Fan assembly, range hood and hob-integrated machine

Abstract

The application provides a fan assembly, an extractor hood and a smoke range all-in-one machine, and a volute includes a shell body, the shell body includes a volute tongue position angle and an outlet angle, and the volute tongue position angle is greater than the outlet angle. By limiting the volute tongue position angle to be greater than the outlet angle, the angle of the airflow flowing out of the shell body can be controlled, the airflow backflow when the airflow flows out of the shell body can be reduced, the negative pressure area is reduced, the airflow velocity is more uniform, the impact between the airflow and the external structure is reduced, the noise generated due to the airflow impact is effectively reduced, and the airflow volume is obviously increased.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of cooking appliances, in particular to a fan assembly, a range hood and a combination of a range hood and a gas stove. BACKGROUND

[0002] The volute is an important component of the fan assembly. In the related art, the volute is designed unreasonably, which causes the airflow of the fan assembly to be too concentrated, and the airflow to produce backflow, increase the air resistance and reduce the air flow. In addition, the airflow produces a large impact force when it is concentrated, and after the airflow flows out of the fan assembly, it directly collides with the pipeline. Due to the large impact force of the airflow, the collision between the airflow and the air duct structure is relatively violent, thereby producing a large impact noise. SUMMARY

[0003] The present application aims to at least solve one of the problems in the prior art.

[0004] To this end, the first aspect of the present application provides a volute.

[0005] The second aspect of the present application provides a fan assembly.

[0006] The third aspect of the present application provides a range hood.

[0007] The fourth aspect of the present application provides a combination of a range hood and a gas stove.

[0008] The first aspect of the present application provides a volute, comprising: a shell body, the shell body comprising a volute tongue position angle and an outlet angle, the volute tongue position angle being greater than the outlet angle.

[0009] The volute provided by the present application comprises a shell body. Specifically, the shell body comprises a volute tongue position angle and an outlet angle, and the angle of the volute tongue position angle is greater than the angle of the outlet angle. In this way, the angle of the airflow flowing out of the shell body can be controlled, and the backflow of the airflow flowing out of the shell body can be reduced, the negative pressure area is reduced, the airflow velocity is more uniform, the impact between the airflow and the external structure is reduced, the noise generated by the impact of the airflow is effectively reduced, and the airflow is significantly increased.

[0010] In some possible designs, the volute tongue position angle is greater than 41° and less than 58°.

[0011] In this design, the volute tongue position angle is greater than 41° and less than 58°. In this way, the shell body can be designed for the existing working conditions, the negative pressure area of the volute tongue position is minimized, the backflow of the airflow flowing out of the shell body is avoided, the airflow velocity flowing out of the shell body is uniform, the impact force of the airflow is reduced, the noise generated by the impact of the airflow is effectively reduced, and the airflow is significantly increased.

[0012] Specifically, the cochlea tongue position angle can be 41°, the cochlea tongue position angle can also be 58°, and the cochlea tongue position angle can also be any value between 41° and 58°. By setting the numerical range of the cochlea tongue position angle, the shell body can adapt to different working environments to achieve the best effect of reducing the negative pressure area, making the airflow flow rate more uniform, thereby reducing the noise generated by airflow impact, and at the same time, the airflow volume is significantly increased.

[0013] In some possible designs, the outlet angle is greater than 29° and less than 38°.

[0014] In this design, the outlet angle is greater than 29° and less than 38°. In this way, the shell body can be designed for different use environments, control the angle of airflow flowing out of the shell body, make the airflow flow more concentrated, and make the flow rate more uniform, thereby effectively reducing the noise generated by airflow impact, and at the same time, the airflow volume is significantly increased.

[0015] Specifically, the outlet angle can be 29°, the outlet angle can also be 38°, and the outlet angle can also be any value between 29° and 38°. By setting the numerical range of the outlet angle, the shell body can adapt to different working environments to achieve the best effect of making the airflow concentrated, thereby making the airflow flow rate more uniform, thereby effectively reducing the noise generated by airflow impact, and at the same time, the airflow volume is significantly increased.

[0016] In some possible designs, the shell body further includes a chamber and an air outlet connected to the chamber, and the chamber is used to place the fan wheel. In a plane perpendicular to the axis of the fan wheel, the ratio of the size D of the air outlet to the outer circle radius r of the fan wheel is greater than or equal to 1.38 and less than or equal to 1.45.

[0017] In this design, the shell body further includes a chamber and an air outlet. The chamber is used to place the fan wheel, and the fan wheel can suck air into the shell body and send air out of the shell body when it operates. Specifically, in a plane perpendicular to the axis of the fan wheel, the ratio of the size of the air outlet to the outer circle radius r of the fan wheel is greater than or equal to 1.38 and less than or equal to 1.45. In this way, the size of the air outlet can be designed according to different fan wheels, and the size of the air outlet can be matched with the fan wheel, thereby enabling the air outlet to ensure airflow volume while reducing the negative pressure area and preventing airflow backflow, thereby making the airflow flow rate more uniform, effectively reducing the noise generated by airflow impact, and at the same time, the airflow volume is significantly increased.

[0018] Specifically, the ratio of the size of the air outlet to the outer circle radius of the impeller can be 1.38, the ratio of the size of the air outlet to the outer circle radius of the impeller can also be 1.45, and the ratio of the size of the air outlet to the outer circle radius of the impeller can also be any value between 1.38 and 1.45. By limiting the value range of the ratio of the size of the air outlet to the outer circle radius of the impeller, the size of the air outlet can be matched with the impeller, so that the air outlet can ensure the flow rate and reduce the negative pressure area to prevent air flow backflow, thereby making the air flow rate more uniform, effectively reducing the noise generated by air flow impact, and significantly increasing the air flow rate.

[0019] The second aspect of the present application provides a fan assembly, comprising: a volute as described in any of the above first aspects, an impeller, and a volute is arranged in the volute.

[0020] The fan assembly provided by the present application comprises the volute of any of the above technical solutions. Therefore, the fan assembly has all the beneficial effects of the above-mentioned volute, which will not be repeated here.

[0021] In addition, the fan assembly further comprises an impeller. Specifically, the impeller is arranged in the chamber of the volute. Specifically, when the fan assembly is working, the impeller sucks air into the shell body and sends the air out of the shell body from the air outlet connected with the chamber. The volute tongue position angle of the shell body is greater than the outlet angle, and the ratio of the size of the air outlet to the outer circle radius of the impeller is greater than or equal to 1.38 and less than or equal to 1.45 (in a plane perpendicular to the axis of the impeller), which can control the angle of the air flow when it flows out of the shell body, reduce the air flow backflow when it flows out of the shell body, reduce the negative pressure area, make the air flow rate more uniform, thereby reducing the impact between the air flow and the flue, effectively reducing the noise generated by the air flow impact, and significantly increasing the air flow rate.

[0022] In some possible designs, the fan assembly further comprises: a vortex prevention ring arranged on the volute at the air inlet of the volute.

[0023] In this design, the fan assembly further comprises a vortex prevention ring. The vortex prevention ring is arranged on the air inlet of the volute. In this way, the vortex prevention ring can reduce or avoid air leakage and prevent the air flow in the chamber from forming a vortex. In this way, through the arrangement of the vortex prevention ring, on the one hand, the noise generated by the vortex can be reduced, and on the other hand, the air flow rate in the chamber can be uniform, thereby making the air flow rate uniform when the air flow enters the volute, effectively reducing the noise generated by the air flow impact, and significantly increasing the air flow rate.

[0024] In some possible designs, the ratio of the outer circle diameter of the vortex prevention ring to the diameter of the impeller is greater than or equal to 1.05 and less than or equal to 1.15.

[0025] In this design, the ratio of the outer diameter of the anti-vortex ring to the diameter of the impeller is greater than or equal to 1.05 and less than or equal to 1.15. This design, tailored to the impeller, ensures the anti-vortex ring effectively blocks airflow leakage, resulting in uniform airflow velocity within the chamber. This reduces the formation of vortices and ensures uniform airflow velocity as it exits the volute, effectively lowering noise generated by airflow impact while significantly increasing airflow volume.

[0026] Specifically, the ratio of the outer diameter of the anti-vortex ring to the diameter of the wind turbine can be 1.05, 1.15, or any value between 1.05 and 1.15.

[0027] In some possible designs, there is a gap between the anti-vortex ring and the wind turbine along the axial direction of the turbine.

