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

Abstract

The utility model relates to the technical field of fans, and discloses a fan unit, a booster fan, an air conditioning system, a heat management system and a vehicle, an impeller wraps a plurality of blades through a blade crown, and the thickness of the blade crown is limited, so that airflow on the pressure surface and the suction surface of the top of each blade is isolated through the blade crown, and the blade crown is sealed. Fluid leakage of a pressure surface and a suction surface at the top of the blade is blocked, so that blade top leakage flow cannot be generated, a large vortex structure is prevented from being generated in a blade top area, noise caused by vortex is avoided, important inducements of order noise are eliminated, and the purpose of reducing the total noise and order noise amplitude of the booster fan is achieved; and the sound quality of the booster fan is improved. Meanwhile, a third gap c is formed between the blade crown and the reinforcing structure in the axial direction of the impeller hub, so that the situation that the blade crown collides with an impeller shell due to axial movement of the impeller is avoided, and normal work of the impeller is guaranteed.

Description

TECHNICAL FIELD

[0001] The utility model relates to fan technical field especially, it relates to a fan unit, booster fan, air conditioning system, heat management system and vehicle. BACKGROUND

[0002] The conventional vehicle booster fan usually adopts centrifugal structure, and the size is relatively large, and the vehicle space is seriously occupied, and the arrangement is not flexible, and no matter the selection of the automobile manufacturer or the use of the consumer causes certain influence. From the view of the supercharging capacity, the centrifugal booster fan structure is simple, and the supercharging capacity is strong, and under the premise of not considering the space occupation, it is the first choice of the pipeline supercharging.

[0003] Considering the crowded parts layout in the vehicle at present, the miniaturized booster fan has more broad market demand, and the axial flow type impeller can be directly matched with the air duct due to the axial inlet and outlet characteristics, avoids the airflow to be greatly turned, and is the best choice for the miniaturization of the booster fan. The axial flow type impeller has the characteristics of large air volume and low wind pressure, but due to the relatively small number of blades, the speed is relatively high, and obvious order noise is often generated, the sound quality is poor, and the application scene is seriously restricted. UTILITY MODEL CONTENTS

[0004] The utility model discloses a fan unit, booster fan, air conditioning system, heat management system and vehicle can reduce the total noise and order noise amplitude of booster fan.

[0005] In order to achieve this purpose, the utility model adopts the following technical scheme:

[0006] The fan unit comprises:

[0007] The inner wall of the impeller shell is provided with a reinforcing structure;

[0008] The impeller comprises an impeller hub, a shroud and a plurality of blades, the impeller hub is rotatably arranged in the impeller shell, and the plurality of blades are arranged on the impeller hub in a circumferential direction of the impeller hub; the shroud is annular, the shroud is arranged on the outer side of the plurality of blades, and the plurality of blades are connected to the shroud in a radial direction of the impeller hub away from one end of the impeller hub; a third gap c is arranged between the shroud and the reinforcing structure in an axial direction of the impeller hub.

[0009] As a preferred technical scheme of the fan unit, the length of the shroud is not less than the length of the blade tip in the axial direction of the impeller hub, and the length of the shroud is not greater than the length of the impeller hub.

[0010] As a preferred technical scheme of the fan unit, the plurality of blades are unevenly distributed in the circumferential direction of the impeller hub.

[0011] As a preferred technical solution of the fan unit, a phase angle a is provided between the blade root and the blade tip of the trailing edge y1 of the blade in the rotation direction of the impeller.

[0012] As a preferred technical solution of the fan unit, the variation law of the outer diameter of the shroud is the same as the variation law of the inner diameter of the impeller shell corresponding to the shroud in the axial direction of the impeller hub.

[0013] As a preferred technical solution of the fan unit, a first gap a is provided between the shroud and the inner wall of the impeller shell.

[0014] As a preferred technical solution of the fan unit, the first gap a is in the range of 0.5mm to 2mm.

[0015] As a preferred technical solution of the fan unit, the thickness b of the shroud is in the range of 0.5mm to 1.5mm in the radial direction of the impeller hub.

[0016] As a preferred technical solution of the fan unit, the third gap c is in the range of 3mm to 8mm.

[0017] As a preferred technical solution of the fan unit, the reinforcing structure is provided on the air outlet side of the impeller; the inner diameter of the shroud on the air outlet side of the impeller is equal to the inner diameter of the impeller shell where the reinforcing structure is provided; and / or,

[0018] The reinforcing structure is provided on the air inlet side of the impeller; the inner diameter of the shroud on the air inlet side of the impeller is equal to the inner diameter of the impeller shell where the reinforcing structure is provided.

[0019] As a preferred technical solution of the fan unit, the impeller shell includes a mounting cavity, the impeller hub is rotatably provided in the mounting cavity; the impeller shell further includes a first opening and a second opening which are in communication with the mounting cavity; the first opening and the second opening are sequentially provided in the axial direction of the impeller hub.

[0020] As a preferred technical solution of the fan unit, a plurality of impellers are provided, and the plurality of impellers are sequentially provided in the axial direction of the impeller hub.

[0021] As a preferred technical solution of the fan unit, the fan unit further includes a guide vane corresponding to the impeller, the air inlet side of the guide vane is oppositely provided with the air outlet side of the corresponding impeller; the guide vane includes a guide vane hub and a plurality of guide vanes, the guide vane hub is fixedly provided in the mounting cavity; the plurality of guide vanes are spaced apart in the circumferential direction of the guide vane hub and provided on the guide vane hub.

[0022] As a preferred technical scheme of the fan unit, a fifth gap is arranged between the shroud and the guide vane along the axial direction of the impeller hub.

[0023] As a preferred technical scheme of the fan unit, the fifth gap is 3mm-8mm.

[0024] As a preferred technical scheme of the fan unit, the guide vanes are unevenly distributed along the circumferential direction of the guide vane hub.

[0025] As a preferred technical scheme of the fan unit, each of the guide vanes is fixedly connected to the impeller shell along the radial direction of the guide vane hub away from one end of the guide vane hub.

[0026] In order to achieve the above-mentioned purpose, the utility model also provides a booster fan, including the fan unit of any one of the above.

[0027] As a preferred technical scheme of the booster fan, the fan unit is provided with a plurality of fan units arranged along the direction perpendicular to the axial direction of the impeller hub.

[0028] In order to achieve the above-mentioned purpose, the utility model also provides an air conditioning system, including the booster fan of the above.

[0029] In order to achieve the above-mentioned purpose, the utility model also provides a thermal management system, including the booster fan of any one of the above or the air conditioning system of the above.

[0030] In order to achieve the above-mentioned purpose, the utility model also provides a vehicle, including the air conditioning system of the above or the thermal management system of the above.

[0031] The utility model has at least the following beneficial effects:

[0032] The fan unit provided by the utility model is wrapped by the shroud, the airflow of the pressure surface and the suction surface at the top of the blade is isolated by the shroud, the fluid leakage of the pressure surface and the suction surface at the top of the blade is hindered, then the tip leakage flow is not generated, the vortex structure in the top area of the blade is avoided, the noise caused by the vortex is avoided, the important inducement of the order noise is eliminated, the purpose that the total noise and the order noise amplitude of the booster fan are reduced is achieved, and the sound quality of the booster fan is improved.

[0033] The booster fan, the air conditioning system, the thermal management system and the vehicle provided by the utility model all include the fan unit of the above, can reduce the total noise and the order noise amplitude of the booster fan, and improve the sound quality of the booster fan. BRIEF DESCRIPTION OF DRAWINGS

[0034] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the description of the embodiments of the present application will be briefly introduced. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can be obtained by those skilled in the art without creative labor on the basis of the contents of the embodiments of the present application and the drawings.

[0035] Figure 1 a The first structure diagram of the impeller provided by the embodiments of the present application is shown in the figure.

[0036] Figure 1 b The second structure diagram of the impeller provided by the embodiments of the present application is shown in the figure.

[0037] Figure 1 c The third structure diagram of the impeller provided by the embodiments of the present application is shown in the figure.

[0038] Figure 1 d The fourth structure diagram of the impeller provided by the embodiments of the present application is shown in the figure.

[0039] Figure 2 The structure diagram of the shroud and the impeller shell provided by the embodiments of the present application is shown in the figure.

[0040] Figure 3 The first structure diagram of the booster fan provided by the embodiments of the present application is shown in the figure.

[0041] Figure 4a The first structure diagram of the air guide provided by the embodiments of the present application is shown in the figure.

[0042] Figure 4b The second structure diagram of the air guide provided by the embodiments of the present application is shown in the figure.

[0043] Figure 5a The second structure diagram of the booster fan provided by the embodiments of the present application is shown in the figure.

[0044] Figure 5b The second structure diagram of the booster fan provided by the embodiments of the present application is shown in the figure.

[0045] Figure 5c The third structure diagram of the booster fan provided by the embodiments of the present application is shown in the figure.

[0046] Figure 6 The structure diagram of the first impeller provided by the embodiments of the present application is shown in the figure.

[0047] Figure 7 The structure diagram of the second impeller provided by the embodiments of the present application is shown in the figure.

[0048] Figure 8 A structure schematic view of the first blade and the second blade is provided for the embodiment of the utility model;

[0049] Figure 9 A sectional view of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0050] Figure 10 A first partial sectional view of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0051] Figure 11 A first structure schematic view of the first impeller of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0052] Figure 12 A first structure schematic view of the second impeller of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0053] Figure 13 A structure schematic view of the fan unit of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0054] Figure 14 A second structure schematic view of the first impeller of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0055] Figure 15 A second structure schematic view of the second impeller of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0056] Figure 16 A structure schematic view of the first blade and the second blade of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0057] Figure 17 A second partial sectional view of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0058] Figure 18 A third partial sectional view of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0059] Figure 19 A third structure schematic view of the first impeller of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0060] Figure 20 A structure schematic view of the axial-flow type booster fan (not including the fan shell) is provided for the embodiment of the utility model;

[0061] Figure 21 A structure schematic view of the axial-flow type booster fan (including the fan shell) is provided for the embodiment of the utility model;

[0062] Figure 22 A structure schematic view of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0063] Figure 23 A fourth structure schematic view of the first impeller of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0064] Figure 24 A fifth structure schematic view of the first impeller of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0065] Figure 25 A third structure schematic view of the second impeller of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0066] Figure 26 A fourth structure schematic view of the second impeller of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0067] Figure 27 A first structure schematic view of the first air guide member of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0068] Figure 28 A second structure schematic view of the first air guide member of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0069] Figure 29 A first structure schematic view of the second air guide member of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0070] Figure 30 A second structure schematic view of the second air guide member of the axial-flow type booster fan is provided for the embodiment of the utility model;

[0071] Figure 31 A structure schematic view of the first heat management system is provided for the embodiment of the utility model;

[0072] Figure 32 A structure schematic view of the second heat management system is provided for the embodiment of the utility model;

[0073] Figure 33 A sectional view of the heat management system is provided for the embodiment of the utility model.

[0074] Figures 1 a to 8 In the middle:

[0075] 10, booster fan; 101, fan unit;

[0076] 1', impeller; 1a', first impeller; 1b', second impeller; 11', impeller hub; 12', blade; 13', shroud;

[0077] 3a, impeller housing; 31, mounting cavity; 311, reinforcing structure; 312, support structure; 32, first opening; 33, second opening; 3a1, first housing; 3a2, second housing; 3b1, first locking member; 3b2, second locking member; 3c, fan housing; 3c1, first housing part; 3c2, second housing part; 3d, damping structure;

[0078] 5', air guide member; 5a', first air guide member; 5b', second air guide member; 51', air guide hub; 52', guide vane.

[0079] Figures 9 to 33 In:

[0080] 10, booster fan; 101, fan unit;

[0081] 1, first impeller; 11, first hub; 12, first blade; 13, first shroud;

[0082] 2, second impeller; 21, second hub; 22, second blade; 23, second shroud;

[0083] 3a, impeller housing; 31, mounting cavity; 311, reinforcing structure; 312, support structure; 32, first opening; 33, second opening; 3a1, first housing; 3a2, second housing; 3b1, first locking member; 3b2, second locking member; 3c, fan housing; 3c1, first housing part; 3c2, second housing part; 3d, damping structure;

[0084] 41, first driving member; 42, second driving member;

[0085] 5, first air guide member; 51, third hub; 52, first guide vane;

[0086] 6, second air guide member; 61, fourth hub; 62, second guide vane;

[0087] 71, cap; 72, tail vertebra;

[0088] 20, air conditioner box; 201, air conditioner air outlet; 301, connecting pipeline; 302, transition pipeline. DETAILED DESCRIPTION

[0089] The utility model will be described in further detail below in combination with the drawings and embodiments. It can be understood that the specific embodiments described herein are only used to explain the utility model and are not limited to the utility model. In addition, it should be noted that only the parts related to the utility model are shown in the drawings for the convenience of description, not all the structures.

