CN116336518A

CN116336518A - Spiral case, fan subassembly, range hood and range hood all-in-one

Info

Publication number: CN116336518A
Application number: CN202111604350.5A
Authority: CN
Inventors: 雷国茂; 陈飞帆; 吴慧民; 王凯; 张素凌; 张乾; 谢歆雯
Original assignee: Foshan Shunde Midea Electrical Heating Appliances Manufacturing Co Ltd
Current assignee: Foshan Shunde Midea Electrical Heating Appliances Manufacturing Co Ltd
Priority date: 2021-12-24
Filing date: 2021-12-24
Publication date: 2023-06-27

Abstract

The invention provides a volute, a fan assembly, a range hood and a range hood integrated machine, wherein the volute comprises: the shell body comprises a volute tongue position angle and an outlet angle, and the volute tongue position angle is larger than the outlet angle. According to the invention, the volute tongue position angle is limited to be larger than the outlet angle, so that the angle of the airflow flowing out of the shell body can be controlled, the airflow 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 an external structure is reduced, the noise generated by the airflow impact is effectively reduced, and meanwhile, the airflow quantity is obviously increased.

Description

Spiral case, fan subassembly, range hood and range hood all-in-one

Technical Field

The invention relates to the technical field of cooking appliances, in particular to a volute, a fan assembly, a range hood and a range hood integrated machine.

Background

The volute is an important component of the overall fan assembly. In the related art, the design of the volute is unreasonable, so that the airflow of the fan assembly is too concentrated, the airflow can flow back, the wind resistance is increased, and the airflow is reduced. In addition, the air current can produce great impact force when concentrating, and the air current can directly collide with the pipeline after flowing out the fan subassembly, because the impact force of air current is big, the air current can be comparatively violent with the collision that wind channel structure took place to produce very big impact noise.

Disclosure of Invention

The present invention aims to solve at least one of the technical problems existing in the prior art.

To this end, a first aspect of the invention provides a volute.

A second aspect of the invention provides a fan assembly.

In a third aspect, the present invention provides a range hood.

The fourth aspect of the invention provides a smoke kitchen integrated machine.

A first aspect of the present invention proposes a volute comprising: the shell body comprises a volute tongue position angle and an outlet angle, and the volute tongue position angle is larger than the outlet angle.

The volute provided by the invention comprises a housing body. Specifically, the housing body includes a volute tongue position angle and an outlet angle, the angle of the volute tongue position angle being greater than the angle of the outlet angle. Like this, the angle when can controlling the air current and flow out the shell body can also reduce the air current backward flow when the air current flows out the shell body, reduces the negative pressure district, lets the air current velocity of flow more even to reduce the impact between air current and the external structure, reduce effectively because the noise that the air current impacted and produced, the air current obviously increases simultaneously.

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

In this design, the volute tongue position angle is greater than 41 ° and less than 58 °. Like this, can let the shell body design to current operating mode, furthest reduces the negative pressure district that makes the volute tongue position, can not take place the backward flow when letting the air current flow out the shell body to make the air current velocity of flow that flows out the shell body even, the impact force of air current reduces, reduces effectively because the noise that the air current impacted and produced, and the air current obviously increases simultaneously.

Specifically, the volute tongue position angle may be 41 °, the volute tongue position angle may be 58 °, and the volute tongue position angle may be any value between 41 ° and 58 °. Through setting for the numerical range of volute tongue position angle, can let the shell body adapt to different operational environment, reach the best effect of reducing the negative pressure district, let the velocity of flow of air flow more even to reduce the noise that produces because the air current strikes, the air current obviously increases simultaneously.

In some possible designs, the exit angle is greater than 29 ° and less than 38 °.

In this design, the exit angle is greater than 29 ° and less than 38 °. Like this, can let the shell body carry out the pertinence design to different service environment, control the angle of air current outflow shell body, let the flow of air current more concentrate, make the velocity of flow more even to reduce effectively because the noise that the air current strikeed to produce, the air current obviously increases simultaneously.

Specifically, the outlet angle may be 29 °, the outlet angle may be 38 °, and the outlet angle may be any value between 29 ° and 38 °. Through setting for the numerical range of outlet angle, can let the shell body adapt to different operational environment, reach the effect that makes the air current concentrate to let the velocity of flow of air current more even, thereby reduce effectively because the noise that the air current impacted and produced, the air current obviously increases simultaneously.

In some possible designs, the housing body further comprises a chamber for housing the wind wheel and an air outlet in communication with the chamber, wherein the ratio of the dimension D of the air outlet to the outer radius r of the wind wheel in a plane perpendicular to the axis of the wind wheel is greater than or equal to 1.38 and less than or equal to 1.45.

In this design, the housing body further includes a chamber and an air outlet. The cavity is used for placing the wind wheel, and when the wind wheel operates, the air flow can be sucked into the shell body and sent out of the shell body from the air outlet. Specifically, in a plane perpendicular to the axis of the wind wheel, the ratio of the size of the air outlet to the radius r of the outer ring of the wind wheel is greater than or equal to 1.38 and less than or equal to 1.45. The size of the air outlet can be designed according to different wind wheels, the size of the air outlet is matched with the wind wheels, the negative pressure area is reduced while the air flow rate of the air outlet can be ensured, the air flow is prevented from flowing back, the air flow speed is more uniform, the noise generated by air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

Specifically, the ratio of the size of the air outlet to the outer ring radius of the wind wheel may be 1.38, the ratio of the size of the air outlet to the outer ring radius of the wind wheel may also be 1.45, and the ratio of the size of the air outlet to the outer ring radius of the wind wheel may also be any value between 1.38 and 1.45. Through limiting the numerical range of the ratio of the size of the air outlet to the radius of the outer ring of the wind wheel, the size of the air outlet can be matched with the wind wheel, so that the air outlet can ensure the flow, reduce the negative pressure area and prevent the air flow from flowing back, the flow speed of the air flow is more uniform, the noise generated by the air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

A second aspect of the present invention proposes a fan assembly comprising: the volute of any one of the above first aspect, wherein the wind wheel is disposed in the volute.

The fan assembly provided by the invention comprises the volute of any one of the technical schemes. Therefore, the above-mentioned spiral case has all the beneficial effects, and will not be described herein.

In addition, the fan assembly further comprises a wind wheel. In particular, the wind wheel is arranged in the chamber of the volute. Specifically, when the fan assembly works, the wind wheel sucks air flow into the shell body and sends the air flow out of the shell body from the air outlet connected with the cavity, the volute tongue position angle of the shell body is larger than the outlet angle, the ratio of the size of the air outlet to the radius of the outer ring of the wind wheel is larger than or equal to 1.38 and smaller than or equal to 1.45 (in the plane perpendicular to the axis of the wind wheel), the angle of the air flow when the air flow flows out of the shell body can be controlled, the air flow backflow of the air flow when the air flow flows out of the shell body can be reduced, the negative pressure area is reduced, the air flow speed is more uniform, the impact between the air flow and the smoke tube is reduced, the noise generated by the air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

In some possible designs, the fan assembly further comprises: the vortex-preventing ring is arranged on the volute and is positioned at the air inlet of the volute.

In this design, the fan assembly also includes an anti-vortex ring. Wherein, prevent vortex ring setting in the air intake department on the spiral case. Thus, the vortex-preventing ring can reduce or prevent the air flow from leaking, and the air flow in the cavity is prevented from flowing back to generate vortex. Like this, through the setting of vortex ring, on the one hand can reduce the noise that the vortex produced, on the other hand can let the air current velocity of flow in the cavity even to the velocity of flow when making the air current flow into the spiral case is even, reduces effectively because the noise that the air current impacted and produced, and the air current obviously increases simultaneously.

In some possible designs, the ratio of the outer ring diameter of the anti-vortex ring to the diameter of the rotor is greater than or equal to 1.05 and less than or equal to 1.15.

