangement is beneficial for further improving the noise reduction effect.

[0135] It should be noted that, since the guide vanes 52 ′ are stationary structural components and do not rotate, the guide vanes 52 ′ of the air guide member 5 ′ can be arranged in a more uneven manner compared to the blades 12 ′ of the impeller 1 ′.

[0136] In some embodiments, the guide vanes 52′ are fixedly connected to the impeller housing 3a at one end radially away from the guide hub 51′. The guide hub 51′ can be supported and fixed by the guide vanes 52′, and the installation stability of the guide vanes 52′ can be improved. Not only is the structure simple, but the wind guiding effect and noise reduction effect can also be improved.

[0137] In some embodiments, the bending angle of the guide vane 52 ′ ranges from 30° to 50°, and the bending angle of the guide vane 52 ′ gradually increases from the blade root to the blade tip, thereby improving the deswirl effect.

[0138] For example, the bending angle of the guide vanes 52 ′ may be any value between 30° and 50°, such as 30°, 35°, 40°, 45° or 50°.

[0139] In some embodiments, the geometric outlet angle of the guide vane 52 ′ ranges from 80° to 100°, thereby improving the deswirl effect.

[0140] For example, the geometric outlet angle of the guide vane 52 ′ may be any value between 80° and 100°, such as 80°, 85°, 90°, 95° or 100°.

[0141] In some embodiments, the plurality of guide vanes 52 ′ includes a first preset guide vane and a plurality of second preset guide vanes, and the second preset guide vanes located on both sides of the first preset guide vane are symmetrically arranged with respect to the first preset guide vane.

[0142] The arrangement of the guide vanes 52 ′ can better eliminate the order noise generated by the interference between the impeller 1 ′ and the air guide member 5 ′.

[0143] It should be noted that, in some other embodiments, the second preset guide vanes located on both sides of the first preset guide vane may be arranged asymmetrically with respect to the first preset guide vane, which can also achieve the effect of noise reduction.

[0144] In some embodiments, the projection of the leading edge of one of the two adjacent guide vanes 52' on a predetermined plane does not intersect with the trailing edge of the other guide vane 52', thereby improving the convenience of industrial mold making. The predetermined plane is perpendicular to the axial direction of the third hub.

[0145] It should be noted that the driving member for driving the impeller 1 ′ to rotate may be installed on the air guide hub 51 ′, so that the guide vanes 52 ′ can support the air guide hub 51 ′ and improve the installation stability of the driving member.

[0146] In some embodiments, the number of the guide vanes 52 ′ is 9 to 15. Compared to the impeller 1 ′, the guide vanes 52 ′ are smaller in size, so more guide vanes 52 ′ can be provided, which is beneficial to improving the support stability of the guide vanes 52 ′ on the driving member.

[0147] In some embodiments, a plurality of impellers 1 ′ are provided, and the plurality of impellers 1 ′ are sequentially arranged along the axial direction of the impeller hub 11 ′.

[0148] In a specific embodiment of the present invention, Figure 5a and 5b As shown, there are two impellers 1'. For the convenience of description, the two impellers 1' are respectively recorded as a first impeller 1a' and a second impeller 1b'. The air inlet side of the second impeller 1b' is arranged opposite to the air outlet side of the first impeller 1a'.

[0149] It should be noted that if Figure 5a As shown, for the series axial booster fan, the first impeller 1a′ and the second impeller 1b′ have the same rotation direction. By arranging the first impeller 1a′ and the second impeller 1b′ in series, the air is combined and boosted, thereby achieving a higher boosting capacity.

[0150] Furthermore, the impellers 1′ and the air guides 5′ are provided in a one-to-one correspondence. In other words, the air guides 5′ are provided on the outlet side of the corresponding impeller 1′. The air guides 5′ can deflect the airflow generated by the corresponding impeller 1′ to the axial direction of the impeller hub 11′ of the impeller 1′ to ensure a supercharging effect. Specifically, two air guides 5′ are provided. For ease of description, the air guide 5′ corresponding to the first impeller 1a′ is referred to as the first air guide 5a′, and the air guide 5′ corresponding to the second impeller 1b′ is referred to as the second air guide 5b′.

[0151] In some embodiments, the number of the first guide vanes of the first air guide 5a' is not equal to the number of the second guide vanes of the second air guide 5b', thereby avoiding the first impeller 1a' and the first air guide 5a' from interfering with each other, and the order noise derived from the second impeller 1b' and the second air guide 5b' from interfering with each other, so as to avoid the main order overlap of the first impeller 1a' and the second impeller 1b' resulting in noise amplification of certain frequencies (such as 450Hz~800Hz), thereby improving the noise reduction effect. Preferably, the number of the first guide vanes of the first air guide 5a' is less than the number of the second guide vanes of the second air guide 5b', and the noise reduction effect is better.

[0152] In a specific embodiment of the present invention, the quantity of the first guide vane of the first air guide member 5a ' is 11, and in the first air guide member 5a ', the range of the phase angle between adjacent two first guide vanes is 17.1 °~49.1 ° (i.e. 180 ° / 11~540 ° / 11). Exemplarily, in the first air guide member 5a ', the range of the phase angle between adjacent two first guide vanes is 36.5 °, 35.3 °, 33.3 °, 31.1 °, 29.4 °, 28.8 °, 29.4 °, 31.1 °, 33.3 °, 35.3 ° and 36.5 °. The quantity of the second guide vane of the second air guide member 5b ' is 13, and in the second air guide member 5b ', the range of the phase angle between adjacent two second guide vanes is 13.8 °~41.5 ° (i.e. 180 ° / 13~540 ° / 13). Illustratively, 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.

[0153] In some embodiments, the phase angle between two adjacent first guide vanes of the first air guide 5a′ is not equal to the phase angle between two adjacent second guide vanes of the second air guide 5b′, thereby making the uneven distribution of multiple first guide vanes of the first air guide 5a′ and the uneven distribution of multiple second guide vanes of the second air guide 5b′ differentiated, so as to further reduce the mutual interference between the first impeller 1a′ and the first air guide 5a′, and the order noise derived from the mutual interference between the second impeller 1b′ and the second air guide 5b′, avoid the overlap of the main orders of the first impeller 1a′ and the second impeller 1b′, and cause the noise of certain frequencies (such as 450Hz~800Hz) to be amplified, thereby further improving the noise reduction effect.

[0154] It should be noted that, in other embodiments, the quantity of the first guide vanes of the first air guide member 5a′ and the quantity of the second guide vanes of the second air guide member 5b′ can also be equal, further, the phase angle between adjacent two first guide vanes of the first air guide member 5a′ and the phase angle between adjacent two second guide vanes of the second air guide member 5b′ are unequal. When the quantity of the first guide vanes of the first air guide member 5a′ and the quantity of the second guide vanes of the second air guide member 5b′ can't accomplish unequal designs, the phase angle between adjacent two first guide vanes of the first air guide member 5a′ and the phase angle between adjacent two second guide vanes of the second air guide member 5b′ can be unequal, and then the first impeller 1a′ and the first air guide member 5a′ are interfered with each other, and the order noise that the second impeller 1b′ and the second air guide member 5b′ interfere with each other is further reduced, to achieve the purpose of noise reduction.

[0155] In a specific embodiment of the present invention, the quantity of the first guide vane of the first air guide member 5a ' is 13, and the range of the phase angle between adjacent two first guide vanes of the first air guide member 5a ' is 13.8 ° ~ 41.5 ° (i.e. 180 ° / 13 ~ 540 ° / 13). Exemplarily, the phase angle between adjacent two first guide vanes of the first air guide member 5a ' is 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 quantity of the second guide vane of the second air guide member 5b ' is 13, and the range of the phase angle between adjacent two second guide vanes of the second air guide member 5b ' is 13.8 ° ~ 41.5 ° (i.e. 180 ° / 13 ~ 540 ° / 13). Exemplarily, the phase angles between two adjacent second guide vanes of the second air guide 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.

[0156] like Figure 5b As shown, for the counter-rotating axial flow booster fan, the rotation directions of the first impeller 1a′ and the second impeller 1b′ are opposite. When working, the first impeller 1a′ and the second impeller 1b′ rotate in opposite directions respectively, and perform combined boosting on the air, thereby achieving a higher boosting capacity.