[0028] In this design, a gap exists between the anti-vortex ring and the wind turbine along the axial direction of the rotor. That is, a certain distance is maintained between the anti-vortex ring and the rotor along the axial direction of the rotor. This avoids the anti-vortex ring restricting the radial dimensions of the rotor during the installation and use of the wind turbine components, preventing interference between the outer ring of the rotor and the anti-vortex ring. Furthermore, the gap between the anti-vortex ring and the rotor allows users or operators to select an appropriate rotor size according to actual airflow requirements, reducing the assembly difficulty of the wind turbine components and improving assembly efficiency.

[0029] Specifically, when the diameter of the wind turbine is large, a gap can be set between the anti-vortex ring and the wind turbine to ensure that the anti-vortex ring and the wind turbine do not interfere with each other structurally while avoiding the generation of vortices.

[0030] In some possible designs, the anti-vortex ring partially overlaps with the wind turbine along its axial direction.

[0031] In this design, the anti-vortex ring partially overlaps with the wind turbine along its axial direction. That is, a portion of the wind turbine extends into the interior of the anti-vortex ring along its axial direction. This ensures that the anti-vortex ring covers the wind turbine along its axial direction, further enhancing its ability to block airflow and thus greatly reducing the likelihood of vortex formation.

[0032] Specifically, when the diameter of the wind turbine is small, the anti-vortex ring can be partially overlapped with the wind turbine to enhance the blocking effect of the anti-vortex ring on the airflow.

[0033] In some possible designs, where there is a gap between the anti-vortex ring and the impeller, the size of the gap is less than or equal to 2 mm.

[0034] In this design, when there is a gap between the vortex prevention ring and the wind wheel, the size of the gap is less than or equal to 2mm. In this way, on the premise of ensuring that there is no structural interference between the vortex prevention ring and the wind wheel, the distance between the vortex prevention ring and the wind wheel is reduced as much as possible, thereby reducing the leakage of air flow, ensuring that most of the air flow can enter the inside of the volute, and thereby avoiding the generation of vortex.

[0035] Specifically, the size of the gap can be 2mm, and the size H of the gap can also be any size less than 2mm. Through the size of the linear gap, the vortex prevention ring can achieve the best working effect, block the air flow leakage and guide the flow direction of the air flow, make the flow rate of the air flow uniform, thereby effectively reducing the noise generated by the air flow impact, and at the same time, the air flow is significantly increased.

[0036] In some possible designs, when the vortex prevention ring partially overlaps the wind wheel, the size of the overlapping part is less than or equal to 4mm.

[0037] In this design, when the vortex prevention ring partially overlaps the wind wheel, the size of the overlapping part is less than or equal to 4mm. In this way, on the premise of ensuring that the vortex prevention ring can block the air flow leakage, the size of the overlapping part between the vortex prevention ring and the wind wheel is avoided to be too large, which can avoid the waste of materials of the vortex prevention ring on the one hand, and reduce the assembly difficulty of the vortex prevention ring on the other hand, and reduce the possibility of interference between the vortex prevention ring and the wind wheel.

[0038] Specifically, the size of the overlapping part can be 4mm, and the size of the overlapping part can also be any value less than 4mm. By limiting the numerical range of the size of the overlapping part, the working effect of the vortex prevention ring can be ensured, the air flow leakage is blocked and the flow direction of the air flow is guided, the flow rate of the air flow is uniform, thereby effectively reducing the noise generated by the air flow impact, and at the same time, the air flow is significantly increased.

[0039] In some possible designs, the fan assembly further includes: a flow collector arranged on the volute at the air inlet of the volute, the flow collector comprising an opening; and a flow regulator covering the opening and connected with the flow collector, the flow regulator comprising a plurality of air inlet holes.

[0040] In this design, the fan assembly further includes a flow collector and a flow regulator. The flow collector is arranged at the air inlet of the volute, and the flow regulator is arranged on the opening of the flow collector. The air flow passes through the flow regulator and is divided by the air inlet holes on the flow regulator, and then enters the volute through the flow collector. In this way, the air flow is divided by the air inlet holes and then combined, so that the flow rate of the air flow is uniform, thereby making the flow rate of the air flow out of the volute more uniform, effectively reducing the noise generated by the air flow impact, and at the same time, the air flow is significantly increased.

[0041] In some possible design, the rectifier comprises a mounting edge connected with the current collector, and a cover arranged on the mounting edge, and a plurality of air inlets arranged on the cover.

[0042] In this design, the rectifier comprises a mounting edge and a cover. The mounting edge is connected with the current collector, and the cover is arranged on the opening of the current collector through a connecting edge, and a plurality of air inlets are arranged on the cover. By arranging the air inlets on the cover, the airflow can be divided into a plurality of airflows by the air inlets, and then the airflows are combined, so that the flow rate of the airflow is uniform, and the flow rate of the airflow flowing out of the volute is more uniform, effectively reducing the noise generated by the airflow impact, and the airflow is obviously increased.

[0043] In some possible design, the ratio of the diameter of the outer ring of the rectifier to the diameter of the opening is greater than or equal to 1.04 and less than or equal to 1.12.

[0044] In this design, the ratio of the diameter of the outer ring of the rectifier to the diameter of the opening is greater than or equal to 1.04 and less than or equal to 1.12. In this way, the diameter of the outer ring of the rectifier can be designed according to the diameter of the opening, so that the diameter of the outer ring of the rectifier is always greater than the diameter of the opening, so that the outer ring of the rectifier does not block the airflow from entering the cover, and the working reliability of the rectifier is ensured.

[0045] Specifically, the ratio of the diameter of the outer ring of the rectifier to the diameter of the opening can be 1.04, the ratio of the diameter of the outer ring of the rectifier to the diameter of the opening can also be 1.12, and the ratio of the diameter of the outer ring of the rectifier to the diameter of the opening can also be any value between 1.04 and 1.12. By limiting the ratio of the diameter of the outer ring of the rectifier to the diameter of the opening, it is ensured that the mounting edge is always greater than the opening, so that the airflow can enter the opening, and the working reliability of the rectifier is ensured.

[0046] In some possible design, the ratio of the diameter of the cover to the diameter of the opening is greater than or equal to 0.965 and less than or equal to 1.01.

[0047] In this design, the ratio of the diameter of the cover to the diameter of the opening is greater than or equal to 0.965 and less than or equal to 1.01. In this way, the cover can be designed according to the diameter of the opening, so that the cover matches the opening, and the airflow divided by the air inlets can enter the volute through the opening, thereby ensuring the working reliability of the rectifier.

[0048] Specifically, the ratio of the diameter of the cover body to the diameter of the opening can be 0.965, the ratio of the diameter of the cover body to the diameter of the opening can also be 1.01, and the ratio of the diameter R4 of the cover body to the diameter of the opening can also be any value between 0.965 and 1.01. By limiting the ratio of the diameter of the cover body to the diameter of the opening, the airflow that is divided by the air inlet hole can enter the volute through the opening, thereby ensuring the working reliability of the rectifier.

[0049] In some possible designs, the air inlet hole is a regular polygon hole.

[0050] In this design, the air inlet hole is a regular polygon hole. Specifically, the regular polygon hole can save space, improve the utilization rate of the cover body space, ensure that the air inlet hole can be concentrated in the central part of the cover body, thereby ensuring the air distribution effect of the air inlet hole on the airflow, making the airflow velocity uniform, and further making the airflow velocity out of the volute more uniform, effectively reducing the noise generated by airflow impact, while the airflow is significantly increased.

[0051] In some possible designs, the ratio of the length of the regular polygon hole to the diameter of the opening is greater than or equal to 0.018 and less than or equal to 0.031.

[0052] In this design, the ratio of the length of the regular polygon hole to the diameter of the opening is greater than or equal to 0.018 and less than or equal to 0.031. In this way, the regular polygon hole can be designed differently according to the opening, thereby ensuring the air distribution effect of the air inlet hole on the airflow, making the airflow velocity uniform, and further making the airflow velocity out of the volute more uniform, effectively reducing the noise generated by airflow impact, while the airflow is significantly increased.

[0053] Specifically, the ratio of the length of the regular polygon hole to the diameter of the opening can be 0.018, the ratio of the length of the regular polygon hole to the diameter of the opening can also be 0.031, and the ratio of the length of the regular polygon hole to the diameter of the opening can also be any value between 0.018 and 0.031. In this way, by limiting the ratio of the length of the regular polygon hole to the diameter of the opening, the working effect of the air inlet hole is ensured, the airflow velocity is uniform, and further the airflow velocity out of the volute is more uniform, effectively reducing the noise generated by airflow impact, while the airflow is significantly increased.