In this design, the ratio of the outer ring diameter of the anti-vortex ring to the diameter of the wind wheel is greater than or equal to 1.05 and less than or equal to 1.15. Like this, prevent the vortex ring and design according to the wind wheel for prevent vortex ring matching wind wheel, thereby make prevent vortex ring can block the leakage of air current effectively, make the air current velocity of flow in the cavity even. On one hand, the vortex can be prevented from occurring, on the other hand, the flow velocity of the airflow flowing out of the volute is uniform, noise generated by airflow impact is effectively reduced, and meanwhile, the airflow is obviously increased.

Specifically, the ratio of the diameter of the outer ring of the vortex-preventing ring to the diameter of the wind wheel can be 1.05, the ratio of the diameter of the outer ring of the vortex-preventing ring to the diameter of the wind wheel can be 1.15, and the ratio of the diameter of the outer ring of the vortex-preventing ring to the diameter of the wind wheel can be any value between 1.05 and 1.15.

In some possible designs, there is a gap between the anti-vortex ring and the rotor in the axial direction of the rotor.

In this design, there is a gap between the anti-vortex ring and the rotor in the axial direction of the rotor. That is, in the axial direction of the wind wheel, a certain distance is ensured between the anti-vortex ring and the wind wheel. Therefore, in the process of installing and using the fan assembly, the radial dimension limitation of the vortex-preventing ring to the wind wheel can be avoided, and the condition that the outer ring of the wind wheel and the vortex-preventing ring interfere with each other can not occur. Moreover, due to the existence of the space between the vortex-preventing ring and the wind wheel, a user or a worker can select the wind wheel with proper size according to the actual air quantity demand, the assembly difficulty of the fan assembly can be reduced, and the assembly efficiency of the fan assembly is improved.

Specifically, under the condition that the diameter of the wind wheel is large, a gap exists between the vortex-preventing ring and the wind wheel, so that structural interference between the vortex-preventing ring and the wind wheel is avoided on the basis of avoiding vortex generation.

In some possible designs, the anti-vortex ring partially overlaps the rotor in the axial direction of the rotor.

In this design, the anti-vortex ring and the wind wheel are partially overlapped along the axial direction of the wind wheel. That is, in the axial direction of the wind wheel, a section of the wind wheel is made to extend into the inside of the vortex ring. Therefore, in the axial direction of the wind wheel, the coverage of the vortex-preventing ring to the wind wheel is ensured, the blocking effect of the vortex-preventing ring on the airflow is further improved, and the generation of vortex is further avoided to a great extent.

Specifically, under the condition that the diameter of the wind wheel is smaller, the anti-vortex ring and the wind wheel can be partially overlapped, so that the blocking effect of the anti-vortex ring on the air flow is improved.

In some possible designs, with a gap between the anti-vortex ring and the rotor, the size of the gap is less than or equal to 2mm.

In this design, when there is a gap between the anti-vortex ring and the wind wheel, the size of the gap is less than or equal to 2m. Therefore, on the basis of ensuring that structural interference can not occur between the vortex-preventing ring and the wind wheel, the distance between the vortex-preventing ring and the wind wheel is reduced as much as possible, the leakage amount of air flow is reduced, most of air flow can enter the volute, and vortex generation is avoided.

Specifically, the size of the gap may be 2mm, and the size H of the gap may be any size smaller than 2 mm. Through the size of the linear gap, the anti-vortex ring can achieve the optimal working effect, the air flow is blocked from leaking and guided in the flowing direction, and the flow speed of the air flow is uniform, so that noise generated by air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

In some possible designs, where the anti-vortex ring overlaps the rotor portion, the overlap is less than or equal to 4mm in size.

In this design, when the anti-vortex ring overlaps the rotor portion, the size of the overlapping portion is less than or equal to 4mm. Therefore, on the basis that the vortex-preventing ring can block the leakage of air flow, the overlapping size of the vortex-preventing ring and the wind wheel is avoided, on one hand, the waste of materials of the vortex-preventing ring can be avoided, on the other hand, the assembly difficulty of the vortex-preventing ring can be reduced, and the possibility of interference between the vortex-preventing ring and the wind wheel is reduced.

Specifically, the size of the overlapping portion may be 4mm, and the size of the overlapping portion may be any value smaller than 4mm. By limiting the numerical range of the size of the overlapped part, the working effect of the vortex-preventing ring can be ensured, the leakage of the air flow is blocked, the flowing direction of the air flow is guided, and the flow speed of the air flow is uniform, so that the noise generated by the impact of the air flow is effectively reduced, and meanwhile, the air flow is obviously increased.

In some possible designs, the fan assembly further comprises: the current collector is arranged on the volute, is positioned at the air inlet of the volute and comprises an opening; and the rectifier is covered on the opening and connected with the current collector, and comprises a plurality of air inlet holes.

In this design, the fan assembly also includes a current collector and a rectifier. The flow collector is arranged at an air inlet on the volute, the rectifier is arranged on an opening of the flow collector, and air flow passes through the rectifier and is split by the air inlet on the rectifier and then enters the volute through the flow collector. Therefore, the air flows can be split by the air inlet and then combined, so that the flow speed of the air flows is uniform, the flow speed of the air flows out of the volute is more uniform, the noise generated by air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

In some possible designs, the rectifier includes: the mounting edge is connected with the current collector; the cover body is arranged on the mounting edge, and the air inlets are arranged on the cover body.

In this design, the rectifier includes a mounting edge and a cover. The installation edge is connected with the current collector, the cover body is arranged on the opening of the current collector through the connection edge, and a plurality of air inlet holes are formed in the cover body. Through set up the fresh air inlet on the cover body, can let the air current by fresh air inlet reposition of redundant personnel become the stranded air current, then merge again to make the velocity of flow of air current even, and then make the air current velocity of flow that flows out the spiral case more even, reduce effectively because the noise that the air current impacted and produced, the air current obviously increases simultaneously.

In some possible designs, 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 design, the ratio of the diameter of the outer race 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. Therefore, the diameter of the outer ring of the rectifier can be designed in a targeted mode according to the diameter of the opening, and the diameter of the outer ring of the rectifier is always larger than the diameter of the opening to be matched, so that the outer ring of the rectifier can not block air flow to enter the cover body, and the working reliability of the rectifier is guaranteed.

Specifically, the ratio of the diameter of the outer ring of the rectifier to the diameter of the opening may be 1.04, the ratio of the diameter of the outer ring of the rectifier to the diameter of the opening may be 1.12, and the ratio of the diameter of the outer ring of the rectifier to the diameter of the opening may be any one value between 1.04 and 1.12. The ratio of the diameter of the outer ring of the rectifier to the diameter of the opening is limited, so that the mounting edge can be always larger than the opening, and the air flow can enter the opening, so that the working reliability of the rectifier is guaranteed.

In some possible designs, the ratio of the diameter of the cap to the diameter of the opening is greater than or equal to 0.965 and less than or equal to 1.01.

In this design, the ratio of the diameter of the cap to the diameter of the opening is greater than or equal to 0.965 and less than or equal to 1.01. Like this, can let the cover body carry out different designs according to the opening diameter, let the cover body match opening, make the air current after the inlet opening reposition of redundant personnel can get into in the spiral case through the opening to guarantee the operational reliability of rectifier.

Specifically, the ratio of the diameter of the cover to the diameter of the opening may be 0.965, the ratio of the diameter of the cover to the diameter of the opening may be 1.01, and the ratio of the diameter R4 of the cover to the diameter of the opening may be any value between 0.965 and 1.01. Through limiting the ratio of the diameter of the cover body to the diameter of the opening, the air flow which is split by the air inlet hole can enter the volute through the opening, so that the working reliability of the rectifier is ensured.

In some possible designs, the air inlet holes are regular polygonal holes.

In this design, the air inlet is a regular polygon. Specifically, regular polygon hole can save space, improves the utilization ratio in cover body space, guarantees that the fresh air inlet can concentrate in the central part of cover body to guarantee the reposition of redundant personnel effect of fresh air inlet to the air current, make the velocity of flow of air current even, and then make the air current velocity of flow that flows out the spiral case more even, reduce effectively because the noise that the air current impacted and produced, the air current obviously increases simultaneously.

