A current collector and a range hood

Abstract

The application discloses a current collector and a range hood. The current collector is installed at an air inlet of a fan of the range hood, and comprises a current collector body, a plurality of pre-swirl guide vanes arranged at an inner side of the current collector body, first ends of the pre-swirl guide vanes being connected with the current collector body, and adjacent two pre-swirl guide vanes being spaced apart, and an air uniformizing net arranged at an inner side of the pre-swirl guide vanes and connected with second ends of the pre-swirl guide vanes. A relationship D b -D a1 ≥ 2W is met between an impeller of the fan and the current collector; wherein D b is an inner diameter of the impeller of the fan, D a1 is an inner diameter of the pre-swirl guide vanes, and W is a minimum radial gap requirement between the current collector and the impeller.

Description

Technical Field

[0001] This invention relates to the field of kitchen appliance technology, and in particular to a collector and a range hood. Background Technology

[0002] Please refer to Figure 1 and Figure 2 The fan of a range hood includes a fan housing 1', a collector 2', and a fan assembly. The fan assembly includes an impeller 3' and a motor that drives the impeller to rotate. When the range hood is operating, a safe clearance must be maintained between the collector 2' and the impeller 3'. Generally, the axial or radial clearance between the collector 2' and the impeller 3' is specified to be greater than or equal to 8mm to meet the requirements of transportation and drop tests.

[0003] Range hoods typically need to overcome significant duct resistance during operation. Therefore, the collector 2' is usually extended into the impeller 3' to prioritize radial clearance, thereby improving the fan's anti-surge capability and reducing leakage losses. This design leads to the following two problems:

[0004] Question 1: The radial dimension D of the collector 2' extending into the impeller 3' a0 It must be smaller than the impeller's inner diameter D. b0 Furthermore, in the actual process, when the clearance of moving parts needs to be ensured and the material thickness needs to be considered, the effective air intake area of ​​collector 2' is further reduced.

[0005] Question 2: Because the portion of impeller 3' near the air inlet is blocked by collector 2', this part of the impeller 3' blades does not perform work on the airflow and is actually an ineffective area (e.g., Figure 2 As shown, arrow A indicates the ineffective work area of ​​impeller 3'.

[0006] The two traditional approaches to addressing the above problems are as follows:

[0007] Traditional Solution 1: Maintain a structural clearance between the impeller 3' and the collector 2' in the axial direction, ensuring that the collector 2' does not penetrate deep into the impeller 3', thereby reducing the radial dimension D of the collector 2'. a0 The inner diameter D of the impeller is greater than or equal to 3'. b0 Increase the effective air intake area of ​​the collector 2'.

[0008] The drawback of this design is that there is an axial clearance between the impeller 3' and the collector 2', which leads to increased leakage losses and decreased fan performance. a0 ≥D b0 The reduced coverage area of ​​the collector on the 3' air inlet side of the impeller makes the fan outlet prone to surge under high back pressure.

[0009] Traditional Solution Two: Maintain the structural clearance between the impeller 3' and the collector 2' in the radial direction, with the collector 2' extending deep into the impeller 3' (e.g., Figure 2 As shown, the depth of the collector 2' inside the impeller 3' is H), and D a0 ≥D b0 At this point, the impeller 3' and the collector 2' will interfere or have insufficient structural clearance. Therefore, the inner side of the blades at the air inlet of the impeller 3' is chamfered at a large angle or cut off to make room for the collector 2' and meet the minimum radial clearance requirements.

[0010] The drawback of this solution is that after the inner side of the blades at the 3' air inlet of the impeller is chamfered or cut off at a large angle, the working capacity of the blades at this point is weakened or even lost, and the problem of reduced effective blade width still exists.

