Range hood assembly and integrated cooker

Abstract

The utility model provides a range hood assembly and an integrated cooker, and relates to the technical field of cooking equipment. The range hood assembly comprises a volute; the impeller is arranged in the volute, the impeller comprises a hub and a plurality of blades, and the plurality of blades are arranged around the hub; wherein the impeller is intercepted through the first face, the first face is perpendicular to the axis of the impeller, on the section, each blade comprises a plurality of first arc sections, the first arc sections are sequentially connected, every two adjacent first arc sections are tangent, and the radiuses of every two adjacent first arc sections are different. The molded line similar to the swinging posture is constructed through the multiple first arc sections, and the technical effects of improving the energy efficiency of the range hood assembly and reducing the turbulence noise of the impeller are achieved.

Description

Technical Field

[0001] The utility model relates to the technical field of cooking equipment, and more specifically, to a smoke machine assembly and an integrated stove. Background Art

[0002] At present, for the integrated smoke stove products on the market, by adding a smoke extraction module on the induction cooker, the cooking fumes generated during cooking can be inhaled into the smoke extraction module through the air inlet of the induction cooker panel.

[0003] In the related art, the impellers of the range hoods all adopt single-arc impellers with simple manufacturing processes (that is, the blade profile is composed of a single arc).

[0004] However, the flow separation between the blades of the single-arc impeller is very large, resulting in the technical problems of low work efficiency and high noise of the range hood. Summary of the Utility Model

[0005] The utility model aims to solve at least one of the technical problems existing in the prior art.

[0006] To this end, a first aspect of the utility model proposes a smoke machine assembly.

[0007] A second aspect of the utility model proposes an integrated stove.

[0008] In view of this, a first aspect of the utility model provides a smoke machine assembly, which includes: a volute; an impeller disposed in the volute, the impeller including a hub and a plurality of blades, the plurality of blades being arranged around the hub; wherein, when the impeller is intercepted by a first plane perpendicular to the axis of the impeller, on the cross-section, the blades include a plurality of first arc segments, the plurality of first arc segments are connected in sequence, adjacent two first arc segments are tangent to each other, and the radii of adjacent two first arc segments are different.

[0009] This application proposes a smoke machine assembly, which belongs to the power structure on the integrated stove. Specifically, the smoke machine assembly can suck the cooking fumes and discharge the sucked cooking fumes to a designated area through the flue.

[0010] The smoke machine assembly includes a volute, a motor and an impeller. The volute is the main frame structure of the smoke machine assembly, which is used to position and support other working structures on the smoke machine assembly. A cavity is formed inside the volute, and the volute is provided with a smoke inlet and an outlet communicating the cavity with the external space of the volute. The motor is installed in the cavity, and the power output end of the motor is connected to the impeller. The motor is used to drive the impeller to rotate, so as to suck the cooking fumes into the volute through the smoke inlet by the impeller, and discharge the cooking fumes from the outlet of the volute after pressurization and acceleration, thereby realizing the suction and centralized discharge of the cooking fumes. Specifically, the motor is connected to the volute, and the motor is fixed inside the volute after assembly.

[0011] On this basis, the impeller includes a hub and a plurality of blades. The blades are fixed on the circumferential side of the hub, and the plurality of blades are evenly distributed around the hub. The hub can provide positioning and support for the blades on the circumferential side. The rotating shaft of the motor is connected to the hub, and the motor drives the hub to rotate through the rotating shaft. The rotating hub drives the surrounding blades to rotate synchronously, so as to form a unidirectional flowing air flow through the rotating blades, so as to realize the functions of fume suction and fume unidirectional discharge.

[0012] Among them, a plane perpendicular to the axis of the impeller is selected as the first plane. By intercepting the impeller through the first plane, the shape of the blade can be observed on the intercepted cross-section, and the profile line of the blade can be obtained correspondingly. Specifically, on the cross-section, the blade includes a plurality of first arc segments, and the plurality of first arc segments are bent in the same direction and are connected in sequence. Specifically, among the plurality of first arc segments connected in sequence, two adjacent first arc segments are tangent in the intersection area, and the radii of two adjacent first arc segments are different, and the corresponding centers do not coincide.

[0013] Compared with the blade designed by a single arc profile line, by constructing a plurality of first arc segments with different radii on the blade, the flow separation between the blades can be reduced. Specifically, the profile line formed by a plurality of first arc segments with different radii and tangent to each other is similar to the swinging posture of a fish swimming, and this posture can effectively reduce the resistance suffered by the fish when swimming.

[0014] It can be seen that in this application, a profile line similar to the above swinging posture is constructed through a plurality of first arc segments, so as to realize the bionic design of the blade, reduce the resistance suffered by the blade during rotation by reducing the flow separation between the blades, and reduce the driving resistance of the motor to the impeller, thereby achieving the technical effects of improving the energy efficiency of the range hood assembly and reducing the turbulent noise of the impeller, and solving the technical problems of low working efficiency and high noise in the related technology.

[0015] In addition, the above range hood assembly provided by the present utility model may also have the following additional technical features:

[0016] In some technical solutions of the present utility model, optionally, in the direction away from the hub, the radii of the plurality of first arc segments gradually increase; in the direction away from the hub, the central angles of the plurality of first arc segments gradually decrease.

[0017] In this technical solution, the blade is bent in the radial direction with respect to the hub, so that the plurality of first arc segments extend sequentially to the area away from the hub.

[0018] On this basis, the radius of the first arc segment close to the hub is smaller, the radius of the first arc segment far from the hub is larger, and the central angle of the first arc segment close to the hub is larger, and the central angle of the first arc segment far from the hub is smaller.

[0019] By defining the gradual change relationship of the above radius and central angle, the profile of the blade has a smaller bending amplitude at the edge of the impeller and a larger bending amplitude on the inner side of the blade, thereby reducing the incident angle of the oil fume between multiple blades, increasing the exit angle of the oil fume flowing out between multiple blades, and further achieving the technical effects of reducing the flow separation of the blade, reducing the flow resistance of the oil fume between the blades, and reducing the turbulent noise of the blade.

[0020] In some technical solutions of the present invention, optionally, the first arc segment includes: a first segment; a second segment; a third segment, and the first segment, the second segment and the third segment are sequentially connected in a direction away from the hub.

[0021] In this technical solution, the first arc segment includes three segments, namely the first segment, the second segment and the third segment. Among them, the first segment is close to the hub, the third segment is far from the hub, and the second segment is located between the first segment and the third segment.

[0022] By limiting the number of the first arc segments to three, the processing difficulty of the blade can be reduced on the basis of meeting the requirements of improving the energy efficiency ratio and noise reduction requirements, thereby reducing the production cost. At the same time, it can also provide convenient conditions for the miniaturized design of the blade, so that the range hood component is applicable to small-sized integrated stoves.

[0023] In some technical solutions of the present invention, optionally, the radius of the outer circle of the impeller is R0; the radius of the first segment is R1, and R0 and R1 satisfy the relational expression: 0.02 ≤ R1÷R0 ≤ 0.04; the central angle of the first segment is α1, 60° ≤ α1 ≤ 95°; the radius of the second segment is R2, and R0 and R2 satisfy the relational expression: 0.04 ≤ R2÷R0 ≤ 0.08; the central angle of the second segment is α2, 22° ≤ α2 ≤ 39°; the radius of the third segment is R3, and R0 and R3 satisfy the relational expression: 0.12 ≤ R3÷R0 ≤ 0.2; the central angle of the third segment is α3, 10° ≤ α3 ≤ 20°.

[0024] In this technical solution, the profile of the blade is composed of three tangent first arc segments. The design parameters of the specific three first arc segments are as follows:

[0025] R0 is the radius of the outer circle of the impeller, and specifically, R0 can be selected as 105 mm.

[0026] Taking O1 as the center, R1 as the radius, and α1 as the central angle, the first segment can be constructed.

[0027] R1 is the radius of the first segment, 0.02 ≤ R1÷R0 ≤ 0.04, and specifically, 0.024229 ≤ R1÷R0 ≤ 0.036343 can be selected.

[0028] In a specific embodiment, R1÷R0 is selected to be 0.030286, corresponding to R1 = 3.18 mm.

[0029] α1 is the central angle of the first segment, 60° ≤ α1 ≤ 95°, and specifically, 62.4° ≤ α1 ≤ 93.6° can be selected.

[0030] In a specific embodiment, α1 = 78°.

[0031] With O2 as the center, R2 as the radius, and α2 as the central angle, the second segment can be constructed.

[0032] R2 is the radius of the second segment, 0.04 ≤ R2÷R0 ≤ 0.08, and specifically, 0.04899 ≤ R2÷R0 ≤ 0.073486 can be selected.

[0033] In a specific embodiment, R2÷R0 is selected to be 0.061238, corresponding to R2 = 6.43 mm.

[0034] α2 is the central angle of the second segment, 22° ≤ α2 ≤ 39°, and specifically, 25.2° ≤ α2 ≤ 37.8° can be selected.

[0035] In a specific embodiment, α2 = 31.5°.

[0036] With O3 as the center, R3 as the radius, and α3 as the central angle, the third segment can be constructed.

[0037] R3 is the radius of the third segment, 0.12 ≤ R3÷R0 ≤ 0.2, and specifically, 0.13066 ≤ R3÷R0 ≤ 0.1960 can be selected.

[0038] In a specific embodiment, R3÷R0 is selected to be 0.163333, corresponding to R3 = 17.15 mm.