In some possible designs, the ratio of the shape 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.

In this design, the ratio of the shape 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. Like this, can let regular polygon hole carry out different designs according to the opening to guarantee the reposition of redundant personnel effect of fresh air inlet to the air current, let the air current velocity of flow that divides the flow through even, and then make the air current velocity of flow that flows out the spiral case more even, reduce effectively because the noise that the air current strikeed and produce, the air current obviously increases simultaneously.

Specifically, the ratio of the shape length of the regular polygon hole to the diameter of the opening may be 0.018, the ratio of the shape length of the regular polygon hole to the diameter of the opening may also be 0.031, and the ratio of the shape length of the regular polygon hole to the diameter of the opening may also be any value between 0.018 and 0.031. Therefore, the working effect of the air inlet hole is ensured by limiting the ratio of the shape length of the regular polygon hole to the diameter of the opening, so that the flow velocity of the air flow flowing through the air inlet hole is uniform, the flow velocity of the air flow flowing out of the volute is more uniform, the noise generated by air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

In some possible designs, the ratio of the sum of the areas 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.

In this design, the ratio of the sum of the areas 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. Like this, can design different numbers of inlet openings according to the area of rectifier to guarantee the effect of inlet opening to the windward flow of air current, let the air current velocity of flow that divides the flow through even, and then make the air current velocity of flow that flows out the spiral case more even, reduce effectively because the noise that the air current impacted and produced, the air current obviously increases simultaneously. Specifically, the ratio of the sum of the areas of the air inlet holes to the area of the rectifier is the aperture ratio of the rectifier.

Specifically, the ratio of the sum of the areas of the plurality of air inlet holes to the area of the rectifier may be 0.58, the ratio of the sum of the areas of the plurality of air inlet holes to the area of the rectifier may be 0.68, and the ratio of the sum of the areas of the plurality of air inlet holes to the area of the rectifier may be any value between 0.58 and 0.68. Therefore, the flow dividing effect of the air inlet holes is ensured by limiting the ratio range of the sum of the areas of the air inlet holes to the area of the rectifier, so that the flow velocity of air flow is more uniform, the noise generated by air flow impact is effectively reduced, and the air flow is obviously increased.

A third embodiment of the present invention provides a range hood, including: an air duct structure; the fan assembly according to any of the second aspect, wherein the fan assembly is disposed in the air duct structure.

The range hood provided by the invention comprises the fan assembly according to any one of the technical schemes, so that the range hood has all the beneficial effects of the fan assembly and is not repeated herein.

In addition, the range hood also comprises an air duct structure. Wherein, the fan subassembly sets up in the wind channel structure, and in the fan subassembly operation was inhaled the oil smoke in the wind channel structure.

Specifically, in the working process of the range hood, the wind wheel in the fan assembly works, so that the oil smoke flows into the volute through the current collector and the rectifier, and the oil smoke can be split through the air inlet hole in the rectifier, so that the flow velocity of the oil smoke can enter the volute more uniformly. When the oil smoke is in the spiral case, the vortex-preventing ring can prevent the oil smoke from leaking, guide the flowing direction of the oil smoke, prevent the oil smoke from flowing back and generate vortex, thereby ensuring the uniform flow velocity of the oil smoke in the spiral case. When the oil smoke flows out of the volute casing and enters the air duct structure, the negative pressure area at the air outlet can be reduced by limiting the position angle of the volute tongue to be larger than the outlet angle, so that the oil smoke cannot flow back when flowing out of the air outlet, the negative pressure area is reduced, the flow speed of the oil smoke is more uniform, the impact between the oil smoke and the air duct structure is reduced, noise generated by the impact of the oil smoke is effectively reduced, and meanwhile, the air flow is obviously increased.

A fourth aspect of the present invention provides a smoke kitchen all-in-one machine, including: a stove body; the inlet of the air duct structure is arranged towards the stove body; the fan assembly according to any of the second aspect, wherein the fan assembly is disposed in the air duct structure.

The smoke kitchen all-in-one machine provided by the invention comprises the fan assembly according to any one of the technical schemes, so that the smoke kitchen all-in-one machine has all the beneficial effects of the fan assembly, and the description is omitted here.

In addition, the smoke kitchen all-in-one still includes kitchen body and air duct structure. Wherein, the kitchen body generates high temperature for the culinary art. The opening of wind channel structure is towards the kitchen body, and fan assembly sets up in wind channel mechanism, and fan assembly is inhaled the oil smoke that the culinary art produced from the import in the wind channel structure.

Specifically, in the working process of the smoke kitchen all-in-one machine, the kitchen body generates high temperature to provide a heat source for cooking, and oil smoke can be continuously generated in the cooking process. The opening of wind channel structure is towards the kitchen body, and the wind wheel work in the fan subassembly makes the oil smoke flow into the spiral case through current collector and rectifier in, and the fresh air inlet in the rectifier can shunt the oil smoke, makes the velocity of flow of oil smoke comparatively evenly get into in the spiral case. When the oil smoke is in the spiral case, the vortex-preventing ring can prevent the oil smoke from leaking, guide the flowing direction of the oil smoke, prevent the oil smoke from flowing back and generate vortex, thereby ensuring the uniform flow velocity of the oil smoke in the spiral case. When the oil smoke flows out of the volute casing and enters the air duct structure, the negative pressure area at the air outlet can be reduced by limiting the position angle of the volute tongue to be larger than the outlet angle, so that the oil smoke cannot flow back when flowing out of the air outlet, the negative pressure area is reduced, the flow speed of the oil smoke is more uniform, the impact between the oil smoke and the air duct structure is reduced, noise generated by the impact of the oil smoke is effectively reduced, and meanwhile, the air flow is obviously increased.

Additional aspects and advantages of the invention will be set forth in part in the description which follows, or may be learned by practice of the invention.

Drawings

The foregoing and/or additional aspects and advantages of the invention will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:

FIG. 1 is a schematic illustration of the construction of a volute of one embodiment of the invention;

FIG. 2 is a rear view of the volute of the embodiment of FIG. 1;

FIG. 3 is a cross-sectional view of the volute of the embodiment of FIG. 2 taken along line A-A;

FIG. 4 is a schematic view of the structure of a wind turbine according to an embodiment of the present invention;

FIG. 5 is a schematic structural view of a fan assembly according to one embodiment of the present invention;

FIG. 6 is a top view of the blower assembly of the embodiment of FIG. 5;

FIG. 7 is a cross-sectional view of the blower assembly of the embodiment shown in FIG. 6 taken along line B-B;

FIG. 8 is a schematic structural view of a fan assembly according to one embodiment of the present invention;

FIG. 9 is a cross-sectional view of the blower assembly of the embodiment shown in FIG. 8 taken along line C-C;

FIG. 10 is a schematic diagram of a rectifier according to one embodiment of the invention;

FIG. 11 is a cross-sectional view of the rectifier of the embodiment of FIG. 10 taken along D-D;

FIG. 12 is a schematic view of the structure of an air intake according to an embodiment of the present invention;

FIG. 13 is a flow velocity vector diagram of the airflow when the scroll casing is used in the related art;

FIG. 14 is a flow vector diagram of airflow when the volute of one embodiment of the invention is in use;

FIG. 15 is a flow velocity vector diagram of the air flow when the fan assembly of the related art is in use;

FIG. 16 is a flow velocity vector diagram of the airflow when the fan assembly of one embodiment of the present invention is in use.

The correspondence between the reference numerals and the component names in fig. 1 to 12 is:

10 spiral case, 12 fan subassembly, 100 shell body, 102 cavity, 104 air outlet, 106 wind wheel, 108 vortex-preventing ring, 110 collector, 112 rectifier, 114 installation limit, 116 cover body, 118 inlet opening, 120 opening.

Detailed Description

In order that the above-recited objects, features and advantages of the present invention will be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings and appended detailed description. It should be noted that, in the case of no conflict, the embodiments of the present application and the features in the embodiments may be combined with each other.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced otherwise than as described herein, and therefore the scope of the present invention is not limited to the specific embodiments disclosed below.