[0054] In some possible designs, the ratio of the total area of the plurality of air inlet holes to the area of the rectifier is greater than or equal to 0.58 and less than or equal to 0.68.

[0055] In the design, the ratio of the total area of the plurality of air inlets to the area of the rectifier is greater than or equal to 0.58 and less than or equal to 0.68. In this way, the number of air inlets can be designed according to the area of the rectifier, so as to ensure the air flow effect of the air inlets on the airflow, make the flow rate of the divided airflow uniform, and further make the flow rate of the airflow out of the volute more uniform, effectively reduce the noise generated by the airflow impact, and at the same time, the air flow is obviously increased. Specifically, the ratio of the total area of the plurality of air inlets to the area of the rectifier is the opening rate of the rectifier.

[0056] Specifically, the ratio of the total area of the plurality of air inlets to the area of the rectifier can be 0.58, the ratio of the total area of the plurality of air inlets to the area of the rectifier can also be 0.68, and the ratio of the total area of the plurality of air inlets to the area of the rectifier can also be any value between 0.58 and 0.68. In this way, by limiting the range of the ratio of the total area of the plurality of air inlets to the area of the rectifier, the air flow effect of the air inlets is ensured, the flow rate of the airflow is more uniform, the noise generated by the airflow impact is effectively reduced, and at the same time, the air flow is obviously increased.

[0057] The third embodiment of the present application provides an extractor hood, comprising: an air duct structure; and a fan assembly according to any one of the second aspects.

[0058] The extractor hood provided by the present application comprises the fan assembly according to any one of the above technical solutions, and therefore has all the beneficial effects of the fan assembly, which will not be described herein again.

[0059] In addition, the extractor hood further comprises an air duct structure. The fan assembly is arranged in the air duct structure, and the fan assembly sucks oil fume into the air duct structure when operating.

[0060] Specifically, in the working process of the extractor hood, the fan wheel in the fan assembly works, so that the oil fume flows into the volute through the flow collector and the rectifier. The air inlets in the rectifier can divide the oil fume, so that the flow rate of the oil fume entering the volute is relatively uniform. When the oil fume flows out of the volute and enters the air duct structure, by limiting the position angle of the volute tongue to be greater than the outlet angle, the negative pressure area at the air outlet can be reduced, so that the oil fume does not backflow when flowing out of the air outlet, the negative pressure area is reduced, the flow rate of the oil fume is more uniform, the impact between the oil fume and the air duct structure is reduced, the noise generated by the impact of the oil fume is effectively reduced, and at the same time, the air flow is obviously increased.

[0061] The fourth aspect of the present invention provides an integrated range hood and cooktop, comprising: a cooktop body; an air duct structure, wherein the inlet of the air duct structure is disposed toward the cooktop body; and a fan assembly as described in any of the technical solutions of the second aspect above, wherein the fan assembly is disposed within the air duct structure.

[0062] The integrated range hood and cooktop proposed in this invention includes a fan assembly as described in any of the above technical solutions, and therefore has all the beneficial effects of the aforementioned fan assembly, which will not be repeated here.

[0063] In addition, the integrated range hood and cooktop also includes a cooktop body and an air duct structure. The cooktop body generates high temperatures for cooking. The opening of the air duct structure faces the cooktop body, and the fan assembly is located inside the air duct structure. The fan assembly draws the cooking fumes from the inlet into the air duct structure.

[0064] Specifically, during the operation of the integrated range hood and cooktop, the cooktop generates high temperatures to provide a heat source for cooking, continuously producing fumes. The opening of the duct structure faces the cooktop, and the impeller in the fan assembly operates, causing the fumes to flow into the volute through the collector and rectifier. The air inlet in the rectifier can divert the fumes, ensuring a more even flow rate into the volute. While the fumes are in the volute, the anti-vortex ring prevents leakage and guides the flow direction, preventing backflow and vortex formation, thus ensuring a uniform flow rate within the volute. When the fumes exit the volute and enter the duct structure, by limiting the volute tongue position angle to be greater than the outlet angle, the negative pressure zone at the outlet is reduced, preventing backflow of fumes as they exit the outlet. This reduced negative pressure zone and more even flow rate of fumes reduces the impact between the fumes and the duct structure, effectively reducing noise caused by the fumes' impact, while significantly increasing the airflow.

[0065] Additional aspects and advantages of the invention will become apparent in the following description or may be learned by practice of the invention. Attached Figure Description

[0066] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0067] Figure 1 This is a schematic diagram of the structure of the volute shell according to an embodiment of the present invention;

[0068] Figure 2 for Figure 1 Rear view of the volute casing in the illustrated embodiment;

[0069] Figure 3 for Figure 2 A cross-sectional view of the volute along AA in the embodiment shown;

[0070] Figure 4is a structural schematic diagram of a fan wheel of one embodiment of the present application;

[0071] Figure 5 is a structural schematic diagram of a fan assembly of one embodiment of the present application;

[0072] Figure 6 is Figure 5 is a top view of the fan assembly of the embodiment shown;

[0073] Figure 7 is Figure 6 is a sectional view along B-B of the fan assembly of the embodiment shown;

[0074] Figure 8 is a structural schematic diagram of a fan assembly of one embodiment of the present application;

[0075] Figure 9 is Figure 8 is a sectional view along C-C of the fan assembly of the embodiment shown;

[0076] Figure 10 is a structural schematic diagram of a rectifier of one embodiment of the present application;

[0077] Figure 11 is Figure 10 is a sectional view along D-D of the rectifier of the embodiment shown;

[0078] Figure 12 is a structural schematic diagram of an air inlet hole of one embodiment of the present application;

[0079] Figure 13 is a flow velocity vector diagram of air flow when a volute is used in the related art;

[0080] Figure 14 is a flow velocity vector diagram of air flow when a volute is used in one embodiment of the present application;

[0081] Figure 15 is a flow velocity vector diagram of air flow when a fan assembly is used in the related art;

[0082] Figure 16 is a flow velocity vector diagram of air flow when a fan assembly is used in one embodiment of the present application.

[0083] wherein, Figures 1 to 12 the correspondence between the reference signs and the component names in the drawings is as follows:

[0084] 10 volute, 12 fan assembly, 100 shell body, 102 chamber, 104 air outlet, 106 fan wheel, 108 vortex prevention ring, 110 current collector, 112 rectifier, 114 mounting edge, 116 cover body, 118 air inlet hole, 120 opening. DETAILED DESCRIPTION

[0085] In order to more clearly understand the above-mentioned purposes, features and advantages of the present application, the present application will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that the embodiments of the present application and the features in the embodiments can be combined with each other without conflict.

[0086] In the following description, a large number of specific details are set forth in order to facilitate a thorough understanding of the present application, however, the present application can also be implemented in other different manners from those described herein, and therefore, the protection scope of the present application is not limited by the specific embodiments disclosed below.

[0087] The volute 10, the fan assembly 12, the range hood and the integrated range hood and cooker according to some embodiments of the present application will be described below with reference to the accompanying drawings. Figures 1 to 16

[0088] As shown in Figure 1 and Figure 2 , a first embodiment of the present application proposes a volute 10, which comprises a shell body 100.

[0089] As shown in Figures 1 to 4 , the shell body 100 comprises a volute tongue position angle α and an outlet angle β, and the angle of the volute tongue position angle α is greater than the angle of the outlet angle β. In this way, the angle of the airflow flowing out of the shell body 100 can be controlled, and the backflow of the airflow flowing out of the shell body 100 can be reduced, the negative pressure area is reduced, the airflow velocity is more uniform, the impact between the airflow and the external structure is reduced, the noise generated by the impact of the airflow is effectively reduced, and the airflow volume is significantly increased.

[0090] In this embodiment, further, as shown in Figure 3 , the volute tongue position angle α is greater than 41° and less than 58°. In this way, the shell body 100 can be designed for existing working conditions, the negative pressure area of the volute tongue position is minimized, the backflow of the airflow flowing out of the shell body 100 is avoided, the airflow velocity flowing out of the shell body 100 is uniform, the impact force of the airflow is reduced, the noise generated by the impact of the airflow is effectively reduced, and the airflow volume is significantly increased.