[0090] In the description of the utility model, unless another definite provision and limitation, the term "link", "connect", "fix" should do broad sense understanding, for example, can be fixed connection, also can be detachable connection, or be integrated;Can be mechanical connection, also can be electrical connection;Can be directly connected, also can be indirectly connected through the intermediate medium, can be two elements inside the communication or two element's interaction relationship. For ordinary skilled in the art, the specific meaning of the above terms in the utility model can be understood according to specific circumstances.

[0091] In the utility model, unless another definite provision and limitation, the first feature is "on" or "under" the second feature can include the first and second features direct contact, also can include the first and second features is not direct contact but is through the contact between other features between them.And, the first feature is "on", "above" and "on" the second feature includes the first feature is directly above and obliquely above the second feature, or just indicates that the first feature horizontal height is higher than the second feature.The first feature is "under", "below" and "under" the second feature includes the first feature is directly below and obliquely below the second feature, or just indicates that the first feature horizontal height is less than the second feature.

[0092] In the description of the embodiment, the terms "on", "under", "right", etc. Orientation or positional relationship is based on the orientation or positional relationship shown in the drawing, only for the convenience of description and simplification operation, and does not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, therefore cannot be understood as a limitation on the utility model. In addition, the terms "first", "second" are only used to distinguish in the description, and have no special meaning.

[0093] In the embodiment, the phase angle between the two adjacent blades is the difference in the circumferential angle of the leading edge root of the two adjacent blades. The phase angle between the two adjacent guide vanes is the difference in the circumferential angle of the leading edge root of the two adjacent guide vanes.

[0094] Embodiment one

[0095] As Figures 1 a to 8 shown, the embodiment of the application provides a blade crown, a guide vane, an impeller, a fan unit and a booster fan. The booster fan 10 comprises a fan unit 101, the fan unit 101 comprises an impeller 1' and an impeller shell 3a, the impeller shell 3a comprises a mounting cavity 31 and a first opening 32 and a second opening 33 which are in communication with 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.

[0096] As Figure 1 a and Figure 1 bAs shown, the impeller 1' includes an impeller hub 11' and a plurality of blades 12' which are arranged along the circumference of the impeller hub 11' and 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'.

[0097] The blades 12' are arranged as described above, which can effectively reduce the total noise generated by the rotation of the impeller 1' under the premise of ensuring the dynamic balance and static balance of the supercharging fan 10, and solve the problems of large order noise, poor sound quality and low NVH level of the supercharging fan 10, so as to meet the requirements of low noise and good sound quality under the premise of providing the required air volume and air pressure of the supercharging fan 10.

[0098] Specifically, the first opening 32 and the second opening 33 are arranged along the axis of the impeller hub 11' in sequence.

[0099] In some embodiments, as shown, Figure 1 c The projection of the leading edge x1 of one of the two adjacent blades 12' on the preset plane does not intersect with the trailing edge y1 of the other blade 12'. The preset plane is perpendicular to the axis of the impeller hub 11'. In this way, the convenience of industrial mold opening and the air volume and air pressure performance of the supercharging fan can be further improved.

[0100] In some embodiments, the plurality of blades 12' includes a first preset blade and a plurality of second preset blades, and the second preset blades on both sides of the first preset blade are symmetrically arranged about the first preset blade, which is conducive to better reducing the order noise.

[0101] In some embodiments, the number of blades 12' ranges from 5 to 11. By limiting the number of blades 12' as described above, the convenience of industrial mold opening can be ensured, and the air volume and air pressure performance of the supercharging fan 10 can be maintained.

[0102] The impeller 1' further includes a shroud 13' which is annular and is arranged outside the plurality of blades 12', and each of the plurality of blades 12' away from one end of the impeller hub 11' in the radial direction of the impeller hub 11' is fixedly connected to the shroud 13'.

[0103] By wrapping the plurality of blades 12' with the shroud 13', the airflow of the pressure surface and the suction surface at the top of the blades 12' is isolated, the fluid leakage of the pressure surface and the suction surface at the top of the blades 12' is hindered, and thus the tip leakage flow is not generated, the vortex structure in the top region of the blades 12' is avoided, the noise caused by the vortex is avoided, and the important cause of the order noise is eliminated, so as to reduce the total noise and the amplitude of the order noise of the supercharging fan 10 and improve the sound quality of the supercharging fan 10.

[0104] In some embodiments, along the axial direction of the impeller hub 11′, the variation law of the outer diameter of the blade crown 13′ is the same as the variation law of the inner diameter of the impeller housing 3a corresponding to the blade crown 13′, so as to ensure the smooth axial flow of airflow.

[0105] Specifically, when the inner wall of the impeller housing 3a corresponding to the blade crown 13′ is a cylindrical surface, the outer circumferential surface of the blade crown 13′ is also a cylindrical surface. When the inner wall of the impeller housing 3a corresponding to the blade crown 13′ is a gradually expanding or contracting conical surface, the blade crown 13′ is also a gradually expanding or contracting conical surface.

[0106] In some embodiments, such as Figure 2 As shown, a first gap a is provided between the blade crown 13′ and the inner wall of the impeller housing 3a, thereby preventing radial runout of the impeller 1′ from causing friction and scratching between the blade crown 13′ and the inner wall of the impeller housing 3a.

[0107] In some embodiments, the value of the first gap a ranges from 0.5 mm to 2 mm, which ensures that the blade crown 13′ and the inner wall of the impeller housing 3a will not rub against each other, while also helping to reduce the size of the booster fan 10.

[0108] For example, the first gap a can be any value between 0.5mm and 2mm, such as 0.5mm, 1mm, 1.5mm or 2mm.

[0109] In some embodiments, the thickness b of the blade crown 13' is in the range of 0.5 mm to 1.5 mm along the radial direction of the impeller hub 11', thereby ensuring the structural strength of the blade crown 13' and enabling the blade crown 13' to better isolate the airflow between the pressure surface and the suction surface of the blade 12'.

[0110] For example, the thickness b of the leaf crown 13′ can be any value between 0.5 mm and 1.5 mm, such as 0.5 mm, 1 mm or 1.5 mm.

[0111] In some embodiments, along the axial direction of the impeller hub 11′, the length of the blade crown 13′ is not less than the length of the blade tip of the blade 12′, and the length of the blade crown 13′ is not greater than the length of the impeller hub 11′.

[0112] For ease of understanding, such as Figure 1 d As shown, along the axial direction of the impeller hub 11′, the length of the blade crown 13′ is denoted as d, the length of the blade tip of the blade 12′ is denoted as e, and the length of the impeller hub 11′ is denoted as f, where e≤d≤f.

[0113] It should be noted that the shroud 13' can completely cover the plurality of blades 12' in the axial direction of the impeller hub 11' or in the circumferential direction of the impeller hub 11', so that the shroud 13' completely isolates the air flows on the pressure surface and the suction surface of the blades 12', and the noise reduction effect is better.

[0114] In some embodiments, as shown in Figure 2 The inner wall of the impeller shell 3a is provided with a reinforcing structure 311; and a third gap c is arranged between the shroud 13' and the reinforcing structure 311 in the axial direction of the impeller hub 11', so that axial movement of the impeller 1' can be prevented from causing axial impact between the shroud 13' and the impeller shell 3a, and normal operation of the impeller 1' is ensured.

[0115] In some embodiments, the third gap c has a value ranging from 3 mm to 8 mm, which is conducive to reducing the volume of the booster fan 10 while ensuring that the shroud 13' and the impeller shell 3a will not be axially impacted.

[0116] For example, the third gap c can have any value between 3 mm and 8 mm, such as 3 mm, 4 mm, 5 mm, 6 mm, 7 mm or 8 mm.

[0117] In some embodiments, the reinforcing structure 311 is arranged on the air outlet side of the impeller 1', and the inner diameter of the shroud 13' on the air outlet side of the impeller 1' is equal to the inner diameter of the impeller shell 3a at the position where the reinforcing structure 311 is arranged, so that the shroud 13' can isolate the air flows on the pressure surface and the suction surface of the blades 12' and will not affect the axial flow of the air flow.

[0118] In other embodiments, the reinforcing structure 311 can also be arranged on the air inlet side of the impeller 1', and the inner diameter of the shroud 13' on the air inlet side of the impeller 1' is equal to the inner diameter of the impeller shell 3a at the position where the reinforcing structure 311 is arranged, so that the shroud 13' can isolate the air flows on the pressure surface and the suction surface of the blades 12' and will not affect the axial flow of the air flow.

[0119] As shown in Figure 3 The fan unit 101 further includes a wind guide 5' which is fixedly arranged in the mounting cavity 31, the air inlet side of the impeller 1' faces the first opening 32, the air outlet side of the impeller 1' is arranged opposite to the air inlet side of the wind guide 5', the air outlet side of the wind guide 5' faces the second opening 33, and the wind guide 5' is used to turn the air flow generated by the impeller 1' to the axial direction of the impeller 1'.

[0120] In some embodiments, a fifth gap is arranged between the shroud 13' and the wind guide 5' in the axial direction of the impeller hub 11', so that axial movement of the impeller 1' can be prevented from causing axial impact between the shroud 13' and the wind guide 5'.

[0121] In some embodiments, the fifth gap is in a range of 3mm to 8mm, which is conducive to reducing the volume of the booster fan 10 while ensuring that the leaf crown 13' and the guide vane 5' do not collide in the axial direction

[0122] For example, the fifth gap can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0123] As shown in Figure 4a and Figure 4b The guide vane 5' includes a guide vane hub 51' and a plurality of guide vanes 52'. The guide vane hub 51' is fixedly arranged in the mounting cavity 31, and the plurality of guide vanes 52' are arranged along the circumference of the guide vane hub 51'.

[0124] Since the impeller 1' rotates to work, the airflow has a certain vorticity. The above-mentioned guide vane 5' can turn the airflow with a certain vorticity to the axial direction of the impeller hub 11' of the impeller 1', convert part of the dynamic pressure into static pressure, realize de-rotation, and improve the boosting effect.

[0125] In this embodiment, the axis of the guide vane hub 51' coincides with the axis of the impeller hub 11' of the impeller 1'.

[0126] It should be noted that the noise generated by the airflow generated by the rotation of the impeller 1' and the interference of the guide vane 5' is the main source of noise, especially the order noise, which is most obvious and easy to form very sharp sound, causing discomfort to the ears of the crew.

[0127] In some embodiments, the plurality of guide vanes 52' are unevenly distributed along the circumference of the guide vane hub 51', thereby effectively avoiding the airflow generated by the rotation of the impeller 1' from continuously hitting the guide vanes 52' at a frequency related to the rotational speed of the impeller 1' (including a frequency several times the rotational speed of the impeller 1'), thereby avoiding causing discomfort to the ears of the crew.

[0128] The phase angle between the adjacent two guide vanes 52' is in a range of 180° / n1 to 540° / n1, and n1 is the number of guide vanes 52'. Such arrangement is conducive to further improving the noise reduction effect.

[0129] It should be noted that since the guide vane 52' is a static structural member and does not rotate, compared with the plurality of blades 12' of the impeller 1', the plurality of guide vanes 52' of the guide vane 5' can be unevenly arranged to a greater extent.

[0130] In some embodiments, the plurality of guide vanes 52' are fixedly connected to the impeller shell 3a along the radial direction away from one end of the guide wheel hub 51', so as to support and fix the guide wheel hub 51' through the plurality of guide vanes 52', and improve the installation stability of the guide vanes 52'. In addition, the guide vanes 52' have simple structure, and can improve the guiding effect and noise reduction effect.

[0131] 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 of the guide vane 52', so as to improve the de-rotation effect.

[0132] For example, the bending angle of the guide vane 52' can be any value between 30° and 50°, such as 30°, 35°, 40°, 45° or 50°.

[0133] In some embodiments, the geometric outflow angle of the guide vane 52' ranges from 80° to 100°, so as to improve the de-rotation effect.

[0134] For example, the geometric outflow angle of the guide vane 52' can be any value between 80° and 100°, such as 80°, 85°, 90°, 95° or 100°.

[0135] In some embodiments, the plurality of guide vanes 52' 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 about the first preset guide vane.

[0136] The above-mentioned guide vane 52' can better eliminate the order noise generated by the mutual interference between the impeller 1' and the air guide 5'.

[0137] It should be noted that in other embodiments, the second preset guide vanes located on both sides of the first preset guide vane can also be asymmetrically arranged about the first preset guide vane, which can also achieve the effect of noise reduction.

[0138] In some embodiments, the projection of the leading edge of one of the two adjacent guide vanes 52' on a preset plane does not intersect with the trailing edge of the other guide vane 52', so as to improve the convenience of industrial mold opening. The preset plane is perpendicular to the axial direction of the third hub.

[0139] It should be noted that the driving member for driving the rotation of the impeller 1' can be installed on the guide wheel hub 51', so as to support the guide wheel hub 51' through the guide vanes 52' and improve the installation stability of the driving member.