A volute 10, a fan assembly 12, a range hood, and a range hood all-in-one provided according to some embodiments of the present invention are described below with reference to fig. 1 to 16.

As shown in fig. 1 and 2, a first embodiment of the present invention proposes a scroll casing 10 including a casing body 100.

As shown in fig. 1 to 4, the casing body 100 includes 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. Like this, the angle when can controlling the air current and flow out shell body 100 can also reduce the air current backward flow when air current flows out shell body 100, reduces the negative pressure district, lets the air current velocity of flow more even to reduce the impact between air current and the external structure, reduce effectively because the noise that the air current impacted and produced, the air current obviously increases simultaneously.

In this embodiment, further, as shown in fig. 3, the volute tongue position angle α is greater than 41 ° and less than 58 °. Like this, can let shell body 100 design to current operating mode, furthest reduces the negative pressure district that makes the volute tongue position, can not take place the backward flow when letting the air current flow out shell body 100 to make the air current velocity of flow that flows out shell body 100 even, the impact force of air current reduces, reduces effectively because the noise that the air current impacted and produced, and the air current obviously increases simultaneously.

Specifically, the volute tongue position angle α may be 41 °, the volute tongue position angle α may be 58 °, and the volute tongue position angle α may be any value between 41 ° and 58 °. By setting the numerical range of the volute tongue position angle alpha, the shell body 100 can adapt to different working environments, the best effect of reducing the negative pressure area is achieved, the flow velocity of the air flow is more uniform, thereby reducing noise generated by air flow impact and obviously increasing the air flow.

Specifically, as shown in fig. 3, the volute tongue position angle α may be 41 °, 43 °, 45 °, 47 °, 49 °, 51 °, 53 °, 55 °, 57 °, 58 °, and the like, which are not further listed herein. Those skilled in the art will appreciate that this may be accomplished as long as it is ensured that the reduced pressure area is minimized.

Specifically, under a certain working condition, the volute tongue position angle α may be α=50°, so that the negative pressure area at the air outlet 104 of the volute 10 is minimized, and the air flow is prevented from flowing back, so that the uniform flow velocity of the air flow is ensured, the noise generated by the air flow impact is effectively reduced, and the air flow is obviously increased.

Specifically, under another working condition, the volute tongue position angle α may be α=42°, so that the negative pressure area at the air outlet 104 of the volute 10 is minimized, and the air flow is prevented from flowing back, so that the uniform flow velocity of the air flow is ensured, the noise generated by the air flow impact is effectively reduced, and the air flow is obviously increased.

In this embodiment, further, as shown in fig. 3, the outlet angle β is greater than 29 ° and less than 38 °. Like this, can let shell body 100 carry out the pertinence design to different service environment, control the angle that the air current flows out shell body 100, let the flow of air current more concentrate, make the velocity of flow more even to reduce effectively because the noise that the air current impacted and produced, the air current obviously increases simultaneously.

Specifically, the outlet angle β may be 29 °, the outlet angle β may be 38 °, and the outlet angle β may be any value between 29 ° and 38 °. By setting the numerical range of the outlet angle beta, the shell body 100 can adapt to different working environments, and the best effect of centralizing the air flow is achieved, so that the flow speed of the air flow is more uniform, the noise generated by the air flow impact is effectively reduced, and the air flow is obviously increased.

Specifically, as shown in fig. 3, the outlet angle β may be 29 °, 30 °, 32 °, 34 °, 36 °, 38 °, etc., which are not listed here. Those skilled in the art will appreciate that it is possible to achieve a concentration of the airflow as long as it is ensured.

Specifically, under a certain working condition, the outlet angle β may be β=32°, so as to control the angle of the airflow flowing out of the shell body 100, so that the airflow is concentrated, and the flow velocity is more uniform, thereby effectively reducing noise generated by airflow impact, and meanwhile, the airflow volume is obviously increased.

Specifically, under another working condition, the outlet angle β may be β=37°, so as to control the angle of the airflow flowing out of the housing body 100, so that the airflow is concentrated, and the flow rate is more uniform, thereby effectively reducing noise generated by airflow impact, and simultaneously the airflow volume is obviously increased.

A second embodiment of the invention proposes a volute 10, which, on the basis of the first embodiment described above, further,

as shown in fig. 3 and 4, the housing body 100 further includes a chamber 102 and an air outlet 104. The chamber 102 is used for placing a wind wheel 106, and when the wind wheel 106 operates, air flow can be sucked into the shell body 100 and sent out of the shell body 100 from an air outlet 104 connected with the chamber 102.

Specifically, in a plane perpendicular to the axis of the wind wheel 106, the ratio of the dimension D of the air outlet 104 to the outer radius r of the wind wheel 106 is greater than or equal to 1.38 and less than or equal to 1.45. The dimension D of the air outlet 104 can be designed according to different wind wheels 106, the dimension D of the air outlet 104 is matched with the wind wheels 106, so that the air outlet 104 can ensure the air flow rate and simultaneously reduce the negative pressure area to prevent the air flow from flowing back, the air flow rate is more uniform, the noise generated by the air flow impact is effectively reduced, and the air flow rate is obviously increased.

Specifically, the ratio of the dimension D of the air outlet 104 to the outer radius r of the wind wheel 106 may be 1.38, the ratio of the dimension D of the air outlet 104 to the outer radius r of the wind wheel 106 may also be 1.45, and the ratio of the dimension D of the air outlet 104 to the outer radius r of the wind wheel 106 may also be any value between 1.38 and 1.45. Through limiting the numerical range of the ratio of the dimension D of the air outlet 104 to the radius r of the outer ring of the wind wheel 106, the dimension D of the air outlet 104 can be matched with the wind wheel 106, so that the air outlet 104 can ensure the flow, reduce the negative pressure area and prevent the air flow from flowing back, the flow speed of the air flow is more uniform, the noise generated by the air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

Specifically, as shown in fig. 3 and 4, the ratio of the dimension D of the air outlet 104 to the outer radius r of the wind wheel 106 may be 1.38, 1.39, 1.40, 1.41, 1.42, 1.43, 1.44, 1.45, etc., which are not listed herein. Those skilled in the art will appreciate that this may be accomplished so long as the concentration of the air flow at the outlet 104 is ensured.

Specifically, under a certain working condition, the ratio of the dimension 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 102mm, and the dimension d=142.8mm of the air outlet 104 is calculated according to a formula. It can be understood that when the ratio of the dimension D of the air outlet 104 to the outer radius r of the wind wheel 106 is 1.4, when the outer radius r of the wind wheel 106=102 mm, the dimension d=142.8 mm of the air outlet 104 can be calculated according to a formula, that is, under the working condition, the optimal dimension of the air outlet 104 is 142.8mm.

Specifically, under a certain working condition, the ratio of the dimension 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 20mm, and the dimension d=165.6mm of the air outlet 104 is calculated according to a formula. It can be understood that when the ratio of the dimension D of the air outlet 104 to the outer radius r of the wind wheel 106 is 1.38, when the outer radius r of the wind wheel 106=120 mm, the dimension d=165.6 mm of the air outlet 104 can be calculated according to a formula, that is, under the working condition, the optimal dimension of the air outlet 104 is 165.6mm.

Specifically, the calculation formula is D/r=1.4 or 1.38, where D is the size of the air outlet 104, and r is the outer ring radius of the wind wheel 106.

Specifically, as can be seen from comparing fig. 13 and 14, in the volute 10 proposed by the present invention, 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 dimension D of the air outlet 104 to the outer ring 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 airflow rate while reducing the negative pressure area, and prevent the airflow from flowing back (particularly in the circled position of fig. 13 and 14). Thus, the volute 10 provided by the invention can make the airflow velocity more uniform, effectively reduce noise generated by airflow impact, and obviously increase the airflow.

A third embodiment of the present invention contemplates a fan assembly 12 that includes a volute 10 as in any of the embodiments described above.

Accordingly, the fan assembly 12 of the present embodiment has all of the benefits of the volute 10 described above and will not be discussed in detail herein.