[0011] Furthermore, during range hood operation, the impeller 3' rotates, creating negative pressure inside the centrifugal fan. The airflow then flows through the collector 2' into the volute. Due to the asymmetry of the volute's profile design, the shape of the range hood's smoke collection structure, space constraints within the casing, and obstructions from other components, the internal airflow layout of the range hood is relatively complex. This results in the negative pressure distribution around the collector 2' not being symmetrical along the center of rotation. Consequently, the airflow when smoke enters the impeller is turbulent and uneven in speed, which to some extent affects the fan's performance and generates significant aerodynamic noise.

[0012] To improve the air intake conditions, resistance or guide components, such as annular iron grids or honeycomb iron grids, are usually applied to the collector 2' to make the air intake pressure of the collector 2' more uniform, or to improve the airflow direction so that the air intake airflow direction is consistent with the rotation direction of the impeller 3', in order to improve aerodynamic noise. However, the flow state of the part of the impeller 3' air inlet covered by the collector 2' cannot be improved.

[0013] Therefore, a current collector is urgently needed to solve the above problems. Summary of the Invention

[0014] The present invention aims to at least partially solve one of the problems existing in the prior art. To this end, the present invention proposes a collector that, by setting pre-rotating guide vanes, pre-rotates the ball near the impeller of the fan, improves the smoothness of air intake, makes the airflow intake speed more uniform, reduces aerodynamic noise, and ensures the performance of the fan.

[0015] The above objectives are achieved through the following technical solutions:

[0016] A collector is installed at the air inlet of a range hood fan, the collector comprising:

[0017] Current collection body;

[0018] A plurality of pre-rotation guide vanes are arranged on the inner side of the flow collector body, and the first end of the pre-rotation guide vanes is connected to the flow collector body, and the adjacent two pre-rotation guide vanes are arranged at intervals;

[0019] A uniform gas net is arranged on the inner side of the pre-rotation guide vanes and connected to the second end of the pre-rotation guide vanes;

[0020] The impeller of the fan and the flow collector satisfy the relationship: D b -D a1 ≥2W;

[0021] Wherein, D b is the inner diameter of the impeller of the fan, D a1 is the inner diameter of the pre-rotation guide vanes, and W is the minimum radial gap requirement between the flow collector and the impeller.

[0022] Optionally, the air inlet diameter D a of the flow collector body is D b , the flow collector body is located on the outer side of the end surface of the impeller, and the flow collector body has a gap t with the side surface of the impeller, and the impeller of the fan and the flow collector also satisfy the relationship: t≥t min , D a1min -D b ≥2t min ;

[0023] Wherein, t min is the minimum axial gap between the flow collector body and the impeller, and D is the diameter at the minimum distance between the pre-rotation guide vanes and the impeller.

[0024] Optionally, the distance between the pre-rotation guide vanes and the end surface of the impeller is L, and L≤0.

[0025] Optionally, the adjacent two pre-rotation guide vanes are arranged at the same distance, the number of the pre-rotation guide vanes is M, the thickness of the pre-rotation guide vanes is A, the number of the blades of the impeller of the fan is N, and the thickness of the blades is B, and 0.5N≤M≤1.5N, 0.3B≤A≤10B.

[0026] Optionally, the pre-rotation guide vanes are twisted along the axial direction to form a first twisted top end and a second twisted top end, the convex directions of the first twisted top end and the second twisted top end are the same as the rotation direction of the impeller, the first twisted top end is an air inlet, the second twisted top end is an air outlet, and the angle between the tangent line of the first twisted top end and the tangent line of the circular air inlet diameter D a of the flow collector body is F2, and the angle between the tangent line of the second twisted top end and the inner diameter D a1The angle between the tangent lines of the circle is F1, F1, F2∈[0°-90°], F1∈[0-α+25°], F1≤F2;

[0027] Wherein, α is the angle of the air inlet of the blade.

[0028] Optionally, in the axial direction, the first twisted top end of the pre-swirl guide vane is in a straight line with the air inlet of the blade.

[0029] Optionally, the circumferential projection of the pre-swirl guide vane is a smooth curve composed of one or more of a circular arc, a Bezier curve and a multi-segment curve.