[0140] In some embodiments, the number of guide vanes 52' ranges from 9 to 15. Compared with the impeller 1', the guide vanes 52' have smaller size, so more guide vanes 52' can be arranged, which is conducive to improving the support stability of the guide vanes 52' to the driving member.

[0141] In some embodiments, the impeller 1' is provided with a plurality of impellers 1', and the plurality of impellers 1' are arranged in sequence along the axial direction of the impeller hub 11'.

[0142] In specific embodiments of the present application, as shown in Figure 5a and 5b , the impeller 1' is provided with two impellers 1', for the convenience of description, the two impellers 1' are respectively denoted as a first impeller 1a' and a second impeller 1b', and the air inlet side of the second impeller 1b' is arranged opposite to the air outlet side of the first impeller 1a'.

[0143] It should be noted that, as shown in Figure 5a , for the series axial flow type supercharging fan, the rotation directions of the first impeller 1a' and the second impeller 1b' are the same, and by arranging the first impeller 1a' and the second impeller 1b' in series, the air is combined to be supercharged, thereby realizing higher supercharging capacity.

[0144] Further, the impeller 1' is arranged one-to-one with the air guide 5', in other words, the air guide 5' is arranged at the air outlet side of the corresponding impeller 1', and the air guide 5' can turn the air flow generated by the corresponding impeller 1' to the axial direction of the impeller hub 11' of the impeller 1', so as to ensure the supercharging effect. Specifically, the air guide 5' is provided with two air guides 5', for the convenience of description, the air guide 5' corresponding to the first impeller 1a' is denoted as a first air guide 5a', and the air guide 5' corresponding to the second impeller 1b' is denoted as a second air guide 5b'.

[0145] In some embodiments, the number of first guide vanes of the first air guide 5a' is not equal to the number of second guide vanes of the second air guide 5b', thereby avoiding the derived order noise caused by the mutual interference of the first impeller 1a' and the first air guide 5a' and the mutual interference of the second impeller 1b' and the second air guide 5b', so as to avoid the amplification of noise at certain frequencies (such as 450Hz-800Hz) caused by the coincidence of the main orders of the first impeller 1a' and the second impeller 1b', and improve the noise reduction effect. Preferably, the number of first guide vanes of the first air guide 5a' is less than the number of second guide vanes of the second air guide 5b', and the noise reduction effect is better.

[0146] In the specific embodiments of the present application, the number of the first vanes of the first air guide 5a' is 11, and the included angle between two adjacent first vanes in the first air guide 5a' ranges from 17.1° to 49.1° (i.e. 180° / 11 to 540° / 11). For example, the included angle between two adjacent first vanes in the first air guide 5a' is 36.5°, 35.3°, 33.3°, 31.1°, 29.4°, 28.8°, 29.4°, 31.1°, 33.3°, 35.3° and 36.5°, respectively. The number of the second vanes of the second air guide 5b' is 13, and the included angle between two adjacent second vanes in the second air guide 5b' ranges from 13.8° to 41.5° (i.e. 180° / 13 to 540° / 13). For example, the included angle between two adjacent second vanes in the second air guide 5b' is 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.

[0147] In some embodiments, the included angle between two adjacent first vanes of the first air guide 5a' is not equal to the included angle between two adjacent second vanes of the second air guide 5b', so that the uneven distribution of the first vanes of the first air guide 5a' and the uneven distribution of the second vanes of the second air guide 5b' are different, so as to further reduce the order noise derived from the mutual interference between the first impeller 1a' and the first air guide 5a' and the mutual interference between the second impeller 1b' and the second air guide 5b', and avoid the amplification of noise at certain frequencies (such as 450 Hz to 800 Hz) caused by the coincidence of the main orders of the first impeller 1a' and the second impeller 1b', so as to further improve the noise reduction effect.

[0148] It should be noted that in other embodiments, the number of the first vanes of the first air guide 5a' can be equal to the number of the second vanes of the second air guide 5b', and further, the included angle between two adjacent first vanes of the first air guide 5a' is not equal to the included angle between two adjacent second vanes of the second air guide 5b'. When the number of the first vanes of the first air guide 5a' cannot be designed to be not equal to the number of the second vanes of the second air guide 5b', the included angle between two adjacent first vanes of the first air guide 5a' can be designed to be not equal to the included angle between two adjacent second vanes of the second air guide 5b', so as to further reduce the order noise derived from the mutual interference between the first impeller 1a' and the first air guide 5a' and the mutual interference between the second impeller 1b' and the second air guide 5b', so as to achieve the purpose of noise reduction.

[0149] In a specific embodiment of the present invention, the first guide vane of the first guide element 5a′ is 13 in number, and the phase angle between two adjacent first guide vanes of the first guide element 5a′ ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, the phase angles between two adjacent first guide vanes of the first guide element 5a′ are successively 31.4°, 30.6°, 29.1°, 27.2°, 25.5°, 24.3°, 23.9°, 24.3°, 25.5°, 27.2°, 29.1°, 30.6°, and 31.4°. The second guide vane of the second guide element 5b′ is 13 in number, and the phase angle between two adjacent second guide vanes of the second guide element 5b′ ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, the phase angles between two adjacent second guide vanes of the second guide element 5b′ are 35.1°, 33.4°, 30.4°, 26.8°, 23.3°, 20.9°, 20.0°, 20.9°, 23.3°, 26.8°, 30.4°, 33.4° and 35.1° respectively.

[0150] like Figure 5b As shown, for the counter-rotating axial flow booster fan, the first impeller 1a′ and the second impeller 1b′ rotate in opposite directions. During operation, the first impeller 1a′ and the second impeller 1b′ rotate in opposite directions to combine and boost the air, thereby achieving a higher boosting capacity.

[0151] In a specific embodiment of the present invention, the first impeller 1a′ has nine first blades, and the phase angle between two adjacent first blades ranges from 32° to 48° (288° / 9 to 432° / 9). Exemplarily, the phase angles between two adjacent first blades are 43.9°, 34.7°, 39.3°, 44.2°, 35.9°, 44.2°, 39.3°, 34.7°, and 43.9°, respectively, and these values ​​ensure that the first blades of the first impeller 1a′ do not overlap along the axial direction of the first impeller 1a′. Further, the second impeller 1b′ has seven second blades, and the phase angle between two adjacent second blades ranges from 41.1° to 61.7° (288° / 7 to 432° / 7). For example, the phase angles between two adjacent second blades are 50.4°, 52.4°, 53.7°, 47.1°, 53.7°, 52.4° and 50.4° respectively, and can satisfy that the second blades of the second impeller 1b′ do not overlap each other along the axial direction of the second impeller 1b′.

[0152] In some embodiments, a phase angle a is provided between the root and the tip of the trailing edge y1 of the blade 12' in the direction of rotation of the impeller 1' and with the direction of rotation of the impeller 1' as a positive value, in other words, the blade 12' is designed with a curved angle.

[0153] The above arrangement can disperse the phenomenon that the pressure fluctuation caused by the wake of the blade 12' at different radial heights impacts other structures of the downstream booster fan 10 in time, in other words, the phenomenon that the pressure fluctuation caused by the wake of the blade 12' at different radial heights impacts other structures of the downstream booster fan 10 is distributed at different times, thereby eliminating the pressure fluctuation, which can greatly reduce the order noise problem of the booster fan 10 and slightly reduce the total noise of the booster fan 10.

[0154] In specific embodiments of the present application, as shown in Figures 6 to 8 a first phase angle a is provided between the root and the tip of the trailing edge y1 of the first blade of the first impeller 1a' in the direction of rotation of the first impeller 1a' and with the direction of rotation of the first impeller 1a' as a positive value; and a second phase angle β is provided between the root and the tip of the leading edge x2 of the second blade of the second impeller 1b' in the direction of rotation of the second impeller 1b' and with the direction of rotation of the second impeller 1b' as a positive value.

[0155] In this way, the phenomenon that the pressure fluctuation caused by the wake of the first blade of the first impeller 1a' at different radial heights impacts the leading edge x2 of the second blade of the second impeller 1b' can be dispersed in time, in other words, the phenomenon that the pressure fluctuation caused by the wake of the first blade of the first impeller 1a' at different radial heights impacts the leading edge x2 of the second blade of the second impeller 1b' is distributed at different times, thereby eliminating the pressure fluctuation, which can greatly reduce the order noise problem of the booster fan 10 and slightly reduce the total noise of the booster fan 10.

[0156] In some embodiments, the value of α+β ranges from 50%*360° / N1 to 150%*360° / N1, and both α and β are not less than 20°; N1 is the number of the first blades of the first impeller 1a′. α+β being greater than 50%*360° / N1 allows the impacts at different radial heights to be dispersed at different times when the trailing edge x2 of the first blade of the first impeller 1a′ interferes with the leading edge x2 of the second blade of the second impeller 1b′ during rotation. This avoids noise amplification caused by simultaneous or short-term impacts, thus preventing the formation of prominent order noise. If α+β is less than 150%*360° / N1, the demolding difficulties caused by excessive bending of the first blade of the first impeller 1a′ and the second blade of the second impeller 1b′ can be avoided. If α+β exceeds 360° / N1, the effect of improving the order noise by the bending angle of the second blade of the first impeller 1a′ and the second impeller 1b′ will be weakened. Therefore, it is not necessary to excessively bend the second blade of the first impeller 1a′ and the second impeller 1b′.

[0157] In a specific embodiment of the present invention, the first impeller 1a′ has 9 first blades, α is 20°, β is 21°, α+β=41°, which satisfies the range of 20°~60° (50%*360° / 9~150%*360° / 9).

[0158] In some embodiments, such as Figure 5c As shown, multiple first impellers 1a′ and second impellers 1b′ are provided. One first impeller 1a′ and a second impeller 1b′ disposed opposite to the air outlet side of the first impeller 1a′ form a fan unit 101. In other words, in this embodiment, the booster fan 10 includes multiple fan units 101, which are arranged along an axial direction perpendicular to the impeller hub 11′. This arrangement allows multiple fan units 101 to correspond to different areas within the vehicle cabin, enabling independent adjustment of airflow and speed in different areas of the cabin, thereby improving the comfort of the driver and passengers.

[0159] 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.

[0160] The booster fan 10 in this embodiment has the advantages of low total noise, low order noise, and friendly sound quality while meeting the air volume and air pressure requirements. It has a high NVH level and can solve the problems of large size and difficult layout of existing booster fans. In this way, it can greatly free up the storage space in the vehicle, improve the usability of the product in the vehicle, and bring greater improvement to the vehicle product competitiveness.

[0161] Example 2

[0162] In the prior art, the axial flow type booster fan can be directly matched with an air duct due to its axial air inlet and outlet characteristics, avoiding large air flow deflection, and is the best choice for the miniaturization of the booster fan. The axial flow type booster fan has the characteristics of large air volume and low air pressure, but due to the relatively small number of blades and the relatively high speed, the wake of the blades or the related vortex generated by the blades will continuously hit the structure located downstream of the impeller at a frequency related to the rotational speed of the impeller or a frequency several times the rotational speed of the impeller, generating certain fixed frequency noise, especially the order noise, which is most obvious. Such sound is easy to be distinguished by the human ear, thus causing discomfort in sound, and further causing poor sound quality of the axial flow type booster fan, which seriously restricts its application scenarios.

[0163] To solve this problem, as shown in Figure 9 and Figure 10 The embodiment of the present application also provides a booster fan, in the embodiment, the booster fan 10 is a contra-rotating axial flow type booster fan, and the booster fan 10 comprises a fan unit 101, the fan unit 101 comprising a first impeller 1, a second impeller 2 and an impeller shell 3a.

[0164] The impeller shell 3a comprises a mounting cavity 31 and a first opening 32 and a second opening 33 which are both in communication with the mounting cavity 31, the first impeller 1 and the second impeller 2 are both rotatably arranged in the mounting cavity 31, the air inlet side of the first impeller 1 faces the first opening 32, and the air outlet side of the second impeller 2 faces the second opening 33. In the embodiment, the first opening 32 and the second opening 33 are sequentially arranged along the first hub 11 in the axial direction.

[0165] The rotation directions of the first impeller 1 and the second impeller 2 are opposite. In operation, the first impeller 1 and the second impeller 2 rotate in opposite directions to combine the air pressure, thereby achieving high air pressure.

[0166] As shown in Figure 11 The first impeller 1 comprises a first hub 11 and a plurality of first blades 12, the plurality of first blades 12 are arranged on the first hub 11 in a circumferential direction of the first hub 11, and the plurality of first blades 12 are unevenly distributed along the circumferential direction of the first hub 11; the phase angle between adjacent two first blades 12 is in the range of 288° / N1~432° / N1, and N1 is the number of the first blades 12.

[0167] As shown in 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 comprises a second hub 21 and a plurality of second blades 22, the plurality of second blades 22 are arranged on the second hub 21 in a circumferential direction of the second hub 21, and the plurality of second blades 22 are unevenly distributed along the circumferential direction of the second hub 21; the phase angle between adjacent two second blades 22 ranges from 288° / N2 to 432° / N2, and N2 is the number of the second blades 22.

