A fan system and a range hood

Abstract

The application relates to a fan system and an extractor hood, the fan system comprising an impeller, the impeller comprising a front disc, a rear disc and blades arranged in sequence along the circumference between the front disc and the rear disc, a middle disc connected with each blade being arranged between the front disc and the rear disc, an elastic flow regulator being arranged in sequence along the circumference on the outer periphery of the middle disc, a lever mechanism being arranged on the outer periphery of the middle disc at the region corresponding to each elastic flow regulator, the lever mechanism being capable of acting on the elastic flow regulator in the radial direction of the middle disc with the change of the pressure difference between the front and rear sides of the middle disc, and correspondingly changing the protruding degree of the corresponding elastic flow regulator in the radial direction of the middle disc. The elastic flow regulator is lifted and deformed into a certain steady flow structure, so that the pressure difference between the front and rear surfaces of the middle disc is reduced, the transition of small vortexes to large vortexes at the blade tail edge of the middle disc is avoided, the airflow stability is greatly increased, and the fan efficiency is improved.

Description

Technical Field

[0001] This invention relates to the field of fan system technology, and more particularly to a fan system and a range hood. Background Technology

[0002] Fan systems are crucial air supply devices, commonly used in products such as range hoods and air conditioners. Most existing range hoods employ multi-blade centrifugal fans. To improve fan performance, the overall size of the fan is often increased, and the impeller typically uses a structure with a central partition, as disclosed in patent application CN201910354996.9 (publication number CN110145488A). When a centrifugal fan uses an impeller with a central partition, a pressure difference is created on both sides of the partition. This pressure difference increases with the impeller diameter and shaft height. This pressure difference easily causes unstable airflow at the impeller outlet. Furthermore, the impeller blades' pressure and suction surfaces already contain separation vortices, making it even more prone to the transformation of small vortices into large vortices at the partition outlet. The existing technology mainly uses an impeller without a partition plate in the middle to solve the above problem. However, this does not fundamentally solve the problem. Moreover, once the problem occurs, it is very easy to cause unstable airflow at the impeller outlet, resulting in increased airflow noise and greatly affecting the user's cooking experience.

[0003] Therefore, the existing wind turbine system still needs further improvement. Summary of the Invention

[0004] The first technical problem to be solved by the present invention is to provide a fan system that can avoid the transformation of small vortices into large vortices at the trailing edge of the blades, greatly increase airflow stability, and improve fan efficiency, in light of the current state of the technology.

[0005] The second technical problem to be solved by the present invention is to provide a range hood that uses the above-mentioned fan system, in view of the current state of the prior art.

[0006] The technical solution adopted by the present invention to solve the first technical problem mentioned above is as follows: a fan system, including an impeller, the impeller including a front plate, a rear plate and blades arranged sequentially between the front plate and the rear plate in a circumferential direction, a middle plate connected to each of the blades is also provided between the front plate and the rear plate, elastic rectifiers are sequentially provided along the circumferential direction on the outer periphery of the middle plate, and a lever mechanism is provided at the area corresponding to each elastic rectifier on the outer periphery of the middle plate. The lever mechanism can act on the elastic rectifiers in the radial direction of the middle plate according to the change of the pressure difference between the front and rear sides of the middle plate, and correspondingly change the degree of radial protrusion of the corresponding elastic rectifier relative to the middle plate.

[0007] To utilize the pressure difference between the front and rear sides of the mid-plate as a power source to resist the deformation of the elastic rectifier and to simplify the structure of the lever mechanism, the lever mechanism includes a lever and a swing arm:

[0008] The outer periphery of the middle disk is provided with a first mounting channel that runs through the front and rear at the region corresponding to each of the elastic rectifiers. The lever is disposed in the first mounting channel and can slide back and forth in the first mounting channel as the pressure difference between the front and rear sides of the middle disk changes. The outer periphery of the middle disk is also provided with a second mounting channel that extends radially and runs through the first mounting channel at the region corresponding to each of the elastic rectifiers. The swing arm is disposed in the second mounting channel and is arranged along the extension direction of the second mounting channel. The lever is movably connected to the swing arm and can drive the swing arm to deflect back and forth with its inner end as the rotation center, so that the outer end of the swing arm acts on the elastic rectifier.