As shown in fig. 5, the fan assembly 12 further includes a wind wheel 106. Specifically, the wind wheel 106 is disposed in the chamber 102 of the volute 10. Specifically, when the fan assembly 12 works, the wind wheel 106 sucks air flow into the shell body 100 and sends the air flow out of the shell body 100 from the air outlet 104 connected with the cavity 102, the volute tongue position angle α on the shell body 100 is larger than the outlet angle β, the dimension D of the air outlet 104 and the outer circle radius r of the wind wheel 106 are larger than or equal to 1.38 and smaller than or equal to 1.45 (in a plane perpendicular to the axis of the wind wheel 106), the angle of the air flow when the air flow flows out of the shell body 100 can be controlled, the air flow backflow of the air flow when the air flow flows out of the shell body 100 can be reduced, the negative pressure area is reduced, the air flow velocity is more uniform, the impact between the air flow and the smoke tube is reduced, noise generated by the air flow impact is effectively reduced, and the air flow is obviously increased.

A fourth embodiment of the present invention provides a fan assembly 12, which, based on the third embodiment described above, further,

As shown in fig. 6 and 7, the fan assembly 12 also includes an anti-vortex ring 108. Wherein the anti-vortex ring 108 is disposed at the air inlet on the volute 10. In this way, vortex ring 108 reduces or prevents leakage of the airflow, preventing backflow of the airflow in chamber 102. In this way, by the arrangement of the vortex-preventing ring 108, on one hand, noise generated by vortex can be reduced, and on the other hand, the flow rate of the air flow in the chamber 102 can be uniform, so that the flow rate of the air flow when the air flow flows out of the volute 10 is uniform, noise generated by air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

In this embodiment, further, as shown in fig. 7, the ratio of the outer ring diameter R1 of the anti-vortex ring 108 to the diameter R of the wind wheel 106 is greater than or equal to 1.05 and less than or equal to 1.15. In this way, the anti-vortex ring 108 can be designed according to the wind wheel 106, the anti-vortex ring 108 is matched with the wind wheel 106, so that the anti-vortex ring 108 can effectively block the leakage of air flow, the air flow velocity in the chamber 102 is uniform, on one hand, vortex can be prevented from appearing, on the other hand, the air flow velocity when the air flow flows out of the volute 10 is uniform, noise generated by air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

Specifically, the ratio of the outer ring diameter R1 of the anti-vortex ring 108 to the diameter R of the wind wheel 106 may be 1.05, the ratio of the outer ring diameter R1 of the anti-vortex ring 108 to the diameter R of the wind wheel 106 may be 1.15, and the ratio of the outer ring diameter R1 of the anti-vortex ring 108 to the diameter R of the wind wheel 106 may be any value between 1.05 and 1.15. By limiting the ratio of the diameter R1 of the outer ring of the vortex-preventing ring 108 to the diameter R of the wind wheel 106, the vortex-preventing ring 108 can effectively prevent the air flow from leaking, so that the air flow velocity in the chamber 102 is uniform, on one hand, vortex can be prevented from appearing, on the other hand, the air flow velocity when the air flow flows out of the volute 10 is uniform, noise generated by air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

Specifically, as shown in fig. 7, the ratio of the outer ring diameter R1 of the vortex ring 108 to the diameter R of the wind wheel 106 may 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 are not listed here. Those skilled in the art will appreciate that it is possible to ensure that the anti-vortex ring 108 covers the rotor 106.

Specifically, under a certain working condition, the ratio of the outer ring diameter R1 of the anti-vortex ring 108 to the diameter R of the wind wheel 106 is 1.12, and the diameter R of the wind wheel 106 is 209mm, so that the outer ring diameter r1=234 mm of the anti-vortex ring 108 can be calculated according to a formula. It will be appreciated that when the ratio of the outer ring diameter R1 of the anti-vortex ring 108 to the diameter R of the wind wheel 106 is 1.12, the outer ring diameter r1=234 mm of the anti-vortex ring 108 can be calculated when the diameter r=209 mm of the wind wheel 106, that is, under this condition, the optimal size of the outer ring diameter R1 of the anti-vortex ring 108 is 234mm.

Specifically, under another working condition, the ratio of the outer ring diameter R1 of the anti-vortex ring 108 to the diameter R of the wind wheel 106 is 1.06, and the diameter R of the wind wheel 106 is 150mm, so that the outer ring diameter r1=159 mm of the anti-vortex ring 108 can be calculated according to a formula. It will be appreciated that when the ratio of the outer diameter R1 of the anti-vortex ring 108 to the diameter R of the wind wheel 106 is 1.06, the diameter r=150 mm of the wind wheel 106 may be calculated to obtain the outer diameter r1=159 mm of the anti-vortex ring 108, i.e. in this condition, the optimal size of the outer diameter R1 of the anti-vortex ring 108 is 159mm.

Specifically, the calculation formula is R1/r=1.12 or 1.06, where R1 is the outer ring diameter of the anti-vortex ring 108 and R is the diameter of the wind wheel 106.

A fifth embodiment of the present invention provides a fan assembly 12, which, based on the fourth embodiment described above, further,

as shown in fig. 7, in the axial direction of the wind wheel 106, a gap is provided between the anti-vortex ring 108 and the wind wheel 106. That is, a certain distance is ensured between the anti-vortex ring 108 and the wind wheel 106 in the axial direction of the wind wheel 106. In this way, during installation and use of the fan assembly 12, the radial dimension limitation of the anti-vortex ring 108 to the wind wheel 106 can be avoided, and the situation that the outer ring of the wind wheel 106 and the anti-vortex ring 108 interfere with each other does not occur. Moreover, due to the existence of the space between the vortex-preventing ring 108 and the wind wheel 106, a user or a worker can select the wind wheel 106 with proper size according to the actual air volume demand, the assembly difficulty of the fan assembly 12 can be reduced, and the assembly efficiency of the fan assembly 12 can be improved.

Specifically, in the case of a larger diameter of the wind wheel 106, a space between the anti-vortex ring 108 and the wind wheel 106 may be provided, so that on the basis of avoiding vortex generation, structural interference between the anti-vortex ring 108 and the wind wheel 106 is ensured.

In this embodiment, further, as shown in fig. 7, when there is a gap between the anti-vortex ring 108 and the wind wheel 106, the size H of the gap is less than or equal to 2m. In this way, the vortex ring 108 can be designed differently to achieve the best working effect, block the air flow from leaking and guide the flow direction of the air flow, and make the flow velocity of the air flow uniform, thereby effectively reducing the noise generated by the air flow impact and increasing the air flow obviously.

Specifically, the dimension H of the gap may be 2mm, or the dimension H of the gap may be any dimension smaller than 2 mm. Through the dimension H of the linear gap, the anti-vortex ring 108 can achieve the optimal working effect, the air flow is blocked from leaking, the flowing direction of the air flow is guided, and the flow speed of the air flow is uniform, so that noise generated by air flow impact is effectively reduced, and meanwhile, the air flow is obviously increased.

Specifically, as shown in FIG. 7, the dimension H of the gap may be 2mm, 1.9mm, 1.8mm, 1.7mm, 1.6mm, 1.5mm, 1.4mm, 1.3mm, 1.2mm, 1.1mm, 1.0mm, etc., which are not specifically exemplified herein. Those skilled in the art will appreciate that it is possible to provide anti-vortex ring 108 with a resistance to back flow.

Specifically, under a certain working condition, the size h=2mm of the gap, so that the vortex-preventing ring 108 can exert the best working effect under the working condition, and the best effect of guiding the airflow flowing direction is achieved, so that vortex is avoided, the airflow velocity is uniform, noise generated by airflow impact is effectively reduced, and meanwhile, the airflow quantity is obviously increased.

Specifically, under another working condition, the size h=1mm of the gap, so that the vortex-preventing ring 108 can exert the best working effect under the working condition, and the best effect of guiding the airflow flowing direction is achieved, so that vortex is avoided, the airflow velocity is uniform, noise generated by airflow impact is effectively reduced, and meanwhile, the airflow quantity is obviously increased.