[0168] The first blades 12 and the second blades 22 are arranged as described above, which can effectively reduce the total noise generated by the rotation of the first impeller 1 and the second impeller 2 under the premise of ensuring the dynamic balance and static balance of the axial booster fan, and solve the problems of large 10-order noise, poor sound quality and low NVH level of the axial booster fan 10, so as to meet the requirements of the axial booster fan 10 to provide wind pressure and wind volume, and at the same time meet the requirements of low noise and good sound quality.

[0169] In some embodiments, the booster fan 10 comprises a plurality of fan units 101, and the plurality of fan units 101 are arranged in a direction perpendicular to the axial direction of the first hub 11. In this way, the plurality of fan units 101 can correspond to different areas in the vehicle cabin, and the wind volume and wind speed of different areas in the vehicle cabin can be independently adjusted by the plurality of fan units 101, thereby improving the comfort of the driver and passengers.

[0170] In specific embodiments of the present application, as shown in Figure 13 Of course, the fan unit 101 can also be one, three, four or even more, which is not limited here.

[0171] 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 is coaxially arranged with the first hub 11.

[0172] In some embodiments, as shown in Figure 9 The booster fan 10 further comprises a first driving member 41 corresponding to each first impeller 1 and a second driving member 42 corresponding to each second impeller 2, the first driving member 41 is in transmission connection with the corresponding first impeller 1 to drive the corresponding first impeller 1 to rotate, and the second driving member 42 is in transmission connection with the corresponding second blade 22 to drive the corresponding second impeller 2 to rotate.

[0173] Specifically, the first driving member 41 comprises a first motor, and the second driving member 42 comprises a second motor. The output shaft of the first motor is connected with the first hub 11 of the corresponding first impeller 1, and the output shaft of the second motor is connected with the second hub 21 of the corresponding second impeller 2, and then the rotation speed of the first impeller 1 and the second impeller 2 is controlled by controlling the first motor and the second motor respectively.

[0174] Exemplarily, the output shaft of the first motor and the first hub 11 of the corresponding first impeller 1 are connected through a connecting flange, and the output shaft of the second motor and the second hub 21 of the corresponding second impeller 2 are connected through a connecting flange.

[0175] In other embodiments, the booster fan 10 comprises a driving mechanism corresponding to each fan unit 101, which drives the first impeller 1 and the second impeller 2 of the same fan unit 101 to rotate, such as a driving mechanism comprising a driving member and a reversing assembly, the first impeller 1 is directly connected with the output shaft of the driving member, and the second impeller 2 is connected with the output shaft of the driving member through the reversing assembly, so that the rotation directions of the first impeller 1 and the second impeller 2 are opposite. Specifically, the driving member is a motor, and the reversing assembly is a gear set, of course, the reversing assembly can also be other reversing structures in the prior art, which are not limited here.

[0176] In some embodiments, the number of first blades 12 is 5-11, and by limiting the number of first blades 12 as described above, the convenience of industrial mold opening can be ensured, and the air volume and pressure performance of the axial-flow booster fan can be maintained.

[0177] In some embodiments, the number of second blades 22 is 5-11, and by limiting the number of second blades 22 as described above, the convenience of industrial mold opening can be ensured, and the air volume and pressure performance of the axial-flow booster fan can be maintained.

[0178] In some embodiments, as shown in Figure 14 The projection of the leading edge x1 of one of the two adjacent first blades 12 on the preset plane does not intersect with the trailing edge y1 of the other first blade 12. The preset plane is perpendicular to the axial direction of the first hub 11. In this way, the convenience of industrial mold opening can be further improved, and the air volume and pressure performance of the axial-flow booster fan can be further improved.

[0179] In some embodiments, as shown in Figure 15 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. In this way, the convenience of industrial mold opening can be further improved, and the air volume and pressure performance of the axial-flow booster fan can be further improved.

[0180] In some embodiments, the number of first blades 12 and the number of second blades 22 are not equal, which is beneficial to improve the order noise of the contra-rotating axial-flow booster fan and avoid the order noise generated by the airflow interference between the first impeller 1 and the second impeller 2.

[0181] In some embodiments, the number of the first blades 12 is greater than the number of the second blades 22, which is conducive to further improving the order noise of the contra-rotating axial-flow booster fan and further avoiding the order noise generated by the airflow interference between the first impeller 1 and the second impeller 2.

[0182] In some embodiments, the plurality of first 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 about the first preset blade, which is conducive to better reducing the order noise.

[0183] In some embodiments, the plurality of second blades 22 includes a third preset blade and a plurality of fourth preset blades, the fourth preset blades located on both sides of the third preset blade are symmetrically arranged about the third preset blade, which is conducive to better reducing the order noise.

[0184] It should be noted that in other embodiments, the second preset blades located on both sides of the first preset blade can be asymmetrically arranged, and the fourth preset blades located on both sides of the third preset blade can also be asymmetrically arranged, which can also achieve the purpose of improving the noise reduction effect.

[0185] In specific embodiments of the present application, the number of the first blades 12 is 9, and the phase angles between adjacent two first blades 12 are 43.9°, 34.7°, 39.3°, 44.2°, 35.9°, 44.2°, 39.3°, 34.7° and 43.9° in sequence. The number of the second blades 22 is 7, and the phase angles between adjacent two second blades 22 are 50.4°, 52.4°, 53.7°, 47.1°, 53.7°, 52.4° and 50.4° in sequence.

[0186] In some embodiments, as shown in FIG. 2, along the rotation direction of the first impeller 1 and taking the rotation direction of the first impeller 1 as a positive value, a first phase angle α is provided between the root and the top of the trailing edge y1 of the first blade 12, in other words, the first blade 12 adopts a curved angle design. Figure 16

[0187] In some embodiments, along the rotation direction of the second impeller 2 and taking the rotation direction of the second impeller 2 as a positive value, a second phase angle β is provided between the root and the top of the leading edge x2 of the second blade 22, in other words, the second blade 22 adopts a curved angle design.

[0188] ​In this way, the pressure fluctuation caused by the wake of the first blades 12 at different radial heights can be dispersed in time, that is, the pressure fluctuation caused by the wake of the first blades 12 at different radial heights can be distributed at different times, thereby eliminating the pressure fluctuation, which can greatly reduce the order noise of the contra-rotating axial booster fan and slightly reduce the total noise of the contra-rotating axial booster fan.

[0189] In some embodiments, the value of α+β ranges from 50%*360° / N1 to 150%*360° / N1, and both α and β are not less than 20°. When α+β is greater than 50%*360° / N1, the first impeller 1 and the second impeller 2 can be allowed to interfere with the wake of the first blades 12 and the leading edge x2 of the second blades 22 during rotation, and the impact at different radial heights can be dispersed at different times to avoid noise amplification caused by simultaneous or short-term impact, thereby forming protruding order noise. When α+β is less than 150%*360° / N1, the difficulty of the first blades 12 and the second blades 22 in being molded can be avoided, and if α+β exceeds 360° / N1, the effect of improving order noise by the bending angle of the first blades 12 and the second blades 22 will also be weakened, so it is not necessary to excessively bend the first blades 12 and the second blades 22.

[0190] In specific embodiments of the present application, the number of the first blades 12 is 9, the first phase angle α is 20°, and the second phase angle β is 21°, which can greatly reduce the order noise of the contra-rotating axial booster fan, facilitate the first blades 12 and the second blades 22 to be molded, and reduce the processing difficulty of the first blades 12 and the second blades 22.

[0191] In some embodiments, the first impeller 1 further comprises a first shroud 13, the first shroud 13 is annular, the first shroud 13 is sleeved on the outer side of the plurality of first blades 12, and the plurality of first blades 12 are fixedly connected to the first shroud 13 away from the one end of the first hub 11 in the radial direction of the first hub 11.

[0192] By wrapping the plurality of first blades 12 with the first shroud 13, the airflow of the pressure surface and the suction surface at the top of the first blades 12 can be isolated, which can hinder the leakage of the airflow of the pressure surface and the suction surface at the top of the first blades 12 to generate a larger vortex, thereby avoiding the noise caused by the vortex, 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.

[0193] In some embodiments, the second impeller 2 further comprises a second shroud 23, the second shroud 23 is annular, and the second shroud 23 is sleeved outside the plurality of second blades 22, and the plurality of second blades 22 are fixedly connected to the second shroud 23 away from one end of the second hub 21 in the radial direction of the second hub 21.

[0194] By wrapping the plurality of second blades 22 with the second shroud 23, the airflow of the pressure surface and the suction surface at the top of the second blade 22 is isolated, which can hinder the leakage of the airflow of the pressure surface and the suction surface at the top of the second blade 22 to generate a larger vortex, thereby avoiding the vortex from causing noise, achieving the purpose of reducing the total noise of the supercharging fan 10, improving the order noise level, and improving the sound quality of the supercharging fan 10.

[0195] In some embodiments, as shown in FIG. 1, Figure 17 a first gap a1 is provided between the first shroud 13 and the inner wall of the impeller shell 3a in the radial direction of the first hub 11, thereby preventing the first shroud 13 from rubbing against the inner wall of the impeller shell 3a due to radial runout of the first impeller 1.

[0196] In some embodiments, the first gap a1 has a value in the range of 0.5mm to 2mm, which not only ensures that the first shroud 13 does not rub against the inner wall of the impeller shell 3a, but also helps to reduce the size of the supercharging fan 10.

[0197] For example, the first gap a1 can be any value between 0.5mm and 2mm, such as 0.5mm, 1mm, 1.5mm, or 2mm.

[0198] In some embodiments, as shown in FIG. 1, Figure 18 a second gap a2 is provided between the second shroud 23 and the inner wall of the impeller shell 3a in the radial direction of the second hub 21, thereby preventing the second shroud 23 from rubbing against the inner wall of the impeller shell 3a due to radial runout of the second impeller 2.

[0199] In some embodiments, the second gap a2 has a value in the range of 0.5mm to 2mm, which not only ensures that the second shroud 23 does not rub against the inner wall of the impeller shell 3a, but also helps to reduce the size of the supercharging fan 10.

[0200] For example, the second gap a2 can be any value between 0.5mm and 2mm, such as 0.5mm, 1mm, 1.5mm, or 2mm.

[0201] It should be noted that the first gap a1 between the first shroud 13 and the inner wall of the impeller shell 3a and the second gap a2 between the second shroud 23 and the inner wall of the impeller shell 3a can be equal or not equal, which is not limited here.

[0202] In some embodiments, as shown in Figure 17 The thickness b1 of the first shroud 13 can be any value between 0.5mm and 1.5mm, such as 0.5mm, 1mm or 1.5mm.

[0203] The thickness b1 of the first shroud 13 can be any value between 0.5mm and 1.5mm, such as 0.5mm, 1mm or 1.5mm.

[0204] In some embodiments, as shown in Figure 18 The thickness b2 of the second shroud 23 can be any value between 0.5mm and 1.5mm, such as 0.5mm, 1mm or 1.5mm.

[0205] The thickness b2 of the second shroud 23 can be any value between 0.5mm and 1.5mm, such as 0.5mm, 1mm or 1.5mm.

[0206] It should be noted that the thickness b1 of the first shroud 13 and the thickness b2 of the second shroud 23 can be equal or not equal, which is not limited here.

[0207] In some embodiments, the inner wall of the impeller shell 3a is provided with a reinforcing structure 311, which is located between the first impeller 1 and the second impeller 2 along the axial direction of the first hub 11, so as to increase the structural strength of the impeller shell 3a through the reinforcing structure 311 and prolong the service life.

[0208] Further, the impeller shell 3a is also provided with a support structure 312 for supporting the first driving member 41 and the second driving member 42, and the support structure 312 is fixedly connected with the reinforcing structure 311, so as to improve the installation stability of the first driving member 41 and the second driving member 42. It should be noted that the support structure 312 can be provided with one, so as to support the first driving member 41 and the second driving member 42 at the same time through one support structure 312. The support structure 312 can also be provided with two, so as to support the first driving member 41 and the second driving member 42 respectively through two support structures 312. Of course, the support structure 312 can also be provided with more, so that the first driving member 41 and the second driving member 42 are supported respectively through multiple support structures 312.

[0209] Exemplarily, the reinforcing structure 311 and the support structure 312 are both protruding ribs protruding on the inner wall of the impeller shell 3a.

[0210] In some embodiments, as shown in Figure 17As shown, along the axial direction of the first hub 11, a third gap c1 is provided between the reinforcing structure 311 and the first blade crown 13, which can prevent the first impeller 1 from axially moving and causing the first blade crown 13 to collide with the impeller housing 3a.

[0211] In some embodiments, the value of the third gap c1 is in the range of 3mm to 8mm, which ensures that the first blade crown 13 and the impeller housing 3a will not have axial impact, and also helps to reduce the volume of the booster fan 10.

