Impeller and blower

Abstract

The utility model provides an impeller and a blower, and relates to the technical field of household appliances. The impeller comprises a hub and a plurality of blades arranged on one side of the hub. The shape of each blade is of a three-dimensional twisted structure. Each blade comprises a suction curved surface, a pressure curved surface, an upper curved surface, a lower curved surface and a trailing edge curved surface. The pressure curved surface and the suction curved surface intersect at the front edge of the blade to form a front edge line. And the pressure curved surface and the suction curved surface intersect with the trailing edge curved surface at the trailing edge of the blade. A plurality of noise reduction tooth grooves are formed in the curved surface of the tail edge of each blade in an inwards-concave mode. The noise reduction tooth grooves are formed in the curved surface of the tail edge, so that the problem that noise is large when the impeller operates can be solved, and the fluid dynamic performance of the impeller can also be improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to the technical field of household appliances, specifically relates to a kind of impeller and hair dryer. BACKGROUND

[0002] Impeller is the core moving part in fan, it plays the purpose of making gas obtain energy and thus achieving the purpose of compressing gas. The design of impeller plays a decisive role in the performance of fan.

[0003] The trailing edge of impeller blade is the last end edge of blade leeward or backflow surface, which is the position where fluid leaves the blade. The design of trailing edge has important influence on the performance and noise of impeller.

[0004] In the prior art, the trailing edge of blade is not reasonably arranged, and vortex and boundary layer separation are easily formed when airflow passes through the trailing edge, resulting in large noise. UTILITY MODEL CONTENT

[0005] The utility model aims to provide an impeller and hair dryer, which can improve the problem of large noise of impeller during operation and improve the fluid dynamics performance of impeller.

[0006] The embodiment of the utility model can be implemented as follows:

[0007] In a first aspect, the application provides an impeller, which comprises a hub and a plurality of blades arranged on one side of the hub.

[0008] The shape of the blade is a three-dimensional twisted structure.

[0009] The blade comprises a suction surface, a pressure surface, an upper surface, a lower surface and a trailing edge surface.

[0010] The pressure surface and the suction surface intersect with the upper surface at the top end of the blade; the pressure surface and the suction surface intersect with the lower surface at the bottom end of the blade; the pressure surface and the suction surface intersect at the leading edge of the blade to form a leading edge line; and the pressure surface and the suction surface intersect with the trailing edge surface at the trailing edge of the blade.

[0011] The trailing edge surface of the blade is concave inwardly and provided with a plurality of noise reduction tooth grooves.

[0012] In an optional embodiment, the noise reduction tooth grooves are triangular.

[0013] In an optional embodiment, the plurality of noise reduction tooth grooves are sequentially and continuously arranged, and a triangular convex tooth is formed between two adjacent noise reduction tooth grooves.

[0014] In an optional embodiment, an included angle between two side walls of the noise reduction tooth groove close to the lower curved surface is smaller than an included angle between two side walls of the noise reduction tooth groove close to the upper curved surface.

[0015] and / or,

[0016] The depth of the noise reduction tooth groove ranges from 0.5 mm to 1 mm.

[0017] and / or,

[0018] All tooth tips of the triangular convex teeth are on a concave spline curve.

[0019] In an optional embodiment, an inlet angle at any point on the leading edge line ranges from -45° to -7°, and an outlet angle ranges from 15° to 30°.

[0020] In an optional embodiment, in the height direction of the blade, the leading edge line has a first control point, a second control point, a third control point, a fourth control point, a fifth control point and a sixth control point arranged in equal intervals from low to high;

[0021] At the first control point, the inlet angle ranges from -45° to -40°, and the outlet angle ranges from 15° to 20°; at the second control point, the inlet angle ranges from -35° to -30°, and the outlet angle ranges from 18° to 23°; at the third control point, the inlet angle ranges from -34° to -32°, and the outlet angle ranges from 19° to 22°; at the fourth control point, the inlet angle ranges from -23° to -28°, and the outlet angle ranges from 21° to 24°; at the fifth control point, the inlet angle ranges from -17° to -13°, and the outlet angle ranges from 23° to 28°; at the sixth control point, the inlet angle ranges from -10° to -7°, and the outlet angle ranges from 25° to 30°.

[0022] In an optional embodiment, the first control point is the intersection of the leading edge line and the lower curved surface, and the sixth control point is the intersection of the leading edge line and the upper curved surface.