[0039] α3 is the central angle of the third segment, 10° ≤ α3 ≤ 20°, and specifically, 12° ≤ α3 ≤ 18° can be selected.

[0040] In a specific embodiment, α3 = 15°.

[0041] Specifically, by designing the profile of the impeller according to the above parameters, the flow separation and vortices between the blades can be reduced, thereby reducing the rotational resistance of the impeller, improving the energy efficiency of the tobacco machine assembly, and reducing the turbulent noise of the impeller.

[0042] In some technical solutions of the present utility model, optionally, the outer diameter of the impeller is D0, the inner diameter of the impeller is D1, and D0 and D1 satisfy the relational expression: 0.7 ≤ D1÷D0 ≤ 0.99; the chord length of the blade is W, and W and D0 satisfy the relational expression: 0.07 ≤ W÷D0 ≤ 0.12; one end of the blade close to the hub is the first end, and the included angle between the section of the blade at the first end and the section of the inner circle of the impeller at the first end is β1, 38° ≤ β1 ≤ 60°; one end of the blade far from the hub is the second end, and the included angle between the section of the blade at the second end and the section of the outer circle of the impeller at the second end is β2, 143° ≤ β2 ≤ 179°.

[0043] In this technical solution, the outer diameter of the impeller is D0, the inner diameter of the impeller is D1. Specifically, D0 can be selected as 210 mm, and D1 can be selected as 182 mm.

[0044] Among them, 0.7 ≤ D1÷D0 ≤ 0.99, specifically, it can be selected as 0.758571 ≤ D1÷D0 ≤ 0.927143. In a specific embodiment, D1÷D0 = 0.842857, that is, D1 = 177 mm.

[0045] W is the chord length of the blade, 0.07 ≤ W÷D0 ≤ 0.12, specifically, it can be selected as 0.078857 ≤ W÷D0 ≤ 0.118286. In a specific embodiment, W÷D0 = 0.098571, that is, W = 20.7 mm.

[0046] One end of the blade close to the hub is the first end, and the included angle between the section of the blade at the first end and the section of the inner circle of the impeller at the first end is β1, and β1 corresponds to the incident angle of the blade.

[0047] Among them, 38° ≤ β1 ≤ 60°, specifically, it can be selected as 39.68° ≤ β1 ≤ 59.5°. In a specific embodiment, β1 = 49.6°.

[0048] One end of the blade far from the hub is the second end, and the included angle between the section of the blade at the second end and the section of the outer circle of the impeller at the second end is β2, and β2 corresponds to the exit angle of the blade.

[0049] Among them, 143° ≤ β2 ≤ 179°, specifically, it can be selected as 145.35° ≤ β1 ≤ 177.6°. In a specific embodiment, β2 = 161.5°.

[0050] Specifically, designing the dimensions of the impeller according to the above parameters can further improve the performance of the impeller, reduce the rotational resistance of the impeller, thereby achieving the technical effects of improving the energy efficiency of the fan component and reducing the turbulent noise of the impeller.

[0051] In some technical solutions of the present utility model, optionally, the volute is intercepted by a first plane. On the cross-section, the volute includes a plurality of second arc segments, and the plurality of second arc segments are connected in sequence, and two adjacent second arc segments are tangent; in the direction away from the impeller, the central angles of the plurality of second arc segments gradually increase.

[0052] In this technical solution, a plane perpendicular to the axis of the impeller is selected as the first plane, and the impeller is intercepted by the first plane. The shape of the side wall of the volute can be observed on the intercepted cross-section, and the profile line of the volute can be obtained correspondingly. Specifically, on the cross-section, the volute includes a plurality of second arc segments, and the plurality of second arc segments are bent in the same direction, and the plurality of second arc segments are connected in sequence. Specifically, among the plurality of second arc segments connected in sequence, two adjacent second arc segments are tangent in the intersection area, and the radii of two adjacent second arc segments are different, and the corresponding centers do not coincide.

[0053] Compared with the volute designed by a single arc profile line, by constructing a plurality of second arc segments with different radii on the side wall of the volute, on the one hand, the small-size requirement of the volute can be met, and on the other hand, the static pressure efficiency of the volute can be improved. Specifically, compared with the volute designed by a single arc profile line, the space size of the volute of the present application can be reduced by 25%. Specifically, when the outer diameter D0 of the impeller is selected to be 210 mm, the width W1 of the volute can be reduced to 283 mm.

[0054] It can be seen that the present application constructs a profile line similar to a spiral shell through a plurality of second arc segments, thereby realizing the bionic design of the volute, thereby reducing the size of the volute and improving the static pressure efficiency of the volute without loss of the aerodynamic performance of the volute, and further realizing the improvement of the oil fume suction rate and the reduction of the aerodynamic noise of the volute, providing convenient conditions for the miniaturized design of the volute.

[0055] In some technical solutions of the present utility model, optionally, the second arc segment includes: a first arc segment; a second arc segment; a third arc segment; a fourth arc segment, and the first arc segment, the second arc segment, the third arc segment and the fourth arc segment are connected in sequence in the direction away from the impeller.

[0056] In this technical solution, the second arc segment includes four segments: a first arc segment, a second arc segment, a third arc segment and a fourth arc segment. Among them, the first arc segment is close to the impeller, the fourth arc segment is far from the impeller, the second arc segment and the third arc segment are located between the first arc segment and the fourth arc segment, and the second arc segment is closer to the impeller than the third arc segment.

[0057] By limiting the number of the second arc segments to four, the processing difficulty of the volute can be reduced on the basis of meeting the requirements of improving the static pressure efficiency and the noise reduction requirements, thereby reducing the production cost. At the same time, it can also provide convenient conditions for the miniaturized design of the volute, so that the range hood assembly is applicable to small-size integrated stoves.

[0058] In some technical solutions of the present utility model, optionally, the outer diameter of the impeller is D0; the radius of the first arc segment is r1, and D0 and r1 satisfy the relational expression: 1.2 ≤ 2×r1÷D0 ≤ 1.5; the central angle of the first arc segment is γ1, 20° ≤ γ1 ≤ 35°; the radius of the second arc segment is r2, and D0 and r2 satisfy the relational expression: 1 ≤ 2×r2÷D0 ≤ 1.3; the central angle of the second arc segment is γ2, 60° ≤ γ2 ≤ 98°; the radius of the third arc segment is r3, and D0 and r3 satisfy the relational expression: 1.1 ≤ 2×r3÷D0 ≤ 1.5; the central angle of the third arc segment is γ3, 70° ≤ γ3 ≤ 115°; the radius of the fourth arc segment is r4, and D0 and r4 satisfy the relational expression: 1.2 ≤ 2×r4÷D0 ≤ 1.6; the central angle of the fourth arc segment is γ4, 80° ≤ γ4 ≤ 125°.

[0059] In this technical solution, the profile line of the volute is composed of four tangent second arc segments. The design parameters of the specific four second arc segments are as follows:

[0060] D0 is the outer diameter of the impeller, and specifically, D0 can be selected as 210 mm.

[0061] Taking c1 as the center, r1 as the radius, and γ1 as the central angle, the first arc segment can be constructed.

[0062] r1 is the radius of the first arc segment, 1.2 ≤ 2×r1÷D0 ≤ 1.5, and specifically, 1.214 ≤ 2×r1÷D0 ≤ 1.483 can be selected.

[0063] In a specific embodiment, 2×r1÷D0 is selected as 1.348, corresponding to r1 = 141.62 mm.

[0064] γ1 is the central angle of the first arc segment, 20° ≤ γ1 ≤ 35°, and specifically, 22.16° ≤ γ1 ≤ 33.24° can be selected.

[0065] In a specific embodiment, γ1 = 27.7°.

[0066] Taking c2 as the center, r2 as the radius, and γ2 as the central angle, the second arc segment can be constructed.

[0067] r2 is the radius of the second arc segment, 1 ≤ 2×r2÷D0 ≤ 1.3, and specifically, 1.039 ≤ 2×r2÷D0 ≤ 1.271 can be selected.

[0068] In a specific embodiment, 2×r2÷D0 is selected as 1.154, corresponding to r2 = 121.24 mm.

[0069] γ2 is the central angle of the second arc segment, 60° ≤ γ2 ≤ 98°, and specifically, 63.92° ≤ γ2 ≤ 95.88° can be selected.

[0070] In a specific embodiment, γ2 = 79.9°.

[0071] Taking c3 as the center, r3 as the radius, and γ3 as the central angle, a third arc segment can be constructed.

[0072] r3 is the radius of the third arc segment, 1.1 ≤ 2×r3÷D0 ≤ 1.5, and specifically 1.169 ≤ 2×r3÷D0 ≤ 1.429 can be selected.

[0073] In a specific embodiment, 2×r3÷D0 is selected to be 1.299, corresponding to r3 = 136.47 mm.

[0074] γ3 is the central angle of the third arc segment, 70° ≤ γ3 ≤ 115°, and specifically 73.60° ≤ γ3 ≤ 110.4° can be selected.

[0075] In a specific embodiment, γ3 = 92.0°.

[0076] Taking c4 as the center, r4 as the radius, and γ4 as the central angle, a fourth arc segment can be constructed.

[0077] r4 is the radius of the fourth arc segment, 1.2 ≤ 2×r4÷D0 ≤ 1.6, and specifically 1.232 ≤ 2×r4÷D0 ≤ 1.506 can be selected.

[0078] In a specific embodiment, 2×r4÷D0 is selected to be 1.369, corresponding to r4 = 143.79 mm.