[0030] Optionally, the pre-swirl guide vane is twisted in the axial direction, and the twist angle is θ, θ∈[0°-90°].

[0031] Optionally, the air distribution net is convexly arranged in the direction opposite to the direction of the airflow, the distance between the highest point of the air distribution net in the axial direction and the air collection body is G2, the distance between the highest point of the air collection body in the axial direction and the side of the air collection body away from the impeller of the fan is G1, 0.5D a2 ≥G2≥G1;

[0032] Wherein, D a2 is the diameter of the air distribution net.

[0033] Optionally, the air distribution net is a honeycomb net, and the cross section of the air distribution net is composed of one or more of a parabola, a circular arc and a Bezier curve.

[0034] Optionally, 0.5D b ≤D a2 ≤0.9D b ;

[0035] Wherein, D b is the inner diameter of the impeller of the fan.

[0036] Another aspect of the present application provides a fan, which comprises a fan cabinet, a fan wheel assembly arranged in the fan cabinet and the above-mentioned air collector, the air collector being mounted on the fan cabinet, and the fan wheel assembly comprising a motor and an impeller in transmission connection with the motor.

[0037] Still another aspect of the present application provides an extractor hood, which comprises the above-mentioned fan.

[0038] Compared with the prior art, the present application has at least the following beneficial effects:

[0039] The current application provides a flow collector which is installed at the air inlet of the fan of the range hood, and the flow collector comprises a flow collector body, a uniform air net and a plurality of pre-swirl guide vanes. The plurality of pre-swirl guide vanes are arranged at the inner side of the flow collector body, the first end of the pre-swirl guide vane is connected with the flow collector body, and the adjacent two pre-swirl guide vanes are arranged at intervals. The uniform air net is arranged at the inner side of the pre-swirl guide vane and connected with the second end of the pre-swirl guide vane. b -D a1 ≥2W。 Wherein, D b is the inner diameter of the impeller of the fan, D a1 is the inner diameter of the pre-swirl guide vane, and W is the minimum gap requirement between the flow collector and the fan in the axial direction or the radial direction, so that the minimum radial gap requirement between the flow collector and the fan is met, and at the same time, by arranging the pre-swirl guide vane, the ball close to the impeller of the fan is pre-swirled, the flow smoothness of the inlet air is improved, the inlet air velocity of the airflow is more uniform, the aerodynamic noise is reduced, and the performance of the fan is ensured. BRIEF DESCRIPTION OF DRAWINGS

[0040] Figure 1 is a partial cross-sectional structure schematic diagram of the fan in the prior art;

[0041] Figure 2 is a cross-sectional structure schematic diagram of the fan in the prior art;

[0042] Figure 3 is a three-dimensional structure schematic diagram of the fan provided by the specific embodiment of the current application;

[0043] Figure 4 is an exploded view of Figure 3 ;

[0044] Figure 5 is a cross-sectional structure schematic diagram of the fan provided by the specific embodiment of the current application;

[0045] Figure 6 is a front view of the flow collector provided by the specific embodiment of the current application;

[0046] Figure 7 is one of the cross-sectional views of the flow collector provided by the specific embodiment of the current application;

[0047] Figure 8 is a schematic diagram of the cooperation between the flow collector and the blades of the fan wheel provided by the specific embodiment of the current application;

[0048] Figure 9 is the second cross-sectional view of the flow collector provided by the specific embodiment of the current application.

[0049] In the drawings:

[0050] 1, the fan cabinet;

[0051] 2, the flow collector; 21, the flow collector body; 22, the pre-swirl guide vane; 23, the uniform air net;

[0052] 3. Impeller; 31. Blade;

[0053] 4. Motor. Detailed Implementation

[0054] The following embodiments illustrate the present invention, but the present invention is not limited to these embodiments. Modifications to the specific embodiments of the present invention or equivalent substitutions for some technical features, without departing from the spirit of the present invention, should all be covered within the scope of the technical solutions claimed in the present invention.