[0023] The second control point, the third control point, the fourth control point and the fifth control point are arranged in equal intervals from low to high on the leading edge line.

[0024] In a second aspect, the application provides a hair dryer, comprising a motor, a shell and the impeller of any one of the above.

[0025] The shell is provided with a cavity, an air inlet and an air outlet which communicate with the cavity.

[0026] The motor is installed in the cavity and fixed to the shell, and the hub is fixedly connected to an output shaft of the motor;

[0027] The motor operates to drive the impeller to rotate, so that external air is sucked into the cavity through the air inlet and discharged through the air outlet.

[0028] In an optional embodiment, the hair dryer further comprises a support seat, an electric heating wire and a plurality of heat insulation sheets;

[0029] The support seat is arranged in the cavity, and the plurality of heat insulation sheets are arranged along the circumference of the support seat and spaced apart from each other on the support seat, and a flow channel is formed between the outer side of the support seat and the inner wall of the shell;

[0030] The length direction of the heat insulation sheet is parallel to the axial direction of the support seat;

[0031] The electric heating wire is wound around the outer periphery of the heat insulation sheet;

[0032] The length of the heat insulation sheet is negatively correlated with the depth of the noise reduction tooth groove.

[0033] In an optional embodiment, the length of the heat insulation sheet is inversely proportional to the depth of the noise reduction tooth groove;

[0034] and / or,

[0035] The length of the heat insulation sheet ranges from 33 mm to 40 mm.

[0036] The impeller and the hair dryer provided by the embodiments of the present application have the following beneficial effects:

[0037] The present application sets a plurality of noise reduction tooth grooves inwards on the trailing edge curved surface of the blade. When the impeller operates, the noise reduction tooth grooves can reduce vortex generation at the trailing edge of the blade, change the frequency of the vortex and reduce the separation of the boundary layer, so as to make the flow field relatively smooth, thereby reducing the noise during the operation of the impeller and improving the fluid dynamics performance of the impeller. BRIEF DESCRIPTION OF DRAWINGS

[0038] In order to more clearly illustrate the technical scheme of the embodiments of the present application, the following will briefly introduce the drawings needed to be used in the embodiments. It should be understood that the following drawings only show some embodiments of the present application, and therefore should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can also be obtained without creative labor on the basis of these drawings.

[0039] Figure 1 The structure diagram of the hair dryer provided by the embodiments of the present application is shown in the figure;

[0040] Figure 2 A partial sectional view schematic diagram of the hair dryer is provided for the embodiment of the utility model;

[0041] Figure 3 An explosion structure schematic diagram of the hair dryer is provided for the embodiment of the utility model;

[0042] Figure 4 A motor installation structure schematic diagram of the hair dryer is provided for the embodiment of the utility model;

[0043] Figure 5 A structure schematic diagram of the middle shell of the hair dryer is provided for the embodiment of the utility model;

[0044] Figure 6 A structure schematic diagram of the impeller is provided for the embodiment of the utility model;

[0045] Figure 7 A structure schematic diagram of another view of the impeller is provided for the embodiment of the utility model;

[0046] Figure 8 A suction surface one side projection schematic diagram of the blade of the impeller is provided for the embodiment of the utility model;

[0047] Figure 9 A pressure surface one side shaft side schematic diagram of the blade of the impeller is provided for the embodiment of the utility model;

[0048] Figure 10 A shaft side schematic diagram of the blade of the impeller is provided for the embodiment of the utility model;

[0049] Figure 11 A fluid simulation schematic diagram before the value range of the inlet angle and the outlet angle of each point on the leading edge line is optimized is provided;

[0050] Figure 12 A fluid simulation schematic diagram after the value range of the inlet angle and the outlet angle of each point on the leading edge line is optimized is provided;

[0051] Figure 13 A test characteristic curve comparison diagram of the impeller of the traditional structure and the impeller provided by the application is provided;

[0052] Figure 14 A test characteristic curve comparison diagram of the inlet angle and the outlet angle in the value range and not in the value range is provided.