[0212] For example, the third gap c1 can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0213] In some embodiments, such as Figure 18 As shown, along the axial direction of the second hub 21, a fourth gap c2 is provided between the reinforcing structure 311 and the second blade crown 23, which can prevent the second impeller 2 from axially moving and causing the second blade crown 23 to collide with the impeller housing 3a.

[0214] In some embodiments, the value of the fourth gap c2 is in the range of 3mm to 8mm, which ensures that the second blade crown 23 and the impeller housing 3a will not have axial impact, and also helps to reduce the volume of the booster fan 10.

[0215] For example, the fourth gap c2 can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0216] It should be noted that the values ​​of the third gap c1 between the reinforcing structure 311 and the first impeller 1 and the fourth gap c2 between the reinforcing structure 311 and the second impeller 2 along the axial direction of the first hub 11 can be equal or unequal, and are not limited here.

[0217] In some embodiments, the inner diameter of the first blade crown 13 on the air outlet side of the first impeller 1 is equal to the inner diameter of the impeller housing 3a at the location where the reinforcing structure 311 is provided.

[0218] In some embodiments, the inner diameter of the second blade crown 23 on the air inlet side of the second impeller 2 is equal to the inner diameter of the impeller housing 3a at the location where the reinforcing structure 311 is provided.

[0219] This configuration ensures that the first blade crown 13 can isolate the airflow on the pressure surface and suction surface of the first blade 12, and the second blade crown 23 can isolate the airflow on the pressure surface and suction surface of the second blade 22, without affecting the axial flow of the airflow.

[0220] In some embodiments, along the axial direction of the first hub 11, the length of the first crown 13 is not less than the length of the tip of the first blade 12, and the length of the first crown 13 is not greater than the length of the first hub 11.

[0221] For the convenience of understanding, as Figure 19 shown, the length of the first crown 13 is denoted as d, the length of the tip of the first blade 12 is denoted as e, and the length of the first hub 11 is denoted as f, e≤d≤f.

[0222] In some embodiments, along the axial direction of the second hub 21, the length of the second crown 23 is not less than the length of the tip of the second blade 22, and the length of the second crown 23 is not greater than the length of the second hub 21.

[0223] It should be noted that, along the axial direction of the first hub 11, the length of the first crown 13 and the length of the second crown 23 can be equal or not equal, which is not limited herein.

[0224] Exemplarily, in the specific embodiments of the present application, the first gap a1 is 1mm. The thickness b1 of the first crown 13 is 1mm. The third gap c1 is 5.5mm. The second gap a2 is 1mm. The thickness b2 of the second crown 23 is 1mm. The fourth gap c2 is 5.5mm. Along the axial direction of the first hub 11, the length of the first crown 13 is 26mm. Along the axial direction of the second hub 21, the length of the second crown 23 is 21mm. By such arrangement, on the basis of improving the structural strength of the first and second impellers 1 and 2 and the smoothness of the axial flow of the airflow, the noise reduction effect can also be improved.

[0225] 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 crown 13 can completely cover the plurality of first blades 12, so that the first crown 13 completely isolates the airflow on the pressure surface and the suction surface of the first blade 12, and the second crown 23 can completely cover the plurality of second blades 22, so that the second crown 23 completely isolates the airflow on the pressure surface and the suction surface of the second blade 22, and the noise reduction effect is better.

[0226] In some embodiments, as Figure 17 shown, along the axial direction of the first hub 11, the variation law of the outer diameter of the first crown 13 is the same as the variation law of the inner diameter of the impeller shell 3a corresponding to the first crown 13.

[0227] In some embodiments, as Figure 18 shown, along the axial direction of the second hub 21, the variation law of the outer diameter of the second crown 23 is the same as the variation law of the inner diameter of the impeller shell 3a corresponding to the second crown 23.

[0228] It should be noted that the shape of the outer circumferential surface of the first shroud 13 is the same as the shape of the inner wall of the impeller housing 3a corresponding to the first shroud 13, and the shape of the outer circumferential surface of the second shroud 23 is the same as the shape of the inner wall of the impeller housing 3a corresponding to the second shroud 23, thereby further improving the smoothness of the axial flow of the airflow.

[0229] Specifically, when the inner wall of the impeller housing 3a corresponding to the first shroud 13 and the inner wall of the impeller housing 3a corresponding to the second shroud 23 are both cylindrical surfaces, the outer circumferential surface of the first shroud 13 and the outer circumferential surface of the second shroud 23 are also both cylindrical surfaces; when the inner wall of the impeller housing 3a corresponding to the first shroud 13 and the inner wall of the impeller housing 3a corresponding to the second shroud 23 are both tapered surfaces gradually expanding or gradually tapering from the first impeller 1 to the second impeller 2, the outer circumferential surface of the first shroud 13 and the outer circumferential surface of the second shroud 23 are also both tapered surfaces gradually expanding or gradually tapering from the first impeller 1 to the second impeller 2.

[0230] In some embodiments, as shown in Figure 9 The fan unit 101 further includes a cap 71 and a tail fin 72, the cap 71 is arranged at one end of the first impeller 1 away from the second impeller 2, and the tail fin 72 is arranged at one end of the second impeller 2 away from the first impeller 1. By arranging the cap 71 and the tail fin 72, the noise generated by the airflow can be reduced.

[0231] Specifically, the cap 71 is fixedly connected with the first hub 11, and the tail fin 72 is fixedly connected with the second hub 21.

[0232] In some embodiments, as shown in Figure 20 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 arranged in the first housing 3a1, and the second impeller 2 and the second driving member 42 are arranged in the second housing 3a2, thereby improving the convenience of assembly.

[0233] It should be noted that when the fan unit 101 is provided in multiple, the first housings 3a1 of the multiple fan units 101 are fixedly connected or integrally formed into one first integrated housing, and the second housings 3a2 of the multiple fan units 101 are fixedly connected or integrally formed into one second integrated housing, thereby reducing the mold opening cost and simplifying the assembly.

[0234] In some embodiments, as shown in Figure 21 The booster fan 10 further includes a fan housing 3c, the first housing 3a1 and the second housing 3a2 are both fixedly arranged in the fan housing 3c, and a damping structure 3d is arranged between the first housing 3a1 and the fan housing 3c and between the second housing 3a2 and the fan housing 3c to achieve the purpose of damping and noise reduction.

[0235] Exemplarily, the fan shell 3c includes a first shell part 3c1 and a second shell part 3c2, and the first shell part 3c1 is detachably connected with the second shell part 3c2 through a second locking member 3b2 such as a second bolt, facilitating assembly of the supercharging fan 10.

[0236] Specifically, the first shell part 3c1 and the second shell part 3c2 are oppositely arranged along the radial direction of the first hub 11, and of course, the first shell part 3c1 and the second shell part 3c2 can also be oppositely arranged along the axial direction of the first hub 11.

[0237] The supercharging fan 10 of the embodiment meets the requirements of air volume and air pressure, has the advantages of low total noise, low order noise and friendly sound quality, has a high NVH level, can solve the problems of large size and difficult arrangement of the existing supercharging fan, can greatly release the storage space in the vehicle, improve the usability of the product in the vehicle, realize the miniaturization of the supercharging fan 10, and bring greater product power improvement of the vehicle.

[0238] Embodiment Three

[0239] In the prior art, the axial flow supercharging fan can be directly matched with an air duct due to its axial inlet and outlet characteristics, air flow is avoided from being greatly turned, and the axial flow supercharging fan is the best choice for miniaturization of the supercharging fan. The axial flow supercharging fan has the characteristics of large air volume and low air pressure, but due to the relatively small number of blades and the relatively high speed, the wake of the blade or the related vortex generated by the blade will continuously hit the structure located downstream of the impeller at a frequency related to the speed of the impeller or a frequency several times the speed of the impeller, thereby generating certain fixed frequency noise, especially order noise, which is most obvious. Such sound is easy to be distinguished by the human ear, thereby causing discomfort in sound, and further causing poor sound quality of the axial flow supercharging fan, which seriously restricts the application scenarios of the axial flow supercharging fan.

[0240] To solve this problem, as shown in Figure 22 The embodiment of the present application also provides a supercharging fan, and in the embodiment, the supercharging fan 10 is a series axial flow supercharging fan, and the supercharging fan 10 includes a fan unit 101, and the fan unit 101 includes a first impeller 1, a second impeller 2 and an impeller shell 3a.

[0241] The impeller shell 3a includes a mounting cavity 31 and a first opening 32 and a second opening 33 which are in communication with the mounting cavity 31, and the first impeller 1 and the second impeller 2 are rotatably arranged in the mounting cavity 31, the air inlet side of the first impeller 1 faces the first opening 32, and the air outlet side of the second impeller 2 faces the second opening 33. In the embodiment, the first opening 32 and the second opening 33 are sequentially arranged along the axial direction of the first hub 11.

[0242] The rotation directions of the first impeller 1 and the second impeller 2 are the same, in other words, the first impeller 1 and the second impeller 2 are coaxially connected in series, under the premise of ensuring the dynamic balance and static balance of the axial booster fan, the purpose of noise reduction is realized, and the problems of large order noise and poor sound quality of the axial booster fan are solved, so that the axial booster fan can provide wind volume and wind pressure that meet the requirements, and at the same time meet the requirements of low noise and good sound quality.

[0243] As shown in Figure 23 and Figure 24 , the first impeller 1 includes a first hub 11 and a plurality of first blades 12, the plurality of first blades 12 are arranged at intervals along the circumference of the first hub 11, and the plurality of first blades 12 are unevenly distributed along the circumference of the first hub 11; the phase angle between adjacent two first blades 12 is in the range of 288° / N1~432° / N1, and N1 is the number of first blades 12.

[0244] As shown in Figure 25 and Figure 26 , the air inlet side of the second impeller 2 is arranged opposite to the air outlet side of the first impeller 1; the second impeller 2 includes a second hub 21 and a plurality of second blades 22, the plurality of second blades 22 are arranged at intervals along the circumference of the second hub 21, and the plurality of second blades 22 are unevenly distributed along the circumference of the second hub 21; the phase angle between adjacent two second blades 22 is in the range of 288° / N2~432° / N2, and N2 is the number of second blades 22.

[0245] The first blades 12 and the second blades 22 are arranged as described above, under the premise of ensuring the dynamic balance and static balance of the axial booster fan, the total noise generated by the rotation of the first impeller 1 and the second impeller 2 can be effectively reduced, and the problems of large order noise, poor sound quality and low NVH level of the axial booster fan are solved, so that the axial booster fan can provide wind volume and wind pressure that meet the requirements, and at the same time meet the requirements of low noise and good sound quality.

[0246] In some embodiments, the booster fan 10 includes a plurality of fan units 101, and the plurality of fan units 101 are arranged in a direction perpendicular to the axial direction of the first hub 11. In this way, the plurality of fan units 101 can correspond to different areas in the vehicle cabin respectively, and the wind volume and wind speed of different areas in the vehicle cabin can be independently adjusted through the plurality of fan units 101, thereby improving the comfort of the driver and passengers.

[0247] In specific embodiments of the present application, two fan units 101 can be provided, of course, one, three, four or even more fan units 101 can also be provided, which are not limited herein.

[0248] 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 is coaxially arranged with the first hub 11.

[0249] In some embodiments, the booster fan 10 further comprises a first driving member corresponding to each first impeller 1, and a second driving member corresponding to each second impeller 2, the first driving member is in transmission connection with the corresponding first impeller 1 to drive the corresponding first impeller 1 to rotate; the second driving member is in transmission connection with the corresponding second blade 22 to drive the corresponding second impeller 2 to rotate.

[0250] Specifically, the first driving member comprises a first motor, and the second driving member comprises a second motor. The output shaft of the first motor is connected with the first hub 11 of the corresponding first impeller 1, and the output shaft of the second motor is connected with the second hub 21 of the corresponding second impeller 2, thereby realizing the control of the rotation speed of the first impeller 1 and the second impeller 2 by controlling the first motor and the second motor respectively.

[0251] Exemplarily, the output shaft of the first motor and the first hub 11 of the corresponding first impeller 1 are connected through a connecting flange, and the output shaft of the second motor and the second hub 21 of the corresponding second impeller 2 are connected through a connecting flange.

[0252] In other embodiments, the first impeller 1 and the second impeller 2 can also be driven to rotate by one driving mechanism, for example, the driving mechanism comprises a driving member and a reversing assembly, the first impeller 1 is directly connected with the output shaft of the driving member, and the second impeller 2 is connected with the output shaft of the driving member through the reversing assembly, thereby making the rotation directions of the first impeller 1 and the second impeller 2 opposite. Specifically, the driving member is a motor, and the reversing assembly is a gear set, of course, the reversing assembly can also be other reversing structures in the prior art, which are not limited here.

[0253] In some embodiments, the number of first blades 12 is 5-11. By limiting the number of first blades 12 as described above, the convenience of industrial mold opening can be ensured, and the air volume and pressure performance of the axial booster fan can be maintained.

[0254] In some embodiments, the number of second blades 22 is 5-11. By limiting the number of second blades 22 as described above, the convenience of industrial mold opening can be ensured, and the air volume and pressure performance of the axial booster fan can be maintained.