[0079] γ4 is the central angle of the fourth arc segment, 80° ≤ γ4 ≤ 125°, and specifically 81.04° ≤ γ4 ≤ 121.56° can be selected.

[0080] In a specific embodiment, γ4 = 101.31°.

[0081] Specifically, by designing the profile of the volute according to the above parameters, it is possible to reduce the size of the volute and improve the static pressure efficiency of the volute without sacrificing the aerodynamic performance of the volute, thereby achieving the technical effects of improving the oil fume suction rate, reducing the aerodynamic noise of the volute, and providing convenient conditions for the miniaturized design of the volute.

[0082] In some technical solutions of the present utility model, optionally, the outer diameter of the impeller is D0; one end of the plurality of second arc segments away from the impeller is the outer end, and the distance between the impeller and the outer end in the radial direction of the impeller is A, and A and D0 satisfy the relationship: 0.2 ≤ A÷D0 ≤ 0.35; the radius of the volute tongue of the volute is R4, and R4 and D0 satisfy the relationship: 0.02 ≤ R4÷D0 ≤ 0.05; one end of the plurality of second arc segments close to the impeller is the inner end, and the distance between the impeller and the inner end in the radial direction of the impeller is t, and t and D0 satisfy the relationship: 0.04 ≤ t÷D0 ≤ 0.08; the included angle between the outer ends of the plurality of second arc segments and the volute tongue is T1, 40° ≤ T1 ≤ 68°; the outer expansion angle of the diffuser section of the volute is B1, 19° ≤ B1 ≤ 35°; the width of the outlet of the diffuser section is L, and L and D0 satisfy the relationship: 0.4 ≤ L÷D0 ≤ 0.7.

[0083] In this technical solution, D0 is the outer diameter of the impeller, and specifically, D0 can be selected as 210 mm.

[0084] On this basis, on the profile line of the volute, the end away from the impeller is the outer end, and the end close to the impeller is the inner end, where the distance between the impeller and the outer end in the radial direction of the impeller is A, and A corresponds to the opening degree of the outlet of the volute.

[0085] Specifically, 0.2 ≤ A÷D0 ≤ 0.35, and specifically, 0.208 ≤ A÷D0 ≤ 0.312 can be selected.

[0086] In a specific embodiment, A÷D0 = 0.26, that is, A = 54.6 mm.

[0087] A volute tongue is connected to the inner end of the profile line of the side wall of the volute, and the volute compresses the oil fume through the volute tongue.

[0088] Specifically, the radius of the volute tongue is R4, 0.02 ≤ R4÷D0 ≤ 0.05, and specifically, 0.02816 ≤ R4÷D0 ≤ 0.04224 can be selected.

[0089] In a specific embodiment, R4÷D0 = 0.0352, that is, R4 = 7.4 mm.

[0090] The distance between the impeller and the inner end of the profile line of the volute in the radial direction of the impeller is t, and t corresponds to the minimum clearance between the volute tongue and the impeller.

[0091] Specifically, 0.04 ≤ t÷D0 ≤ 0.08, and specifically, 0.04832 ≤ t÷D0 ≤ 0.07248 can be selected.

[0092] In a specific embodiment, t÷D0 = 0.0604, that is, t = 12.7 mm.

[0093] The included angle between the outer end of the spiral casing profile and the volute tongue is T1, and T1 corresponds to the position angle of the volute tongue.

[0094] Specifically, 40° ≤ T1 ≤ 68°, and specifically, 43.28° ≤ T1 ≤ 64.92° can be selected.

[0095] In a specific embodiment, T1 = 54.1°.

[0096] At the second end of the spiral casing profile and on the downwind side of the volute tongue, a diffuser section is provided. The diffuser section forms the outlet of the spiral casing, and the oil fume drawn into the spiral casing by the rotating wind wheel is finally discharged from the spiral casing after being diffused and decelerated in the diffuser section. Among them, the outward expansion angle of the diffuser section relative to the opening degree A is B1, and the larger B1 is, the more obvious the effect of diffusing and decelerating the oil fume in the diffuser section is.

[0097] Specifically, 19° ≤ B1 ≤ 35°, and specifically, 20.64° ≤ B1 ≤ 30.96° can be selected.

[0098] In a specific embodiment, B1 = 25.8°.

[0099] The width of the outlet of the diffuser section is L. When the outward expansion angle B1 is determined, the length of the diffuser section and the width L of the outlet of the diffuser section restrict each other.

[0100] Specifically, 0.4 ≤ L÷D0 ≤ 0.7, and specifically, 0.4352 ≤ L÷D0 ≤ 0.6528 can be selected.

[0101] In a specific embodiment, L÷D0 = 0.544, that is, L = 114.3 mm.

[0102] Specifically, designing the volute tongue and the diffuser section according to the above parameters can reduce the probability of vortex problems in the diffuser section without loss of the aerodynamic performance of the spiral casing, reduce the proportion of the low-speed area in the spiral casing, and reduce the proportion of the strong turbulent kinetic energy area in the spiral casing, thereby achieving the technical effects of improving the oil fume suction rate, reducing the aerodynamic noise of the spiral casing, and providing convenient conditions for the miniaturization design of the spiral casing.

[0103] In some technical solutions of the present utility model, optionally, the spiral casing includes an inlet. In the axial direction of the impeller, the inlet is opposite to the impeller; in the direction close to the impeller, the caliber of the inlet gradually decreases; the inner surface of the inlet is an arc surface.

[0104] In this technical solution, an inlet is provided at the top of the spiral casing. In the axial direction of the impeller, the inlet and the impeller are oppositely arranged, and the rotating impeller can draw the oil fume into the spiral casing through the inlet.

[0105] On this basis, the inner surface of the inlet is an arc surface, and in the axial direction close to the impeller, the caliber of the inlet gradually decreases to form an inlet with an arc shape and a gradually decreasing caliber.

[0106] The inlet with an arc shape and a gradually decreasing caliber can play a role in guiding the air flow into the volute, so as to reduce the probability of backflow problems and skew flow problems of the oil fume at the inlet, thereby reducing the backflow noise and skew flow noise at the inlet, and improving the suction efficiency of the oil fume by reducing the flow loss.

[0107] On the other hand, the inlet can reduce the resistance of the oil fume at the inlet through the arc surface, so as to reduce the kinetic energy loss of the oil fume, thereby improving the suction efficiency of the oil fume.

[0108] In some technical solutions of the present utility model, optionally, the outer diameter of the impeller is D0, and the inner diameter of the impeller is D1; the caliber of the end of the inlet far from the impeller is D3, and D3 and D0 satisfy the relational expression: 0.88 ≤ D3÷D0 ≤ 1.03; the caliber of the end of the inlet close to the impeller is D4, and D4 and D1 satisfy the relational expression: 0.97 ≤ D4÷D1 ≤ 1.07; in the radial direction of the impeller, the distance between the inlet and the impeller is h, and h and D1 satisfy the relational expression: 0.01 ≤ h÷D1 ≤ 0.03; the radius of the inner surface of the inlet is R5, and R5 and D1 satisfy the relational expression: 0.04 ≤ R5÷D1 ≤ 0.07.

[0109] In this technical solution, D0 is the outer diameter of the impeller, specifically, D0 can be selected as 210 mm, and D1 is the inner diameter of the impeller, specifically, D1 can be selected as 182 mm.

[0110] On this basis, the caliber of the end of the inlet far from the impeller is D3, 0.88 ≤ D3÷D0 ≤ 1.03, and specifically, 0.89 ≤ D3÷D0 ≤ 1.02 can be selected.

[0111] In a specific embodiment, D3÷D0 = 0.98, that is, D3 = 202 mm.

[0112] The caliber of the end of the inlet close to the impeller is D4, 0.97 ≤ D4÷D1 ≤ 1.07, and specifically, 0.98 ≤ D4÷D1 ≤ 1.06 can be selected.

[0113] In a specific embodiment, D4 = 181 mm.

[0114] In the radial direction of the impeller, the distance h between the inlet and the impeller corresponds to the depth of the inlet. Among them, 0.01 ≤ h÷D1 ≤ 0.03, and specifically, 0.010682 ≤ h÷D1 ≤ 0.0218 can be selected.

[0115] In a specific embodiment, h÷D1 = 0.0109, that is, h = 2 mm.

[0116] The radius of the inner surface of the inlet is R5, where 0.04 ≤ R5÷D1 ≤ 0.07, and specifically, 0.041538 ≤ R5÷D1 ≤ 0.064615 can be selected.

[0117] In a specific embodiment, R5÷D1 = 0.046154, that is, R5 = 8.4 mm.

[0118] Specifically, designing the inlet according to the above parameters can strengthen the function of guiding the air flow at the inlet into the volute, so as to further reduce the probability of the backflow problem and the skew flow problem of the oil fume at the inlet, thereby reducing the backflow noise and the skew flow noise at the inlet, and improving the suction efficiency of the oil fume.

[0119] On the other hand, designing the inlet according to the above parameters can further reduce the resistance of the oil fume at the inlet, so as to reduce the kinetic energy loss of the oil fume, thereby improving the suction efficiency of the oil fume.

[0120] The second aspect of the present utility model provides an integrated range hood, which includes: a main body, and a flue is formed inside the main body; a smoke machine assembly as described in any of the above technical solutions, and the volute is communicated with the flue.