[0091] Specifically, the volute tongue position angle α can be 41°, the volute tongue position angle α can also be 58°, and the volute tongue position angle α can also be any value between 41° and 58°. By setting the value range of the volute tongue position angle α, the shell body 100 can adapt to different working environments, the best effect of reducing the negative pressure area is achieved, the airflow velocity is more uniform, the noise generated by the impact of the airflow is reduced, and the airflow volume is significantly increased.

[0092] Specifically, as shown in Figure 3 ​As shown, the volute tongue position angle a can be 41°, 43°, 45°, 47°, 49°, 51°, 53°, 55°, 57°, 58°, and the like, which are not listed one by one here. Those skilled in the art can understand that as long as the pressure reduction area can be minimized, it can be achieved.

[0093] Specifically, under certain working conditions, the volute tongue position angle a can be a = 50°, so that the negative pressure area at the air outlet 104 of the volute 10 is minimized to prevent backflow of the airflow, thereby ensuring uniform airflow velocity, effectively reducing noise caused by airflow impact, and significantly increasing airflow.

[0094] Specifically, under another working condition, the volute tongue position angle a can be a = 42°, so that the negative pressure area at the air outlet 104 of the volute 10 is minimized to prevent backflow of the airflow, thereby ensuring uniform airflow velocity, effectively reducing noise caused by airflow impact, and significantly increasing airflow.

[0095] In this embodiment, further, as shown in Figure 3 The outlet angle β is greater than 29° and less than 38°. In this way, the shell body 100 can be designed to adapt to different use environments, control the angle at which the airflow flows out of the shell body 100, and make the airflow flow more concentrated, so that the velocity is more uniform, thereby effectively reducing noise caused by airflow impact and significantly increasing airflow.

[0096] Specifically, the outlet angle β can be 29°, the outlet angle β can also be 38°, and the outlet angle β can also be any value between 29° and 38°. By setting the value range of the outlet angle β, the shell body 100 can adapt to different working environments to achieve the best effect of concentrating the airflow, thereby making the airflow velocity more uniform, thereby effectively reducing noise caused by airflow impact and significantly increasing airflow.

[0097] Specifically, as shown in Figure 3 The outlet angle β can be 29°, 30°, 32°, 34°, 36°, 38°, and the like, which are not listed one by one here. Those skilled in the art can understand that as long as the airflow flow is concentrated, it can be achieved.

[0098] Specifically, under certain working conditions, the outlet angle β can be β = 32°, thereby controlling the angle at which the airflow flows out of the shell body 100, making the airflow flow more concentrated, and making the velocity more uniform, thereby effectively reducing noise caused by airflow impact and significantly increasing airflow.

[0099] Specifically, in another working condition, the outlet angle β can be β=37°, so as to control the angle of the airflow flowing out of the shell body 100, make the airflow flow more concentrated, and make the flow rate more uniform, so as to effectively reduce the noise generated by airflow impact, and at the same time, the airflow volume is obviously increased.

[0100] The second embodiment of the present application proposes a volute 10, which is further based on the above-mentioned first embodiment,

[0101] As shown in Figure 3 and Figure 4 , the shell body 100 further comprises a chamber 102 and an air outlet 104. Among them, the chamber 102 is used to place the fan 106, and the fan 106 can suck the airflow into the shell body 100 when running, and send the airflow out of the shell body 100 from the air outlet 104 connected with the chamber 102.

[0102] Specifically, in the plane perpendicular to the axis of the fan 106, the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan 106 is greater than or equal to 1.38 and less than or equal to 1.45. In this way, the size D of the air outlet 104 can be designed according to different fans 106, so that the size D of the air outlet 104 matches the fan 106, so that the air outlet 104 can ensure the airflow volume while reducing the negative pressure area, prevent airflow backflow, so that the airflow flow rate is more uniform, effectively reduces the noise generated by airflow impact, and at the same time, the airflow volume is obviously increased.

[0103] Specifically, the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan 106 can be 1.38, the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan 106 can also be 1.45, and the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan 106 can also be any value between 1.38 and 1.45. By limiting the value range of the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan 106, the size D of the air outlet 104 can match the fan 106, so that the air outlet 104 can ensure the flow rate and reduce the negative pressure area, prevent airflow backflow, so that the airflow flow rate is more uniform, effectively reduces the noise generated by airflow impact, and at the same time, the airflow volume is obviously increased.

[0104] Specifically, as shown in Figure 3 and Figure 4 , the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan 106 can be 1.38, 1.39, 1.40, 1.41, 1.42, 1.43, 1.44, 1.45, etc. Here, it will not be listed one by one. Those skilled in the art can understand that as long as the airflow volume of the air outlet 104 is concentrated, it can be realized.

[0105] Specifically, in a certain working condition, the ratio of the size D of the air outlet 104 to the outer circle radius r of the wind wheel 106 is 1.4, the outer circle radius r of the wind wheel 106 is 102 mm, and the size D of the air outlet 104 is calculated according to the formula to be 142.8 mm. It can be understood that when the ratio of the size D of the air outlet 104 to the outer circle radius r of the wind wheel 106 is 1.4, the outer circle radius r of the wind wheel 106 is 102 mm, and the size D of the air outlet 104 is calculated according to the formula to be 142.8 mm, that is, in this working condition, the optimal size of the air outlet 104 is 142.8 mm.

[0106] Specifically, in a certain working condition, the ratio of the size D of the air outlet 104 to the outer circle radius r of the wind wheel 106 is 1.38, the outer circle radius r of the wind wheel 106 is 120 mm, and the size D of the air outlet 104 is calculated according to the formula to be 165.6 mm. It can be understood that when the ratio of the size D of the air outlet 104 to the outer circle radius r of the wind wheel 106 is 1.38, the outer circle radius r of the wind wheel 106 is 120 mm, and the size D of the air outlet 104 is calculated according to the formula to be 165.6 mm, that is, in this working condition, the optimal size of the air outlet 104 is 165.6 mm.

[0107] Specifically, the calculation formula is D / r=1.4 or 1.38, wherein D is the size of the air outlet 104, and r is the outer circle radius of the wind wheel 106.

[0108] Specifically, by comparing Figure 13 and Figure 14 It can be known that in the volute 10 provided by the present application, the volute tongue position angle α is greater than 41° and less than 58°, the outlet angle β is greater than 29° and less than 38°, and the ratio of the size D of the air outlet 104 to the outer circle radius r of the wind wheel 106 is greater than or equal to 1.38 and less than or equal to 1.45 (in the plane perpendicular to the axis of the wind wheel 106), so that the air outlet 104 can ensure the air flow while reducing the negative pressure area and preventing air flow backflow (especially in the position circled by Figure 13 and Figure 14 ). In this way, the volute 10 provided by the present application can make the air flow more uniform, effectively reduce the noise generated by air flow impact, and at the same time, the air flow is obviously increased.

[0109] The third embodiment of the present application provides a fan assembly 12 comprising the volute 10 according to any one of the above embodiments.

[0110] Therefore, the fan assembly 12 provided by the present embodiment has all the beneficial effects of the above volute 10, which will not be discussed in detail here.

[0111] As Figure 5As shown, the fan assembly 12 further comprises a fan wheel 106. Specifically, the fan wheel 106 is arranged in the chamber 102 of the volute 10. Specifically, when the fan assembly 12 is working, the fan wheel 106 sucks the airflow into the shell body 100 and sends the airflow out of the shell body 100 from the air outlet 104 connected with the chamber 102. The position angle a of the volute tongue on the shell body 100 is greater than the outlet angle b, and the size D of the air outlet 104 is greater than or equal to 1.38 and less than or equal to 1.45 (in a plane perpendicular to the axis of the fan wheel 106). The angle of the airflow flowing out of the shell body 100 can be controlled, the backflow of the airflow flowing out of the shell body 100 can be reduced, the negative pressure area can be reduced, the airflow velocity can be more uniform, the impact between the airflow and the flue can be reduced, the noise generated by the impact of the airflow can be effectively reduced, and the airflow is obviously increased.

[0112] The fourth embodiment of the present application provides a fan assembly 12, which is further based on the third embodiment described above,

[0113] As shown in Figure 6 and Figure 7 , the fan assembly 12 further comprises a vortex prevention ring 108. The vortex prevention ring 108 is arranged at the air inlet of the volute 10. In this way, the vortex prevention ring 108 can reduce or avoid the leakage of the airflow and prevent the backflow of the airflow in the chamber 102 from forming a vortex. In this way, by arranging the vortex prevention ring 108, on the one hand, the noise generated by the vortex can be reduced, and on the other hand, the airflow velocity in the chamber 102 can be uniform, so that the airflow flowing out of the volute 10 has a uniform velocity, the noise generated by the impact of the airflow can be effectively reduced, and the airflow is obviously increased.