[0157] In a specific embodiment of the present invention, the number of first blades of the first impeller 1a' is 9, and the phase angle between two adjacent first blades ranges from 32° to 48° (288° / 9 to 432° / 9). For example, 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 can satisfy that the first blades of the first impeller 1a' do not overlap with each other along the axial direction of the first impeller 1a'. Furthermore, the number of second blades of the second impeller 1b' is 7, and the phase angle between two adjacent second blades ranges from 41.1° to 61.7° (288° / 7 to 432° / 7). Exemplarily, 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 with each other along the axial direction of the second impeller 1b′.

[0158] In some embodiments, along the rotation direction of the impeller 1 ′ and with the rotation direction of the impeller 1 ′ as the positive value, a phase angle α is set between the root and the tip of the trailing edge y1 of the blade 12 ′. In other words, the blade 12 ′ adopts a curved angle design.

[0159] The above arrangement can temporally discretize the phenomenon that the pressure fluctuations generated by the wakes of the blades 12′ at different radial heights hit other structures of the downstream booster fan 10. In other words, the phenomenon that the pressure fluctuations generated by the wakes of the blades 12′ at different radial heights hit other structures of the downstream booster fan 10 can be distributed at different moments, thereby eliminating the pressure fluctuations, which can not only greatly reduce the order noise problem of the booster fan 10, but also slightly reduce the total noise of the booster fan 10.

[0160] In a specific embodiment of the present invention, 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 a positive value, a first phase angle α is provided between the blade root and the blade 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 a 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 of the second impeller 1b′.

[0161] With such an arrangement, the phenomenon in which the pressure fluctuation generated by the wake of the first blade of the first impeller 1a′ at different radial heights hits the leading edge x2 of the second blade of the second impeller 1b′ can be discretized in time. In other words, the phenomenon in which the pressure fluctuation generated by the wake of the first blade of the first impeller 1a′ at different radial heights hits the leading edge x2 of the second blade of the second impeller 1b′ can be distributed at different moments, thereby eliminating the pressure fluctuation, which can not only greatly reduce the order noise problem of the booster fan 10, but also slightly reduce the total noise of the booster fan 10.

[0162] In some embodiments, the value range of α+β is 50%*360° / N1 to 150%*360° / N1, with both α and β being no less than 20°. N1 is the number of first blades of the first impeller 1a′. When α+β is greater than 50%*360° / N1, when the wake 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 of the first impeller 1a′ and the second impeller 1b′, the impact at different radial heights is dispersed at different times, thereby avoiding noise amplification caused by simultaneous or short-term impacts, which in turn may form prominent order noise. α+β is less than 150%*360° / N1, which can avoid the difficulty of demolding due to excessive bending of the first blade of the first impeller 1a′ and the second blade of the second impeller 1b′. If α+β exceeds 360° / N1, the effect of improving the order noise by the angle shaping of the second blades of the first impeller 1a′ and the second impeller 1b′ will also be weakened. Therefore, there is no need to over-bend the second blades of the first impeller 1a′ and the second impeller 1b′.

[0163] In a specific embodiment of the present invention, the number of first blades of the first impeller 1a′ is 9, α is 20°, β is 21°, α+β=41°, which satisfies the range of 20°~60° (50%*360° / 9~150%*360° / 9).

[0164] In some embodiments, as Figure 5c As shown, multiple first impellers 1a' and second impellers 1b' are provided. A first impeller 1a' and a second impeller 1b', located opposite the 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 in a direction perpendicular to the axial direction of the impeller hub 11'. This arrangement allows the multiple fan units 101 to correspond to different areas within the vehicle cabin. Through the multiple fan units 101, the air volume and wind speed in different areas of the cabin can be independently adjusted, thereby improving the comfort of the driver and passengers.

[0165] 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.

[0166] The booster fan 10 of this embodiment, while meeting the requirements of air volume and air pressure, 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. It can thus greatly free up storage space in the vehicle, improve the usability of the product in the vehicle, and bring greater improvement in vehicle product strength.

[0167] Example 2

[0168] In the existing technology, axial-flow booster fans, due to their axial inlet and outlet airflow characteristics, can directly match the air duct and avoid large deflections of the airflow, making them the best choice for miniaturization of booster fans. Axial-flow booster fans have the characteristics of large air volume and low air pressure, but because they have a small number of blades and a relatively high rotational speed, when the impeller rotates, the wake of the blades or the related vortices generated by the blades will continuously hit the structure downstream of the impeller at a frequency related to the impeller's rotational speed or a frequency several times the impeller's rotational speed, generating certain fixed-frequency noises, especially order noise, which is the most obvious. This sound is easily distinguished by the human ear, resulting in a sense of discomfort in the sound, which in turn leads to poor sound quality of the axial-flow booster fan, seriously restricting its application scenarios.

[0169] To solve this problem, Figure 9 and Figure 10 As shown, an embodiment of the present invention further 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. The fan unit 101 includes a first impeller 1, a second impeller 2 and an impeller housing 3a.

[0170] The impeller housing 3a includes a mounting cavity 31 and a first opening 32 and a second opening 33, both communicating with the mounting cavity 31. The first impeller 1 and the second impeller 2 are both rotatably disposed within the mounting cavity 31, with the air inlet side of the first impeller 1 facing the first opening 32, and the air outlet side of the second impeller 2 facing 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.

[0171] The first impeller 1 rotates in opposite directions to the second impeller 2. During operation, the first blades 12 and the second impeller 2 rotate in opposite directions, respectively, to perform combined supercharging on the air, thereby achieving a higher supercharging capacity.

[0172] 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 on the first hub 11 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.

[0173] 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 on the second hub 21 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.

[0174] The first blade 12 and the second blade 22 adopt the above-mentioned arrangement, which can effectively reduce the total noise generated by the rotation of the first impeller 1 and the second impeller 2 while ensuring the dynamic balance and static balance of the axial flow booster fan, and at the same time solve the problems of high order noise, poor sound quality and low NVH level of the axial flow booster fan 10, so that the axial flow booster fan 10 can provide the required air volume and pressure while meeting the requirements of low noise and good sound quality.

[0175] In some embodiments, the booster fan 10 includes multiple fan units 101, which are arranged in a direction perpendicular to the axial direction of the first hub 11. This arrangement allows the multiple fan units 101 to correspond to different areas within the vehicle cabin, allowing the air volume and wind speed in different areas of the cabin to be independently adjusted, thereby improving the comfort of the driver and passengers.

[0176] In a specific embodiment of the present invention, Figure 13 As shown, two fan units 101 are provided. Of course, one, three, four, or even more fan units 101 can also be provided, which is not limited here.

[0177] 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.

[0178] In some embodiments, as Figure 9 As shown, the booster fan 10 also includes a first driving member 41 arranged in a one-to-one correspondence with the first impeller 1, and a second driving member 42 arranged in a one-to-one correspondence with the second impeller 2. The first driving member 41 is transmission-connected to the corresponding first impeller 1 to drive the corresponding first impeller 1 to rotate; the second driving member 42 is transmission-connected to the corresponding second blade 22 to drive the corresponding second impeller 2 to rotate.

[0179] Specifically, the first driving member 41 includes a first motor, and the second driving member 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. The rotational speeds of the first impeller 1 and the second impeller 2 are controlled by controlling the first motor and the second motor respectively.

[0180] Exemplarily, the output shaft of the first motor and the first hub 11 of the corresponding first impeller 1 , as well as the output shaft of the second motor and the second hub 21 of the corresponding second impeller 2 , are both connected via connecting flanges.

[0181] In other embodiments, the booster fan 10 includes a drive mechanism corresponding to each of the plurality of fan units 101, and the first impeller 1 and the second impeller 2 of the same fan unit 101 are driven to rotate by the drive mechanism. For example, the drive mechanism includes a drive member and a reversing assembly, the first impeller 1 is directly connected to the output shaft of the drive member, and the second impeller 2 is connected to the output shaft of the drive member via the reversing assembly, thereby causing the first impeller 1 and the second impeller 2 to rotate in opposite directions. Specifically, the drive member is a motor, and the reversing assembly is a gear set. Of course, the reversing assembly can also be other reversing structures known in the art, which are not limited here.

[0182] In some embodiments, the number of the first blades 12 is 5 to 11. By limiting the number of the first blades 12 as described above, the convenience of industrial mold opening can be ensured, and the air volume and pressure performance of the axial flow booster fan can be maintained.

[0183] In some embodiments, the number of the second blades 22 is 5 to 11. By limiting the number of the second blades 22 as described above, the convenience of industrial mold opening can be ensured, and the air volume and pressure performance of the axial flow booster fan can be maintained.