[0121] In this technical solution, an integrated range hood provided with the smoke machine assembly as described in any of the above technical solutions is defined. Therefore, this integrated range hood has the advantages of the smoke machine assembly as described in any of the above technical solutions and can achieve the technical effects that the smoke machine assembly as described in any of the above technical solutions can achieve. To avoid repetition, it will not be elaborated here.

[0122] On this basis, the integrated range hood includes a main body, and a flue is formed inside the main body. The integrated range hood can suck the oil fume through the flue to realize the collection of the oil fume and avoid the oil fume from spreading everywhere. An air inlet is opened at the top of the main body, and the air inlet is communicated with the flue. A grille is embedded inside the air inlet to block foreign objects through the grille.

[0123] Among them, the integrated range hood further includes an oil-gas separation component and a filtering component.

[0124] The oil-gas separation component is arranged in the flue, and the oil-gas separation component is arranged opposite to the air inlet on the flue. After the oil fume flows into the air inlet, it needs to flow through the oil-gas separation component first. The oil-gas separation component can separate the oil and water vapor mixed in the oil fume to complete the pre-stage oil-water separation of the oil fume, avoid the oil fume from carrying oil and water into the smoke machine assembly, thereby protecting the smoke machine assembly from being polluted by oil and water on the one hand, extending the service life of the integrated range hood, on the other hand, avoiding the generation of peculiar smell by the oil and water accumulated in the flue, and on the third hand, avoiding the secondary pollution of the environment by the oil fume processed by the integrated range hood.

[0125] The filtering component is installed in the flue, and the cooking fume flowing in the flue needs to pass through the filtering component, so that the cooking fume is filtered by the filtering parts in the filtering component, thereby reducing the peculiar smell of the cooking fume and avoiding the secondary pollution of the environment by the cooking fume, and further achieving the technical effects of improving the reliability of the integrated range hood and enhancing the user experience.

[0126] The additional aspects and advantages of the present utility model will become apparent in the following description part or be learned through the practice of the present utility model. BRIEF DESCRIPTION OF THE DRAWINGS

[0127] The above and / or additional aspects and advantages of the present utility model will become apparent and be readily understood from the description of the embodiments in conjunction with the following drawings, wherein:

[0128] Figure 1 FIG. 1 shows a schematic structural diagram of an integrated range hood according to an embodiment of the present utility model;

[0129] Figure 2 FIG. 2 shows an exploded view of an integrated range hood according to an embodiment of the present utility model;

[0130] Figure 3 FIG. 3 shows a schematic structural diagram of a smoke machine component according to an embodiment of the present utility model;

[0131] Figure 4 FIG. 4 shows a schematic structural diagram of an integrated range hood according to an embodiment of the present utility model;

[0132] Figure 5 FIG. 5 shows a schematic structural diagram of an integrated range hood according to an embodiment of the present utility model;

[0133] Figure 6 FIG. 6 shows a schematic structural diagram of an impeller according to an embodiment of the present utility model;

[0134] Figure 7 FIG. 7 shows a schematic structural diagram of an impeller according to an embodiment of the present utility model;

[0135] Figure 8 is Figure 7 a cross-sectional view of the impeller in the B-B direction in the shown embodiment;

[0136] Figure 9 FIG. 8 is a simulation diagram of the fluidity of an impeller in the related art;

[0137] Figure 10 FIG. 9 is a simulation diagram of the fluidity of an impeller according to an embodiment of the present utility model;

[0138] Figure 11 FIG. 10 shows a schematic structural diagram of a volute according to an embodiment of the present utility model;

[0139] Figure 12 Shows a schematic structural diagram of a volute according to an embodiment of the present invention;

[0140] Figure 13 Shows a schematic structural diagram of a volute according to an embodiment of the present invention;

[0141] Figure 14 Shows a schematic structural diagram of a volute according to an embodiment of the present invention;

[0142] Figure 15 Is a simulation diagram of the velocity vector of a volute in the related art;

[0143] Figure 16 Is a simulation diagram of the velocity vector of a volute according to an embodiment of the present invention;

[0144] Figure 17 Is a simulation diagram of the velocity of a volute in the related art;

[0145] Figure 18 Is a simulation diagram of the velocity of a volute according to an embodiment of the present invention;

[0146] Figure 19 Is a simulation diagram of the turbulent kinetic energy of a volute in the related art;

[0147] Figure 20 Is a simulation diagram of the turbulent kinetic energy of a volute according to an embodiment of the present invention;

[0148] Figure 21 Shows an exploded view of a range hood assembly according to an embodiment of the present invention;

[0149] Figure 22 Shows a schematic structural diagram of a range hood assembly according to an embodiment of the present invention;

[0150] Figure 23 Is a simulation diagram of the recirculation velocity of a volute in the related art;

[0151] Figure 24 Is a simulation diagram of the recirculation velocity of a volute according to an embodiment of the present invention;

[0152] Figure 25 Is a simulation diagram of the leakage velocity of a volute in the related art;

[0153] Figure 26 Is a simulation diagram of the leakage velocity of a volute according to an embodiment of the present invention;

[0154] Figure 27 Is a velocity contour map of a volute in the related art;

[0155] Figure 28 The velocity contour map of the volute according to an embodiment of the present utility model.

[0156] Among them, Figures 1 to 22 The corresponding relationship between the reference numerals and the component names in the

[0157] 100 Range hood assembly, 110 Volute, 112 Second arc segment, 1122 First arc section, 1124 Second arc section, 1126 Third arc section, 1128 Fourth arc section, 114 Volute tongue, 116 Diffuser section, 118 Inlet, 120 Impeller, 122 Hub, 124 Blades, 126 First arc segment, 1262 First segment part, 1264 Second segment part, 1266 Third segment part, 130 Motor, 200 Integrated stove, 210 Body, 2102 Flue, 220 Grease separation assembly, 230 Filter assembly, 240 Grille. Detailed implementation manners

[0158] In order to more clearly understand the above objects, features and advantages of the present utility model, the present utility model will be further described in detail below with reference to the drawings and specific implementation manners. It should be noted that, without conflict, the embodiments of the present application and the features in the embodiments can be combined with each other.

[0159] In the following description, many specific details are set forth in order to fully understand the present utility model. However, the present utility model can also be implemented in other ways different from those described herein. Therefore, the protection scope of the present utility model is not limited by the specific embodiments disclosed below.

[0160] Next, refer to Figures 1 to 28 Describe a range hood assembly and an integrated stove according to some embodiments of the present utility model.

[0161] As Figure 3 , Figure 4 , Figure 5 and Figure 6 shown, an embodiment of the present utility model provides a range hood assembly 100, and the range hood assembly 100 includes: a volute 110; an impeller 120, the impeller 120 is disposed inside the volute 110, the impeller 120 includes a hub 122 and a plurality of blades 124, and the plurality of blades 124 are arranged around the hub 122; among them, the impeller 120 is intercepted by a first plane, the first plane is perpendicular to the axis of the impeller 120, and on the cross-section, the blades 124 include a plurality of first arc segments 126, the plurality of first arc segments 126 are connected in sequence, two adjacent first arc segments 126 are tangent to each other, and the radii of two adjacent first arc segments 126 are different.

[0162] Figure 3 The arrow a in

[0163] Figure 4 The middle arrow b shows the flow direction of the cooking fume.

[0164] This application provides a range hood assembly 100. The range hood assembly 100 belongs to the power structure on the integrated stove 200. Specifically, the range hood assembly 100 can suck the cooking fume and discharge the sucked cooking fume to a designated area through the flue 2102.

[0165] The range hood assembly 100 includes a volute 110, a motor 130, and an impeller 120. The volute 110 is the main frame structure of the range hood assembly 100 and is used to position and support other working structures on the range hood assembly 100. A cavity is formed inside the volute 110, and the volute 110 is provided with a smoke inlet and an outlet that communicate the cavity with the external space of the volute 110. The motor 130 is installed in the cavity, and the power output end of the motor 130 is connected to the impeller 120. The motor 130 is used to drive the impeller 120 to rotate, so as to suck the cooking fume into the volute 110 through the impeller 120 from the smoke inlet, and discharge the cooking fume from the outlet of the volute 110 after pressurization and acceleration, thereby realizing the suction and centralized discharge of the cooking fume. Specifically, the motor 130 is connected to the volute 110, and after assembly, the motor 130 is fixed inside the volute 110.

[0166] On this basis, the impeller 120 includes a hub 122 and a plurality of blades 124. The blades 124 are fixed on the circumferential side of the hub 122, and the plurality of blades 124 are evenly distributed around the hub 122. The hub 122 can provide positioning and support for the surrounding blades 124. The rotating shaft of the motor 130 is connected to the hub 122. The motor 130 drives the hub 122 to rotate through the rotating shaft, and the rotating hub 122 drives the surrounding blades 124 to rotate synchronously, so as to form a unidirectional flowing air flow through the rotating blades 124, thereby realizing the cooking fume suction function and the cooking fume unidirectional discharge function.

[0167] Wherein, a plane perpendicular to the axis of the impeller 120 is selected as the first plane. By intercepting the impeller 120 through the first plane, the shape of the blade 124 can be observed on the intercepted section, and the profile line of the blade 124 can be correspondingly obtained. Specifically, on the section, the blade 124 includes a plurality of first arc segments 126. The plurality of first arc segments 126 are bent in the same direction, and the plurality of first arc segments 126 are connected in sequence. Specifically, among the plurality of first arc segments 126 connected in sequence, two adjacent first arc segments 126 are tangent in the intersection area, and the radii of two adjacent first arc segments 126 are different, and the corresponding centers are not coincident.