[0255] In some embodiments, as Figure 14As shown, in the two adjacent first vanes 12, the projection of the leading edge x1 of one of the first vanes 12 on the preset plane does not intersect with the trailing edge y1 of the other first vane 12. The preset plane is perpendicular to the axial direction of the first hub 11. In this way, the convenience of industrial mold opening and the air volume and pressure performance of the axial flow booster fan can be further improved.

[0256] In some embodiments, as shown in FIG. 1, the first vane 12 is provided with a first preset vane and a plurality of second preset vanes, and the second preset vanes on both sides of the first preset vane are symmetrically arranged with respect to the first preset vane, thereby facilitating better reduction of order noise. Figure 15 As shown, in the two adjacent second vanes 22, the projection of the leading edge x2 of one of the second vanes 22 on the preset plane does not intersect with the trailing edge y2 of the other second vane 22. In this way, the convenience of industrial mold opening and the air volume and pressure performance of the axial flow booster fan can be further improved.

[0257] In some embodiments, the plurality of first vanes 12 includes a first preset vane and a plurality of second preset vanes, and the second preset vanes on both sides of the first preset vane are symmetrically arranged with respect to the first preset vane, thereby facilitating better reduction of order noise.

[0258] In some embodiments, the plurality of second vanes 22 includes a third preset vane and a plurality of fourth preset vanes, and the fourth preset vanes on both sides of the third preset vane are symmetrically arranged with respect to the third preset vane, thereby facilitating better reduction of order noise.

[0259] It should be noted that in other embodiments, the second preset vanes on both sides of the first preset vane can also be asymmetrically arranged, and the fourth preset vanes on both sides of the third preset vane can also be asymmetrically arranged, which can also achieve the purpose of improving the noise reduction effect.

[0260] In some embodiments, the number of first vanes 12 and the number of second vanes 22 are both odd.

[0261] In some embodiments, the number of first vanes 12 and the number of second vanes 22 are not equal.

[0262] In this way, it 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.

[0263] In some embodiments, the number of first vanes 12 is greater than the number of second vanes 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 the airflow interference between the first impeller 1 and the second impeller 2.

[0264] In a specific embodiment of the present application, the number of the 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). Exemplarily, the phase angles between two adjacent first blades 12 or 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 the 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.

[0265] In another specific embodiment of the present application, the number of the first blades 12 is 11, and the phase angle between two adjacent first blades 12 ranges from 26° to 39° (i.e. 288° / 11 to 432° / 11). Exemplarily, the phase angles between two adjacent first blades 12 or 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 the 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.

[0266] In some embodiments, as shown in FIG. 2, a first phase angle a is provided between the root and the tip of the trailing edge y1 of the first blade 12 in the rotation direction of the first impeller 1 and with the rotation direction of the first impeller 1 as a positive value, in other words, the first blade 12 is designed with a curved angle. Figure 16

[0267] In some embodiments, a second phase angle β is provided between the root and the tip of the leading edge x2 of the second blade 22 in the rotation direction of the second impeller 2 and with the rotation direction of the second impeller 2 as a positive value, in other words, the second blade 22 is designed with a curved angle.

[0268] ​In this way, the pressure fluctuation caused by the wake of the first blades 12 at different radial heights can be dispersed in time, that is, the pressure fluctuation caused by the wake of the first blades 12 at different radial heights can be distributed at different times, thereby eliminating the pressure fluctuation, which can greatly reduce the order noise problem of the tandem axial supercharging fan and slightly reduce the total noise of the tandem axial supercharging fan.

[0269] In some embodiments, the value of a+β ranges from 50%*360° / N1 to 150%*360° / N1, and both a and β are not less than 20°. When a+β is greater than 50%*360° / N1, the first impeller 1 and the second impeller 2 can be allowed to interfere with the wake of the first blades 12 and the leading edge x2 of the second blades 22 during rotation, and the impact at different radial heights can be dispersed at different times to avoid noise amplification caused by simultaneous or short-term impact, thereby forming protruding order noise. When a+β is less than 150%*360° / N1, the difficulty of demolding caused by excessive bending of the first blades 12 and the second blades 22 can be avoided, and if a+β exceeds 360° / N1, the effect of improving order noise by the bending angle of the first blades 12 and the second blades 22 will also be weakened, so it is not necessary to excessively bend the first blades 12 and the second blades 22.

[0270] In specific embodiments of the present application, the number of first blades 12 is 9, the first phase angle a is 20°, and the second phase angle β is 21°, which can greatly reduce the order noise problem of the tandem axial supercharging fan, and facilitate the demolding of the first blades 12 and the second blades 22, and reduce the processing difficulty of the first blades 12 and the second blades 22.

[0271] In some embodiments, the first impeller 1 further comprises a first shroud 13, the first shroud 13 is annular, the first shroud 13 is sleeved on the outer side of the plurality of first blades 12, and the plurality of first blades 12 are fixedly connected to the first shroud 13 away from the one end of the first hub 11 in the radial direction of the first hub 11.

[0272] By wrapping the plurality of first blades 12 with the first shroud 13, the airflow of the pressure surface and the suction surface at the top of the first blades 12 can be isolated, which can hinder the leakage of the airflow of the pressure surface and the suction surface at the top of the first blades 12 to generate a larger vortex, thereby avoiding the vortex from causing noise, achieving the purpose of reducing the total noise of the supercharging fan 10, improving the order noise level, and improving the sound quality of the supercharging fan 10.

[0273] In some embodiments, the second impeller 2 further comprises a second shroud 23, the second shroud 23 is annular, and the second shroud 23 is sleeved outside the plurality of second blades 22, and the plurality of second blades 22 are fixedly connected to the second shroud 23 away from one end of the second hub 21 in the radial direction of the second hub 21.

[0274] By wrapping the plurality of second blades 22 with the second shroud 23, the airflow of the pressure surface and the suction surface at the top of the second blade 22 is isolated, which can hinder the leakage of the airflow of the pressure surface and the suction surface at the top of the second blade 22 to generate a larger vortex, thereby avoiding the vortex from causing noise, achieving the purpose of reducing the total noise of the supercharging fan 10, improving the order noise level, and improving the sound quality of the supercharging fan 10.

[0275] In some embodiments, as shown in FIG. 1, Figure 17 a first gap a1 is provided between the first shroud 13 and the inner wall of the impeller shell 3a in the radial direction of the first hub 11, thereby preventing the first shroud 13 from rubbing against the inner wall of the impeller shell 3a due to radial runout of the first impeller 1.

[0276] In some embodiments, the first gap a1 has a value in the range of 0.5mm to 2mm, which not only ensures that the first shroud 13 does not rub against the inner wall of the impeller shell 3a, but also helps to reduce the size of the supercharging fan 10.

[0277] For example, the first gap a1 can be any value between 0.5mm and 2mm, such as 0.5mm, 1mm, 1.5mm, or 2mm.

[0278] In some embodiments, as shown in FIG. 1, Figure 18 a second gap a2 is provided between the second shroud 23 and the inner wall of the impeller shell 3a in the radial direction of the second hub 21, thereby preventing the second shroud 23 from rubbing against the inner wall of the impeller shell 3a due to radial runout of the second impeller 2.

[0279] In some embodiments, the second gap a2 has a value in the range of 0.5mm to 2mm, which not only ensures that the second shroud 23 does not rub against the inner wall of the impeller shell 3a, but also helps to reduce the size of the supercharging fan 10.

[0280] For example, the second gap a2 can be any value between 0.5mm and 2mm, such as 0.5mm, 1mm, 1.5mm, or 2mm.

[0281] It should be noted that the first gap a1 between the first shroud 13 and the inner wall of the impeller shell 3a and the second gap a2 between the second shroud 23 and the inner wall of the impeller shell 3a can be equal or not equal, which is not limited here.

[0282] In some embodiments, as shown in FIG. 1, the thickness b1 of the first shroud 13 is in the range of 0.5mm to 1.5mm along the radial direction of the first hub 11, thereby ensuring the structural strength of the first shroud 13 so that the first shroud 13 can better isolate the airflow on the pressure surface and the suction surface of the first blade 12. Figure 17

[0283] Exemplarily, the thickness b1 of the first shroud 13 can be any value between 0.5mm and 1.5mm, such as 0.5mm, 1mm or 1.5mm.

[0284] In some embodiments, as shown in FIG. 1, the thickness b2 of the second shroud 23 is in the range of 0.5mm to 1.5mm along the radial direction of the second hub 21, thereby ensuring the structural strength of the second shroud 23 so that the second shroud 23 can better isolate the airflow on the pressure surface and the suction surface of the second blade 22. Figure 18

[0285] Exemplarily, the thickness b2 of the second shroud 23 can be any value between 0.5mm and 1.5mm, such as 0.5mm, 1mm or 1.5mm.

[0286] It should be noted that the thickness b1 of the first shroud 13 and the thickness b2 of the second shroud 23 can be equal or not equal, which is not limited here.

[0287] In some embodiments, the inner wall of the impeller shell 3a is provided with a reinforcing structure 311, which is located between the first impeller 1 and the second impeller 2 along the axial direction of the first hub 11, so as to increase the structural strength of the impeller shell 3a through the reinforcing structure 311 and prolong the service life.

[0288] Further, the impeller shell 3a is also provided with a support structure 312 for supporting the first driving member and the second driving member, and the support structure 312 is fixedly connected with the reinforcing structure 311, so as to improve the mounting stability of the first driving member and the second driving member. It should be noted that the support structure 312 can be provided with one, so as to simultaneously support the first driving member and the second driving member through one support structure 312. The support structure 312 can also be provided with two, so as to support the first driving member and the second driving member respectively through two support structures. Of course, the support structure 312 can also be provided with more, so that the first driving member and the second driving member are supported respectively through multiple support structures 312.

[0289] Exemplarily, the reinforcing structure 311 and the support structure 312 are both protruding ribs protruding on the inner wall of the impeller shell 3a.

[0290] In some embodiments, as shown in FIG. 1, the thickness b1 of the first shroud 13 is in the range of 0.5mm to 1.5mm along the radial direction of the first hub 11, thereby ensuring the structural strength of the first shroud 13 so that the first shroud 13 can better isolate the airflow on the pressure surface and the suction surface of the first blade 12. Figure 17 ​​As shown, along the axial direction of the first hub 11, a third gap c1 is provided between the reinforcing structure 311 and the first blade crown 13, which can prevent the first impeller 1 from axially moving and causing the first blade crown 13 to collide with the impeller housing 3a.

[0291] In some embodiments, the value of the third gap c1 is in the range of 3mm to 8mm, which ensures that the first blade crown 13 and the impeller housing 3a will not have axial impact, and also helps to reduce the volume of the booster fan 10.

[0292] For example, the third gap c1 can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0293] In some embodiments, such as Figure 18 As shown, along the axial direction of the second hub 21, a fourth gap c2 is provided between the reinforcing structure 311 and the second blade crown 23, which can prevent the second impeller 2 from axially moving and causing the second blade crown 23 to collide with the impeller housing 3a.

[0294] In some embodiments, the value of the fourth gap c2 is in the range of 3mm to 8mm, which ensures that the second blade crown 23 and the impeller housing 3a will not have axial impact, and also helps to reduce the volume of the booster fan 10.

[0295] For example, the fourth gap c2 can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0296] It should be noted that the values ​​of the third gap c1 between the reinforcing structure 311 and the first impeller 1 and the fourth gap c2 between the reinforcing structure 311 and the second impeller 2 along the axial direction of the first hub 11 can be equal or unequal, and are not limited here.

[0297] In some embodiments, the inner diameter of the first blade crown 13 on the air outlet side of the first impeller 1 is equal to the inner diameter of the impeller housing 3a at the location where the reinforcing structure 311 is provided.

[0298] In some embodiments, the inner diameter of the second blade crown 23 on the air inlet side of the second impeller 2 is equal to the inner diameter of the impeller housing 3a at the location where the reinforcing structure 311 is provided.

[0299] This configuration ensures that the first blade crown 13 can isolate the airflow on the pressure surface and suction surface of the first blade 12, and the second blade crown 23 can isolate the airflow on the pressure surface and suction surface of the second blade 22, without affecting the axial flow of the airflow.

[0300] In some embodiments, along the axial direction of the first hub 11, the length of the first blade crown 13 is not less than the length of the tip of the first blade 12, and the length of the first blade crown 13 is not greater than the length of the first hub 11.

[0301] For ease of understanding, such as Figure 19 As shown, the length of the first leaf crown 13 is denoted as d, the length of the tip of the first blade 12 is denoted as e, and the length of the first hub 11 is denoted as f, where e≤d≤f.

[0302] In some embodiments, along the axial direction of the second hub 21, the length of the second blade crown 23 is not less than the length of the blade tip of the second blade 22, and the length of the second blade crown 23 is not greater than the length of the second hub 21.

[0303] It should be noted that the lengths of the first blade crown 13 and the second blade crown 23 along the axial direction of the first hub 11 can be equal or unequal, and no limitation is made here.