[0009] In order to convert the axial movement of the lever into the rotation of the rocker arm, the rocker arm is hollow inside and has a groove extending along its length. The lever passes through the rocker arm and has a protrusion that slides and limits the groove.

[0010] As an improvement, both ends of the lever along its length are provided with sealing end caps that make sealing contact with the outer peripheral wall of the first mounting hole. During impeller rotation, the pressure on the front and rear sides of the central plate is different, which acts on the sealing end caps of the lever, causing the lever to move axially as the pressure difference between the front and rear sides of the central plate changes.

[0011] Because the impeller speed varies under different operating conditions, the separation vortex at the blade trailing edge in the intermediate disk also differs. To enable passive adaptive adjustment based on the pressure difference across the intermediate disk acting as a dynamic force to resist deformation of the elastic rectifier, thus greatly expanding the application conditions of the fan, the lever mechanism also includes:

[0012] A sliding member is radially slidably disposed in the second mounting channel, and the inner end of the rocker arm is rotatably connected to the outer end of the sliding member;

[0013] An elastic element acts on the sliding element, causing the sliding element to always tend to move away from the elastic rectifier.

[0014] When the impeller rotates, the sliding component moves away from the center of the central plate under the drive of centrifugal force, which in turn pushes the pendulum arm to move away from the center of the central plate, thereby realizing the movement of the pendulum arm in the plane of the central plate, applying pressure to the elastic rectifier, so that the elastic rectifier has a corresponding degree of protrusion (protrusion size).

[0015] The aforementioned elastic element can be made using various existing technologies, including compression springs, torsion springs, leaf springs, and other elastic elements. However, in order to better coordinate with the movement of the aforementioned sliding element, the elastic element is a tension spring. The tension spring is located in the second mounting hole, with its first end connected to the side of the sliding element adjacent to the center of the middle plate, and its second end connected to the inner wall of the second mounting hole.

[0016] In order to make the elastic rectifier have a high rectification effect after being lifted, the rotation direction of the impeller is referred to as the first direction. At least two lever mechanisms are provided on the outer periphery of the middle disk at positions corresponding to each elastic rectifier. Each lever mechanism is arranged sequentially along the first direction and acts on the same elastic rectifier at the same time.

[0017] The first and second connected mounting holes are referred to as a set of mounting hole units, and at least two sets of the aforementioned mounting hole units are provided.

[0018] As an improvement, when the impeller is in a non-rotating state, the distance between the sliding member in each set of mounting hole units on the central disk corresponding to one of the elastic rectifiers and the center of the central disk gradually decreases along the first direction.

[0019] During impeller rotation, the distance between the sliding component and the impeller's rotation center is inconsistent, resulting in increased centrifugal force as the rotation speed increases. This force overcomes the tension spring and causes the component to move away from the rotation center. As the pressure difference increases, the pressure at the upper and lower pressure ports of the first mounting channel becomes inconsistent. These upper and lower pressure ports correspond to the sealing end caps at the upper and lower ends of the pressure lever, respectively. This inconsistency in pressure at the upper and lower ends of the pressure lever leads to movement parallel to the impeller's rotation direction. The protrusion in the middle of the lever (usually a spherical structure) is embedded in the groove of the swing arm. The pressure lever drives the swing arm up and down through this spherical structure. The superposition of these two movement modes allows the outer end of the swing arm to move parallel and perpendicular to the rotation axis, partially lifting the elastic rectifier to form an airfoil structure. This airfoil structure guides the airflow to converge at the tail and flow out along the tail tip, effectively eliminating the pressure gradient caused by discontinuous airflow.

[0020] As an improvement, three lever mechanisms are provided at positions corresponding to each elastic rectifier along the outer periphery of the central disk, and three sets of mounting hole units are also provided accordingly. The number of lever mechanisms and mounting hole units is not limited to three (three sets), and can be reasonably selected according to the actual size of the impeller.