[0053] Icon: 100 - impeller; 110 - hub; 111 - conical surface; 130 - blade; 131 - suction surface; 132 - pressure surface; 133 - upper surface; 134 - lower surface; 135 - trailing edge surface; 136 - leading edge line; 137 - noise reduction tooth slot; 138 - triangular convex tooth; 139 - first control point; 141 - second control point; 142 - third control point; 143 - fourth control point; 144 - fifth control point; 145 - sixth control point; 300 - blower; 310 - motor; 330 - shell; 331 - cavity; 333 - air inlet; 335 - air outlet; 337 - front shell; 339 - middle shell; 341 - rear shell; 343 - outer shell; 345 - motor seat; 347 - guide vane; 348 - flow channel; 350 - support seat; 370 - heat insulation sheet. DETAILED DESCRIPTION

[0054] The trailing edge of the impeller blade is the last end edge of the blade leeward surface or back flow surface, and is the position where the fluid finally leaves the blade. The design of the trailing edge has an important influence on the performance and noise of the impeller. In the prior art, the trailing edge of the blade is not reasonably arranged, and when the air flow passes through the trailing edge, vortexes are easily formed and the boundary layer is separated, resulting in relatively large noise.

[0055] In view of the above problems, the utility model provides a kind of impeller and blower, which can improve the problem of large noise of impeller during operation, and also improve the fluid dynamics performance of impeller.

[0056] To make the purpose, technical scheme and advantages of the embodiments of the utility model clearer, the technical scheme in the embodiments of the utility model will be described clearly and completely below with reference to the drawings in the embodiments of the utility model. Obviously, the described embodiments are part of the embodiments of the utility model, not all. The components of the embodiments of the utility model described and shown in the drawings can be arranged and designed in various different configurations.

[0057] Therefore, the following detailed description of the embodiments of the utility model provided in the drawings is not intended to limit the scope of the claimed utility model, but only represents selected embodiments of the utility model. Based on the embodiments in the utility model, all other embodiments obtained by those skilled in the art without creative labor are within the scope of protection of the utility model.

[0058] It should be noted that: similar signs and letters represent similar items in the following drawings, so once an item is defined in one drawing, it does not need to be further defined and explained in subsequent drawings.

[0059] In the description of the utility model, it needs to explain, if the terms "upper", "lower", "inner", "outer" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawing, or the orientation or positional relationship of the utility model product when it is usually placed, only for the convenience of describing the utility model and simplifying the description, and not indicating or implying that the device or element indicated must have a specific orientation, structure and operation, therefore, it cannot be understood as a limitation on the utility model.

[0060] In addition, if the terms "first", "second" and the like are only used for differentiation, and cannot be understood as indicating or implying relative importance.

[0061] It should be noted that the features in the embodiments of the utility model can be combined with each other without conflict.

[0062] The overall structure, working principle and technical effects of the impeller and hair dryer provided by the utility model are described in detail below through embodiments and in combination with the drawings.

[0063] Please refer to Figures 1 to 5 The embodiment provides a hair dryer 300, which comprises a motor 310, a shell 330 and an impeller 100. The shell 330 is provided with a cavity 331, an air inlet 333 and an air outlet 335 which are communicated with the cavity 331. The motor 310 is installed in the cavity 331 and fixed with the shell 330. The impeller 100 is fixedly connected with the output shaft of the motor 310. The motor 310 can drive the impeller 100 to rotate to suck external air into the cavity 331 through the air inlet 333 and send out the external air through the air outlet 335.

[0064] Specifically, the shell 330 comprises a front shell 337, a middle shell 339 and a rear shell 341. The front shell 337 and the rear shell 341 are installed at two ends of the middle shell 339. The air inlet 333 is generally arranged on the rear shell 341 and has the function of collecting air. The motor 310 is installed in the middle shell 339, and the air outlet 335 is arranged on the end face of the front shell 337. The motor 310 drives the impeller 100 to rotate, and the impeller 100 can suck external air into the middle shell 339 through the air inlet 333, and then send out the external air through the air outlet 335 after compression and acceleration.

[0065] Please refer to Figures 1 to 5 In detail, the middle shell 339 comprises an outer shell 343, a motor seat 345 and a plurality of guide vanes 347. The outer shell 343 is in a hollow cylindrical shape. The motor seat 345 is arranged in the outer shell 343, and the outer periphery of the motor seat 345 is arranged with a plurality of guide vanes 347 at equal intervals in the circumferential direction, and the guide vanes 347 are all connected with the inner wall of the outer shell 343.

[0066] The cross section of the guide vane 347 is a spline curve. The guide vane 347 is curved in the direction of rotation of the impeller 100 in the direction from the rear shell 341 to the front shell 337. That is, the end of the guide vane 347 close to the impeller 100 is curved clockwise.

[0067] Please refer to Figures 1 to 5 Specifically, the value of the inlet angle of the front edge of the guide vane 347 is in the range of 28° to 32°, and the value of the inlet angle of the tail edge is 0°. That is, the tail of the guide vane 347 is perpendicular to the axial direction of the impeller 100.