[0168] Compared with the blade 124 designed by a single arc-shaped line, by constructing a plurality of first arc segments 126 with different radii on the blade 124, the flow separation between the blades 124 can be reduced. Specifically, the line formed by a plurality of first arc segments 126 with different radii and tangent to each other is similar to the swinging posture of a fish swimming, and this posture can effectively reduce the resistance suffered by the fish when swimming.

[0169] It can be seen from this that in this application, a line similar to the above swinging posture is constructed through a plurality of first arc segments 126, so as to realize the bionic design of the blade 124. By reducing the flow separation between the blades 124, the resistance suffered by the blade 124 during rotation is reduced, and the driving resistance of the motor 130 to the impeller 120 is reduced. Furthermore, the technical effects of improving the energy efficiency of the cigarette machine assembly 100 and reducing the turbulent noise of the impeller 120 are realized, and the technical problems of low working efficiency and high noise existing in the related technology are solved.

[0170] As Figure 6 shown, in some embodiments of the present invention, optionally, in the direction away from the hub 122, the radii of the plurality of first arc segments 126 gradually increase; in the direction away from the hub 122, the central angles of the plurality of first arc segments 126 gradually decrease.

[0171] In this embodiment, the blade 124 is bent in the radial direction with respect to the hub 122, so that the plurality of first arc segments 126 extend sequentially into the area away from the hub 122.

[0172] On this basis, the radius of the first arc segment 126 close to the hub 122 is smaller, the radius of the first arc segment 126 far from the hub 122 is larger, and the central angle of the first arc segment 126 close to the hub 122 is larger, and the central angle of the first arc segment 126 far from the hub 122 is smaller.

[0173] By defining the above-mentioned gradient relationship between the radius and the central angle, the line of the blade 124 has a smaller bending amplitude at the edge of the impeller 120 and a larger bending amplitude on the inner side of the blade 124, so as to reduce the incident angle of the oil fume between the plurality of blades 124 and increase the exit angle of the oil fume flowing out between the plurality of blades 124. Furthermore, the technical effects of reducing the flow separation of the blade 124, reducing the flow resistance of the oil fume between the blades 124, and reducing the turbulent noise of the blade 124 are realized.

[0174] As Figure 6 shown, in some embodiments of the present invention, optionally, the first arc segment 126 includes: a first segment portion 1262; a second segment portion 1264; a third segment portion 1266, and the first segment portion 1262, the second segment portion 1264 and the third segment portion 1266 are sequentially connected in the direction away from the hub 122.

[0175] In this embodiment, the first arc segment 126 includes three segments: a first segment portion 1262, a second segment portion 1264, and a third segment portion 1266. Among them, the first segment portion 1262 is close to the hub 122, the third segment portion 1266 is far from the hub 122, and the second segment portion 1264 is located between the first segment portion 1262 and the third segment portion 1266.

[0176] By limiting the number of the first arc segments 126 to three, the processing difficulty of the blade 124 can be reduced on the basis of meeting the requirements of improving the energy efficiency ratio and noise reduction requirements, thereby reducing the production cost. At the same time, it can also provide convenient conditions for the miniaturization design of the blade 124, so that the cigarette machine assembly 100 is applicable to the small-sized integrated stove 200.

[0177] As Figure 6 shown, in some embodiments of the present invention, optionally, the radius of the outer circle of the impeller 120 is R0; the radius of the first segment portion 1262 is R1, and R0 and R1 satisfy the relationship: 0.02 ≤ R1÷R0 ≤ 0.04; the central angle of the first segment portion 1262 is α1, 60° ≤ α1 ≤ 95°; the radius of the second segment portion 1264 is R2, and R0 and R2 satisfy the relationship: 0.04 ≤ R2÷R0 ≤ 0.08; the central angle of the second segment portion 1264 is α2, 22° ≤ α2 ≤ 39°; the radius of the third segment portion 1266 is R3, and R0 and R3 satisfy the relationship: 0.12 ≤ R3÷R0 ≤ 0.2; the central angle of the second segment portion 1264 is α3, 10° ≤ α3 ≤ 20°.

[0178] In this embodiment, the profile of the blade 124 is composed of three tangent first arc segments 126. The design parameters of the specific three first arc segments 126 are as follows:

[0179] R0 is the radius of the outer circle of the impeller 120. Specifically, R0 can be selected as 105 mm.

[0180] With O1 as the center, R1 as the radius, and α1 as the central angle, the first segment portion 1262 can be constructed.

[0181] R1 is the radius of the first segment portion 1262, 0.02 ≤ R1÷R0 ≤ 0.04. Specifically, 0.024229 ≤ R1÷R0 ≤ 0.036343 can be selected.

[0182] In a specific embodiment, R1÷R0 is selected as 0.030286, corresponding to R1 = 3.18 mm.

[0183] α1 is the central angle of the first segment portion 1262, 60° ≤ α1 ≤ 95°. Specifically, 62.4° ≤ α1 ≤ 93.6° can be selected.

[0184] In a specific embodiment, α1 = 78°.

[0185] Taking O2 as the center, R2 as the radius, and α2 as the central angle, the second segment 1264 can be constructed.

[0186] R2 is the radius of the second segment 1264, 0.04 ≤ R2÷R0 ≤ 0.08, and specifically, 0.04899 ≤ R2÷R0 ≤ 0.073486 can be selected.

[0187] In a specific embodiment, R2÷R0 is selected to be 0.061238, corresponding to R2 = 6.43 mm.

[0188] α2 is the central angle of the second segment 1264, 22° ≤ α2 ≤ 39°, and specifically, 25.2° ≤ α2 ≤ 37.8° can be selected.

[0189] In a specific embodiment, α2 = 31.5°.

[0190] Taking O3 as the center, R3 as the radius, and α3 as the central angle, the third segment 1266 can be constructed.

[0191] R3 is the radius of the third segment 1266, 0.12 ≤ R3÷R0 ≤ 0.2, and specifically, 0.13066 ≤ R3÷R0 ≤ 0.1960 can be selected.

[0192] In a specific embodiment, R3÷R0 is selected to be 0.163333, corresponding to R3 = 17.15 mm.

[0193] α3 is the central angle of the third segment 1266, 10° ≤ α3 ≤ 20°, and specifically, 12° ≤ α3 ≤ 18° can be selected.

[0194] In a specific embodiment, α3 = 15°.

[0195] Specifically, by designing the profile of the impeller 120 according to the above parameters, the flow separation and vortices between the blades 124 can be reduced, and thereby the rotational resistance of the impeller 120 can be decreased, so as to improve the energy efficiency of the tobacco machine assembly 100 and reduce the turbulent noise of the impeller 120.

[0196] Such as Figure 7 and Figure 8As shown, in some embodiments of the present utility model, optionally, the outer diameter of the impeller 120 is D0, the inner diameter of the impeller 120 is D1, and D0 and D1 satisfy the relationship: 0.7 ≤ D1÷D0 ≤ 0.99; the chord length of the blade 124 is W, and W and D0 satisfy the relationship: 0.07 ≤ W÷D0 ≤ 0.12; one end of the blade 124 close to the hub 122 is the first end, and the included angle between the section of the blade 124 at the first end and the section of the inner circle of the impeller 120 at the first end is β1, 38° ≤ β1 ≤ 60°; one end of the blade 124 far from the hub 122 is the second end, and the included angle between the section of the blade 124 at the second end and the section of the outer circle of the impeller 120 at the second end is β2, 143° ≤ β2 ≤ 179°.

[0197] In this embodiment, the outer diameter of the impeller 120 is D0, the inner diameter of the impeller 120 is D1. Specifically, D0 can be selected as 210 mm, and D1 can be selected as 182 mm.

[0198] Among them, 0.7 ≤ D1÷D0 ≤ 0.99, specifically, it can be selected as 0.758571 ≤ D1÷D0 ≤ 0.927143. In a specific embodiment, D1÷D0 = 0.842857, that is, D1 = 177 mm.

[0199] W is the chord length of the blade 124, 0.07 ≤ W÷D0 ≤ 0.12, specifically, it can be selected as 0.078857 ≤ W÷D0 ≤ 0.118286. In a specific embodiment, W÷D0 = 0.098571, that is, W = 20.7 mm.

[0200] One end of the blade 124 close to the hub 122 is the first end, and the included angle between the section of the blade 124 at the first end and the section of the inner circle of the impeller 120 at the first end is β1, and β1 corresponds to the incident angle of the blade 124.

[0201] Among them, 38° ≤ β1 ≤ 60°, specifically, it can be selected as 39.68° ≤ β1 ≤ 59.5°. In a specific embodiment, β1 = 49.6°.

[0202] One end of the blade 124 close to the hub 122 is the second end, and the included angle between the section of the blade 124 at the second end and the section of the outer circle of the impeller 120 at the second end is β2, and β2 corresponds to the exit angle of the blade 124.

[0203] Among them, 143° ≤ β2 ≤ 179°, specifically, it can be selected as 145.35° ≤ β1 ≤ 177.6°. In a specific embodiment, β2 = 161.5°.

[0204] Specifically, designing the dimensions of the impeller 120 according to the above parameters can further improve the performance of the impeller 120, reduce the rotational resistance of the impeller 120, thereby achieving the technical effects of improving the energy efficiency of the fan unit 100 and reducing the turbulent noise of the impeller 120.