[0021] To improve the overall rectification effect, the number of elastic rectifiers on the middle disk is the same as the number of blades of the impeller, and a flow channel is formed between two adjacent blades. Each of the elastic rectifiers on the middle disk is located at the outlet of the corresponding flow channel.

[0022] As an improvement, the outer periphery of the elastic rectifier is fixed at the outer periphery of the middle plate, and the middle part of the elastic rectifier abuts against the outer end of the swing arm.

[0023] When the impeller is rotating, the elastic rectifier is pushed up by the lever mechanism and takes on an airfoil shape with the center bulging outward.

[0024] The technical solution adopted by the present invention to solve the second technical problem mentioned above is: a range hood, including a fan system, wherein the fan system is the aforementioned fan system.

[0025] Compared with the prior art, the advantages of the present invention are as follows: The lever mechanism provided at the outer periphery of the middle disk can act on the elastic rectifier provided on the outer periphery of the middle disk in the radial direction according to the change of the pressure difference between the front and rear sides of the middle disk, and correspondingly change the degree of radial protrusion of the corresponding elastic rectifier relative to the middle disk. The elastic rectifier is lifted and deformed into a certain flow stabilizing structure, thereby achieving the purpose of reducing the pressure difference between the front and rear surfaces of the middle disk, thus avoiding the transformation of small vortices into large vortices at the blade trailing edge of the middle disk, greatly increasing airflow stability and improving fan efficiency. Attached Figure Description

[0026] Figure 1 This is a three-dimensional structural diagram of the impeller of the wind turbine system according to an embodiment of the present invention (the impeller is in a non-rotating state, that is, the elastic rectifier is not lifted up);

[0027] Figure 2 for Figure 1 A radial sectional view of the impeller of the fan system shown;

[0028] Figure 3 for Figure 1 An axial sectional view of the impeller of the fan system shown.

[0029] Figure 4 This is a three-dimensional structural diagram of the lever mechanism according to an embodiment of the present invention;

[0030] Figure 5 This is a cross-sectional view of the lever mechanism according to an embodiment of the present invention;

[0031] Figure 6 This is a three-dimensional structural diagram of the impeller of the wind turbine system according to an embodiment of the present invention (the impeller is in a rotating state, that is, the elastic rectifier is in a state of being lifted up);

[0032] Figure 7 for Figure 6 A radial sectional view of the impeller of the fan system shown;

[0033] Figure 8This is a vertical sectional view of the range hood of the present invention, cut along the front-to-back direction. Detailed Implementation

[0034] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments.

[0035] The specification and claims of this invention use terms indicating direction, such as "front," "rear," "upper," "lower," "left," "right," "side," "top," and "bottom," to describe various exemplary structural parts and elements of the invention. However, these terms are used herein merely for ease of explanation and are determined based on the exemplary orientations shown in the accompanying drawings. Since the embodiments disclosed in this invention can be arranged in different orientations, these terms indicating direction are for illustrative purposes only and should not be considered as limitations. For example, "upper" and "lower" are not necessarily limited to directions opposite to or consistent with the direction of gravity.

[0036] Figures 1-8 A preferred fan system structure is shown, specifically a fan system structure for use in a range hood. The fan system includes a volute 17, an impeller 10, and a motor 16. The impeller 10 is housed within the volute 17 and connected to the output shaft of the motor 16, which drives the impeller 10 to rotate.

[0037] See Figure 1 The impeller 10 includes a front disc 11, a rear disc 12, a middle disc 13, and blades 14 arranged circumferentially between the front disc 11 and the rear disc 12. The front and rear ends of each blade 14 are connected to the front disc 11 and the rear disc 12, respectively. The middle disc 13 is located between the front disc 11 and the rear disc 12 and is connected to each blade 14. Specifically, considering the installation space of the motor 16, the distance between the middle disc 13 and the front disc 11 is greater than the distance between the middle disc 13 and the rear disc 12. The output shaft of the motor 16 can be connected to the middle disc 13 of the impeller 10 via the impeller disc.