[0184] In some embodiments, as Figure 14 As shown, the projection of the leading edge x1 of one of the two adjacent first blades 12 onto a predetermined plane does not intersect with the trailing edge y1 of the other first blade 12. The predetermined plane is perpendicular to the axial direction of the first hub 11. This arrangement further improves the convenience of industrial mold making and the air volume and pressure performance of the axial flow booster fan.

[0185] In some embodiments, as Figure 15 As shown, the projection of the leading edge x2 of one of the two adjacent second blades 22 on the preset plane does not intersect with the trailing edge y2 of the other second blade 22. This arrangement can further improve the convenience of industrial mold opening and the air volume and pressure performance of the axial flow booster fan.

[0186] In some embodiments, the number of the first blades 12 and the number of the second blades 22 are not equal, which is beneficial to improving the order noise of the counter-rotating axial flow booster fan and avoiding the order noise generated by the airflow interference between the first impeller 1 and the second impeller 2.

[0187] In some embodiments, the number of first blades 12 is greater than the number of second blades 22 , which is beneficial to further improve the order noise of the counter-rotating axial flow booster fan and further avoid the order noise generated by airflow interference between the first impeller 1 and the second impeller 2 .

[0188] In some embodiments, the plurality of first blades 12 include a first preset blade and a plurality of second preset blades, and the second preset blades located on both sides of the first preset blade are symmetrically arranged with respect to the first preset blade, thereby facilitating better reduction of order noise.

[0189] In some embodiments, the plurality of second blades 22 include a third preset blade and a plurality of fourth preset blades, and the fourth preset blades located on both sides of the third preset blade are symmetrically arranged with respect to the third preset blade, thereby facilitating better reduction of order noise.

[0190] It should be noted that in some other embodiments, the second preset blades located on both sides of the first preset blade can be set asymmetrically, and the fourth preset blades located on both sides of the third preset blade can be set asymmetrically, which can also achieve the purpose of improving the noise reduction effect.

[0191] In a specific embodiment of the present invention, the number of first blades 12 is 9, 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. The number of second blades 22 is 7, 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.

[0192] In some embodiments, 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 a positive value, a first phase angle α is provided between the blade root and the blade tip of the trailing edge y1 of the first blade 12. In other words, the first blade 12 adopts a curved angle design.

[0193] 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 root and the tip of the leading edge x2 of the second blade 22. In other words, the second blade 22 adopts a curved angle design.

[0194] With such an arrangement, the phenomenon of the pressure fluctuation generated by the wake of the first blade 12 at different radial heights hitting the leading edge x2 of the second blade 22 can be discretized in time. In other words, the phenomenon of the pressure fluctuation generated by the wake of the first blade 12 at different radial heights hitting the leading edge x2 of the second blade 22 can be distributed at different times, thereby eliminating the pressure fluctuation, which can not only greatly reduce the order noise problem of the counter-rotating axial flow booster fan, but also slightly reduce the total noise of the counter-rotating axial flow booster fan.

[0195] In some embodiments, the value range of α+β is 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 can allow the first impeller 1 and the second impeller 2 to have collisions at different radial heights at different times when the wake of the first blade 12 interferes with the leading edge x2 of the second blade 22 during rotation, thereby avoiding noise amplification caused by collisions at the same time or in a short period of time, thereby forming convex order noise. When α+β is less than 150%*360° / N1, it can avoid the difficulty of demolding caused by excessive bending of the first blade 12 and the second blade 22, and if α+β exceeds 360° / N1, the effect of improving the order noise by the angle shaping of the first blade 12 and the second blade 22 will also be weakened, so there is no need to over-bend the first blade 12 and the second blade 22.

[0196] 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°, which can not only greatly reduce the order noise problem of the counter-rotating axial flow booster fan, but also facilitate the demolding of the first blade 12 and the second blade 22, thereby reducing the processing difficulty of the first blade 12 and the second blade 22.

[0197] In some embodiments, the first impeller 1 further includes a first blade crown 13, which is annular and sleeved on the outside of the plurality of first blades 12. The ends of the plurality of first blades 12 radially away from the first hub 11 are all fixedly connected to the first blade crown 13.

[0198] By wrapping the plurality of first blades 12 with the first blade crown 13 to isolate the airflow on the pressure side and the suction side at the top of the first blade 12, the airflow leakage on the pressure side and the suction side at the top of the first blade 12 can be prevented to generate a larger vortex, thereby preventing the vortex from causing noise, thereby achieving the purpose of reducing the total noise of the booster fan 10, improving the order noise level, and improving the sound quality of the booster fan 10.

[0199] In some embodiments, the second impeller 2 also includes a second blade crown 23, which is annular and is sleeved on the outside of the plurality of second blades 22. The ends of the plurality of second blades 22 radially away from the second hub 21 are all fixedly connected to the second blade crown 23.

[0200] By wrapping the plurality of second blades 22 with the second blade crown 23 to isolate the airflow on the pressure side and the suction side at the top of the second blade 22, the airflow leakage on the pressure side and the suction side at the top of the second blade 22 can be prevented to generate a larger vortex, thereby preventing the vortex from causing noise, thereby achieving the purpose of reducing the total noise of the booster fan 10, improving the order noise level, and improving the sound quality of the booster fan 10.

[0201] In some embodiments, as Figure 17 As shown, along the radial direction of the first hub 11, a first gap a1 is provided between the first blade crown 13 and the inner wall of the impeller housing 3a, 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.

[0202] In some embodiments, the first gap a1 has a value ranging from 0.5 mm to 2 mm, which not only ensures that there is no friction or scratching between the first blade crown 13 and the inner wall of the impeller housing 3 a , but also helps to reduce the volume of the booster fan 10 .

[0203] Exemplarily, the first gap a1 may be any value between 0.5 mm and 2 mm, such as 0.5 mm, 1 mm, 1.5 mm or 2 mm.

[0204] In some embodiments, 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 second impeller 2 from radially jumping and causing friction and scratching between the second blade crown 23 and the inner wall of the impeller housing 3a.

[0205] In some embodiments, the second gap a2 has a value ranging from 0.5 mm to 2 mm, which not only ensures that there is no friction or scratching between the second blade crown 23 and the inner wall of the impeller housing 3 a , but also helps to reduce the volume of the booster fan 10 .

[0206] Exemplarily, the second gap a2 may be any value between 0.5 mm and 2 mm, such as 0.5 mm, 1 mm, 1.5 mm or 2 mm.

[0207] It should be noted that 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 may be equal or unequal, which is not limited here.

[0208] In some embodiments, 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 0.5 mm to 1.5 mm, thereby ensuring the structural strength of the first blade crown 13 and enabling the first blade crown 13 to better isolate the airflow on the pressure side and the suction side of the first blade 12 .

[0209] Illustratively, the thickness b1 of the first blade shroud 13 may be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0210] In some embodiments, 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 0.5 mm to 1.5 mm, thereby ensuring the structural strength of the second blade crown 23 and enabling the second blade crown 23 to better isolate the airflow on the pressure side and the suction side of the second blade 22 .

[0211] Illustratively, the thickness b2 of the second blade shroud 23 may be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0212] It should be noted that the thickness b1 of the first blade crown 13 and the thickness b2 of the second blade crown 23 may be equal or unequal, which is not limited here.

[0213] In some embodiments, the inner wall of the impeller housing 3a is provided with a reinforcement structure 311. Along the axial direction of the first hub 11, the reinforcement 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 through the reinforcement structure 311 and extend its service life.

[0214] Furthermore, the impeller housing 3a is further provided with a support structure 312 for supporting the first drive member 41 and the second drive member 42. The support structure 312 is fixedly connected to the reinforcement structure 311 to improve the installation stability of the first drive member 41 and the second drive member 42. It should be noted that a single support structure 312 can be provided to simultaneously support the first drive member 41 and the second drive member 42 via a single support structure 312. Two support structures 312 can also be provided to respectively support the first drive member 41 and the second drive member 42 via two support structures 312. Of course, more support structures 312 can also be provided so that the first drive member 41 and the second drive member 42 are each supported by multiple support structures 312.

[0215] Exemplarily, the reinforcement structure 311 and the support structure 312 are both ribs protruding from the inner wall of the impeller housing 3 a.

[0216] In some embodiments, as Figure 17As shown, along the axial direction of the first hub 11 , a third gap c1 is provided between the reinforcement structure 311 and the first blade crown 13 , thereby preventing the first impeller 1 from axially moving and causing the first blade crown 13 to collide axially with the impeller housing 3 a .

[0217] In some embodiments, the third gap c1 has a value ranging from 3 mm to 8 mm, which not only ensures that the first blade crown 13 and the impeller housing 3 a do not collide axially, but also helps to reduce the volume of the booster fan 10 .