[0055] Please refer to Figures 1-9 This invention provides a collector installed at the air inlet of a range hood fan. The collector 2 includes a collecting body 21, an air distribution mesh 23, and multiple pre-rotating guide vanes 22. The multiple pre-rotating guide vanes 22 are disposed inside the collecting body 21, with their first ends connected to the collecting body 21, and adjacent pre-rotating guide vanes 22 spaced apart. The air distribution mesh 23 is disposed inside the pre-rotating guide vanes 22 and connected to their second ends. The impeller of the fan and the collector satisfy the following relationship: D b -D a1 ≥2W. Where, D b D is the inner diameter of impeller 3 of the fan. a1 W is the inner diameter of the pre-rotating guide vane 22, and W is the minimum radial clearance requirement between the collector 2 and the impeller 3 of the fan. This ensures that the collector 2 and the fan meet the minimum radial clearance requirement. At the same time, by setting the pre-rotating guide vane 22, the ball near the impeller 3 of the fan is pre-rotated, which improves the smoothness of the air intake, makes the airflow intake speed more uniform, reduces aerodynamic noise, and ensures the performance of the fan.

[0056] Optionally, the air inlet diameter D of the collector body 21 a ≥D b The collector body 21 is located on the outer side of the end face of the impeller 3, and there is a gap t between the collector body 21 and the side of the impeller 3. The impeller and the collector of the fan also satisfy the relationship: t ≥ t min D a1min -D b ≥2t min Among them, t min The minimum axial clearance between the collector body 21 and the impeller 3 is the diameter at the point where the distance between the pre-rotating guide vane 22 and the impeller 3 is the smallest. This setting can effectively reduce the airflow leakage loss of the fan without reducing the effective working width of the impeller 3.

[0057] Optionally, the distance between the pre-swirl guide vane 22 and the end face of the impeller 3 is L, L≤0. L=0 means that the pre-swirl guide vane 22 is flush with the air inlet of the fan, and L<0 means that the second end of the pre-swirl guide vane 22 extends into the air inlet of the fan, so as to further reduce the leakage loss of the air flow.

[0058] Optionally, the adjacent two pre-swirl guide vanes 22 are arranged at the same distance, the number of the pre-swirl guide vanes 22 is M, the thickness of the pre-swirl guide vane 22 is A, the number of the blades 31 of the impeller 3 of the fan is N, and the thickness of the blade 31 is B, and 0.5N≤M≤1.5N and 0.3B≤A≤10B, so as to simultaneously consider the pre-swirl guide effect on the air flow and the effective passing property of the air flow.

[0059] Further, when A takes a large value, N takes a small value.

[0060] Optionally, the pre-swirl guide vane 22 is twisted along the axial direction to form a first twisted top end and a second twisted top end, the convex directions of the first twisted top end and the second twisted top end are the same as the rotation direction of the impeller 3, the first twisted top end is the air inlet, the second twisted top end is the air outlet, the tangent line of the first twisted top end is at an angle F2 with the tangent line of the circular air inlet diameter D a of the collector body 21, and the tangent line of the second twisted top end is at an angle F1 with the tangent line of the circular inner diameter D a1 of the pre-swirl guide vane 22, F1, F2∈[0°-90°], F1∈[0-α+25°], F1≤F2. Wherein, α is the air inlet installation angle of the blade 31, and β is the air outlet installation angle of the blade 31. F1, F2 are the radial angles of the pre-swirl guide vane 22, so as to match the air inlet installation angle of the blade 31, so that the inlet air flow is consistent with the rotation direction of the impeller 3 (i.e. Figure 6 and Figure 8 the direction shown by the arrow B in the figure), effectively reduces the resistance of the air flow channel of the impeller 3 caused by the flow separation of the suction surface of the impeller 3 due to the air flow impact loss of the air inlet of the blade 31, and thus solves the problem of the performance reduction of the fan to a large extent.