A sixth embodiment of the present invention provides a fan assembly 12, which, based on the fourth embodiment described above, further,

in the axial direction of the wind wheel 106, the vortex ring 108 is partially overlapped with the wind wheel 106. That is, in the axial direction of the wind wheel 106, a section of the wind wheel 106 is made to protrude into the inside of the vortex ring 108. In this way, in the axial direction of the wind wheel 106, the coverage of the vortex-preventing ring 108 to the wind wheel 106 is ensured, the blocking effect of the vortex-preventing ring 108 to the airflow is further improved, and the generation of vortex is further avoided to a great extent.

Specifically, in the case where the diameter of the wind wheel 106 is smaller, a partial overlap between the vortex ring 108 and the wind wheel 106 may be provided, so as to improve the blocking effect of the vortex ring 108 on the airflow.

In this embodiment, further, as shown in fig. 7, when the anti-vortex ring 108 is partially overlapped with the wind wheel 106, the size D1 of the overlapped portion is less than or equal to 4mm. Like this, can let prevent vortex ring 108 design according to wind wheel 106, make prevent vortex ring 108 match wind wheel 106, can let prevent vortex ring 108 stop the air current and leak to the direction of flow of air current, let the air current flow to a direction all the time, prevent that the air current from taking place to flow backward, thereby prevent that the air current from producing the vortex, make the air current velocity of flow even, thereby the velocity of flow when making the air current flow out spiral case 10 is even, reduce effectively because the noise that the air current strikeed and produces, the air current is obviously increased simultaneously.

Specifically, the size D1 of the overlapping portion may be 4mm, and the size D1 of the overlapping portion may be any value smaller than 4mm. By limiting the numerical range of the dimension D1 of the overlapping portion, the working effect of the vortex ring 108 can be ensured, the leakage of the air flow is blocked, the flow direction of the air flow is guided, and the flow velocity of the air flow is uniform, so that the noise generated by the impact of the air flow is effectively reduced, and the air flow is obviously increased.

Specifically, as shown in fig. 7, the dimension D1 of the overlapping portion may be 4mm, 3.8mm, 3.6mm, 3.4mm, 3.2mm, 3.0mm, 2.8mm, 2.6mm, 2.4mm, 2.2mm, 2.0mm, etc., which are not exemplified herein. Those skilled in the art will appreciate that it is possible to provide anti-vortex ring 108 that blocks the flow of air and directs the flow direction of the air.

Specifically, under a certain working condition, the size d1=3.8mm of the overlapped part, so that the vortex ring 108 can exert the best working effect under the working condition, the leakage of the air flow is blocked, the flowing direction of the air flow is guided, the flow speed of the air flow is uniform, the noise generated by the impact of the air flow is effectively reduced, and meanwhile, the air flow is obviously increased.

Specifically, in another working condition, the size d1=2.0 mm of the overlapping portion, so that the anti-vortex ring 108 can exert the best working effect under the working condition, block the air flow from leaking and guide the flowing direction of the air flow, and make the flow velocity of the air flow uniform, thereby effectively reducing noise generated by the impact of the air flow, and meanwhile, the air flow is obviously increased.

In particular, as can be seen by comparing fig. 15 and 16, the present invention has the anti-vortex ring 108 disposed at the air inlet of the volute 10, which can significantly make the air flow velocity uniform (particularly, the circled position in fig. 15 and 16) compared with the case that no anti-vortex ring is disposed in fig. 15, thereby effectively reducing the noise generated by the air flow impact and significantly increasing the air flow.

A seventh embodiment of the present invention provides a fan assembly 12, which, on the basis of the above-described third to sixth embodiments, further,

as shown in fig. 8 and 9, the fan assembly 12 further includes a current collector 110 and a rectifier 112. The current collector 110 is disposed at an air inlet on the volute 10, the rectifier 112 is disposed on the current collector 110, and the air flow passes through the rectifier 112, is split by the air inlet on the rectifier 112, and then enters the volute 10 through the current collector 110. In this way, the air flows can be split by the air inlet holes and then combined, so that the flow speed of the air flows is uniform, the flow speed of the air flows out of the volute 10 is more uniform, noise generated by air flow impact is effectively reduced, and the air flow is obviously increased.

An eighth embodiment of the present invention provides a fan assembly 12, which, on the basis of the third to seventh embodiments described above, further,

as shown in fig. 10, rectifier 112 includes a mounting edge 114 and a shroud 116. Wherein, the mounting edge 114 is connected with the current collector 110, the cover 116 is arranged on the opening 120 of the current collector 110 through the connecting edge, and a plurality of air inlet holes 118 are arranged on the cover 116. Through set up the fresh air inlet 118 on the cover body 116, can let the air current by fresh air inlet 118 reposition of redundant personnel become the stranded air current, then merge again to make the velocity of flow of air current even, and then make the air current velocity of flow of the spiral case 10 more even, effectively reduce the noise that produces because the air current strikes, the air current obviously increases simultaneously.

Specifically, screw holes are provided on the mounting edge 114, and the mounting edge 114 can be fastened to the current collector 110 using a snap fit, thereby fastening the current collector 112 to the current collector 110.

In this embodiment, further, as shown in fig. 9 and 11, the ratio of the outer ring 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 ring diameter R2 of the rectifier 112 can be designed specifically according to the diameter R3 of the opening 120, so that the outer ring diameter R2 of the rectifier 112 is always larger than the diameter of the opening 120 to match, and therefore the outer ring of the rectifier 112 will not block the air flow from entering the cover 116, and the reliability of the operation of the rectifier 112 is ensured.

Specifically, the ratio of the outer ring diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 may be 1.04, the ratio of the outer ring diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 may be 1.12, and the ratio of the outer ring diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 may be any value between 1.04 and 1.12. By defining the ratio of the diameter R2 of the outer ring of the rectifier 112 to the diameter R3 of the opening 120, it is ensured that the mounting edge 114 can always be larger than the opening 120, thereby ensuring the operational reliability of the rectifier 112.

Specifically, as shown in fig. 9 and 11, the ratio of the outer ring diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 may be 1.04, 1.05, 1.06, 1.07, 1.08, 1.09, 1.10, 1.11, 1.12, etc., which are not listed here. Those skilled in the art will appreciate that this may be accomplished so long as it is ensured that the outer ring of the rectifier 112 is larger than the opening 120.

Preferably, under a certain working condition, the ratio of the diameter R2 of the outer ring 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, so that the diameter r2=186 mm of the outer ring of the rectifier 112 can be calculated according to a formula. It will be appreciated that when the ratio of the outer ring diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 is 1.07, when the diameter r3=168 mm of the opening 120, the outer ring diameter r2=186 mm of the rectifier 112 is calculated according to the formula, i.e. the optimum size of the outer ring diameter R2 of the rectifier 112 is 186mm under this condition.

Preferably, under another working condition, the ratio of the diameter R2 of the outer ring 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, and then the diameter r2=224 mm of the outer ring of the rectifier 112 can be calculated according to a formula. It will be appreciated that when the ratio of the outer ring diameter R2 of the rectifier 112 to the diameter R3 of the opening 120 is 1.12, when the diameter r3=200 mm of the opening 120, the outer ring diameter r2=224 mm of the rectifier 112 is calculated according to the formula, i.e. the optimum size of the outer ring diameter R2 of the rectifier 112 is 224mm under this condition.

Specifically, the calculation formula is r2/r3=1.07 or 1.12, where R2 is the outer ring diameter of the rectifier 112 and R3 is the diameter of the opening 120.

In this embodiment, further, as shown in fig. 9 and 11, 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. In this way, the cover 116 can be designed differently according to the diameter of the opening 120, so that the cover 116 is matched with the opening 120, and the air flow split by the air inlet 118 can enter the volute 10 through the opening 120, thereby ensuring the working reliability of the rectifier 112.