[0218] Exemplarily, the third gap c1 may be any value between 3 mm and 8 mm, such as 3 mm, 4 mm, 5 mm, 6 mm, 7 mm or 8 mm.

[0219] In some embodiments, as Figure 18 As shown, a fourth gap c2 is provided between the reinforcement structure 311 and the second blade crown 23 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 axially with the impeller housing 3 a.

[0220] In some embodiments, the fourth gap c2 has a value ranging from 3 mm to 8 mm, which not only ensures that the second blade crown 23 and the impeller housing 3 a do not collide axially, but also helps to reduce the volume of the booster fan 10 .

[0221] Exemplarily, the fourth gap c2 may be any value between 3 mm and 8 mm, such as 3 mm, 4 mm, 5 mm, 6 mm, 7 mm or 8 mm.

[0222] It should be noted that, along the axial direction of the first hub 11 , the third gap c1 between the reinforcement structure 311 and the first impeller 1 and the fourth gap c2 between the reinforcement structure 311 and the second impeller 2 may be equal or unequal, which is not limited here.

[0223] 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 where the reinforcement structure 311 is provided.

[0224] 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 where the reinforcement structure 311 is provided.

[0225] Such an arrangement ensures that the first blade crown 13 can isolate the airflow on the pressure side and the suction side of the first blade 12, and the second blade crown 23 can isolate the airflow on the pressure side and the suction side of the second blade 22 without affecting the axial flow of the airflow.

[0226] In some embodiments, along the axial direction of the first hub 11 , the length of the first blade shroud 13 is not less than the length of the blade tip of the first blade 12 , and the length of the first blade shroud 13 is not greater than the length of the first hub 11 .

[0227] For ease of understanding, Figure 19 As shown, the length of the first blade crown 13 is recorded as d, the length of the blade tip of the first blade 12 is recorded as e, and the length of the first hub 11 is recorded as f, where e≤d≤f.

[0228] In some embodiments, along the axial direction of the second hub 21 , the length of the second blade shroud 23 is not less than the length of the blade tip of the second blade 22 , and the length of the second blade shroud 23 is not greater than the length of the second hub 21 .

[0229] It should be noted that, along the axial direction of the first hub 11 , the length of the first blade crown 13 and the length of the second blade crown 23 may be equal or unequal, which is not limited here.

[0230] For example, in a specific embodiment of the present invention, the first gap a1 is 1 mm. The thickness b1 of the first impeller 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 impeller 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 impeller 13 is 26 mm. Along the axial direction of the second hub 21, the length of the second impeller 23 is 21 mm. This arrangement not only improves the structural strength of the first and second impellers 1 and 2 and enhances the smoothness of the axial airflow, but also enhances the noise reduction effect.

[0231] It should be noted that, whether along the axial direction of the first hub 11 or along 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 blade 12 by the first blade crown 13, and 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 blade 22 by the second blade crown 23, thereby better reducing the noise effect.

[0232] In some embodiments, as Figure 17 As shown, along the axial direction of the first hub 11 , the variation pattern of the outer diameter of the first blade crown 13 is the same as the variation pattern of the inner diameter of the impeller casing 3 a corresponding to the first blade crown 13 .

[0233] In some embodiments, as Figure 18 As shown, along the axial direction of the second hub 21 , the variation pattern of the outer diameter of the second blade crown 23 is the same as the variation pattern of the inner diameter of the impeller housing 3 a corresponding to the second blade crown 23 .

[0234] 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 the airflow.

[0235] 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.

[0236] In some embodiments, as Figure 9 As shown, the fan unit 101 further includes a cap 71 and a tail cone 72. The cap 71 is provided at an end of the first impeller 1 away from the second impeller 2, and the tail cone 72 is provided at an 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.

[0237] Specifically, the cap 71 is fixedly connected to the first hub 11 , and the tail cone 72 is fixedly connected to the second hub 21 .

[0238] In some embodiments, 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 arranged in the first housing 3a1, and the second impeller 2 and the second driving member 42 are both arranged in the second housing 3a2, thereby improving the convenience of assembly.

[0239] It should be noted that when there are multiple fan units 101, the first shells 3a1 of the multiple fan units 101 are fixedly connected or integrally formed into a first integrated shell, and the second shells 3a2 of the multiple fan units 101 are fixedly connected or integrally formed into a second integrated shell, thereby reducing the mold opening cost and simplifying assembly.

[0240] In some embodiments, 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 in the fan housing 3c, and a vibration reduction structure 3d is provided between the first housing 3a1 and the fan housing 3c, as well as between the second housing 3a2 and the fan housing 3c, to achieve the purpose of vibration reduction and noise reduction.

[0241] Illustratively, the fan housing 3c includes a first shell portion 3c1 and a second shell portion 3c2. The first shell portion 3c1 and the second shell portion 3c2 are detachably connected via a second locking member 3b2 such as a second bolt, thereby facilitating assembly of the booster fan 10.

[0242] Specifically, the first shell portion 3c1 and the second shell portion 3c2 are arranged opposite to 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 to each other along the axial direction of the first hub 11 .

[0243] The booster fan 10 of this embodiment, while meeting the requirements of air volume and air pressure, 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. It can thus greatly free up 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 in vehicle product strength.

[0244] Example 3

[0245] In the existing technology, axial-flow booster fans, due to their axial inlet and outlet characteristics, can directly match the air duct and avoid large deflections of the airflow, making them the best choice for miniaturization of booster fans. Axial-flow booster fans have the characteristics of large air volume and low air pressure, but because they have a small number of blades and a relatively high rotational speed, when the impeller rotates, the wake of the blades or the related vortices generated by the blades will continuously hit the structure downstream of the impeller at a frequency related to the impeller's rotational speed or a frequency several times the impeller's rotational speed, generating certain fixed-frequency noises, especially order noise, which is the most obvious. This sound is easily distinguished by the human ear, resulting in a sense of discomfort in the sound, which in turn leads to poor sound quality of the axial-flow booster fan, seriously restricting its application scenarios.

[0246] To solve this problem, Figure 22 As shown, an embodiment of the present invention further 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. The fan unit 101 includes a first impeller 1, a second impeller 2 and an impeller housing 3a.

[0247] The impeller housing 3a includes a mounting cavity 31 and a first opening 32 and a second opening 33, both communicating with the mounting cavity 31. The first impeller 1 and the second impeller 2 are both rotatably disposed within the mounting cavity 31, with the air inlet side of the first impeller 1 facing the first opening 32, and the air outlet side of the second impeller 2 facing 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.

[0248] The first impeller 1 and the second impeller 2 have the same rotation direction. In other words, the first impeller 1 and the second impeller 2 are coaxially arranged in series, which achieves the purpose of noise reduction while ensuring the dynamic balance and static balance of the axial flow booster fan, and solves the problems of high order noise and poor sound quality of the axial flow booster fan, so that the axial flow booster fan can provide the required air volume and pressure while meeting the requirements of low noise and good sound quality.

[0249] 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 on the first hub 11 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.

[0250] 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 on the second hub 21 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.

[0251] The first blade 12 and the second blade 22 adopt the above-mentioned arrangement, which can effectively reduce the total noise generated by the rotation of the first impeller 1 and the second impeller 2 while ensuring the dynamic balance and static balance of the axial flow booster fan, and at the same time solve the problems of large order noise, poor sound quality and low NVH level of the axial flow booster fan, so that the axial flow booster fan can provide the required air volume and air pressure while meeting the requirements of low noise and good sound quality.

[0252] In some embodiments, the booster fan 10 includes multiple fan units 101, which are arranged in a direction perpendicular to the axial direction of the first hub 11. This arrangement allows the multiple fan units 101 to correspond to different areas within the vehicle cabin, allowing the air volume and wind speed in different areas of the cabin to be independently adjusted, thereby improving the comfort of the driver and passengers.

[0253] 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.

[0254] 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.

[0255] In some embodiments, the booster fan 10 also includes a first driving member arranged in a one-to-one correspondence with the first impeller 1, and a second driving member arranged in a one-to-one correspondence with the second impeller 2. The first driving member is transmission-connected to the corresponding first impeller 1 to drive the corresponding first impeller 1 to rotate; the second driving member is transmission-connected to the corresponding second blade 22 to drive the corresponding second impeller 2 to rotate.

[0256] Specifically, the first driving member includes a first motor, and the second driving member 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. The rotational speeds of the first impeller 1 and the second impeller 2 are controlled by controlling the first motor and the second motor respectively.