[0038] During the rotation of the impeller 10, the impeller 10, which is divided into two sections by the central disk 13, has different maximum pressures due to the different heights of the two sections. In addition, the sizes of the two air inlets at the front and rear of the volute are different. These two factors result in different pressures and flow rates at the front and rear of the central disk 13, forming a pressure gradient. The direction of this pressure gradient is generally from the front of the impeller 10 (the higher end, usually the main air inlet side) to the rear of the impeller 10. As the speed of the impeller 10 increases, this pressure gradient will continue to increase. In addition, the trailing edge of the blades 14 of the impeller 10 will generate separation vortices on both the front and rear sides of the central disk 13. After the pressure gradient at the central disk 13 is enhanced, part of the separation vortex is enhanced into a larger vortex, and part of it causes a secondary vortex, increasing the airflow instability. In order to specifically improve the flow situation at this point, this embodiment designs a flow stabilization structure for the impeller 10. Specifically, an elastic rectifier 33 and a lever mechanism that can press against the elastic rectifier 33 to deform it are also provided at the outer periphery of the central disk 13.

[0039] In this embodiment, the flexible rectifiers 33 are arranged sequentially along the circumferential direction of the outer periphery of the central disk 13, and their number is consistent with that of the blades 14 of the impeller 10. Specifically, a flow channel 15 is formed between two adjacent blades 14 on the impeller 10, and each flexible rectifier 33 is disposed on the central disk 13 in a region corresponding to the outlet of the flow channel 15 of each blade 14. In this embodiment, the flexible rectifiers 33 are fixed on the outer periphery of the central disk 13.

[0040] See Figure 2 The outer periphery of the impeller 10's central disk 13 is provided with a lever mechanism in the area corresponding to each elastic rectifier 33.

[0041] The lever mechanism includes a lever 21, a rocker arm 31, a slider 41, and an elastic element 42.

[0042] To accommodate the aforementioned lever mechanism on the central plate 13, a first mounting channel 131 extending through the central plate 13 (i.e., extending along the thickness direction of the central plate 13) is provided along the outer periphery of the central plate 13 in the area corresponding to each elastic rectifier 33. The lever 21 is disposed in the first mounting channel 131, and each of the two ends of the lever 21 is provided with a sealing end cap 22. The outer periphery of the two sealing end caps 22 is in sealing contact with the inner peripheral wall of the first mounting channel 131. During the rotation of the impeller 10, due to the pressure difference between the front and rear sides of the central plate 13, the lever 21 can slide back and forth in the first mounting channel 131 as the pressure difference between the front and rear sides of the central plate 13 changes.

[0043] The outer periphery of the center plate 13 is further provided with a radially extending second mounting channel 132 in the region corresponding to each elastic rectifier 33, which communicates with the first mounting channel 131. This second mounting channel 132 has an inner section near the center of the center plate 13 and an outer section away from the axis of the center plate 13. The outer end of the second mounting channel 132 forms an opening at the outer periphery of the center plate 13, and the elastic rectifier 33 fixed at the outer periphery of the center plate 13 precisely covers the opening of the second mounting channel 132. Furthermore, in this embodiment, the inner section of the second mounting channel 132 is essentially a straight channel structure of equal diameter, while the outer section of the second mounting channel 132 is a flat channel structure extending in the front-rear direction, thereby providing corresponding movement space for the swing arm 31.