Specifically, the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120 may be 0.965, the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120 may be 1.01, and the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120 may be any value between 0.965 and 1.01. By defining the ratio of the diameter R4 of the shroud 116 to the diameter R3 of the opening 120, the air flow split through the inlet aperture 118 is allowed to enter the volute 10 through the opening 120, thereby ensuring operational reliability of the rectifier 112.

Specifically, as shown in fig. 9 and 11, the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120 may 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 further listed herein. Those skilled in the art will appreciate that this may be accomplished so long as the split airflow from the enclosure 116 is ensured to enter the opening 120.

Preferably, under a certain working condition, the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120 is 0.976, and the diameter R3 of the opening 120 is 168mm, so that the diameter r4=164 mm of the cover 116 can be calculated according to a formula. It will be appreciated that when the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120 is 0.976, the diameter of the opening 120=168 mm, the cover 116 diameter=164 mm can be calculated, i.e. the optimum size of the cover 116 diameter is 164mm under this condition.

Preferably, under another working condition, the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120 is 0.994, and the diameter R3 of the opening 120 is 200mm, so that the diameter r4= 198.8mm of the cover 116 can be calculated according to a formula. It will be appreciated that when the ratio of the diameter R4 of the cover 116 to the diameter R3 of the opening 120 is 0.994, the diameter of the opening 120=200 mm, the cover 116 diameter= 198.8mm can be calculated, i.e. the optimum size of the cover 116 diameter is 198.8mm under this condition.

Specifically, the calculation formula is R4/r3=0.976 or 0.994, where R4 is the diameter of the cover 116 and R3 is the diameter of the opening 120.

A ninth embodiment of the present invention provides a fan assembly 12, which, on the basis of the above-described third to eighth embodiments, further,

As shown in fig. 12, the air intake 118 is a regular polygon. Specifically, the regular polygon hole can save space, improve the utilization ratio of the space of the cover 116, ensure that the air inlet hole 118 can be concentrated at the central part of the cover 116, thereby ensuring the air flow splitting effect of the air inlet hole 118 on the air flow, ensuring that the air flow speed is uniform, further ensuring that the air flow speed of the air flow flowing out of the volute 10 is more uniform, effectively reducing noise generated by air flow impact, and obviously increasing the air flow.

In this embodiment, further, as shown in fig. 9 and 12, the ratio of the shape 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 polygon holes can be designed differently according to the openings 120, so that the air inlet 118 can be guaranteed to split the airflow, the flow speed of the split airflow is uniform, the flow speed of the airflow flowing out of the volute 10 is more uniform, noise generated by airflow impact is effectively reduced, and meanwhile, the airflow quantity is obviously increased.

Specifically, the ratio of the shape length W of the regular polygon hole to the diameter R3 of the opening 120 may be 0.018, the ratio of the shape length W of the regular polygon hole to the diameter R3 of the opening 120 may also be 0.031, and the ratio of the shape length W of the regular polygon hole to the diameter R3 of the opening 120 may also be any one value between 0.018 and 0.031. In this way, the ratio of the length W of the regular polygon hole to the diameter R3 of the opening 120 is limited to ensure the working effect of the air inlet 118, so that the flow rate of the air flowing through the air inlet is uniform, and the flow rate of the air flowing out of the volute 10 is more uniform, thereby effectively reducing noise generated by air impact, and meanwhile, the air flow is obviously increased.

Specifically, as shown in fig. 9 and 12, the ratio of the shape length W of the regular polygonal hole to the diameter R3 of the opening 120 may be 0.018, 0.020, 0.022, 0.024, 0.026, 0.028, 0.030, 0.031, etc., which are not listed here. Those skilled in the art will appreciate that this may be accomplished so long as the air intake effect of the air intake openings 118 is ensured.

Specifically, under a certain working condition, the ratio of the shape length W of the regular polygon hole to the diameter R3 of the opening 120 is 0.023, and the diameter R3 of the opening 120 is 168mm, and the shape length w=4.05 mm of the regular polygon hole is calculated according to a formula. It will be appreciated that when the ratio of the shape length W of the regular polygon hole to the diameter R3 of the opening 120 is 0.023, the shape length W of the regular polygon hole can be calculated to be 4.05mm when the diameter r3=168 mm of the opening 120, i.e. the optimum size of the shape length W of the regular polygon hole is 4.05mm under this condition.

Specifically, under another working condition, the ratio of the shape 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 200mm, and the shape length w=6mm of the regular polygon hole is calculated according to a formula. It will be appreciated that when the ratio of the shape length W of the regular polygonal hole to the diameter R3 of the opening 120 is 0.030, the shape length W of the regular polygonal hole may be calculated to be 6mm when the diameter r3=200 mm of the opening 120, i.e. the optimum size of the shape length W of the regular polygonal hole is 6mm under this condition.

Specifically, the calculation formula is W/r3=0.023 or 0.030, where W is the shape length of the W regular polygonal hole, and R3 is the diameter of the opening 120.

In this embodiment, further, as shown in fig. 10, the ratio of the sum of the areas 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, the number of the air inlets 118 can be designed according to the area S1 of the rectifier 112, so as to ensure the airflow effect of the air inlets 118 on the airflow, and the flow velocity of the airflow flowing through the volute 10 is uniform, so that the flow velocity of the airflow flowing out of the volute 10 is more uniform, the noise generated by airflow impact is effectively reduced, and the airflow is obviously increased.

Specifically, the ratio of the sum of the areas S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 may be 0.58, the ratio of the sum of the areas S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 may be 0.68, and the ratio of the sum of the areas S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 may be any value between 0.58 and 0.68. In this way, by limiting the ratio range of the sum of the areas S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112, the flow dividing effect of the air inlet holes 118 is ensured, the flow velocity of the air flow is more uniform, the noise generated by the air flow impact is effectively reduced, and the air flow is obviously increased.

Specifically, as shown in fig. 10, the ratio of the sum of the areas S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 may 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 are not listed herein. Those skilled in the art will appreciate that this may be accomplished so long as the diverting effect of the inlet vents 118 is ensured.

Specifically, under a certain working condition, the ratio of the sum of the areas S of the air inlet holes 118 to the area S1 of the rectifier 112 is 0.58, and the area S1 of the rectifier 112 is 100mm ² The sum of the areas of the plurality of air inlet holes 118 s=58 mm is calculated according to the formula ² ,. It will be appreciated that when the ratio of the sum of the areas S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 is 0.58, the area s1=100 mm of the rectifier 112 ² At this time, the sum of the areas of the plurality of air inlet holes 118 s=58 mm can be calculated ² That is, under this condition, the optimum area of the plurality of air inlet holes 118 is 58mm in total ² 。

Specifically, under another working condition, the ratio of the sum of the areas S of the air inlet holes 118 to the area S1 of the rectifier 112 is 0.68, and the area S1 of the rectifier 112 is 150mm ² The sum of the areas of the plurality of air inlet holes 118 s=102 mm is calculated according to the formula ² ,. It will be appreciated that when the ratio of the sum of the areas S of the plurality of air inlet holes 118 to the area S1 of the rectifier 112 is 0.58, the area s1=150mm of the rectifier 112 ² At this time, the sum of the areas s=102 mm of the plurality of air inlet holes 118 can be calculated ² That is, under this condition, the optimum area of the plurality of air inlet holes 118 is 102mm in total ² 。

Specifically, the calculation formula is s1=0.58 or 0.68, where S is the sum of the areas of the plurality of air intake holes 118 and S1 is the area of the rectifier 112.

A tenth embodiment of the present invention provides a range hood (not shown) including a fan assembly 12 as in any of the embodiments described above.

Therefore, the range hood provided by the invention comprises all the beneficial effects of the fan assembly 12, and the description is omitted herein.

In addition, the range hood also comprises an air duct structure. Wherein, fan assembly 12 sets up in the wind channel structure, and in the time of fan assembly 12 operation will the oil smoke inhale the wind channel structure.