[0257] Exemplarily, the output shaft of the first motor and the first hub 11 of the corresponding first impeller 1 , as well as the output shaft of the second motor and the second hub 21 of the corresponding second impeller 2 , are both connected via connecting flanges.

[0258] In other embodiments, the first impeller 1 and the second impeller 2 may be driven to rotate by a single drive mechanism. For example, the drive mechanism includes a drive member and a reversing assembly, wherein the first impeller 1 is directly connected to the output shaft of the drive member, and the second impeller 2 is connected to the output shaft of the drive member via the reversing assembly, thereby causing the first impeller 1 and the second impeller 2 to rotate in opposite directions. Specifically, the drive member is a motor, and the reversing assembly is a gear set. Of course, the reversing assembly may also be other reversing structures known in the art, which are not limited herein.

[0259] In some embodiments, the number of the first blades 12 is 5 to 11. By limiting the number of the first blades 12 as described above, the convenience of industrial mold opening can be ensured while maintaining the air volume and pressure performance of the axial flow booster fan.

[0260] In some embodiments, the number of the second blades 22 is 5 to 11. By limiting the number of the second blades 22 as described above, the convenience of industrial mold opening can be ensured while maintaining the air volume and pressure performance of the axial flow booster fan.

[0261] In some embodiments, as Figure 14As shown, the projection of the leading edge x1 of one of the two adjacent first blades 12 onto a predetermined plane does not intersect with the trailing edge y1 of the other first blade 12. The predetermined plane is perpendicular to the axial direction of the first hub 11. This arrangement further improves the convenience of industrial mold making and the air volume and pressure performance of the axial flow booster fan.

[0262] In some embodiments, as Figure 15 As shown, the projection of the leading edge x2 of one of the two adjacent second blades 22 on the preset plane does not intersect with the trailing edge y2 of the other second blade 22. This arrangement can further improve the convenience of industrial mold opening and the air volume and pressure performance of the axial flow booster fan.

[0263] In some embodiments, the plurality of first blades 12 include a first preset blade and a plurality of second preset blades, and the second preset blades located on both sides of the first preset blade are symmetrically arranged with respect to the first preset blade, thereby facilitating better reduction of order noise.

[0264] In some embodiments, the plurality of second blades 22 include a third preset blade and a plurality of fourth preset blades, and the fourth preset blades located on both sides of the third preset blade are symmetrically arranged with respect to the third preset blade, thereby facilitating better reduction of order noise.

[0265] It should be noted that in some other embodiments, the second preset blades located on both sides of the first preset blade can be set asymmetrically, and the fourth preset blades located on both sides of the third preset blade can be set asymmetrically, which can also achieve the purpose of improving the noise reduction effect.

[0266] In some embodiments, the number of the first blades 12 and the number of the second blades 22 are both odd numbers.

[0267] In some embodiments, the number of first blades 12 is not equal to the number of second blades 22 .

[0268] Such an arrangement is beneficial to further improve the order noise of the series axial flow booster fan and avoid the order noise generated by the airflow interference between the first impeller 1 and the second impeller 2.

[0269] In some embodiments, the number of first blades 12 is greater than the number of second blades 22 , which is beneficial to further improve the order noise of the series axial flow booster fan and further avoid the order noise generated by airflow interference between the first impeller 1 and the second impeller 2 .

[0270] In a specific embodiment of the present invention, the number of first blades 12 is 9, 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. The number of second blades 22 is 9, and the phase angle between two adjacent second blades 22 ranges from 32° to 48° (i.e., 288° / 9 to 432° / 9). Exemplarily, 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.

[0271] 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). For example, 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). Exemplarily, 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.

[0272] In some embodiments, 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, a first phase angle α is provided between the blade root and the blade tip of the trailing edge y1 of the first blade 12. In other words, the first blade 12 adopts a curved angle design.

[0273] 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 root and the tip of the leading edge x2 of the second blade 22. In other words, the second blade 22 adopts a curved angle design.

[0274] With such an arrangement, the phenomenon of the pressure fluctuation generated by the wake of the first blade 12 at different radial heights hitting the leading edge x2 of the second blade 22 can be discretized in time. In other words, the phenomenon of the pressure fluctuation generated by the wake of the first blade 12 at different radial heights hitting the leading edge x2 of the second blade 22 can be distributed at different times, thereby eliminating the pressure fluctuation, which can not only greatly reduce the order noise problem of the series axial flow booster fan, but also slightly reduce the total noise of the series axial flow booster fan.

[0275] In some embodiments, the value range of α+β is 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 can allow the first impeller 1 and the second impeller 2 to have collisions at different radial heights at different times when the wake of the first blade 12 interferes with the leading edge x2 of the second blade 22 during rotation, thereby avoiding noise amplification caused by collisions at the same time or in a short period of time, thereby forming convex order noise. When α+β is less than 150%*360° / N1, it can avoid the difficulty of demolding caused by excessive bending of the first blade 12 and the second blade 22, and if α+β exceeds 360° / N1, the effect of improving the order noise by the angled shaping of the first blade 12 and the second blade 22 will also be weakened, so there is no need to over-bend the first blade 12 and the second blade 22.

[0276] 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°, which can not only greatly reduce the order noise problem of the series axial flow booster fan, but also facilitate the demolding of the first blade 12 and the second blade 22, thereby reducing the processing difficulty of the first blade 12 and the second blade 22.

[0277] In some embodiments, the first impeller 1 further includes a first blade crown 13, which is annular and sleeved on the outside of the plurality of first blades 12. The ends of the plurality of first blades 12 radially away from the first hub 11 are all fixedly connected to the first blade crown 13.

[0278] By wrapping the plurality of first blades 12 with the first blade crown 13 to isolate the airflow on the pressure side and the suction side at the top of the first blade 12, the airflow leakage on the pressure side and the suction side at the top of the first blade 12 can be prevented to generate a larger vortex, thereby preventing the vortex from causing noise, thereby achieving the purpose of reducing the total noise of the booster fan 10, improving the order noise level, and improving the sound quality of the booster fan 10.

[0279] In some embodiments, the second impeller 2 also includes a second blade crown 23, which is annular and is sleeved on the outside of the plurality of second blades 22. The ends of the plurality of second blades 22 radially away from the second hub 21 are all fixedly connected to the second blade crown 23.

[0280] By wrapping the plurality of second blades 22 with the second blade crown 23 to isolate the airflow on the pressure side and the suction side at the top of the second blade 22, the airflow leakage on the pressure side and the suction side at the top of the second blade 22 can be prevented to generate a larger vortex, thereby preventing the vortex from causing noise, thereby achieving the purpose of reducing the total noise of the booster fan 10, improving the order noise level, and improving the sound quality of the booster fan 10.

[0281] In some embodiments, as Figure 17 As shown, along the radial direction of the first hub 11, a first gap a1 is provided between the first blade crown 13 and the inner wall of the impeller housing 3a, 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.

[0282] In some embodiments, the first gap a1 has a value ranging from 0.5 mm to 2 mm, which not only ensures that there is no friction or scratching between the first blade crown 13 and the inner wall of the impeller housing 3 a , but also helps to reduce the volume of the booster fan 10 .

[0283] Exemplarily, the first gap a1 may be any value between 0.5 mm and 2 mm, such as 0.5 mm, 1 mm, 1.5 mm or 2 mm.

[0284] In some embodiments, 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 second impeller 2 from radially jumping and causing friction and scratching between the second blade crown 23 and the inner wall of the impeller housing 3a.

[0285] In some embodiments, the second gap a2 has a value ranging from 0.5 mm to 2 mm, which not only ensures that there is no friction or scratching between the second blade crown 23 and the inner wall of the impeller housing 3 a , but also helps to reduce the volume of the booster fan 10 .

[0286] Exemplarily, the second gap a2 may be any value between 0.5 mm and 2 mm, such as 0.5 mm, 1 mm, 1.5 mm or 2 mm.

[0287] It should be noted that 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 may be equal or unequal, which is not limited here.

[0288] In some embodiments, 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 0.5 mm to 1.5 mm, thereby ensuring the structural strength of the first blade crown 13 and enabling the first blade crown 13 to better isolate the airflow on the pressure side and the suction side of the first blade 12 .

[0289] Illustratively, the thickness b1 of the first blade shroud 13 may be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0290] In some embodiments, 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 0.5 mm to 1.5 mm, thereby ensuring the structural strength of the second blade crown 23 and enabling the second blade crown 23 to better isolate the airflow on the pressure side and the suction side of the second blade 22 .