[0304] For example, in a specific embodiment of the present invention, the first gap a1 is 1 mm. The thickness b1 of the first blade crown 13 is 1 mm. The third gap c1 is 5.5 mm. The second gap a2 is 1 mm. The thickness b2 of the second blade crown 23 is 1 mm. The fourth gap c2 is 5.5 mm. Along the axial direction of the first hub 11, the length of the first blade crown 13 is 26 mm. Along the axial direction of the second hub 21, the length of the second blade crown 23 is 21 mm. This configuration improves the structural strength of the first impeller 1 and the second impeller 2, as well as the smoothness of the axial flow of airflow, and also enhances the noise reduction effect.

[0305] It should be noted that, whether along the axial direction or the circumferential direction of the first hub 11, the first blade crown 13 can completely cover the multiple first blades 12, thereby completely isolating the airflow on the pressure surface and suction surface of the first blades 12. Similarly, the second blade crown 23 can completely cover the multiple second blades 22, thereby completely isolating the airflow on the pressure surface and suction surface of the second blades 22, resulting in better noise reduction.

[0306] In some embodiments, such as Figure 17 As shown, along the axial direction of the first hub 11, the variation law of the outer diameter of the first blade crown 13 is the same as the variation law of the inner diameter of the impeller housing 3a corresponding to the first blade crown 13.

[0307] In some embodiments, such as Figure 18 As shown, along the axial direction of the second hub 21, the variation law of the outer diameter of the second blade crown 23 is the same as the variation law of the inner diameter of the impeller housing 3a corresponding to the second blade crown 23.

[0308] It should be noted that the shape of the outer peripheral surface of the first blade crown 13 is the same as the shape of the inner wall of the impeller housing 3a corresponding to the first blade crown 13, and the shape of the outer peripheral surface of the second blade crown 23 is the same as the shape of the inner wall of the impeller housing 3a corresponding to the second blade crown 23, which is conducive to further improving the smoothness of the axial flow of air.

[0309] Specifically, when the inner walls of the impeller housing 3a corresponding to the first blade crown 13 and the inner walls of the impeller housing 3a corresponding to the second blade crown 23 are both cylindrical surfaces, the outer peripheral surfaces of the first blade crown 13 and the second blade crown 23 are also cylindrical surfaces; when the inner walls of the impeller housing 3a corresponding to the first blade crown 13 and the inner walls of the impeller housing 3a corresponding to the second blade crown 23 are both conical surfaces that gradually expand or contract from the first impeller 1 to the second impeller 2, the outer peripheral surfaces of the first blade crown 13 and the second blade crown 23 are also conical surfaces that gradually expand or contract from the first impeller 1 to the second impeller 2.

[0310] In some embodiments, such as Figure 22 as well as Figures 27 to 28 As shown, the series axial flow booster fan also includes a first air guide 5 corresponding to the first impeller 1. The first air guide 5 is located on the air outlet side of the first impeller 1. The first air guide 5 includes a third hub 51 and a plurality of first guide vanes 52. The third hub 51 is fixed in the mounting cavity 31. The plurality of first guide vanes 52 are arranged at intervals along the circumference of the third hub 51. The ends of the plurality of first guide vanes 52 that are radially away from the third hub 51 are all fixedly connected to the impeller housing 3a.

[0311] Because the rotation of the first impeller 1 imparts a certain degree of vortex to the airflow, the first air guide 5 can deflect the vortex-bearing airflow to the axial direction of the first hub 11, converting some of the dynamic pressure into static pressure, thus eliminating vortex and improving the pressurization effect. Simultaneously, the first drive component used to drive the rotation of the first impeller 1 can be installed on the third hub 51, so that the first guide vane 52 can support the third hub 51, improving the installation stability of the first drive component.

[0312] In some embodiments, such as Figure 22 as well as Figures 29 to 30 As shown, the series axial flow booster fan also includes a second air guide 6 corresponding to the second impeller 2. The second air guide 6 is located on the air outlet side of the second impeller 2. The second air guide 6 includes a fourth hub 61 and a plurality of second guide vanes 62. The fourth hub 61 is fixedly installed in the mounting cavity 31. The plurality of second guide vanes 62 are spaced apart on the fourth hub 61 along the circumference of the fourth hub 61. The ends of the plurality of second guide vanes 62 that are radially away from the fourth hub 61 are all fixedly connected to the impeller housing 3a.

[0313] Because the rotation of the second impeller 2 imparts a certain degree of vortex to the airflow, the aforementioned second air guide 6 can deflect the vortex-bearing airflow to the axial direction of the second hub 21, converting some of the dynamic pressure into static pressure, thus achieving devortexing and improving the pressurization effect. Simultaneously, the second drive component used to drive the rotation of the second impeller 2 is installed on the fourth hub 61, so that the second guide vane 62 provides support to the fourth hub 61, improving the installation stability of the second drive component.

[0314] 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.

[0315] It should be noted that the axis of the third hub 51 coincides with the axis of the first hub 11, and the axis of the fourth hub 61 coincides with the axis of the second hub 21. Since the axis of the second hub 21 coincides with the axis of the first hub 11, it means that the second hub 21, the third hub 51, and the fourth hub 61 are all coaxially set with the first hub 11.

[0316] The main sources of noise in a series axial flow booster fan are the interference between the airflow generated by the rotation of the first impeller 1 and the first air guide 5, and the noise generated by the interference between the airflow generated by the rotation of the second impeller 2 and the second air guide 6. In particular, the order noise is the most obvious and can easily form a very sharp sound, causing discomfort to the ears of drivers and passengers.

[0317] To address this issue, in embodiments of the present invention, a plurality of first guide vanes 52 are unevenly distributed along the circumference of the third hub 51, and a plurality of second guide vanes 62 are unevenly distributed along the circumference of the fourth hub 61.

[0318] The aforementioned first guide vane 52 and second guide vane 62 can effectively prevent the airflow generated by the rotation of the first impeller 1 and the second impeller 2 from continuously striking the first guide vane 52 and the second guide vane 62 at frequencies related to the rotational speed of the first impeller 1 (including frequencies several times the rotational speed of the first impeller 1) and frequencies related to the rotational speed of the second impeller 2 (including frequencies several times the rotational speed of the second impeller 2), thereby avoiding discomfort to the ears of the driver and passengers.

[0319] In some embodiments, the phase angle between two adjacent first guide vanes 52 ranges from 180° / n1 to 540° / n1, where n1 is the number of first guide vanes 52. The phase angle between two adjacent second guide vanes 62 ranges from 180° / n2 to 540° / n2, where n2 is the number of second guide vanes 62. This arrangement helps to further improve the noise reduction effect. Since both the first guide vanes 52 and the second guide vanes 62 are stationary structural components and do not rotate, the multiple first guide vanes 52 of the first air guide 5 can be arranged with a greater degree of non-uniformity compared to the multiple first blades 12 of the first impeller 1; similarly, the multiple second guide vanes 62 of the second air guide 6 can be arranged with a greater degree of non-uniformity compared to the multiple second blades 22 of the second impeller 2.

[0320] In some embodiments, the number of first guide vanes 52 is 9 to 15. Compared to the first blade 12, the first guide vanes 52 are smaller in size, so a larger number can be provided, which is beneficial to improving the support stability of the first guide vanes 52 for the first drive member.

[0321] In some embodiments, the number of second guide vanes 62 is 9 to 15. Compared to the second blade 22, the second guide vanes 62 are smaller in size, so a larger number can be provided, which is beneficial to improving the support stability of the second guide vanes 62 for the second drive member.

[0322] In some embodiments, the bending angle of the first guide vane 52 is in the range of 30° to 50°, and the bending angle of the first guide vane 52 gradually increases from the root to the tip of the first guide vane 52, thereby improving the despinning effect.

[0323] For example, the bending angle of the first guide vane 52 can be any value between 30° and 50°, such as 30°, 35°, 40°, 45° or 50°.

[0324] In some embodiments, the bending angle of the second guide vane 62 is in the range of 30° to 50°, and the bending angle of the second guide vane 62 gradually increases from the root to the tip, thereby improving the despinning effect.

[0325] For example, the bending angle of the second guide vane 62 can be any value between 30° and 50°, such as 30°, 35°, 40°, 45° or 50°.

[0326] In some embodiments, the geometric outlet angle of the first guide vane 52 is in the range of 80° to 100°, thereby improving the deswirl effect.

[0327] For example, the geometric outlet angle of the first guide vane 52 can be any value between 80° and 100°, such as 80°, 85°, 90°, 95° or 100°.

[0328] In some embodiments, the geometric outlet angle of the second guide vane 62 is in the range of 80° to 100°, thereby improving the deswirl effect.

[0329] For example, the geometric outlet angle of the second guide vane 62 can be any value between 80° and 100°, such as 80°, 85°, 90°, 95° or 100°.

[0330] In some embodiments, the plurality of first guide vanes 52 include a first preset guide vane and a plurality of second preset guide vanes. The second preset guide vanes located on both sides of the first preset guide vane are symmetrically arranged about the first preset guide vane, thereby better eliminating the order noise generated by the mutual interference between the first impeller 1 and the first air guide 5.

[0331] In some embodiments, the plurality of second guide vanes 62 include a third preset guide vane and a plurality of fourth preset guide vanes. The fourth preset guide vanes located on both sides of the third preset guide vane are symmetrically arranged about the third preset guide vane, thereby better eliminating the order noise generated by the mutual interference between the second impeller 2 and the second air guide 6.

[0332] It should be noted that in some other embodiments, the second preset guide vanes located on both sides of the first preset guide vane can be asymmetrically arranged with respect to the first preset guide vane, and the fourth preset guide vanes located on both sides of the third preset guide vane can also be asymmetrically arranged with respect to the first preset guide vane, which can also achieve the effect of noise reduction.

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

[0334] In a specific embodiment of the present invention, the number of first guide vanes 52 is 11, and the phase angle between two adjacent first guide vanes 52 ranges from 17.1° to 49.1° (i.e., 180° / 11 to 540° / 11). For example, the phase angle between two adjacent first guide vanes 52 is 36.5°, 35.3°, 33.3°, 31.1°, 29.4°, 28.8°, 29.4°, 31.1°, 33.3°, 35.3° and 36.5° respectively. The number of second guide vanes 62 is 13, and the phase angle between two adjacent second guide vanes 62 ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, the phase angles between two adjacent second guide vanes 62 are 35.1°, 33.4°, 30.4°, 26.8°, 23.3°, 20.9°, 20.0°, 20.9°, 23.3°, 26.8°, 30.4°, 33.4° and 35.1° respectively.

[0335] In some embodiments, the phase angle between two adjacent first guide vanes 52 is not equal to the phase angle between two adjacent second guide vanes 62, thereby making the uneven distribution of the multiple first guide vanes 52 of the first air guide 5 different from the uneven distribution of the multiple second guide vanes 62 of the second air guide 6, so as to further reduce the order noise derived from the mutual interference between the first impeller 1 and the first air guide 5, and the mutual interference between the second impeller 2 and the second air guide 6, and avoid the main order overlap of the first impeller 1 and the second impeller 2, which would lead to the amplification of noise at certain frequencies (such as 450Hz to 800Hz), and further improve the noise reduction effect.

[0336] It should be noted that in some other embodiments, the number of first guide vanes 52 can be equal to the number of second guide vanes 62. Furthermore, the phase angle between two adjacent first guide vanes 52 is not equal to the phase angle between two adjacent second guide vanes 62. When it is not possible to design the number of first guide vanes 52 and the number of second guide vanes 62 to be unequal, the phase angle between two adjacent first guide vanes 52 can be made unequal to the phase angle between two adjacent second guide vanes 62, thereby further reducing the order noise generated by the interference between the first impeller 1 and the first air guide 5, and the second impeller 2 and the second air guide 6, to achieve the purpose of noise reduction.

[0337] In a specific embodiment of the present invention, there are 13 first guide vanes 52, and the phase angle between two adjacent first guide vanes 52 ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, the phase angles between two adjacent first guide vanes 52 are 31.4°, 30.6°, 29.1°, 27.2°, 25.5°, 24.3°, 23.9°, 24.3°, 25.5°, 27.2°, 29.1°, 30.6°, and 31.4° respectively. There are also 13 second guide vanes 62, and the phase angle between two adjacent second guide vanes 62 ranges from 13.8° to 41.5° (i.e., 180° / 13 to 540° / 13). For example, the phase angles between two adjacent second guide vanes 62 are 35.1°, 33.4°, 30.4°, 26.8°, 23.3°, 20.9°, 20.0°, 20.9°, 23.3°, 26.8°, 30.4°, 33.4° and 35.1° respectively.

[0338] In some embodiments, in two adjacent first guide vanes 52, the projection of the leading edge of one first guide vane 52 onto a preset plane does not intersect with the trailing edge of the other first guide vane 52, thereby improving the convenience of industrial mold making.