[0114] In this embodiment, further, as shown in Figure 7 , the ratio of the outer diameter R1 of the vortex prevention ring 108 to the diameter R of the fan wheel 106 is greater than or equal to 1.05 and less than or equal to 1.15. In this way, the vortex prevention ring 108 can be designed according to the fan wheel 106, so that the vortex prevention ring 108 matches the fan wheel 106, thereby effectively preventing the leakage of the airflow, making the airflow velocity in the chamber 102 uniform, preventing the vortex, making the airflow flowing out of the volute 10 have a uniform velocity, effectively reducing the noise generated by the impact of the airflow, and obviously increasing the airflow.

[0115] Specifically, the ratio of the outer diameter R1 of the vortex prevention ring 108 to the diameter R of the wind wheel 106 can be 1.05, the ratio of the outer diameter R1 of the vortex prevention ring 108 to the diameter R of the wind wheel 106 can also be 1.15, and the ratio of the outer diameter R1 of the vortex prevention ring 108 to the diameter R of the wind wheel 106 can also be any value between 1.05 and 1.15. By limiting the ratio of the outer diameter R1 of the vortex prevention ring 108 to the diameter R of the wind wheel 106, the effective blocking of air flow leakage by the vortex prevention ring 108 can be ensured, thereby making the air flow in the chamber 102 uniform, which can prevent the occurrence of vortex on the one hand and make the flow rate of the air flow out of the volute 10 uniform on the other hand, effectively reducing the noise generated by the air flow impact, while the air flow is significantly increased.

[0116] Specifically, as shown in FIG. 1, Figure 7 the ratio of the outer diameter R1 of the vortex prevention ring 108 to the diameter R of the wind wheel 106 can be 1.05, 1.06, 1.07, 1.08, 1.09, 1.10, 1.11, 1.12, 1.13, 1.14, 1.15, etc., which will not be listed one by one here. Those skilled in the art can understand that as long as the vortex prevention ring 108 can cover the wind wheel 106, it can be realized.

[0117] Specifically, under a certain working condition, the ratio of the outer diameter R1 of the vortex prevention ring 108 to the diameter R of the wind wheel 106 is 1.12, and the diameter R of the wind wheel 106 is 209 mm, then the outer diameter R1 of the vortex prevention ring 108 can be calculated according to the formula to be 234 mm. It can be understood that when the ratio of the outer diameter R1 of the vortex prevention ring 108 to the diameter R of the wind wheel 106 is 1.12 and the diameter R of the wind wheel 106 is 209 mm, the outer diameter R1 of the vortex prevention ring 108 can be calculated to be 234 mm, i.e. under this working condition, the optimal size of the outer diameter R1 of the vortex prevention ring 108 is 234 mm.

[0118] Specifically, under another working condition, the ratio of the outer diameter R1 of the vortex prevention ring 108 to the diameter R of the wind wheel 106 is 1.06, and the diameter R of the wind wheel 106 is 150 mm, then the outer diameter R1 of the vortex prevention ring 108 can be calculated according to the formula to be 159 mm. It can be understood that when the ratio of the outer diameter R1 of the vortex prevention ring 108 to the diameter R of the wind wheel 106 is 1.06 and the diameter R of the wind wheel 106 is 150 mm, the outer diameter R1 of the vortex prevention ring 108 can be calculated to be 159 mm, i.e. under this working condition, the optimal size of the outer diameter R1 of the vortex prevention ring 108 is 159 mm.

[0119] Specifically, the calculation formula is R1 / R=1.12 or 1.06, wherein R1 is the outer diameter of the vortex prevention ring 108, and R is the diameter of the wind wheel 106.

[0120] The fifth embodiment of the present invention proposes a fan assembly 12, which, based on the fourth embodiment described above, further...

[0121] like Figure 7 As shown, there is a gap between the anti-vortex ring 108 and the impeller 106 along the axial direction of the impeller 106. That is, a certain distance is maintained between the anti-vortex ring 108 and the impeller 106 along the axial direction of the impeller 106. This avoids the anti-vortex ring 108 restricting the radial dimension of the impeller 106 during the installation and use of the fan assembly 12, preventing interference between the outer ring of the impeller 106 and the anti-vortex ring 108. Furthermore, the gap between the anti-vortex ring 108 and the impeller 106 allows users or staff to select an appropriate size impeller 106 according to actual airflow requirements, reducing the assembly difficulty of the fan assembly 12 and improving its assembly efficiency.

[0122] Specifically, when the diameter of the wind turbine 106 is large, a gap can be set between the anti-vortex ring 108 and the wind turbine 106, thereby ensuring that the anti-vortex ring 108 and the wind turbine 106 will not interfere with each other structurally while avoiding the generation of vortices.

[0123] In this embodiment, further, as Figure 7 As shown, when there is a gap between the anti-vortex ring 108 and the impeller 106, the size of the gap H is less than or equal to 2m. This allows the anti-vortex ring 108 to be designed in different ways to achieve the best working effect, blocking airflow leakage and guiding the direction of airflow, making the airflow velocity uniform, thereby effectively reducing the noise generated by airflow impact, while significantly increasing the airflow rate.

[0124] Specifically, the gap size H can be 2mm, or any size smaller than 2mm. By using the linear gap size H, the anti-vortex ring 108 can achieve its optimal working effect, blocking airflow leakage and guiding the airflow direction, making the airflow velocity uniform, thereby effectively reducing the noise generated by airflow impact, while significantly increasing the airflow rate.

[0125] Specifically, such as Figure 7 As shown, the gap size H can be 2 mm, 1.9 mm, 1.8 mm, 1.7 mm, 1.6 mm, 1.5 mm, 1.4 mm, 1.3 mm, 1.2 mm, 1.1 mm, 1.0 mm, etc., and will not be listed here. Those skilled in the art will understand that any design can be achieved as long as the anti-vortex ring 108 can block the backflow of airflow.

[0126] Specifically, in a certain working condition, the size of the gap H=2mm, so that the anti-vortex ring 108 can play the best working effect in this working condition, achieve the best effect of guiding the flow direction of the air flow, so as to avoid the occurrence of vortex, make the flow rate of the air flow uniform, and further effectively reduce the noise generated by the air flow impact, while the air flow is significantly increased.

[0127] Specifically, in another working condition, the size of the gap H=1mm, so that the anti-vortex ring 108 can play the best working effect in this working condition, achieve the best effect of guiding the flow direction of the air flow, so as to avoid the occurrence of vortex, make the flow rate of the air flow uniform, and further effectively reduce the noise generated by the air flow impact, while the air flow is significantly increased.

[0128] The sixth embodiment of the present application proposes a fan assembly 12, which is further based on the above-mentioned fourth embodiment,

[0129] Along the axial direction of the impeller 106, the anti-vortex ring 108 and the impeller 106 partially overlap. That is, in the axial direction of the impeller 106, a part of the impeller 106 extends into the inside of the anti-vortex ring 108. In this way, in the axial direction of the impeller 106, the coverage of the anti-vortex ring 108 to the impeller 106 is ensured, and the blocking effect of the anti-vortex ring 108 to the air flow is further improved, thereby greatly avoiding the generation of vortex.

[0130] Specifically, in the case where the diameter of the impeller 106 is small, the anti-vortex ring 108 and the impeller 106 can be partially overlapped, thereby improving the blocking effect of the anti-vortex ring 108 to the air flow.

[0131] In this embodiment, further, as shown in Figure 7 When the anti-vortex ring 108 and the impeller 106 partially overlap, the size D1 of the overlapping part is less than or equal to 4mm. In this way, the anti-vortex ring 108 can be designed according to the impeller 106, so that the anti-vortex ring 108 matches the impeller 106, can block the air flow from leaking out, guide the flow direction of the air flow, make the air flow always flow in one direction, prevent the air flow from flowing back, thereby preventing the air flow from generating vortex, making the flow rate of the air flow uniform, thereby effectively reducing the noise generated by the air flow impact, while the air flow is significantly increased.