[0291] Illustratively, the thickness b2 of the second blade shroud 23 may be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0292] It should be noted that the thickness b1 of the first blade crown 13 and the thickness b2 of the second blade crown 23 may be equal or unequal, which is not limited here.

[0293] In some embodiments, the inner wall of the impeller housing 3a is provided with a reinforcement structure 311. Along the axial direction of the first hub 11, the reinforcement 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 through the reinforcement structure 311 and extend its service life.

[0294] Furthermore, the impeller housing 3a is further provided with a support structure 312 for supporting the first and second drive members. The support structure 312 is fixedly connected to the reinforcement structure 311 to improve the installation stability of the first and second drive members. It should be noted that a single support structure 312 can be provided to simultaneously support the first and second drive members through a single support structure 312. Two support structures 312 can also be provided to respectively support the first and second drive members through two support structures. Of course, more support structures 312 can also be provided so that the first and second drive members are respectively supported by multiple support structures 312.

[0295] Exemplarily, the reinforcement structure 311 and the support structure 312 are both ribs protruding from the inner wall of the impeller housing 3 a.

[0296] In some embodiments, as Figure 17As shown, along the axial direction of the first hub 11 , a third gap c1 is provided between the reinforcement structure 311 and the first blade crown 13 , thereby preventing the first impeller 1 from axially moving and causing the first blade crown 13 to collide axially with the impeller housing 3 a .

[0297] In some embodiments, the third gap c1 has a value ranging from 3 mm to 8 mm, which not only ensures that the first blade crown 13 and the impeller housing 3 a do not collide axially, but also helps to reduce the volume of the booster fan 10 .

[0298] Exemplarily, the third gap c1 may be any value between 3 mm and 8 mm, such as 3 mm, 4 mm, 5 mm, 6 mm, 7 mm or 8 mm.

[0299] In some embodiments, as Figure 18 As shown, a fourth gap c2 is provided between the reinforcement structure 311 and the second blade crown 23 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 axially with the impeller housing 3 a.

[0300] In some embodiments, the fourth gap c2 has a value ranging from 3 mm to 8 mm, which not only ensures that the second blade crown 23 and the impeller housing 3 a do not collide axially, but also helps to reduce the volume of the booster fan 10 .

[0301] Exemplarily, the fourth gap c2 may be any value between 3 mm and 8 mm, such as 3 mm, 4 mm, 5 mm, 6 mm, 7 mm or 8 mm.

[0302] It should be noted that, along the axial direction of the first hub 11 , the third gap c1 between the reinforcement structure 311 and the first impeller 1 and the fourth gap c2 between the reinforcement structure 311 and the second impeller 2 may be equal or unequal, which is not limited here.

[0303] 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 where the reinforcement structure 311 is provided.

[0304] 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 where the reinforcement structure 311 is provided.

[0305] Such an arrangement ensures that the first blade crown 13 can isolate the airflow on the pressure side and the suction side of the first blade 12, and the second blade crown 23 can isolate the airflow on the pressure side and the suction side of the second blade 22 without affecting the axial flow of the airflow.

[0306] In some embodiments, along the axial direction of the first hub 11 , the length of the first blade shroud 13 is not less than the length of the blade tip of the first blade 12 , and the length of the first blade shroud 13 is not greater than the length of the first hub 11 .

[0307] For ease of understanding, Figure 19 As shown, the length of the first blade crown 13 is recorded as d, the length of the blade tip of the first blade 12 is recorded as e, and the length of the first hub 11 is recorded as f, where e≤d≤f.

[0308] In some embodiments, along the axial direction of the second hub 21 , the length of the second blade shroud 23 is not less than the length of the blade tip of the second blade 22 , and the length of the second blade shroud 23 is not greater than the length of the second hub 21 .

[0309] It should be noted that, along the axial direction of the first hub 11 , the length of the first blade crown 13 and the length of the second blade crown 23 may be equal or unequal, which is not limited here.

[0310] For example, in a specific embodiment of the present invention, the first gap a1 is 1 mm. The thickness b1 of the first impeller 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 impeller 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 impeller 13 is 26 mm. Along the axial direction of the second hub 21, the length of the second impeller 23 is 21 mm. This arrangement not only improves the structural strength of the first and second impellers 1 and 2 and enhances the smoothness of the axial airflow, but also enhances the noise reduction effect.

[0311] It should be noted that, whether along the axial direction of the first hub 11 or along 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 blade 12 by the first blade crown 13, and 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 blade 22 by the second blade crown 23, thereby better reducing the noise effect.

[0312] In some embodiments, as Figure 17 As shown, along the axial direction of the first hub 11 , the variation pattern of the outer diameter of the first blade crown 13 is the same as the variation pattern of the inner diameter of the impeller casing 3 a corresponding to the first blade crown 13 .

[0313] In some embodiments, as Figure 18 As shown, along the axial direction of the second hub 21 , the variation pattern of the outer diameter of the second blade crown 23 is the same as the variation pattern of the inner diameter of the impeller housing 3 a corresponding to the second blade crown 23 .

[0314] 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 the airflow.

[0315] 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.

[0316] In some embodiments, as Figure 22 as well as Figures 27 and 28 As shown, the series axial flow booster fan also includes a first air guide member 5 arranged corresponding to the first impeller 1, the first air guide member 5 is located on the air outlet side of the first impeller 1, the first air guide member 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 on the third hub 51 at circumferential intervals along the third hub 51, and the plurality of first guide vanes 52 are fixedly connected to the impeller housing 3a at one end radially away from the third hub 51 along the third hub 51.

[0317] Because the first impeller 1 rotates and generates work, imparting a certain degree of curl to the airflow, the first air guide 5 can deflect the airflow with a certain degree of curl in the axial direction of the first hub 11, converting some of the dynamic pressure into static pressure, thereby removing the swirl and improving the supercharging effect. Simultaneously, the first drive member for rotating the first impeller 1 can be mounted on the third hub 51, thereby supporting the third hub 51 through the first guide vanes 52 and improving the installation stability of the first drive member.

[0318] In some embodiments, as Figure 22 as well as Figures 29 to 30 As shown, the tandem axial-flow booster fan further 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 and includes a fourth hub 61 and a plurality of second guide vanes 62. The fourth hub 61 is fixedly disposed in the mounting cavity 31. The plurality of second guide vanes 62 are spaced apart circumferentially from the fourth hub 61. The plurality of second guide vanes 62 are fixedly connected to the impeller housing 3a at one end radially away from the fourth hub 61.

[0319] Because the second impeller 2 rotates and generates work, imparting a certain degree of curl to the airflow, the second air guide 6 deflects the airflow in the axial direction of the second hub 21, converting some of the dynamic pressure into static pressure, thereby removing the swirl and improving the supercharging effect. Simultaneously, the second drive member, which drives the second impeller 2 in rotation, is mounted on the fourth hub 61. The second guide vanes 62 support the fourth hub 61, improving the installation stability of the second drive member.

[0320] 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.

[0321] 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, that is to say, the second hub 21, the third hub 51, and the fourth hub 61 are all coaxially arranged with the first hub 11.

[0322] The main sources of noise of the 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.

[0323] To solve this problem, in an embodiment of the present invention, the plurality of first guide vanes 52 are unevenly distributed along the circumference of the third hub 51 , and the plurality of second guide vanes 62 are unevenly distributed along the circumference of the fourth hub 61 .

[0324] The arrangement of the above-mentioned first guide vanes 52 and second guide vanes 62 can effectively prevent the airflow generated by the rotation of the first impeller 1 and the second impeller 2 from continuously hitting the first guide vanes 52 and the second guide vanes 62 at a frequency related to the rotational speed of the first impeller 1 (including a frequency several times the rotational speed of the first impeller 1) and a frequency related to the rotational speed of the second impeller 2 (including a frequency several times the rotational speed of the second impeller 2) to generate some fixed-frequency noise, thereby avoiding causing discomfort to the ears of the driver and passengers.

[0325] 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. Such an arrangement is conducive to further improving the noise reduction effect. Since the first guide vanes 52 and the second guide vanes 62 are both stationary structural components and do not rotate, the multiple first guide vanes 52 of the first air guide member 5 can allow a greater degree of uneven setting compared to the multiple first blades 12 of the first impeller 1; and the multiple second guide vanes 62 of the second air guide member 6 can allow a greater degree of uneven setting compared to the multiple second blades 22 of the second impeller 2.