[0061] Optionally, in the axial direction, the first twisted top end of the pre-swirl guide vane 22 is on the same straight line with the air inlet of the blade 31, and in this case, the pre-swirl guide vane 22 has the best effect of reducing the resistance of the air flow channel of the impeller 3 caused by the flow separation of the suction surface of the impeller 3 due to the air flow impact loss of the air inlet of the blade 31, and the performance of the fan can be optimized.

[0062] Optionally, the orthographic projection of the pre-swirl guide vane 22 in the circumferential direction is a smooth curve, which is composed of one or more of a circular arc line, a Bezier curve and a multi-segment curve, as long as the air flow can flow smoothly.

[0063] Specifically, in the embodiment, the circumferential orthographic projection of the pre-swirl guide vane 22 is composed of two circular arc lines.

[0064] Optionally, the pre-swirl guide vane 22 is twisted in the axial direction, and the twist angle is θ, θ ∈ [0°-90°], so that the air flow narrow strip channels with a specific axial inclination angle formed between the pre-swirl guide vanes 22 periodically distributed on the inner side of the collector 2 body have a certain degree of sound insulation, reflection and noise reduction effect on the radiation sound field inside the centrifugal fan, and the pre-swirl guide vane 22 can reduce the aerodynamic noise generated by impact, thereby achieving the noise reduction effect. Furthermore, due to the existence of the axial inclination angle θ of the pre-swirl guide vane 22, the area of the collector 2 in the axial projection is increased, and the coverage area of the impeller 3 on the inlet side is increased, which can reduce the risk of surge phenomenon of the fan outlet under high back pressure.

[0065] Optionally, as shown in Figure 9 , the direction indicated by the arrow C is the air flow direction. The air uniformizing net 23 is protrusively arranged in the direction opposite to the air flow direction, the distance between the highest point of the air uniformizing net 23 in the axial direction and the collector body 21 is G2, the distance between the highest point of the collector body 21 in the axial direction and the side of the collector body 21 away from the impeller 3 of the fan is G1, 0.5D a2 ≥G2≥G1. Wherein, D a2 is the diameter of the air uniformizing net 23. The air uniformizing net 23 is protrusively arranged in the direction opposite to the air flow direction, which has a certain degree of sound insulation, reflection and noise reduction effect on the radiation sound field inside the centrifugal fan. At the same time, the air flow uniformity is improved, thereby further reducing the aerodynamic noise caused by vortex.

[0066] Optionally, the air uniformizing net 23 is a honeycomb net, and the cross section of the air uniformizing net 23 is composed of one or more of a parabola, a circular arc and a Bezier curve. The air uniformizing net 23 is arranged as a honeycomb net, which has a better sound insulation, reflection and noise reduction effect on the radiation sound field inside the centrifugal fan.

[0067] Optionally, 0.5D b ≤D a2 ≤0.9D b . Wherein, D b is the inner diameter of the impeller 3 of the fan. Under this kind of arrangement, the air uniformizing net 23 has good air guiding effect and air flow performance.

[0068] Another aspect of the present application provides a fan, which comprises a fan cabinet 1, a fan wheel assembly arranged in the fan cabinet 1 and the above-mentioned collector 2, the collector 2 is installed on the fan cabinet 1, the fan wheel assembly comprises a motor 4 and an impeller 3 in driving connection with the motor 4, and the impeller 3 comprises a plurality of blades 31.

[0069] Still another aspect of the present application provides an extractor hood, which comprises the above-mentioned fan.

[0070] The above merely describes some embodiments of the present application. For those skilled in the art, several modifications and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application.