[0132] Specifically, the size D1 of the overlapping part can be 4mm, and the size D1 of the overlapping part can also be any value less than 4mm. By limiting the value range of the size D1 of the overlapping part, the working effect of the anti-vortex ring 108 can be ensured, the air flow can be blocked from leaking out and the flow direction of the air flow can be guided, so that the flow rate of the air flow is uniform, thereby effectively reducing the noise generated by the air flow impact, while the air flow is significantly increased.

[0133] Specifically, as shown in Figure 7 the size D1 of the overlapping portion can be 4 mm, 3.8 mm, 3.6 mm, 3.4 mm, 3.2 mm, 3.0 mm, 2.8 mm, 2.6 mm, 2.4 mm, 2.2 mm, 2.0 mm, etc., which are not listed one by one here. Those skilled in the art can understand that as long as the vortex prevention ring 108 can block the air flow from leaking and guide the flow direction of the air flow, it can be achieved.

[0134] Specifically, under a certain working condition, the size D1 of the overlapping portion is 3.8 mm, so that the vortex prevention ring 108 can play the best working effect under this working condition, block the air flow from leaking and guide the flow direction of the air flow, make the flow rate of the air flow uniform, thereby effectively reducing the noise generated by the air flow impact, and at the same time, the air flow rate is significantly increased.

[0135] Specifically, under another working condition, the size D1 of the overlapping portion is 2.0 mm, so that the vortex prevention ring 108 can play the best working effect under this working condition, block the air flow from leaking and guide the flow direction of the air flow, make the flow rate of the air flow uniform, thereby effectively reducing the noise generated by the air flow impact, and at the same time, the air flow rate is significantly increased.

[0136] In particular, by comparing Figure 15 and Figure 16 It can be seen that the present application is provided with the vortex prevention ring 108 at the air inlet of the volute 10, compared with Figure 15 without setting the vortex prevention ring, the flow rate of the air flow can be obviously uniform (especially at the positions circled in Figure 15 and Figure 16 ), thereby effectively reducing the noise generated by the air flow impact, and at the same time, the air flow rate is significantly increased.

[0137] The seventh embodiment of the present application proposes a fan assembly 12, which is further provided with

[0138] As shown in Figure 8 and Figure 9 , the fan assembly 12 further comprises a flow collector 110 and a flow rectifier 112. The flow collector 110 is arranged at the air inlet of the volute 10, and the flow rectifier 112 is arranged on the flow collector 110. The air flow passes through the flow rectifier 112, is divided by the air inlet on the flow rectifier 112, and then enters the volute 10 through the flow collector 110. In this way, the air flow is divided by the air inlet and then combined, so that the flow rate of the air flow is uniform, thereby making the flow rate of the air flow out of the volute 10 more uniform, effectively reducing the noise generated by the air flow impact, and at the same time, the air flow rate is significantly increased.

[0139] The eighth embodiment of the present application proposes a fan assembly 12, which is further based on the above-mentioned embodiments three to seven,

[0140] As shown in Figure 10 , the rectifier 112 comprises a mounting edge 114 and a cover body 116. The mounting edge 114 is connected with the current collector 110, and the cover body 116 is arranged on the opening 120 of the current collector 110 through a connecting edge, and a plurality of air inlet holes 118 are arranged on the cover body 116. By arranging the air inlet holes 118 on the cover body 116, the airflow can be divided into multiple airflows by the air inlet holes 118, and then the airflows are combined, so that the flow rate of the airflow is uniform, and the flow rate of the airflow flowing out of the volute 10 is more uniform, effectively reducing the noise generated by the airflow impact, and at the same time, the airflow is obviously increased.

[0141] Specifically, the mounting edge 114 is provided with a screw hole, and the mounting edge 114 can be fixed on the current collector 110 by using a buckle, so as to fix the rectifier 112 on the current collector 110.

[0142] In this embodiment, further as shown in Figure 9 and Figure 11 , the ratio of the outer diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 is greater than or equal to 1.04 and less than or equal to 1.12. In this way, the outer diameter R2 of the rectifier 112 can be designed according to the diameter R3 of the opening 120, so that the outer diameter R2 of the rectifier 112 is always greater than the diameter of the opening 120, so that the outer circle of the rectifier 112 does not block the airflow into the cover body 116, and the working reliability of the rectifier 112 is ensured.

[0143] Specifically, the ratio of the outer diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 can be 1.04, the ratio of the outer diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 can also be 1.12, and the ratio of the outer diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 can also be any value between 1.04 and 1.12. By limiting the ratio of the outer diameter R2 of the rectifier 112 to the diameter R3 of the opening 120, it is ensured that the mounting edge 114 can always be greater than the opening 120, and the working reliability of the rectifier 112 is ensured.

[0144] Specifically, as shown in Figure 9 and Figure 11 , the ratio of the outer diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 can be 1.04, 1.05, 1.06, 1.07, 1.08, 1.09, 1.10, 1.11, 1.12, etc. The skilled person in the art can understand that as long as the outer circle of the rectifier 112 can be greater than the opening 120, it can be realized.

[0145] Preferably, under a certain operating condition, the ratio of the outer diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 is 1.07, and the diameter R3 of the opening 120 is 168mm. Therefore, the outer diameter R2 of the rectifier 112 can be calculated as 186mm according to the formula. It can be understood that when the ratio of the outer diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 is 1.07, and the diameter R3 of the opening 120 is 168mm, the calculated outer diameter R2 of the rectifier 112 is 186mm. That is, under this operating condition, the optimal size of the outer diameter R2 of the rectifier 112 is 186mm.

[0146] Preferably, under another operating condition, the ratio of the outer diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 is 1.12, and the diameter R3 of the opening 120 is 200mm. Therefore, the outer diameter R2 of the rectifier 112 can be calculated as 224mm according to the formula. It can be understood that when the ratio of the outer diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 is 1.12, and the diameter R3 of the opening 120 is 200mm, the calculated outer diameter R2 of the rectifier 112 is 224mm. That is, under this operating condition, the optimal size of the outer diameter R2 of the rectifier 112 is 224mm.

[0147] Specifically, the calculation formula is R2 / R3 = 1.07 or 1.12, where R2 is the outer diameter of the rectifier 112 and R3 is the diameter of the opening 120.

[0148] In this embodiment, further, as Figure 9 and Figure 11 As shown, the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120 is greater than or equal to 0.965 and less than or equal to 1.01. This allows the cover 116 to be designed differently according to the diameter of the opening 120, ensuring the cover 116 matches the opening 120. This allows the airflow, after being diverted by the air inlet 118, to enter the volute 10 through the opening 120, thereby guaranteeing the reliable operation of the rectifier 112.

[0149] Specifically, the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120 can be 0.965, 1.01, or any value between 0.965 and 1.01. By limiting the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120, the airflow after being diverted by the air inlet 118 can enter the volute 10 through the opening 120, thereby ensuring the reliable operation of the rectifier 112.

[0150] Specifically, as shown in Figure 9 and Figure 11 the ratio of the diameter R4 of the cover body 116 to the diameter R3 of the opening 120 can be 0.965, 0.968, 0.971, 0.974, 0.977, 0.980, 0.983, 0.986, 0.983, 0.991, 0.995, 1.01, etc., which are not listed one by one here. Those skilled in the art can understand that as long as the airflow after the cover body 116 is divided can enter the opening 120, it can be realized.

[0151] Preferably, under a certain working condition, the ratio of the diameter R4 of the cover body 116 to the diameter R3 of the opening 120 is 0.976, and the diameter R3 of the opening 120 is 168 mm, then the diameter R4 of the cover body 116 can be calculated according to the formula to be 164 mm. It can be understood that when the ratio of the diameter R4 of the cover body 116 to the diameter R3 of the opening 120 is 0.976 and the diameter of the opening 120 is 168 mm, the diameter of the cover body 116 can be calculated to be 164 mm, that is, under this working condition, the optimal size of the diameter of the cover body 116 is 164 mm.

[0152] Preferably, under another working condition, the ratio of the diameter R4 of the cover body 116 to the diameter R3 of the opening 120 is 0.994, and the diameter R3 of the opening 120 is 200 mm, then the diameter R4 of the cover body 116 can be calculated according to the formula to be 198.8 mm. It can be understood that when the ratio of the diameter R4 of the cover body 116 to the diameter R3 of the opening 120 is 0.994 and the diameter of the opening 120 is 200 mm, the diameter of the cover body 116 can be calculated to be 198.8 mm, that is, under this working condition, the optimal size of the diameter of the cover body 116 is 198.8 mm.