[0326] In some embodiments, the number of the first guide vanes 52 is 9 to 15. Compared to the first blades 12, the first guide vanes 52 are smaller in size, so more first guide vanes 52 can be provided, which is beneficial to improving the support stability of the first guide vanes 52 on the first driving member.

[0327] In some embodiments, the number of the second guide vanes 62 is 9 to 15. Compared to the second blades 22, the second guide vanes 62 are smaller in size, so more second guide vanes 62 can be provided, which helps to improve the support stability of the second guide vanes 62 on the second driving member.

[0328] In some embodiments, the bending angle of the first guide vane 52 ranges from 30° to 50°, and the bending angle of the first guide vane 52 gradually increases from the blade root to the blade tip, thereby improving the deswirl effect.

[0329] Illustratively, the bending angle of the first guide vane 52 may be any value between 30° and 50°, such as 30°, 35°, 40°, 45° or 50°.

[0330] In some embodiments, the bending angle of the second guide vane 62 ranges from 30° to 50°, and the bending angle of the second guide vane 62 gradually increases from the blade root to the blade tip, thereby improving the deswirl effect.

[0331] Illustratively, the bending angle of the second guide vane 62 may be any value between 30° and 50°, such as 30°, 35°, 40°, 45° or 50°.

[0332] In some embodiments, the geometric outlet angle of the first guide vane 52 ranges from 80° to 100°, thereby improving the deswirl effect.

[0333] Illustratively, the geometric outlet angle of the first guide vane 52 may be any value between 80° and 100°, such as 80°, 85°, 90°, 95°, or 100°.

[0334] In some embodiments, the geometric outlet angle of the second guide vane 62 ranges from 80° to 100°, thereby improving the deswirl effect.

[0335] Illustratively, the geometric outlet angle of the second guide vane 62 may be any value between 80° and 100°, such as 80°, 85°, 90°, 95° or 100°.

[0336] In some embodiments, the multiple 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 with respect to 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 member 5.

[0337] In some embodiments, the multiple second guide vanes 62 include a third preset guide vane and multiple fourth preset guide vanes. The fourth preset guide vanes located on both sides of the third preset guide vane are symmetrically arranged with respect to 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 member 6.

[0338] 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 set asymmetrically 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 be set asymmetrically with respect to the first preset guide vane, which can also achieve the effect of noise reduction.

[0339] 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 member 5, and the mutual interference between the second impeller 2 and the second air guide member 6, so as to avoid the main order overlap of the first impeller 1 and the second impeller 2, resulting in the amplification of noise of certain frequencies (such as 450Hz~800Hz), thereby improving the noise reduction effect.

[0340] 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 angles between two adjacent first guide vanes 52 are 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.

[0341] 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 member 5 and the uneven distribution of the multiple second guide vanes 62 of the second air guide member 6 differentiated, so as to further reduce the order noise derived from the mutual interference between the first impeller 1 and the first air guide member 5, and the mutual interference between the second impeller 2 and the second air guide member 6, avoid the overlap of the main orders of the first impeller 1 and the second impeller 2, and cause the noise of certain frequencies (such as 450Hz~800Hz) to be amplified, thereby further improving the noise reduction effect.

[0342] It should be noted that, in some other embodiments, the number of first guide vanes 52 and the number of second guide vanes 62 may be equal, and further, the phase angle between two adjacent first guide vanes 52 and the phase angle between two adjacent second guide vanes 62 may be unequal. When the number of first guide vanes 52 and the number of second guide vanes 62 cannot be designed to be unequal, the phase angle between two adjacent first guide vanes 52 and the phase angle between two adjacent second guide vanes 62 may be unequal, thereby further reducing the order noise generated by the mutual interference between the first impeller 1 and the first air guide member 5, and between the second impeller 2 and the second air guide member 6, thereby achieving the purpose of noise reduction.

[0343] In a specific embodiment of the present invention, the number of first guide vanes 52 is 13, 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. 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). Exemplarily, 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.

[0344] In some embodiments, a projection of a leading edge of one of two adjacent first guide vanes 52 on a preset plane does not intersect with a trailing edge of the other first guide vane 52 , so as to improve the convenience of industrial mold opening.

[0345] In some embodiments, the projection of the leading edge of one of the two adjacent second guide vanes 62 on the preset plane does not intersect with the trailing edge of the other second guide vane 62 , so as to improve the convenience of industrial mold opening.

[0346] 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 an axial collision between the first blade crown 13 and the first air guide 5 .

[0347] In some embodiments, the fifth gap is in the range of 3 mm to 8 mm, which ensures that the first blade crown 13 and the first air guide 5 do not collide axially and is also beneficial to reducing the volume of the booster fan 10.

[0348] Illustratively, the fifth gap may be any value between 3 mm and 8 mm, such as 3 mm, 4 mm, 5 mm, 6 mm, 7 mm or 8 mm.

[0349] 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 an axial collision between the second blade crown 23 and the first air guide 5 .

[0350] In some embodiments, the sixth gap has a value range of 3 mm to 8 mm, which ensures that the first blade crown 13 and the first air guide 5 do not collide axially and is also beneficial to reducing the volume of the booster fan 10.

[0351] Illustratively, the sixth gap may be any value between 3 mm and 8 mm, such as 3 mm, 4 mm, 5 mm, 6 mm, 7 mm or 8 mm.

[0352] It should be noted that, along the axial direction of the first hub 11 , 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 may be the same or different, which is not limited here.

[0353] In some embodiments, as Figure 22 As shown, the fan unit 101 further includes a cap 71 and a tail cone 72. The cap 71 is provided at an end of the first impeller 1 away from the second impeller 2, and the tail cone 72 is provided at an 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.

[0354] Specifically, the cap 71 is fixedly connected to the first hub 11 , and the tail cone 72 is fixedly connected to the second hub 21 .

[0355] In some embodiments, 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 member 5 and the first driving member are all arranged in the first housing 3a1, and the second impeller 2, the second air guide member 6 and the second driving member are all arranged in the second housing 3a2, thereby improving the convenience of assembly.

[0356] It should be noted that when there are multiple fan units 101, the first shells 3a1 of the multiple fan units 101 can be fixedly connected or integrally formed into a first integrated shell, and the second shells 3a2 of the multiple fan units 101 can be fixedly connected or integrally formed into a second integrated shell, thereby reducing the mold opening cost and simplifying assembly.

[0357] In some embodiments, as Figure 21 As shown, the booster fan 10 also includes a fan casing 3c, the first casing 3a1 and the second casing 3a2 are both fixedly arranged in the fan casing 3c, and a vibration reduction structure 3d is provided between the first casing 3a1 and the fan casing 3c, as well as between the second casing 3a2 and the fan casing 3c, to achieve the purpose of vibration reduction and noise reduction.

[0358] Illustratively, the fan housing 3c includes a first shell portion 3c1 and a second shell portion 3c2. The first shell portion 3c1 and the second shell portion 3c2 are detachably connected via a second locking member 3b2 such as a second bolt, thereby facilitating assembly of the booster fan 10.

[0359] Specifically, the first shell portion 3c1 and the second shell portion 3c2 are arranged opposite to 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 to each other along the axial direction of the first hub 11 .

[0360] The booster fan 10 of this embodiment, while meeting the requirements of air volume and air pressure, 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. It can thus greatly free up 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 in vehicle product strength.

[0361] Example 4

[0362] like Figures 31 to 33 As shown, an embodiment of the present invention further provides an air-conditioning system, a thermal management system and a vehicle. The vehicle includes a vehicle cabin and a thermal management system. The thermal management system includes an air-conditioning system, and the air-conditioning system is used to supply air to the space in the vehicle cabin.

[0363] The air-conditioning system includes an air-conditioning box 20 and any one 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 in the above-mentioned embodiment of the present invention), the air-conditioning box 20 includes an air-conditioning outlet 201 (specifically, it can be a face-blowing outlet, such as a rear-blowing outlet), the booster fan 10 is arranged at the air-conditioning outlet 201, and 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 boosts the air.

[0364] It should be noted that the traditional vehicle air-conditioning box and the booster fan 10 are both independently arranged, and the traditional booster fan 10 is large in size and difficult to be integrated behind the air-conditioning outlet 201 of the vehicle air-conditioning box, and requires a larger layout space.

[0365] The thermal management system of this embodiment integrates the booster fan 10 with the air-conditioning outlet 201 of the air-conditioning box 20, which can significantly reduce the space occupied by the air-conditioning system while ensuring that the air volume and pressure provided by the air-conditioning system meet the requirements, thereby realizing a compact design of the air-conditioning system.