Claims

1. A collector, installed at the air inlet of a range hood fan, characterized in that, The collector includes: Current collecting body (21); Multiple pre-swirling guide vanes (22) are disposed inside the flow collecting body (21). The first end of each pre-swirling guide vane (22) is connected to the flow collecting body (21). Two adjacent pre-swirling guide vanes (22) are spaced apart and are spaced at the same distance apart. A uniform air distribution net (23) is disposed on the inner side of the pre-rotating guide vane (22) and connected to the second end of the pre-rotating guide vane (22); The impeller (3) of the fan and the collector satisfy the following relationship: D b -D a1 ≥2W; Among them, D b D is the inner diameter of the impeller (3) of the fan. a1 W is the inner diameter of the pre-rotating guide vane (22), W is the minimum radial clearance requirement between the collector and the impeller (3), and D is the inlet diameter of the collector body (21). a ≥D b The collector body (21) is located outside the air inlet end face of the impeller (3), and there is a gap t between the collector body (21) and the air inlet end face of the impeller (3). The impeller (3) of the fan and the collector also satisfy the relationship: t≥t min D a1min -D b ≥2t min ; Among them, t min D is the minimum axial clearance between the collector body (21) and the impeller (3). a1min The diameter is the diameter at the point where the distance between the pre-rotating guide vane (22) and the impeller (3) is the smallest.

2. The current collector according to claim 1, characterized in that, The number of the pre-rotating guide vanes (22) is M, the thickness of the pre-rotating guide vanes (22) is A, the number of blades (31) of the impeller (3) of the fan is N, the thickness of the blades (31) is B, and 0.5N≤M≤1.5N, 0.3B≤A≤10B.

3. The current collector according to claim 2, characterized in that, The pre-rotating guide vane (22) is twisted axially to form a first twisted tip and a second twisted tip. The protrusion direction of the first twisted tip and the second twisted tip is the same as the rotation direction of the impeller (3). The first twisted tip is the air inlet, and the second twisted tip is the air outlet. The tangent of the first twisted tip is perpendicular to the air inlet diameter D of the collector body (21). a The angle between the tangents of the circle is F2, and the tangent at the second twisted tip is perpendicular to the inner diameter D of the pre-rotating guide vane. a1 The angle between the tangents of the circle is F1, F1, F2∈[0°, 90°], F1∈[0, α+25°], F1≤F2; Wherein, α is the air inlet placement angle of the blade (31).

4. The current collector according to claim 3, characterized in that, In the axial direction, the first twisted tip of the pre-rotating guide vane (22) is on the same straight line as the air inlet of the blade (31).

5. The current collector according to claim 3, characterized in that, The orthographic projection of the pre-rotating guide vane (22) in the circumferential direction is a smooth curve, which is composed of one or more of a circular arc and multiple curve segments.

6. The current collector according to claim 3, characterized in that, The pre-rotating guide vane (22) is twisted along the axial direction, and the twist angle is θ, θ∈(0°, 90°).

7. The current collector according to any one of claims 1-6, characterized in that, The air distribution mesh (23) is convex in the direction opposite to the airflow direction. The distance between the highest point of the air distribution mesh (23) in the axial direction and the side of the outer end of the collector body (21) away from the impeller (3) is G2. The distance between the highest point of the collector body (21) in the axial direction and the side of the outer end of the collector body (21) away from the impeller (3) of the fan is G1. 0.5D a2 ≥G2≥G1; Among them, D a2 The diameter of the uniform air network (23) is given.

8. The current collector according to claim 7, characterized in that, The gas distribution mesh (23) is a honeycomb mesh, and the cross-section of the gas distribution mesh (23) is composed of one or more of the following: parabola, circular arc, and Bezier curve.

9. The current collector according to claim 7, characterized in that, 0.5D b ≤D a2 ≤0.9D b ; Among them, D b The inner diameter of the impeller (3) of the fan is given.

10. A fan, characterized in that, The device includes a wind cabinet (1), a wind turbine assembly disposed within the wind cabinet (1), and a collector (2) as described in any one of claims 1-9, wherein the collector (2) is mounted on the wind cabinet (1), and the wind turbine assembly includes a motor (4) and an impeller (3) that is drivenly connected to the motor (4).

11. A range hood, characterized in that, Includes the wind turbine as described in claim 10.

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