[0205] Figure 9 and Figure 10 Fig. shows the simulation effect comparison between the single-arc impeller in the related art and the bionic multi-arc impeller 120 of the present application. From the comparison results of regions d1 and d2 in the figure, and the comparison results of e1 and e2, it can be seen that the flow separation of the blades 124 of the single-arc impeller in the related art is very serious, which is also the reason for the low energy efficiency and high noise of the whole machine caused by the single-arc impeller 120. However, the inter-blade flow separation of the bionic multi-arc impeller 120 of the present application is weakened or even disappears, resulting in enhanced work capacity, improved energy efficiency of the whole machine, and reduced noise.

[0206] Such as Figure 11 , Figure 12 and Figure 13 As shown in, in some embodiments of the present invention, optionally, the volute 110 is intercepted by a first plane. On the cross-section, the volute 110 includes a plurality of second arc segments 112, and the plurality of second arc segments 112 are connected in sequence, and two adjacent second arc segments 112 are tangent; in the direction away from the impeller 120, the central angles of the plurality of second arc segments 112 gradually increase.

[0207] In this embodiment, a plane perpendicular to the axis of the impeller 120 is selected as the first plane, and the impeller 120 is intercepted by the first plane. The shape of the side wall of the volute 110 can be observed on the intercepted cross-section, and the profile line of the volute 110 can be obtained accordingly. Specifically, on the cross-section, the volute 110 includes a plurality of second arc segments 112, and the plurality of second arc segments 112 are bent in the same direction, and the plurality of second arc segments 112 are connected in sequence. Specifically, among the plurality of second arc segments 112 connected in sequence, two adjacent second arc segments 112 are tangent in the intersection area, and the radii of two adjacent second arc segments 112 are different, and the corresponding centers do not coincide.

[0208] Compared with the volute 110 designed by a single arc profile line, by constructing a plurality of second arc segments 112 with different radii on the side wall of the volute 110, on the one hand, the small size requirement of the volute 110 can be met, and on the other hand, the static pressure efficiency of the volute 110 can be improved. Specifically, compared with the volute 110 designed by a single arc profile line, the space size of the volute 110 of the present application can be reduced by 25%. Specifically, when the outer diameter D0 of the impeller 120 is selected to be 210 mm, the width W1 of the volute 110 can be reduced to 283 mm.

[0209] It can be seen that in this application, a profile similar to a spiral shell is constructed by multiple second arc segments 112, thereby realizing the bionic design of the volute 110. Thus, without sacrificing the aerodynamic performance of the volute 110, the size of the volute 110 can be reduced, the static pressure efficiency of the volute 110 can be improved, and further, the oil fume suction rate can be increased, the aerodynamic noise of the volute 110 can be reduced, providing convenient conditions for the miniaturization design of the volute 110.

[0210] As Figure 13 shown, in some embodiments of the present utility model, optionally, the second arc segment 112 includes: a first arc segment 1122; a second arc segment 1124; a third arc segment 1126; a fourth arc segment 1128. The first arc segment 1122, the second arc segment 1124, the third arc segment 1126, and the fourth arc segment 1128 are sequentially connected in a direction away from the impeller 120.

[0211] In this embodiment, the second arc segment 112 includes four segments: a first arc segment 1122, a second arc segment 1124, a third arc segment 1126, and a fourth arc segment 1128. Among them, the first arc segment 1122 is close to the impeller 120, the fourth arc segment 1128 is far from the impeller 120, the second arc segment 1124 and the third arc segment 1126 are located between the first arc segment 1122 and the fourth arc segment 1128, and the second arc segment 1124 is closer to the impeller 120 than the third arc segment 1126.

[0212] By limiting the number of the second arc segments 112 to four, the processing difficulty of the volute 110 can be reduced on the basis of meeting the requirements of improving the static pressure efficiency and noise reduction requirements, thereby reducing the production cost. At the same time, it can also provide convenient conditions for the miniaturization design of the volute 110, making the range hood assembly 100 applicable to the small-sized integrated stove 200.

[0213] As Figure 13 shown, in some embodiments of the present utility model, optionally, the outer diameter of the impeller 120 is D0; the radius of the first arc segment 1122 is r1, and D0 and r1 satisfy the relationship: 1.2 ≤ 2×r1÷D0 ≤ 1.5; the central angle of the first arc segment 1122 is γ1, 20° ≤ γ1 ≤ 35°; the radius of the second arc segment 1124 is r2, and D0 and r2 satisfy the relationship: 1 ≤ 2×r2÷D0 ≤ 1.3; the central angle of the second arc segment 1124 is γ2, 60° ≤ γ2 ≤ 98°; the radius of the third arc segment 1126 is r3, and D0 and r3 satisfy the relationship: 1.1 ≤ 2×r3÷D0 ≤ 1.5; the central angle of the third arc segment 1126 is γ3, 70° ≤ γ3 ≤ 115°; the radius of the fourth arc segment 1128 is r4, and D0 and r4 satisfy the relationship: 1.2 ≤ 2×r4÷D0 ≤ 1.6; the central angle of the fourth arc segment 1128 is γ4, 80° ≤ γ4 ≤ 125°.

[0214] In this embodiment, the profile of the volute 110 is composed of four tangent second arc segments 112. The design parameters of the specific four second arc segments 112 are as follows:

[0215] D0 is the outer diameter of the impeller 120. Specifically, D0 can be selected as 210 mm.

[0216] Taking c1 as the center, r1 as the radius, and γ1 as the central angle, the first arc segment 1122 can be constructed.

[0217] r1 is the radius of the first arc segment 1122, and 1.2 ≤ 2×r1÷D0 ≤ 1.5. Specifically, 1.214 ≤ 2×r1÷D0 ≤ 1.483 can be selected.

[0218] In a specific embodiment, 2×r1÷D0 is selected as 1.348, corresponding to r1 = 141.62 mm.

[0219] γ1 is the central angle of the first arc segment 1122, and 20° ≤ γ1 ≤ 35°. Specifically, 22.16° ≤ γ1 ≤ 33.24° can be selected.

[0220] In a specific embodiment, γ1 = 27.7°.

[0221] Taking c2 as the center, r2 as the radius, and γ2 as the central angle, the second arc segment 1124 can be constructed.

[0222] r2 is the radius of the second arc segment 1124, and 1 ≤ 2×r2÷D0 ≤ 1.3. Specifically, 1.039 ≤ 2×r2÷D0 ≤ 1.271 can be selected.

[0223] In a specific embodiment, 2×r2÷D0 is selected as 1.154, corresponding to r2 = 121.24 mm.

[0224] γ2 is the central angle of the second arc segment 1124, and 60° ≤ γ2 ≤ 98°. Specifically, 63.92° ≤ γ2 ≤ 95.88° can be selected.

[0225] In a specific embodiment, γ2 = 79.9°.

[0226] Taking c3 as the center, r3 as the radius, and γ3 as the central angle, the third arc segment 1126 can be constructed.

[0227] r3 is the radius of the third arc segment 1126, and 1.1 ≤ 2×r3÷D0 ≤ 1.5. Specifically, 1.169 ≤ 2×r3÷D0 ≤ 1.429 can be selected.

[0228] In a specific embodiment, 2×r3÷D0 is selected as 1.299, corresponding to r3 = 136.47 mm.

[0229] γ3 is the central angle of the third arc segment 1126, 70° ≤ γ3 ≤ 115°, and specifically, 73.60° ≤ γ3 ≤ 110.4° can be selected.

[0230] In a specific embodiment, γ3 = 92.0°.

[0231] Taking c4 as the center, r4 as the radius, and γ4 as the central angle, the fourth arc segment 1128 can be constructed.

[0232] r4 is the radius of the fourth arc segment 1128, 1.2 ≤ 2×r4÷D0 ≤ 1.6, and specifically, 1.232 ≤ 2×r4÷D0 ≤ 1.506 can be selected.

[0233] In a specific embodiment, 2×r4÷D0 is selected to be 1.369, corresponding to r4 = 143.79 mm.

[0234] γ4 is the central angle of the fourth arc segment 1128, 80° ≤ γ4 ≤ 125°, and specifically, 81.04° ≤ γ4 ≤ 121.56° can be selected.

[0235] In a specific embodiment, γ4 = 101.31°.

[0236] Specifically, by designing the profile line of the volute 110 according to the above parameters, it is possible to reduce the size of the volute 110 and improve the static pressure efficiency of the volute 110 without sacrificing the aerodynamic performance of the volute 110, thereby achieving the technical effects of improving the oil fume suction rate, reducing the aerodynamic noise of the volute 110, and providing convenient conditions for the miniaturization design of the volute 110.

[0237] As Figure 14 shown, in some embodiments of the present invention, optionally, the outer diameter of the impeller 120 is D0; one end of the plurality of second arc segments 112 away from the impeller 120 is the outer end, and the distance between the impeller 120 and the outer end in the radial direction of the impeller 120 is A, and A and D0 satisfy the relationship: 0.2 ≤ A÷D0 ≤ 0.35; the radius of the volute tongue 114 of the volute 110 is R4, and R4 and D0 satisfy the relationship: 0.02 ≤ R4÷D0 ≤ 0.05; one end of the plurality of second arc segments 112 close to the impeller 120 is the inner end, and the distance between the impeller 120 and the inner end in the radial direction of the impeller 120 is t, and t and D0 satisfy the relationship: 0.04 ≤ t÷D0 ≤ 0.08; the included angle between the outer ends of the plurality of second arc segments 112 and the volute tongue 114 is T1, 40° ≤ T1 ≤ 68°; the outward expansion angle of the diffuser section 116 of the volute 110 is B1, 19° ≤ B1 ≤ 35°; the width of the outlet of the diffuser section 116 is L, and L and D0 satisfy the relationship: 0.4 ≤ L÷D0 ≤ 0.7.