[0153] Specifically, the calculation formula is R4 / R3=0.976 or 0.994, wherein R4 is the diameter of the cover body 116, and R3 is the diameter of the opening 120.

[0154] The ninth embodiment of the present application proposes a fan assembly 12, which is further based on the above-mentioned embodiments three to eight,

[0155] As shown in Figure 12 the air inlet hole 118 is a regular polygon hole. Specifically, the regular polygon hole can save space, improve the utilization rate of the space of the cover body 116, ensure that the air inlet hole 118 can be concentrated in the central part of the cover body 116, thereby ensuring the air flow dividing effect of the air inlet hole 118, making the flow rate of the airflow more uniform, and effectively reducing the noise generated by the airflow impact, while the air flow is significantly increased.

[0156] In this embodiment, further, asFigure 9 and Figure 12 As shown in Figs. 1 and 2, the ratio of the length W of the regular polygonal hole to the diameter R3 of the opening 120 is greater than or equal to 0.018 and less than or equal to 0.031. In this way, the regular polygonal hole can be designed differently according to the opening 120, thereby ensuring the shunting effect of the air flow by the air inlet hole 118, making the flow rate of the shunted air flow uniform, and further making the flow rate of the air flow out of the volute 10 more uniform, effectively reducing the noise generated by the air flow impact, while the air flow is significantly increased.

[0157] Specifically, the ratio of the length W of the regular polygonal hole to the diameter R3 of the opening 120 can be 0.018, the ratio of the length W of the regular polygonal hole to the diameter R3 of the opening 120 can be 0.031, and the ratio of the length W of the regular polygonal hole to the diameter R3 of the opening 120 can also be any value between 0.018 and 0.031. In this way, by limiting the ratio of the length W of the regular polygonal hole to the diameter R3 of the opening 120, the working effect of the air inlet hole 118 is ensured, the flow rate of the shunted air flow is uniform, and further the flow rate of the air flow out of the volute 10 is more uniform, effectively reducing the noise generated by the air flow impact, while the air flow is significantly increased.

[0158] Specifically, as shown in Figs. 1 and 2, the ratio of the length W of the regular polygonal hole to the diameter R3 of the opening 120 can be 0.018, 0.020, 0.022, 0.024, 0.026, 0.028, 0.030, 0.031, etc. The skilled person in the art can understand that as long as the air inlet effect of the air inlet hole 118 can be ensured, it can be realized. Figure 9 and Figure 12 Specifically, as shown in Figs. 1 and 2, the ratio of the length W of the regular polygonal hole to the diameter R3 of the opening 120 can be 0.018, 0.020, 0.022, 0.024, 0.026, 0.028, 0.030, 0.031, etc. The skilled person in the art can understand that as long as the air inlet effect of the air inlet hole 118 can be ensured, it can be realized.

[0159] Specifically, under certain working conditions, the ratio of the length W of the regular polygonal hole to the diameter R3 of the opening 120 is 0.023, and the diameter R3 of the opening 120 is 168 mm, then the length W of the regular polygonal hole is calculated to be 4.05 mm according to the formula. It can be understood that when the ratio of the length W of the regular polygonal hole to the diameter R3 of the opening 120 is 0.023 and the diameter R3 of the opening 120 is 168 mm, the length W of the regular polygonal hole can be calculated to be 4.05 mm, i.e. under this working condition, the optimal size of the length W of the regular polygonal hole is 4.05 mm.

[0160] Specifically, in another working condition, the ratio of the length W of the regular polygon hole to the diameter R3 of the opening 120 is 0.030, and the diameter R3 of the opening 120 is 200 mm, so the length W of the regular polygon hole is calculated to be 6 mm according to the formula. It can be understood that when the ratio of the length W of the regular polygon hole to the diameter R3 of the opening 120 is 0.030, and the diameter R3 of the opening 120 is 200 mm, the length W of the regular polygon hole is calculated to be 6 mm, that is, in this working condition, the optimal size of the length W of the regular polygon hole is 6 mm.

[0161] Specifically, the calculation formula is W / R3=0.023 or 0.030, where W is the length of the regular polygon hole, and R3 is the diameter of the opening 120.

[0162] In this embodiment, further, as shown in Figure 10 the ratio of the total area S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 is greater than or equal to 0.58 and less than or equal to 0.68. In this way, different numbers of air inlet holes 118 can be designed according to the area S1 of the rectifier 112, so as to ensure the air flow effect of the air inlet holes 118 on the airflow, make the flow rate of the divided airflow uniform, and further make the flow rate of the airflow flowing out of the volute 10 more uniform, effectively reduce the noise generated by airflow impact, and at the same time, the air flow is obviously increased.

[0163] Specifically, the ratio of the total area S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 can be 0.58, and the ratio of the total area S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 can also be 0.68. The ratio of the total area S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 can also be any value between 0.58 and 0.68. In this way, by limiting the range of the ratio of the total area S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112, the air flow effect of the air inlet holes 118 is ensured, the flow rate of the airflow is more uniform, the noise generated by airflow impact is effectively reduced, and at the same time, the air flow is obviously increased.

[0164] Specifically, as shown in Figure 10 the ratio of the total area S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 can be 0.58, 0.59, 0.60, 0.61, 0.62, 0.63, 0.64, 0.65, 0.66, 0.67, 0.68, etc., which will not be listed one by one. Those skilled in the art can understand that as long as the air flow effect of the air inlet holes 118 can be ensured, it can be realized.

[0165] Specifically, in a certain working condition, the ratio of the total area S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 is 0.58, and the area S1 of the rectifier 112 is 100 mm2 , the area sum S of the plurality of air inlets 118 is calculated as S = 58 mm 2 , according to the formula. It can be understood that when the ratio of the area sum S of the plurality of air inlets 118 to the area S1 of the rectifier 112 is 0.58, the area S1 of the rectifier 112 is 100 mm 2 , the area sum S of the plurality of air inlets 118 is calculated as S = 58 mm 2 , that is, in this working condition, the optimal area sum of the plurality of air inlets 118 is 58 mm 2 .

[0166] Specifically, in another working condition, the ratio of the area sum S of the plurality of air inlets 118 to the area S1 of the rectifier 112 is 0.68, and the area S1 of the rectifier 112 is 150 mm 2 , the area sum S of the plurality of air inlets 118 is calculated as S = 102 mm 2 , according to the formula. It can be understood that when the ratio of the area sum S of the plurality of air inlets 118 to the area S1 of the rectifier 112 is 0.58, the area S1 of the rectifier 112 is 150 mm 2 , the area sum S of the plurality of air inlets 118 is calculated as S = 102 mm 2 , that is, in this working condition, the optimal area sum of the plurality of air inlets 118 is 102 mm 2 .

[0167] Specifically, the calculation formula is S / S1 = 0.58 or 0.68, wherein S is the area sum of the plurality of air inlets 118, and S1 is the area of the rectifier 112.

[0168] The tenth embodiment of the present application provides an extractor hood (not shown in the figure) comprising the fan assembly 12 according to any of the above embodiments.

[0169] Therefore, the extractor hood provided by the present application has all the beneficial effects of the fan assembly 12 described above, which will not be repeated here.

[0170] In addition, the extractor hood further comprises an air duct structure. The fan assembly 12 is arranged in the air duct structure, and the fan assembly 12 sucks the oil fume into the air duct structure when it operates.

[0171] Specifically, in the working process of the range hood, the fan wheel 106 in the fan assembly 12 works, so that the oil fume flows into the volute 10 through the flow collector 110 and the rectifier 112, and the air inlet hole 118 in the rectifier 112 can divide the flow of the oil fume, so that the flow rate of the oil fume entering the volute 10 is relatively uniform. When the oil fume is in the volute 10, the vortex prevention ring 108 can prevent the oil fume from leaking and guide the flow direction of the oil fume, so as to prevent the oil fume from backflowing and generating vortex, thereby ensuring that the flow rate of the oil fume in the volute 10 is uniform. When the oil fume flows out of the volute 10 into the air duct structure, by limiting the volute tongue position angle α to be greater than the outlet angle β, the negative pressure area at the air outlet 104 can be reduced, so that the oil fume does not backflow when flowing out of the air outlet 104, the negative pressure area is reduced, the flow rate of the oil fume is more uniform, the impact between the oil fume and the air duct structure is reduced, the noise generated due to the impact of the oil fume is effectively reduced, and the air flow is obviously increased.

[0172] Eleventh embodiment of the present application proposes a range hood integrated machine (not shown in the figure), which comprises the fan assembly 12 of any of the above embodiments.