Specifically, during the operation of the range hood, the wind wheel 106 in the fan assembly 12 operates, so that the oil smoke flows into the volute 10 through the current collector 110 and the rectifier 112, and the air inlet 118 in the rectifier 112 can split the oil smoke, so that the flow rate of the oil smoke enters the volute 10 more uniformly. When the oil smoke is in the volute 10, the vortex-preventing ring 108 can prevent the oil smoke from leaking, guide the flowing direction of the oil smoke, prevent the oil smoke from flowing back and generate vortex, thereby ensuring the uniform flow velocity of the oil smoke in the volute 10. When the oil smoke flows out of the volute 10 and enters the air duct structure, the negative pressure area at the air outlet 104 can be reduced by limiting the volute tongue position angle alpha to be larger than the outlet angle beta, so that the oil smoke cannot flow back when flowing out of the air outlet 104, the negative pressure area is reduced, the flow speed of the oil smoke is more uniform, the impact between the oil smoke and the air duct structure is reduced, the noise generated by the impact of the oil smoke is effectively reduced, and meanwhile, the air flow is obviously increased.

An eleventh embodiment of the present invention contemplates a range hood integrated machine (not shown) including a fan assembly 12 as in any of the embodiments described above.

Therefore, the smoke kitchen all-in-one machine provided by the invention comprises all the beneficial effects of the fan assembly 12, and is not repeated herein.

In addition, the smoke kitchen all-in-one still includes kitchen body and air duct structure. Wherein, the kitchen body generates high temperature for the culinary art. The opening 120 of the air duct structure is oriented toward the oven body, the fan assembly 12 is disposed within the air duct mechanism, and the fan assembly 12 draws cooking fumes from the inlet into the air duct structure.

Specifically, in the working process of the smoke kitchen all-in-one machine, the kitchen body generates high temperature to provide a heat source for cooking, and oil smoke can be continuously generated in the cooking process. The opening 120 of the air duct structure faces the kitchen body, the wind wheel 106 in the fan assembly 12 works, so that the oil smoke flows into the volute 10 through the current collector 110 and the rectifier 112, and the air inlet 118 in the rectifier 112 can split the oil smoke, so that the flow velocity of the oil smoke enters the volute 10 more uniformly. When the oil smoke is in the volute 10, the vortex-preventing ring 108 can prevent the oil smoke from leaking, guide the flowing direction of the oil smoke, prevent the oil smoke from flowing back and generate vortex, thereby ensuring the uniform flow velocity of the oil smoke in the volute 10. When the oil smoke flows out of the volute 10 and enters the air duct structure, the negative pressure area at the air outlet 104 can be reduced by limiting the volute tongue position angle alpha to be larger than the outlet angle beta, so that the oil smoke cannot flow back when flowing out of the air outlet 104, the negative pressure area is reduced, the flow speed of the oil smoke is more uniform, the impact between the oil smoke and the air duct structure is reduced, the noise generated by the impact of the oil smoke is effectively reduced, and meanwhile, the air flow is obviously increased.

In summary, the scroll casing 10 according to the present invention includes a casing body 100. Specifically, the casing body 100 includes a volute tongue position angle α and an outlet angle β, the angle of the volute tongue position angle α being greater than the outlet angle β. Like this, the angle when can controlling the air current and flow out shell body 100 can also reduce the air current backward flow when air current flows out shell body 100, reduces the negative pressure district, lets the air current velocity of flow more even to reduce the impact between air current and the tobacco pipe, reduce effectively because the noise that the air current impacted and produced, the air current obviously increases simultaneously.

Further, the housing body 100 further includes a chamber 102 and an air outlet 104. The chamber 102 is used for placing a wind wheel 106, and when the wind wheel 106 operates, air flow can be sucked into the shell body 100 and sent out of the shell body 100 from an air outlet 104 connected with the chamber 102. Specifically, in a plane perpendicular to the axis of the wind wheel 106, the ratio of the dimension D of the air outlet 104 to the outer radius r of the wind wheel 106 is greater than or equal to 1.38 and less than or equal to 1.45. The dimension D of the air outlet 104 can be designed according to different wind wheels 106, the dimension D of the air outlet 104 is matched with the wind wheels 106, so that the air outlet 104 can ensure the air flow rate and simultaneously reduce the negative pressure area to prevent the air flow from flowing back, the air flow rate is more uniform, the noise generated by the air flow impact is effectively reduced, and the air flow rate is obviously increased.

In the description of the present invention, the term "plurality" means two or more, unless explicitly defined otherwise, the orientation or positional relationship indicated by the terms "upper", "lower", etc. are based on the orientation or positional relationship shown in the drawings, merely for convenience of description of the present invention and to simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as limiting the present invention; the terms "coupled," "mounted," "secured," and the like are to be construed broadly, and may be fixedly coupled, detachably coupled, or integrally connected, for example; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.

In the description of the present specification, the terms "one embodiment," "some embodiments," "particular embodiments," and the like, mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above is only a preferred embodiment of the present invention, and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A volute, comprising:

the shell body comprises a volute tongue position angle and an outlet angle, and the volute tongue position angle is larger than the outlet angle.

2. The volute of claim 1 wherein the flow path is defined by a flow path,

the volute tongue position angle is greater than 41 degrees and less than 58 degrees.

3. The volute of claim 1 wherein the flow path is defined by a flow path,

the outlet angle is greater than 29 ° and less than 38 °.

4. A volute according to any one of claims 1 to 3, characterized in that,

the shell body further comprises a cavity and an air outlet communicated with the cavity, wherein the cavity is used for placing the wind wheel, and the ratio of the size of the air outlet to the radius of the outer ring of the wind wheel is larger than or equal to 1.38 and smaller than or equal to 1.45 in a plane perpendicular to the axis of the wind wheel.

5. A fan assembly, comprising:

A volute according to any one of claims 1 to 4;

the wind wheel is arranged in the volute.

6. The fan assembly of claim 5, further comprising:

the vortex-preventing ring is arranged on the volute and is positioned at the air inlet of the volute.

7. The fan assembly of claim 6 wherein the fan assembly comprises,

the ratio of the diameter of the outer ring of the vortex-preventing ring to the diameter of the wind wheel is more than or equal to 1.05 and less than or equal to 1.15.

8. The fan assembly of claim 6 wherein the fan assembly comprises,

and a gap or partial overlap is arranged between the vortex-preventing ring and the wind wheel along the axial direction of the wind wheel.

9. The fan assembly of claim 8 wherein the fan assembly comprises,

and under the condition that a gap is formed between the vortex-preventing ring and the wind wheel, the size of the gap is smaller than or equal to 2mm.

10. The fan assembly of claim 8 wherein the fan assembly comprises,

and under the condition that the vortex-preventing ring is partially overlapped with the wind wheel, the size of the overlapped part is smaller than or equal to 4mm.

11. The fan assembly of any of claims 5 to 10 further comprising:

the current collector is arranged on the volute and positioned at an air inlet of the volute, and the current collector comprises an opening;

And the rectifier is covered on the opening and connected with the current collector, and comprises a plurality of air inlet holes.

12. The fan assembly of claim 11 wherein the rectifier comprises;

the mounting edge is connected with the current collector;

the cover body is arranged on the mounting edge, and the air inlet holes are formed in the cover body.

13. The fan assembly of claim 11 wherein the fan assembly comprises,

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.

14. The fan assembly of claim 12 wherein the fan assembly comprises,

the ratio of the diameter of the cap to the diameter of the opening is greater than or equal to 0.965 and less than or equal to 1.01.

15. The fan assembly of claim 11 wherein the fan assembly comprises,

the air inlet hole is a regular polygon hole.

16. The fan assembly of claim 15 wherein the fan assembly comprises,

the ratio of the shape 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.

17. The fan assembly of claim 11 wherein the fan assembly comprises,

the ratio of the sum of the areas of the air inlets to the area of the rectifier is greater than or equal to 0.58 and less than or equal to 0.68.

18. A range hood, comprising:

an air duct structure;

the blower assembly of any one of claims 5-17 disposed within the duct structure.

19. The utility model provides a cigarette kitchen all-in-one which characterized in that includes:

a stove body;

the inlet of the air duct structure is arranged towards the stove body;