[0339] In some embodiments, in two adjacent second guide vanes 62, the projection of the leading edge of one second guide vane 62 onto a preset plane does not intersect with the trailing edge of the other second guide vane 62, thereby improving the convenience of industrial mold making.

[0340] In some embodiments, a fifth gap is provided between the first blade crown 13 and the first air guide 5 along the axial direction of the first hub 11, thereby preventing the first impeller 1 from axially moving and causing the first blade crown 13 and the first air guide 5 to collide axially.

[0341] In some embodiments, the fifth gap ranges from 3mm to 8mm, which ensures that the first blade crown 13 and the first air guide 5 will not have axial impact, while also helping to reduce the size of the booster fan 10.

[0342] For example, the fifth gap can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0343] In some embodiments, a sixth gap is provided between the second blade crown 23 and the second air guide 6 along the axial direction of the second hub 21, thereby preventing the second impeller 2 from axially moving and causing the second blade crown 23 to collide with the first air guide 5.

[0344] In some embodiments, the sixth gap ranges from 3mm to 8mm, which ensures that the first blade crown 13 and the first air guide 5 will not have axial impact, while also helping to reduce the size of the booster fan 10.

[0345] For example, the sixth gap can be any value between 3mm and 8mm, such as 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0346] It should be noted that the values ​​of the fifth gap between the first blade crown 13 and the first air guide 5 and the sixth gap between the second blade crown 23 and the second air guide 6 along the axial direction of the first hub 11 can be the same or different, and are not limited here.

[0347] In some embodiments, such as Figure 22 As shown, the fan unit 101 also includes a cap 71 and a tail cone 72. The cap 71 is located at the end of the first impeller 1 away from the second impeller 2, and the tail cone 72 is located at the end of the second impeller 2 away from the first impeller 1. By providing the cap 71 and the tail cone 72, the noise generated by the airflow can be reduced.

[0348] Specifically, the cap 71 is fixedly connected to the first wheel hub 11, and the tail cone 72 is fixedly connected to the second wheel hub 21.

[0349] In some embodiments, such as Figure 20 As shown, the impeller housing 3a includes a first housing 3a1 and a second housing 3a2. The first housing 3a1 and the second housing 3a2 are detachably connected by a first locking member 3b1, such as a first bolt. The first impeller 1, the first air guide 5 and the first drive member are all located in the first housing 3a1, and the second impeller 2, the second air guide 6 and the second drive member are all located in the second housing 3a2, thereby improving the convenience of assembly.

[0350] It should be noted that when there are multiple fan units 101, the first housings 3a1 of the multiple fan units 101 can be fixedly connected or integrally formed into a first integrated housing, and the second housings 3a2 of the multiple fan units 101 can be fixedly connected or integrally formed into a second integrated housing, thereby reducing the mold opening cost and simplifying the assembly.

[0351] In some embodiments, such as Figure 21 As shown, the booster fan 10 also includes a fan housing 3c. The first housing 3a1 and the second housing 3a2 are both fixed inside the fan housing 3c. A vibration damping structure 3d is provided between the first housing 3a1 and the fan housing 3c, and between the second housing 3a2 and the fan housing 3c, in order to achieve the purpose of vibration reduction and noise reduction.

[0352] For example, the fan housing 3c includes a first housing portion 3c1 and a second housing portion 3c2. The first housing portion 3c1 and the second housing portion 3c2 are detachably connected by a second locking member 3b2 such as a second bolt, which facilitates the assembly of the booster fan 10.

[0353] Specifically, the first shell portion 3c1 and the second shell portion 3c2 are arranged opposite each other along the radial direction of the first hub 11. Of course, the first shell portion 3c1 and the second shell portion 3c2 can also be arranged opposite each other along the axial direction of the first hub 11.

[0354] The booster fan 10 in this embodiment, while meeting the air volume and air pressure requirements, has the advantages of low total noise, low order noise, and friendly sound quality. It has a high NVH level and can solve the problems of large size and difficult layout of existing booster fans. In this way, it can greatly free up the storage space in the vehicle, improve the usability of the product in the vehicle, realize the miniaturization of the booster fan 10, and bring greater improvement to the vehicle product competitiveness.

[0355] Example 4

[0356] like Figures 31 to 33 As shown, embodiments of the present invention also provide an air conditioning system, a thermal management system, and a vehicle. The vehicle includes a cabin and a thermal management system. The thermal management system includes an air conditioning system for supplying air to the space inside the cabin.

[0357] The air conditioning system includes an air conditioning unit 20 and any of the above-mentioned booster fans 10 (for example, the booster fan 10 can be a counter-rotating axial flow booster fan or a series axial flow booster fan according to the above embodiments of the present invention). The air conditioning unit 20 includes an air conditioning outlet 201 (specifically, it can be a front-blowing air outlet, such as a rear-blowing air outlet). The booster fan 10 is located at the air conditioning outlet 201. The air inlet of the booster fan 10 is connected to the air conditioning outlet 201 so that the booster fan 10 draws air from the air conditioning outlet 201 and pressurizes it.

[0358] It should be noted that traditional automotive air conditioning units and booster fans 10 are set up independently, and traditional booster fans 10 are relatively large in size, making it difficult to integrate them behind the air conditioning outlet 201 of the automotive air conditioning unit, and requiring a large amount of installation space.

[0359] The thermal management system in this embodiment integrates the booster fan 10 with the air conditioning outlet 201 of the air conditioning unit 20, which can significantly reduce the space occupied by the air conditioning system while ensuring that the air volume and air pressure provided by the air conditioning system meet the requirements, thus achieving a compact design of the air conditioning system.

[0360] In this embodiment, the air outlet of the booster fan 10 is connected to the vehicle cabin, thereby enabling the booster fan 10 to adjust the air volume and speed delivered into the vehicle cabin while significantly reducing the space required for the air conditioning system.

[0361] The air conditioning system, thermal management system, and vehicle of the present invention, by applying the above-mentioned booster fan 10, can achieve a compact design of the thermal management system, while matching the NVH requirements of the vehicle, enhancing the usability of the compact thermal management system in the vehicle, and improving the product competitiveness of the vehicle.

[0362] When the booster fan 10 includes multiple fan units 101, the multiple fan units 101 are arranged along the air outlet direction perpendicular to the air outlet 201.

[0363] Specifically, such as Figure 31 and Figure 32 As shown, the air outlet of the booster fan 10 can be directly connected to the vehicle cabin, or it can be connected via a connecting pipe 301. Of course, one or more connecting pipes 301 can be provided; in other words, each connecting pipe 301 corresponds to one of the fan units 101. Specifically, the connecting pipe 301 connects the air outlet (i.e., the aforementioned second opening 33) of the corresponding fan unit 101 to the vehicle cabin. The air inlet of the booster fan 10 can be directly connected to the air conditioning outlet 201, or it can be connected via a transition pipe 302, thus adapting to different layout spaces and increasing its versatility. Furthermore, the booster fan 10 is connected to the air conditioning outlet 201 via a connecting structure.

[0364] For example, the connection structure can be a plug-in structure or a snap-fit ​​structure.

[0365] Specifically, the connection structure includes a first connecting part located at the air inlet of the booster fan and a second connecting part located at the air outlet of the air conditioner. The first connecting part and the second connecting part are plugged in or snapped together. For example, one end of the air inlet of the booster fan 10 is provided with a buckle, and the air outlet 201 is provided with a slot. The buckle and the slot are snapped together to connect the booster fan 10 and the air outlet 201.

[0366] In some embodiments, a sealing element, such as foam, is provided between the air inlet of the booster fan 10 and the air outlet 201 of the air conditioner to improve the sealing performance between the air inlet of the booster fan 10 and the air outlet 201 of the air conditioner.

[0367] In specific embodiments of the present invention, such as Figure 33As shown, there are two fan units 101, referred to as the first fan unit and the second fan unit. The first fan unit is connected to the left side of the vehicle cabin to supply air to the left side of the cabin, and the second fan unit is connected to the right side of the vehicle cabin to supply air to the right side of the cabin. For example, a connecting pipe 301 connects the first fan unit to the left side of the cabin, and another connecting pipe 301 connects the second fan unit to the right side of the cabin. By adjusting the speeds of the first and second motors corresponding to the left side, the airflow speed and volume in the left side can be adjusted; similarly, by adjusting the speeds of the first and second motors corresponding to the right side, the airflow speed and volume in the right side can be adjusted, achieving independent zoned airflow control. Alternatively, both the first and second motors corresponding to the left side can be stopped, thus supplying air only to the right side; conversely, both the first and second motors corresponding to the right side can be stopped, thus supplying air only to the left side.

[0368] Furthermore, the above description is merely a preferred embodiment of the present invention and the technical principles employed. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein, and various obvious changes, readjustments, and substitutions can be made without departing from the scope of protection of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments. Many other equivalent embodiments may be included without departing from the concept of the present invention, and the scope of the present invention is determined by the scope of the appended claims.

Claims

1. A fan unit, characterized in that, include: Impeller housing, wherein the inner wall of the impeller housing is provided with a reinforcing structure; An impeller includes an impeller hub, a blade crown, and multiple blades. The impeller hub is rotatably disposed within an impeller housing. The multiple blades are spaced apart from the impeller hub circumferentially. The blade crown is annular and is fitted over the outer side of the multiple blades. The ends of the multiple blades radially away from the impeller hub are all connected to the blade crown. Along the axial direction of the impeller hub, a third gap c is provided between the blade crown and the reinforcing structure.

2. The fan unit according to claim 1, characterized in that, Along the axial direction of the impeller hub, the length of the blade crown is not less than the length of the blade tip, and the length of the blade crown is not greater than the length of the impeller hub.

3. The fan unit according to claim 1, characterized in that, The multiple blades are unevenly distributed along the circumference of the impeller hub.

4. The fan unit according to claim 1, characterized in that, Along the rotation direction of the impeller, there is a phase angle α between the blade root and the blade tip at the trailing edge y1 of the blade.

5. The fan unit according to claim 1, characterized in that, Along the axial direction of the impeller hub, the variation pattern of the outer diameter of the blade crown is the same as the variation pattern of the inner diameter of the impeller housing corresponding to the blade crown.

6. The fan unit according to claim 1, characterized in that, A first gap a is provided between the blade crown and the inner wall of the impeller housing.

7. The fan unit according to claim 6, characterized in that, The value of the first gap a ranges from 0.5 mm to 2 mm.

8. The fan unit according to claim 1, characterized in that, Along the radial direction of the impeller hub, the thickness b of the blade crown ranges from 0.5 mm to 1.5 mm.

9. The fan unit according to claim 1, characterized in that, The value of the third gap c ranges from 3mm to 8mm.

10. The fan unit according to claim 1, characterized in that, The reinforcing structure is located on the air outlet side of the impeller; the inner diameter of the blade crown on the air outlet side of the impeller is equal to the inner diameter of the impeller housing at the location where the reinforcing structure is located; and / or, The reinforcing structure is located on the air inlet side of the impeller; the inner diameter of the blade crown on the air inlet side of the impeller is equal to the inner diameter of the impeller housing where the reinforcing structure is located.

11. The fan unit according to any one of claims 1-10, characterized in that, The impeller housing includes a mounting cavity, and the impeller hub is rotatably disposed within the mounting cavity; the impeller housing also includes a first opening and a second opening, both of which communicate with the mounting cavity; the first opening and the second opening are arranged sequentially along the axial direction of the impeller hub.

12. The fan unit according to claim 11, characterized in that, The impeller is provided in multiple manner, and the multiple impellers are arranged sequentially along the axial direction of the impeller hub.

13. The fan unit according to claim 12, characterized in that, The fan unit also includes an air guide component corresponding to the impeller, with the air inlet side of the air guide component facing the air outlet side of the corresponding impeller; the air guide component includes an air guide hub and a plurality of guide vanes, the air guide hub being fixed in the mounting cavity; the plurality of guide vanes are spaced apart on the air guide hub along the circumference of the air guide hub.

14. The fan unit according to claim 13, characterized in that, Along the axial direction of the impeller hub, a fifth gap is provided between the blade crown and the air guide.

15. The fan unit according to claim 14, characterized in that, The value of the fifth gap ranges from 3mm to 8mm.

16. The fan unit according to claim 13, characterized in that, The multiple guide vanes are unevenly distributed along the circumference of the wind guide hub.

17. The fan unit according to claim 13, characterized in that, The ends of the multiple guide vanes radially away from the guide vane hub are all fixedly connected to the impeller housing.

18. A booster fan, characterized in that, Includes the wind turbine unit as described in any one of claims 1-17.

19. The booster fan according to claim 18, characterized in that, The fan unit is provided in multiple ways, and the multiple fan units are arranged in a direction perpendicular to the axis of the impeller hub.

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

21. A thermal management system, characterized in that, This includes the booster fan as described in any one of claims 18-19 or the air conditioning system as described in claim 20.

22. A vehicle, characterized in that, This includes the air conditioning system as described in claim 20 or the thermal management system as described in claim 21.

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