[0044] The swing arm 31 is disposed in the second mounting channel 132 and is arranged along the extending direction of the second mounting channel 132. A sliding member 41 and an elastic member 42 are also provided in the inner section of the second mounting channel 132 near the axis of the central plate 13. Specifically, the sliding member 41 is rod-shaped and extends along the inner section of the second mounting channel 132. The elastic member 42 is preferably a tension spring, with its first end connected to one side (one end) of the sliding member 41 near the center of the central plate 13, and its second end connected to the inner wall of the second mounting channel 132. The outer end of the sliding member 41 is rotatably connected to the inner end of the swing arm 31 via a pin, and the outer end of the swing arm 31 abuts against the back of the elastic rectifier 33. Specifically, the swing arm 31 can deflect back and forth with its inner end as the center of rotation, thereby causing the outer end of the swing arm 31 to act on the elastic rectifier 33, causing the elastic rectifier 33 to be lifted by the pressure of the swing arm 31 and form an airfoil shape with its center bulging outwards. By guiding the airflow to converge at the tail and then flow out along the tail tip, the pressure gradient caused by the discontinuous airflow can be eliminated. In order to facilitate the sliding contact between the outer end of the swing arm 31 and the elastic rectifier 33, the outer end of the swing arm 31 has a spherical structure 310.

[0045] When the impeller 10 rotates, the sliding member 41 moves away from the center of the middle disk 13 under the drive of centrifugal force, thereby pushing the swing arm 31 to move away from the center of the middle disk 13, thus realizing the movement of the swing arm 31 in the plane of the middle disk 13, applying pressure to the elastic rectifier 33, so that the elastic rectifier 33 has a matching degree of protrusion (protrusion size).

[0046] See Figure 4 and Figure 5The swing arm 31 has a hollow interior with a groove 32 extending along its length. The groove 32 passes through the two symmetrical sides of the outer peripheral wall of the swing arm 31 to form a strip-shaped opening. The middle part of the lever 21 has a spherical protrusion 23. The lever 21 passes through the swing arm 31, so that its protrusion 23 is slidably limited in the groove 32 of the swing arm 31. As the lever 21 moves axially, the protrusion 23 of the lever 21 moves in the groove 32 of the swing arm 31 and drives the swing arm to deflect. When the swing arm 31 deflects to different angles, the force of the outer end of the swing arm 31 pressing against the elastic rectifier 33 is different.

[0047] In this embodiment, the rotation direction S of the impeller 10 is denoted as the first direction. At least two lever mechanisms are provided at positions corresponding to each elastic rectifier 33 along the outer periphery of the central disk 13. These lever mechanisms are arranged sequentially along the first direction and simultaneously act on the same elastic rectifier 33. Correspondingly, the connected first mounting channel 131 and second mounting channel 132 are denoted as a set of mounting channel units. At least two sets of these mounting channel units are also provided, arranged sequentially along the first direction. Specifically, as... Figure 2 and Figure 7 As shown, in this embodiment, three lever mechanisms are provided at the outer periphery of the middle plate 13 at positions corresponding to each elastic rectifier 33, and there are also three sets of mounting hole units.

[0048] See also Figure 7 When the impeller 10 is not rotating, the distance between the sliding member 41 in each set of mounting hole units on the central disk 13 corresponding to one of the elastic rectifiers 33 and the center of the central disk 13 gradually decreases along the first direction. That is, in this embodiment, the distances between the three sliding members 41 and the center of the central disk 13 are not uniform. The sliding member 41 at the front in the rotation direction is closest to the center of the central disk 13, and the distance increases sequentially thereafter. Since centrifugal force is proportional to the square of the distance of the object from the center of rotation, the distances of the three sliding members 41 from the center of rotation increase sequentially at the same rotation speed.

[0049] During the rotation of the impeller 10, due to the inconsistent distance between the sliding member 41 and the rotation center of the impeller 10, the centrifugal force increases with the increase of rotation speed. This force then overcomes the elastic force of the tension spring and moves away from the rotation center of the impeller 10. Simultaneously, as the pressure difference between the front and rear sides of the disc 13 increases, the pressure at the upper and lower pressure ports of the first mounting channel 131 will become inconsistent. The upper and lower pressure ports correspond to the sealing end caps 22 at the upper and lower ends of the pressure lever 21, respectively; that is, the pressure on the upper and lower ends of the pressure lever 21 is inconsistent. This causes the movement to occur parallel to the rotation direction of the impeller 10. The middle protrusion 23 of the lever 21 (generally a spherical structure) slides in the groove 32 of the swing arm 31, driving the swing arm 31 to move up and down. The superposition of the two movement modes makes the outer end of the swing arm 31 move parallel and perpendicular to the axis of the impeller 10, which partially lifts the elastic rectifier 33 to form an airfoil structure. The airfoil structure guides the airflow to converge at the tail and flow out along the tip of the airfoil, which can effectively eliminate the pressure gradient caused by the discontinuous airflow.