[0238] In this embodiment, D0 is the outer diameter of the impeller 120. Specifically, D0 can be selected as 210 mm.

[0239] On this basis, on the profile line of the volute 110, the end far from the impeller 120 is the outer end, and the end close to the impeller 120 is the inner end. The distance between the impeller 120 and the outer end in the radial direction of the impeller 120 is A, and A corresponds to the opening degree of the outlet of the volute 110.

[0240] Specifically, 0.2 ≤ A÷D0 ≤ 0.35, and specifically, 0.208 ≤ A÷D0 ≤ 0.312 can be selected.

[0241] In a specific embodiment, A÷D0 = 0.26, that is, A = 54.6 mm.

[0242] A volute tongue 114 is connected to the inner end of the profile line of the side wall of the volute 110, and the volute 110 compresses the oil fume through the volute tongue 114.

[0243] Specifically, the radius of the volute tongue 114 is R4, 0.02 ≤ R4÷D0 ≤ 0.05, and specifically, 0.02816 ≤ R4÷D0 ≤ 0.04224 can be selected.

[0244] In a specific embodiment, R4÷D0 = 0.0352, that is, R4 = 7.4 mm.

[0245] The distance between the inner ends of the profile lines of the impeller 120 and the volute 110 in the radial direction of the impeller 120 is t, and t corresponds to the minimum clearance between the volute tongue 114 and the impeller 120.

[0246] Specifically, 0.04 ≤ t÷D0 ≤ 0.08, and specifically, 0.04832 ≤ t÷D0 ≤ 0.07248 can be selected.

[0247] In a specific embodiment, t÷D0 = 0.0604, that is, t = 12.7 mm.

[0248] The included angle between the outer end of the profile line of the volute 110 and the volute tongue 114 is T1, and T1 corresponds to the position angle of the volute tongue 114.

[0249] Specifically, 40° ≤ T1 ≤ 68°, and specifically, 43.28° ≤ T1 ≤ 64.92° can be selected.

[0250] In a specific embodiment, T1 = 54.1°.

[0251] At the second end of the profile line of the volute 110 and on the downwind side of the volute tongue 114, a diffuser section 116 is provided. The diffuser section 116 forms the outlet of the volute 110. The oil fume drawn into the volute 110 by the rotating wind wheel is finally discharged from the volute 110 after being diffused and decelerated in the diffuser section 116. Among them, the outer diffusion angle of the diffuser section 116 relative to the opening degree A is B1, and the larger B1 is, the more obvious the effect of diffusing and decelerating the oil fume in the diffuser section 116 is.

[0252] Specifically, 19° ≤ B1 ≤ 35°, and specifically, 20.64° ≤ B1 ≤ 30.96° can be selected.

[0253] In a specific embodiment, B1 = 25.8°.

[0254] The width of the outlet of the diffuser section 116 is L. When the outer diffusion angle B1 is determined, the length of the diffuser section 116 and the width L of the outlet of the diffuser section 116 restrict each other.

[0255] Specifically, 0.4 ≤ L÷D0 ≤ 0.7, and specifically, 0.4352 ≤ L÷D0 ≤ 0.6528 can be selected.

[0256] In a specific embodiment, L÷D0 = 0.544, that is, L = 114.3 mm.

[0257] Specifically, by designing the volute 110, the volute tongue 114 and the diffuser section 116 according to the above parameters, the probability of the occurrence of vortex problems in the diffuser section 116 can be reduced without loss of the aerodynamic performance of the volute 110, the proportion of the low-speed area in the volute 110 can be reduced, and the proportion of the area with strong turbulent kinetic energy in the volute 110 can be reduced. Furthermore, the technical effects of improving the oil fume suction rate, reducing the aerodynamic noise of the volute 110, and providing convenient conditions for the miniaturization design of the volute 110 can be achieved.

[0258] As Figure 15 、 Figure 16 、 Figure 17 、 Figure 18 、 Figure 19 and Figure 20 shown, compared with the single-arc volute in the related art and the bionic multi-arc volute 110 of the present application, the vortex at the outlet of the diffuser of the single-arc volute is larger, the low-speed area is more, and the area with turbulent kinetic energy is more. While in the multi-arc volute 110 of the present application, the vortex is reduced, the proportion of the low-speed area is reduced, and the proportion of the area with strong turbulent kinetic energy is reduced.

[0259] As Figure 21 and Figure 22As shown, in some embodiments of the present utility model, optionally, the volute 110 includes an inlet 118. In the axial direction of the impeller 120, the inlet 118 is opposite to the impeller 120; in the direction approaching the impeller 120, the caliber of the inlet 118 gradually decreases; the inner surface of the inlet 118 is an arc surface.

[0260] In this embodiment, the inlet 118 is provided at the top of the volute 110. In the axial direction of the impeller 120, the inlet 118 and the impeller 120 are oppositely arranged, and the rotating impeller 120 can suck cooking fumes into the volute 110 through the inlet 118.

[0261] On this basis, the inner surface of the inlet 118 is an arc surface, and in the axial direction approaching the impeller 120, the caliber of the inlet 118 gradually decreases to form an inlet 118 with an arc shape and a gradually decreasing caliber.

[0262] The inlet 118 with an arc shape and a gradually decreasing caliber can play a role in guiding the airflow into the volute 110, so as to reduce the probability of backflow problems and cross-flow problems of the cooking fumes at the inlet 118, thereby reducing the backflow noise and cross-flow noise at the inlet 118, and improving the suction efficiency of the cooking fumes by reducing the flow loss.

[0263] On the other hand, the inlet 118 can reduce the resistance of the cooking fumes at the inlet 118 through the arc surface, so as to reduce the kinetic energy loss of the cooking fumes, thereby improving the suction efficiency of the cooking fumes.

[0264] As Figure 22 shown, in some embodiments of the present utility model, optionally, the outer diameter of the impeller 120 is D0, and the inner diameter of the impeller 120 is D1; the caliber of one end of the inlet 118 far from the impeller 120 is D3, and D3 and D0 satisfy the relationship: 0.88 ≤ D3÷D0 ≤ 1.03; the caliber of one end of the inlet 118 close to the impeller 120 is D4, and D4 and D1 satisfy the relationship: 0.97 ≤ D4÷D1 ≤ 1.07; in the radial direction of the impeller 120, the distance between the inlet 118 and the impeller 120 is h, and h and D1 satisfy the relationship: 0.01 ≤ h÷D1 ≤ 0.03; the radius of the inner surface of the inlet 118 is R5, and R5 and D1 satisfy the relationship: 0.04 ≤ R5÷D1 ≤ 0.07.

[0265] In this embodiment, D0 is the outer diameter of the impeller 120, and specifically D0 can be selected as 210 mm, and D1 is the inner diameter of the impeller 120, and specifically D1 can be selected as 182 mm.

[0266] On this basis, the caliber of one end of the inlet 118 far from the impeller 120 is D3, 0.88 ≤ D3÷D0 ≤ 1.03, and specifically 0.89 ≤ D3÷D0 ≤ 1.02 can be selected.

[0267] In a specific embodiment, D3÷D0 = 0.98, that is, D3 = 202 mm.

[0268] The diameter of the inlet 118 at one end close to the impeller 120 is D4, and 0.97 ≤ D4÷D1 ≤ 1.07. Specifically, 0.98 ≤ D4÷D1 ≤ 1.06 can be selected.

[0269] In a specific embodiment, D4 = 181 mm.

[0270] In the radial direction of the impeller 120, the distance h between the inlet 118 and the impeller 120 corresponds to the depth of the inlet 118. Among them, 0.01 ≤ h÷D1 ≤ 0.03. Specifically, 0.010682 ≤ h÷D1 ≤ 0.0218 can be selected.

[0271] In a specific embodiment, h÷D1 = 0.0109, that is, h = 2 mm.

[0272] The radius of the inner surface of the inlet 118 is R5, and 0.04 ≤ R5÷D1 ≤ 0.07. Specifically, 0.041538 ≤ R5÷D1 ≤ 0.064615 can be selected.

[0273] In a specific embodiment, R5÷D1 = 0.046154, that is, R5 = 8.4 mm.

[0274] Specifically, designing the inlet 118 according to the above parameters can strengthen the function of the inlet 118 to guide the air flow into the volute 110, so as to further reduce the probability of backflow problems and skew flow problems of the oil fume at the inlet 118, thereby reducing the backflow noise and skew flow noise at the inlet 118 and improving the suction efficiency of the oil fume.

[0275] On the other hand, designing the inlet 118 according to the above parameters can further reduce the resistance of the oil fume at the inlet 118, so as to reduce the kinetic energy loss of the oil fume, thereby improving the suction efficiency of the oil fume.

[0276] Such as Figure 23 、 Figure 24 、 Figure 25 、 Figure 26 、 Figure 27 and Figure 28 As shown, in the related art, the vertical collector has obvious backflow problems, obvious air leakage, serious flow loss, low speed in the collector, and small overall machine flow. According to the comparison results of the regions f1 and f2, and the comparison results of the regions g1 and g2, it can be seen that at the arc-shaped inlet 118 of the present application, the backflow and air leakage are small, so that the speed of the inlet 118 is greater than that of the collector in the related art, and the overall machine flow is also increased.