[0173] Therefore, the range hood integrated machine proposed by the present application has all the beneficial effects of the above-mentioned fan assembly 12, which will not be described here.

[0174] In addition, the range hood integrated machine further comprises a stove and an air duct structure. The opening 120 of the air duct structure faces the stove, and the fan assembly 12 is arranged in the air duct structure, and the fan assembly 12 sucks the oil fume generated by cooking from the inlet into the air duct structure.

[0175] Specifically, in the working process of the range hood integrated machine, the stove generates high temperature to provide heat source for cooking, and oil fume is continuously generated in the cooking process. The opening 120 of the air duct structure faces the stove, the fan wheel 106 in the fan assembly 12 works, so that the oil fume flows into the volute 10 through the flow collector 110 and the rectifier 112, and the air inlet hole 118 in the rectifier 112 can divide the flow of the oil fume, so that the flow rate of the oil fume entering the volute 10 is relatively uniform. When the oil fume is in the volute 10, the vortex prevention ring 108 can prevent the oil fume from leaking and guide the flow direction of the oil fume, so as to prevent the oil fume from backflowing and generating vortex, thereby ensuring that the flow rate of the oil fume in the volute 10 is uniform. When the oil fume flows out of the volute 10 into the air duct structure, by limiting the volute tongue position angle α to be greater than the outlet angle β, the negative pressure area at the air outlet 104 can be reduced, so that the oil fume does not backflow when flowing out of the air outlet 104, the negative pressure area is reduced, the flow rate of the oil fume is more uniform, the impact between the oil fume and the air duct structure is reduced, the noise generated due to the impact of the oil fume is effectively reduced, and the air flow is obviously increased.

[0176] In summary, the volute 10 provided by the present application comprises a shell body 100. Specifically, the shell body 100 comprises a volute tongue position angle a and an outlet angle β, and the angle of the volute tongue position angle a is greater than the outlet angle β. In this way, the angle of the airflow flowing out of the shell body 100 can be controlled, and the airflow backflow when the airflow flows out of the shell body 100 can be reduced, the negative pressure area can be reduced, the airflow velocity can be more uniform, the impact between the airflow and the flue can be reduced, the noise generated due to the impact of the airflow can be effectively reduced, and the airflow volume is obviously increased.

[0177] Specifically, the volute tongue position angle a can be 41°, the volute tongue position angle a can also be 58°, and the volute tongue position angle a can also be any value between 41° and 58°. By setting the value range of the volute tongue position angle a, the shell body 100 can adapt to different working environments, achieve the best effect of reducing the negative pressure area, make the airflow velocity more uniform, effectively reduce the noise generated due to the impact of the airflow, and obviously increase the airflow volume.

[0178] Specifically, the outlet angle β can be 29°, the outlet angle β can also be 38°, and the outlet angle β can also be any value between 29° and 38°. By setting the value range of the outlet angle β, the shell body 100 can adapt to different working environments, achieve the best effect of concentrating the airflow, make the airflow velocity more uniform, effectively reduce the noise generated due to the impact of the airflow, and obviously increase the airflow volume.

[0179] Further, the shell body 100 further comprises a chamber 102 and an air outlet 104. The chamber 102 is used to place a fan 106, and the fan 106 can suck the airflow into the shell body 100 and send the airflow out of the shell body 100 from the air outlet 104 connected with the chamber 102 when the fan 106 operates. Specifically, in a plane perpendicular to the axis of the fan 106, the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan 106 is greater than or equal to 1.38 and less than or equal to 1.45. In this way, the size D of the air outlet 104 can be designed according to different fans 106, the size D of the air outlet 104 is matched with the fan 106, so that the air outlet 104 can guarantee the airflow volume while reducing the negative pressure area, prevent the airflow backflow, make the airflow velocity more uniform, effectively reduce the noise generated due to the impact of the airflow, and obviously increase the airflow volume.

[0180] Specifically, the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan wheel 106 can be 1.38, the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan wheel 106 can also be 1.45, and the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan wheel 106 can also be any value between 1.38 and 1.45. By limiting the value range of the ratio of the size D of the air outlet 104 to the outer circle radius r of the fan wheel 106, the size D of the air outlet 104 can be matched with the fan wheel 106, so that the air outlet 104 can not only ensure the flow rate, but also reduce the negative pressure area to prevent air backflow, so that the air flow rate is more uniform, effectively reduces the noise generated by air flow impact, and the air flow rate is obviously increased.

[0181] In the description of the present application, the term "a plurality of" refers to two or more, unless otherwise explicitly limited, and the terms "upper", "lower", and the like indicate the orientation or positional relationship shown in the drawings based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application; the terms "connection", "installation", "fixation" and the like should be understood broadly, for example, "connection" can be fixed connection, can also be detachable connection, or integral connection; can be directly connected, or indirectly connected through an intermediate medium. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0182] In the description of the present application, the terms "one embodiment", "some embodiments", "a specific embodiment" and the like are described to mean that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the present description, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0183] The above is only the preferred embodiment of the present application and is not intended to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present application shall be included in the protection scope of the present application.

Claims

1. A fan assembly, characterized in that, The wind turbine assembly includes a volute and a rotor, the rotor being disposed within the volute, the volute comprising: A shell body, the shell body including a volute tongue position angle and an exit angle, wherein the volute tongue position angle is greater than the exit angle; The fan assembly also includes an anti-vortex ring, which is disposed on the volute and located at the air inlet of the volute. Along the axial direction of the wind turbine, the anti-vortex ring has a gap or partially overlaps with the wind turbine; Along the axial direction of the wind turbine, one section of the wind turbine extends into the interior of the anti-vortex ring; The shell body further includes a chamber and an air outlet communicating with the chamber. The chamber is used to house the impeller. In a plane perpendicular to the axis of the impeller, the ratio of the size of the air outlet to the outer radius of the impeller is greater than or equal to 1.38 and less than or equal to 1.

45.

2. The wind turbine assembly according to claim 1, characterized in that, The position angle of the volute tongue is greater than 41° and less than 58°.

3. The wind turbine assembly according to claim 1, characterized in that, The exit angle is greater than 29° and less than 38°.

4. The wind turbine assembly according to claim 1, characterized in that, The ratio of the outer diameter of the anti-vortex ring to the diameter of the wind turbine is greater than or equal to 1.05 and less than or equal to 1.

15.

5. The wind turbine assembly according to claim 1, characterized in that, When there is a gap between the anti-vortex ring and the wind turbine, the size of the gap is less than or equal to 2 mm.

6. The wind turbine assembly according to claim 1, characterized in that, When the anti-vortex ring partially overlaps with the wind turbine, the size of the overlapping portion is less than or equal to 4 mm.

7. The wind turbine assembly according to any one of claims 4 to 6, characterized in that, Also includes: A collector is disposed on the volute and located at the air inlet of the volute; the collector includes an opening. A rectifier, covering the opening and connected to the collector, includes multiple air inlets.

8. The wind turbine assembly according to claim 7, characterized in that, The rectifier includes; The mounting edge is connected to the collector; A cover is provided on the mounting side, and the plurality of air inlets are provided on the cover.

9. The wind turbine assembly according to claim 7, characterized in that, The ratio of the outer diameter of the rectifier to the diameter of the opening is greater than or equal to 1.04 and less than or equal to 1.

12.

10. The wind turbine assembly according to claim 8, characterized in that, The ratio of the diameter of the cover to the diameter of the opening is greater than or equal to 0.965 and less than or equal to 1.

01.

11. The wind turbine assembly according to claim 7, characterized in that, The air inlet is a regular polygonal hole.

12. The wind turbine assembly according to claim 11, characterized in that, The ratio of the length of the regular polygonal hole to the diameter of the opening is greater than or equal to 0.018 and less than or equal to 0.

031.

13. The wind turbine assembly according to claim 7, characterized in that, The ratio of the total area of ​​the plurality of air inlets to the area of ​​the rectifier is greater than or equal to 0.58 and less than or equal to 0.

68.

14. A range hood, characterized in that, include: Air duct structure; The fan assembly as described in any one of claims 1 to 13, wherein the fan assembly is disposed within the duct structure.

15. A range hood and cooktop combo unit, characterized in that, include: stove body; The air duct structure has its inlet facing the stove body; The fan assembly as described in any one of claims 1 to 13, wherein the fan assembly is disposed within the duct structure.

Images