[0050] In this embodiment, the impeller 10 rotates at different speeds, resulting in different pressure differences between the front and rear sides of the central disk 13. Consequently, the deflection angle of the lever 21 driving the swing arm 31 varies, and the centrifugal force experienced by the sliding member 41 also differs. In other words, the force exerted by the sliding member 41 on the elastic rectifier 33 by the swing arm 31 also varies. Thus, as the impeller 10 rotates, the lever mechanism acts on the elastic rectifier 33 in the radial direction of the central disk 13, and can correspondingly change the degree of radial protrusion of the corresponding elastic rectifier 33 relative to the central disk 13, thereby passively and adaptively adjusting and greatly expanding the application conditions of the fan.

[0051] like Figure 7 As shown, for each elastic rectifier 33, since the distances of the three sliding members 41 from the rotation center of the impeller 10 are not consistent, the centrifugal forces on the three sliding members 41 are also different during the rotation of the impeller 10. Consequently, the forces acting on different regions of the elastic rectifier 33 are also different. Thus, when viewed in the circumferential direction of the central disk 13, the degree of protrusion of different regions of the elastic rectifier is different. Specifically, the degree of protrusion of the front region of the elastic rectifier 33 in the rotation direction of the impeller 10 is relatively small, while the degree of protrusion of the rear region is larger. This results in the elastic rectifier 33 having an airfoil shape with a central outward convexity and a guide slope.

[0052] This embodiment also relates to a range hood, including a housing 50 and a fan system disposed within the housing 50, wherein the fan system is the aforementioned fan system.

[0053] The advantages of the fan system in this embodiment are as follows:

[0054] 1. The flow stabilization system of the fan, which consists of a lever mechanism and an elastic rectifier 33, can eliminate the pressure difference between the front and rear surfaces of the middle plate 13, and can prevent the blades 14 from turning from small vortices to large vortices at the trailing edge of the middle plate 13, thus greatly increasing airflow stability and improving fan efficiency.

[0055] 2. The flow stabilization system of the range hood can eliminate the pressure difference between the front and rear surfaces of the middle plate 13, effectively improve the turbulent flow at the tail of the impeller 10 when the middle plate 13 is present, make the flow more stable, and reduce airflow noise.

[0056] 3. The range hood's flow stabilization system adopts passive adaptive adjustment, which greatly expands the application conditions of the fan;

[0057] 4. The range hood's flow stabilization system uses a pressure lever 21 to achieve the movement of the swing arm 31 perpendicular to the surface of the central plate 13. It requires no sensors, has a novel structure, and is ingenious and stable in function.

[0058] 5. The range hood's flow stabilization system uses different centrifugal forces at the same rotation speed to make the swing arm 31 move within the plane of the central plate 13. The structure is simple and highly adaptable.

[0059] 6. The range hood's flow stabilization system achieves different shape adjustments to the elastic modulus through two motion modes, enabling the flow stabilization system to cope with complex airflow problems.

Claims

1. A fan system comprising an impeller (10), the impeller (10) comprising a front disc (11), a rear disc (12), and blades (14) arranged circumferentially between the front disc (11) and the rear disc (12), wherein a middle disc (13) connected to each of the blades (14) is further provided between the front disc (11) and the rear disc (12), characterized in that: Elastic rectifiers (33) are sequentially arranged along the circumferential direction on the outer periphery of the middle disk (13). A lever mechanism is provided in the area corresponding to each elastic rectifier (33) on the outer periphery of the middle disk (13). The lever mechanism can act on the elastic rectifiers (33) in the radial direction of the middle disk (13) as the pressure difference between the front and rear sides of the middle disk (13) changes, and correspondingly change the degree of radial protrusion of the corresponding elastic rectifier (33) relative to the middle disk (13).