[0366] In this embodiment, the air outlet of the booster fan 10 is connected to the vehicle cabin, thereby significantly reducing the layout space of the air conditioning system while adjusting the air volume and wind speed delivered into the vehicle cabin through the booster fan 10.

[0367] The air-conditioning system, thermal management system and vehicle of the embodiments 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 on the vehicle, and improving the product strength of the vehicle.

[0368] When the booster fan 10 includes a plurality of fan units 101 , the plurality of fan units 101 are arranged along an air outlet direction perpendicular to the air outlet 201 .

[0369] Specifically, if Figure 31 and Figure 32 As shown, the air outlet of the booster fan 10 can be directly connected to the vehicle cabin or connected through a connecting pipe 301. Of course, there can be one or more connecting pipes 301. In other words, the connecting pipes 301 are arranged in a one-to-one correspondence with the fan units 101. Specifically, the connecting pipe 301 is connected between the air outlet of the corresponding fan unit 101 (i.e., the second opening 33 mentioned above) and the vehicle cabin; the air inlet of the booster fan 10 can be directly connected to the air-conditioning outlet 201 or connected through a transition pipe 302, thereby being able to adapt to different layout spaces and having greater versatility. Furthermore, the booster fan 10 is connected to the air-conditioning outlet 201 through a connecting structure.

[0370] Illustratively, the connection structure may be a plug-in structure or a snap-in structure.

[0371] Specifically, the connection structure includes a first connection portion provided at the air inlet of the booster fan and a second connection portion provided at the air outlet of the air conditioner, the first connection portion and the second connection portion being plugged or snapped into each other. For example, a buckle is provided at one end of the air inlet of the booster fan 10, and a slot is provided at the air outlet 201. The buckle and the slot snap into each other to connect the booster fan 10 to the air outlet 201.

[0372] In some embodiments, a sealant, such as foam, is provided between the air inlet of the booster fan 10 and the air conditioning outlet 201 to improve the sealing between the air inlet of the booster fan 10 and the air conditioning outlet 201 .

[0373] In a specific embodiment of the present invention, Figure 33As shown, there are two fan units 101, respectively designated as a first fan unit and a second fan unit. The first fan unit is connected to the left side of the vehicle cabin so that air can be supplied to the left side of the vehicle cabin through the first fan unit, and the second fan unit is connected to the right side of the vehicle cabin so that air can be supplied to the right side of the vehicle cabin through the second fan unit. For example, a connecting pipe 301 connects the first fan unit to the left side of the vehicle cabin, and another connecting pipe 301 connects the second fan unit to the right side of the vehicle cabin. By adjusting the speed of the first motor and the second motor corresponding to the left side of the vehicle cabin, the wind speed and air volume corresponding to the left side of the vehicle cabin can be adjusted. By adjusting the speed of the first motor and the second motor corresponding to the right side of the vehicle cabin, the wind speed and air volume corresponding to the right side of the vehicle cabin can be adjusted, thereby achieving independent zoning control of air volume. Of course, the first motor and the second motor corresponding to the left side of the vehicle cabin can also be controlled to stop running, thereby only supplying air to the right side of the vehicle cabin; or the first motor and the second motor corresponding to the right side of the vehicle cabin can also be controlled to stop running, thereby only supplying air to the left side of the vehicle cabin.

[0374] Furthermore, the above are only preferred embodiments of the present invention and the technical principles employed. Those skilled in the art will appreciate that the present invention is not limited to the specific embodiments herein, and that various obvious changes, readjustments, and substitutions are possible for those skilled in the art 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 scope of the present invention. The scope of the present invention is determined by the scope of the appended claims.

Claims

1. Impeller, characterized in that, include: impeller hub; Multiple blades are arranged on the impeller hub at intervals along the circumference of the impeller hub, and the multiple blades are unevenly distributed along the circumference of the impeller hub; the phase angle between two adjacent blades ranges from 288° / N to 432° / N, where N is the number of blades.

2. The impeller according to claim 1, characterized in that The plurality of blades include a first preset blade and a plurality of second preset blades, and the second preset blades located on both sides of the first preset blade are symmetrically arranged with respect to the first preset blade.

3. The impeller according to claim 1, characterized in that Of the two adjacent blades, the projection of the leading edge x1 of one blade on the preset plane does not intersect with the trailing edge y1 of the other blade; The preset plane is perpendicular to the axial direction of the impeller hub.

4. The impeller according to claim 1, characterized in that The number of the blades is 5 to 11.

5. The impeller according to any one of claims 1 to 4, characterized in that: It also includes a blade crown, which is annular and sleeved on the outer sides of the plurality of blades. The ends of the plurality of blades away from the impeller hub in the radial direction of the impeller hub are fixedly connected to the blade crown.

6. A fan unit, characterized in that: include: an impeller housing, the impeller housing including a mounting cavity; The impeller according to any one of claims 1 to 5, wherein the impeller hub is rotatably disposed in the mounting cavity.

7. The fan unit according to claim 6, characterized in that The impeller housing further includes a first opening and a second opening both communicating with the mounting cavity; the first opening and the second opening are sequentially arranged along the axial direction of the impeller hub.

8. The fan unit according to claim 7, characterized in that There are multiple impellers, and the multiple impellers are arranged in sequence along the axial direction of the impeller hub.

9. The fan unit according to claim 8, characterized in that The plurality of impellers include a first impeller and a second impeller, wherein the air inlet side of the first impeller faces the first opening, the air inlet side of the second impeller is arranged opposite to the air outlet side of the first impeller, and the air outlet side of the second impeller faces the second opening.

10. The fan unit according to claim 9, characterized in that The blades of the first impeller are first blades, and the blades of the second impeller are second blades; Along the rotation direction of the first impeller and with the rotation direction of the first impeller as a positive value, a first phase angle α is provided between the blade root and the blade tip of the trailing edge y1 of the first blade of the first impeller; and / or, Along the rotation direction of the second impeller and taking the rotation direction of the second impeller as a 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 of the second impeller.

11. The fan unit according to claim 9, characterized in that The blades of the first impeller are first blades, and the blades of the second impeller are second blades; The number of the first blades of the first impeller is 9, and along the circumference of the first impeller, the phase angles between the first blades of two adjacent first impellers are 43.9°, 34.7°, 39.3°, 44.2°, 35.9°, 44.2°, 39.3°, 34.7° and 43.9° respectively; and / or, The number of the second blades of the second impeller is 7. Along the circumference of the second impeller, the phase angles between the second blades of two adjacent second impellers are 50.4°, 52.4°, 53.7°, 47.1°, 53.7°, 52.4° and 50.4° respectively.

12. The fan unit according to any one of claims 9 to 11, characterized in that: The first impeller and the second impeller rotate in opposite directions.

13. The fan unit according to any one of claims 9 to 11, characterized in that: The blades of the first impeller are first blades, and the blades of the second impeller are second blades; The number of the first blades of the first impeller is not equal to the number of the second blades of the second impeller, and the numbers of the blades are both odd numbers.

14. The fan unit according to any one of claims 9 to 11, characterized in that: The fan unit also includes an air guide member arranged corresponding to the impeller, and the air inlet side of the air guide member is arranged opposite to the air outlet side of the corresponding impeller; the air guide member includes an air guide hub and a plurality of guide vanes, and the air guide hub is fixed in the installation cavity; the plurality of guide vanes are arranged on the air guide hub at intervals along the circumference of the air guide hub.

15. The fan unit according to claim 14, characterized in that The plurality of guide vanes are unevenly distributed along the circumference of the guide hub.

16. The fan unit according to claim 14, characterized in that One end of the plurality of guide vanes radially away from the guide hub is fixedly connected to the impeller housing.

17. The fan unit according to claim 14, characterized in that The plurality of guide vanes include a first preset guide vane and a plurality of second preset guide vanes, and the second preset guide vanes located on both sides of the first preset guide vane are symmetrically arranged with respect to the first preset guide vane.

18. Booster fan, characterized in that: Comprising a fan unit according to any one of claims 7 to 17.

19. The booster fan according to claim 18, characterized in that: There are multiple fan units, and the multiple fan units are arranged in a direction perpendicular to the impeller hub.

20. Air conditioning system, characterized in that Comprising the booster fan as described in any one of claims 18-19.

21. A thermal management system, characterized in that It comprises the booster fan according to any one of claims 18-19 or the air conditioning system according to claim 20.

22. A vehicle, characterized in that Comprising the air conditioning system according to claim 20 or the thermal management system according to claim 21.

Images