[0277] Such as Figure 1 、Figure 2 , Figure 4 and Figure 5 As shown in Figure 2 , Figure 4 and Figure 5 , a second aspect of the present utility model provides an integrated range hood 200, which includes: a main body 210, and a flue 2102 is included in the main body 210; a range hood assembly 100 as in any of the above embodiments, and the volute 110 is communicated with the flue 2102.

[0278] In this embodiment, an integrated range hood 200 provided with the range hood assembly 100 as in any of the above embodiments is defined. Therefore, the integrated range hood 200 has the advantages of the range hood assembly 100 as in any of the above embodiments and can achieve the technical effects that the range hood assembly 100 as in any of the above embodiments can achieve. To avoid repetition, it will not be elaborated here.

[0279] On this basis, the integrated range hood 200 includes a main body 210, and a flue 2102 is formed in the main body 210. The integrated range hood 200 can suck cooking fumes through the flue 2102 to collect the cooking fumes and prevent the cooking fumes from spreading everywhere. An air inlet is opened at the top of the main body 210, and the air inlet is communicated with the flue 2102. A grille 240 is embedded inside the air inlet to block foreign objects through the grille 240.

[0280] Wherein, the integrated range hood 200 further includes an oil-grease separation component 220 and a filtering component 230.

[0281] The oil-grease separation component 220 is arranged in the flue 2102, and the oil-grease separation component 220 is arranged opposite to the air inlet on the flue 2102. After the cooking fumes flow into the air inlet, they need to flow through the oil-grease separation component first. The oil-grease separation component 220 can separate the oil and water vapor mixed in the cooking fumes to complete the pre-stage oil-water separation of the cooking fumes, prevent the cooking fumes from carrying oil and water into the range hood assembly 100, thereby protecting the range hood assembly 100 from being polluted by oil and water on the one hand, extending the service life of the integrated range hood 200, on the other hand, preventing the oil and water accumulated in the flue 2102 from generating peculiar smells, and on the third hand, preventing the cooking fumes processed by the integrated range hood 200 from causing secondary pollution to the environment.

[0282] The filtering component 230 is installed in the flue 2102, and the cooking fumes flowing in the flue 2102 need to pass through the filtering component 230, so that the filtering component 230 filters the cooking fumes through the filtering parts to reduce the peculiar smell of the cooking fumes, prevent the cooking fumes from polluting the environment secondarily, and further achieve the technical effects of improving the reliability of the integrated range hood 200 and enhancing the user experience.

[0283] It should be clear that in the claims, the description and the drawings of the present utility model, the term "a plurality of" means two or more than two, unless there is an additional clear limitation. The orientation or positional relationship indicated by terms such as "upper", "lower", etc. is based on the orientation or positional relationship shown in the drawings. This is only for more convenient description of the present utility model and to make the description process simpler, rather than to indicate or imply that the device or element referred to must have the specific orientation described, be constructed and operated in a specific orientation. Therefore, these descriptions should not be construed as limitations on the present utility model; terms such as "connection", "installation", "fixation", etc. should all be understood in a broad sense. For example, "connection" can be a fixed connection between multiple objects, a detachable connection between multiple objects, or an integral connection; it can be a direct connection between multiple objects, or an indirect connection between multiple objects through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to the specific circumstances of the above data.

[0284] In the claims, the description and the drawings of the present utility model, the description of terms such as "an embodiment", "some embodiments", "specific embodiments", etc. means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present utility model. In the claims, the description and the drawings of the present utility model, the schematic expression of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0285] The above are only the preferred embodiments of the present utility model and are not used to limit the present utility model. For those skilled in the art, the present utility model can have various changes and modifications. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model shall be included within the protection scope of the present utility model.

Claims

1. A range hood assembly, characterized in that: include: snail shell; An impeller, the impeller is arranged in the volute, the impeller comprises a hub and a plurality of blades, and the plurality of blades are arranged around the hub; The impeller is intercepted by a first surface, the first surface is perpendicular to the axis of the impeller, and in the cross section, the blade includes a plurality of first arc segments, the plurality of first arc segments are connected in sequence, two adjacent first arc segments are tangent, and the radii of two adjacent first arc segments are different.

2. The range hood assembly according to claim 1, characterized in that: In a direction away from the wheel hub, the radii of the first arc segments gradually increase; In a direction away from the hub, central angles of the plurality of first arc segments gradually decrease.

3. The range hood assembly according to claim 2, characterized in that: The first arc segment comprises: The first section; The second section; The third section, the first section, the second section and the third section are connected in sequence in a direction away from the wheel hub.

4. The range hood assembly according to claim 3, characterized in that: The radius of the outer circle of the impeller is R0; The radius of the first section is R1, and R0 and R1 satisfy the relationship: 0.02≤R1÷R0≤0.04; The central angle of the first section is α1, 60°≤α1≤95°; The radius of the second section is R2, and R0 and R2 satisfy the relationship: 0.04≤R2÷R0≤0.08; The central angle of the second section is α2, 22°≤α2≤39°; The radius of the third section is R3, and R0 and R3 satisfy the relationship: 0.12≤R3÷R0≤0.2; The central angle of the third section is α3, 10°≤α3≤20°.

5. The range hood assembly according to claim 3, characterized in that: The outer diameter of the impeller is D0, the inner diameter of the impeller is D1, and D0 and D1 satisfy the relationship: 0.7≤D1÷D0≤0.99; The chord length of the blade is W, and W and D0 satisfy the relationship: 0.07≤W÷D0≤0.12; The end of the blade close to the hub is a first end, and the included angle between the tangent plane of the blade at the first end and the tangent plane of the inner circle of the impeller at the first end is β1, 38°≤β1≤60°; The end of the blade away from the hub is the second end, and the included angle between the section of the blade at the second end and the section of the outer circle of the impeller at the second end is β2, 143°≤β2≤179°.

6. The range hood assembly according to claim 1, characterized in that: The volute is cut through the first surface, and in the cross section, the volute includes a plurality of second arc segments, the plurality of second arc segments are sequentially connected, and two adjacent second arc segments are tangent to each other; In a direction away from the impeller, the central angles of the plurality of second arc segments gradually increase.

7. The range hood assembly according to claim 6, characterized in that: The second arc segment comprises: The first arc segment; The second arc segment; The third arc segment; A fourth arc segment, wherein the first arc segment, the second arc segment, the third arc segment and the fourth arc segment are sequentially connected in a direction away from the impeller.

8. The range hood assembly according to claim 7, characterized in that: The outer diameter of the impeller is D0; The radius of the first arc segment is r1, and D0 and r1 satisfy the relationship: 1.2≤2×r1÷D0≤1.5; The central angle of the first arc segment is γ1, 20°≤γ1≤35°; The radius of the second arc segment is r2, and D0 and r2 satisfy the relationship: 1≤2×r2÷D0≤1.3; The central angle of the second arc segment is γ2, 60°≤γ2≤98°; The radius of the third arc segment is r3, and D0 and r3 satisfy the relationship: 1.1≤2×r3÷D0≤1.5; The central angle of the third arc segment is γ3, 70°≤γ3≤115°; The radius of the fourth arc segment is r4, and D0 and r4 satisfy the relationship: 1.2≤2×r4÷D0≤1.6; The central angle of the fourth arc segment is γ4, 80°≤γ4≤125°.

9. The range hood assembly according to claim 7, characterized in that: The outer diameter of the impeller is D0; One end of the plurality of second arc segments away from the impeller is an outer end, a distance between the impeller and the outer end in the radial direction of the impeller is A, and A and D0 satisfy the relationship: 0.2≤A÷D0≤0.35; The radius of the volute tongue of the volute is R4, and R4 and D0 satisfy the relationship: 0.02≤R4÷D0≤0.05; One end of the plurality of second arc segments close to the impeller is an inner end, a distance between the impeller and the inner end in the radial direction of the impeller is t, and t and D0 satisfy the relationship: 0.04≤t÷D0≤0.08; The included angle between the outer ends of the plurality of second arc segments and the volute tongue is T1, 40°≤T1≤68°; The outward expansion angle of the expansion section of the volute is B1, 19°≤B1≤35°; The width of the outlet of the diffuser section is L, and L and D0 satisfy the relationship: 0.4≤L÷D0≤0.

7.

10. The range hood assembly according to claim 1, characterized in that: The volute comprises an inlet, and in the axial direction of the impeller, the inlet is opposite to the impeller; In the direction approaching the impeller, the diameter of the inlet gradually decreases; The inner surface of the inlet is a curved surface.

11. The range hood assembly according to claim 10, characterized in that: The outer diameter of the impeller is D0, and the inner diameter of the impeller is D1; The diameter of the inlet at the end away from the impeller is D3, and D3 and D0 satisfy the relationship: 0.88≤D3÷D0≤1.03; The diameter of the inlet at one end close to the impeller is D4, and D4 and D1 satisfy the relationship: 0.97≤D4÷D1≤1.07; In the radial direction of the impeller, the distance between the inlet and the impeller is h, and h and D1 satisfy the relationship: 0.01≤h÷D1≤0.03; The radius of the inner surface of the inlet is R5, and R5 and D1 satisfy the relationship: 0.04≤R5÷D1≤0.

07.

12. An integrated stove, characterized in that: include: A body, wherein the body includes a flue; The range hood assembly according to any one of claims 1 to 11, wherein the volute is connected to the flue.

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