2. The fan system according to claim 1, characterized in that: The lever mechanism includes a lever (21) and a rocker arm (31): The outer periphery of the middle plate (13) is provided with a first mounting channel (131) that runs through the front and back in the area corresponding to each of the elastic rectifiers (33). The lever (21) is provided in the first mounting channel (131) and can slide back and forth in the first mounting channel (131) as the pressure difference between the front and back sides of the middle plate (13) changes. The outer periphery of the middle plate (13) is also provided with a second mounting channel (132) that extends radially and runs through the first mounting channel (131) in the area corresponding to each of the elastic rectifiers (33). The swing rod (31) is provided in the second mounting channel (132) and is arranged along the extension direction of the second mounting channel (132). The lever (21) is movably connected to the swing rod (31) and can drive the swing rod (31) to deflect back and forth with its inner end as the rotation center, so that the outer end of the swing rod (31) acts on the elastic rectifier (33).

3. The fan system according to claim 2, characterized in that: The swing arm (31) is hollow inside and has a groove (32) extending along its length. The lever (21) passes through the swing arm (31) and has a protrusion (23) that slides and limits the groove (32).

4. The fan system according to claim 2, characterized in that: Both ends of the lever (21) along its length are provided with sealing end caps (22) that are in sealing contact with the outer peripheral wall of the first mounting hole (131).

5. The fan system according to claim 2, characterized in that: The lever mechanism also includes: The sliding member (41) is radially slidably disposed in the second mounting channel (132); The elastic element (42) acts on the sliding element (41) and causes the sliding element (41) to always have a tendency to move away from the elastic rectifier (33); The inner end of the rocker arm (31) is rotatably connected to the outer end of the slider (41).

6. The fan system according to claim 5, characterized in that: The elastic element (42) is a tension spring, which is disposed in the second mounting channel (132), and its first end is connected to the side of the sliding element (41) adjacent to the center of the middle plate (13), and its second end is connected to the inner wall of the second mounting channel (132).

7. The fan system according to claim 2, characterized in that: The rotation direction of the impeller (10) is referred to as the first direction. At least two lever mechanisms are provided on the outer periphery of the middle disk (13) at positions corresponding to each elastic rectifier (33). Each lever mechanism is arranged sequentially along the first direction and acts on the same elastic rectifier (33) at the same time. The first mounting channel (131) and the second mounting channel (132) that are connected are referred to as a set of mounting channel units, and at least two sets of the above-mentioned mounting channel units are provided.

8. The fan system according to claim 7, characterized in that: When the impeller (10) is in a non-rotating state, the distance between the sliding member (41) in each set of mounting hole units on the middle disk (13) corresponding to one of the elastic rectifiers (33) and the center of the middle disk (13) gradually decreases along the first direction.

9. The fan system according to claim 7, characterized in that: The outer periphery of the middle plate (13) is provided with three lever mechanisms at positions corresponding to each elastic rectifier (33), and the mounting hole unit also has three sets.

10. The fan system according to any one of claims 1 to 9, characterized in that: The number of elastic rectifiers (33) on the middle disk (13) is the same as the number of blades (14) of the impeller (10). A flow channel (15) is formed between two adjacent blades (14). Each elastic rectifier (33) on the middle disk (13) is located at the outlet of the corresponding flow channel (15).

11. The fan system according to any one of claims 2 to 9, characterized in that: The outer periphery of the elastic rectifier (33) is fixed at the outer periphery of the middle plate (13), and the middle part of the elastic rectifier (33) abuts against the outer end of the swing rod (31).

12. The fan system according to claim 11, characterized in that: When the impeller (10) is rotating, the elastic rectifier (33) is pushed up by the lever mechanism and forms an airfoil shape with the center bulging outward.

13. A range hood, comprising a fan system, characterized in that: The wind turbine system is the wind turbine system as described in any one of claims 1 to 12.

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