[0068] Since the airflow is accelerated after passing through the impeller 100, there is not only an axial velocity, but also a large circumferential velocity. The airflow of the middle shell 339 of the traditional structure will have a significant impact loss when entering, thereby having a great negative impact on the performance of the hair dryer 300. In the present embodiment, the guide vane 347 is arranged in the gap between the motor base 345 and the outer shell 343. The guide vane 347 can effectively reduce the flow loss of the gas passing through the motor base 345 and the outer shell 343, and inhibit the development of the flow separation vortex formed on the inner side of the channel of the motor base 345 and the outer shell 343, thereby improving the working efficiency of the hair dryer 300. Secondly, the guide vane 347 can also be used as a mechanical connecting component between the motor base 345 and the outer shell 343, thereby improving the structural stability.

[0069] Please refer to Figures 1 to 5 Secondly, in the present embodiment, the hair dryer 300 further comprises a support base 350, an electric heating wire (not shown in the figure) and a plurality of heat insulation sheets 370. The support base 350 is installed at the rear end of the motor base 345 and abuts against the rear shell 341. The plurality of heat insulation sheets 370 are installed on the support base 350 in a circumferential direction of the support base 350 to perform heat insulation. The electric heating wire is wound around the outer periphery of the heat insulation sheet 370. The electric heating wire can heat the passing airflow.

[0070] In the present embodiment, the impeller 100 comprises a hub 110 and a plurality of blades 130 arranged on one side of the hub 110. The shape of the blade 130 is a three-dimensional twisted structure. The blade 130 comprises a suction surface 131, a pressure surface 132, an upper surface 133, a lower surface 134 and a tail edge surface 135. The pressure surface 132 and the suction surface 131 intersect with the upper surface 133 at the top end of the blade 130. The pressure surface 132 and the suction surface 131 intersect with the lower surface 134 at the bottom end of the blade 130. The pressure surface 132 and the suction surface 131 intersect at the leading edge of the blade 130 to form a leading edge line 136. The pressure surface 132 and the suction surface 131 intersect with the tail edge surface 135 at the tail edge of the blade 130. The tail edge surface 135 is concavely provided with a plurality of noise reduction tooth grooves 137.

[0071] The embodiment sets the plurality of noise reduction tooth grooves inwards on the trailing edge curve 135 of the blade 130. When the impeller 100 is running, the noise reduction tooth grooves can reduce vortex generation at the trailing edge of the blade 130, change the frequency of the vortex, and reduce the separation of the boundary layer, thereby making the flow field relatively smooth, so as to reduce the noise when the impeller 100 is running and improve the fluid dynamics performance of the impeller 100.

[0072] It should be further noted that the suction surface 131 of the blade 130 refers to the side of the blade 130 with lower pressure. Usually, this side is on the concave surface of the blade 130, i.e. the upstream side in the direction of fluid flow. Opposite the suction surface 131 is the pressure surface 132, which is the side of the blade 130 with higher pressure, usually on the convex surface of the blade 130, i.e. the downstream side in the direction of fluid flow. There is a transition zone between the pressure surface 132 and the suction surface 131, which is called the leading edge and the trailing edge of the blade 130. The leading edge is the part first contacted by the fluid, and the trailing edge is the part last left by the fluid. The upper curve 133 corresponds to the blade tip of the blade 130. The lower curve 134 corresponds to the blade root of the blade 130. The leading edge line 136 is the intersection line of the pressure surface 132 and the suction surface 131 at the front end of the blade 130, which is the part first contacted by the fluid. The leading edge line 136 is usually a curved line connecting the leading edge points of the blade 130. The trailing edge curve 135 refers to the curve at the trailing edge of the blade 130.

[0073] Further, the noise reduction tooth grooves 137 are triangular. The sharp edges of the triangular noise reduction tooth grooves 137 can more effectively break up large vortexes and reduce noise. Disturbances can also be introduced in multiple directions, further smoothing the flow field. Secondly, symmetry can ensure uniform distribution of airflow at the trailing edge, reducing irregular vortex generation.

[0074] In some embodiments of the present application, the noise reduction tooth grooves 137 can be equilateral triangles. Equilateral triangles have high symmetry, each angle is 60 degrees, and each side is equal in length. Symmetry ensures uniform distribution of airflow at the trailing edge, reduces irregular vortex generation, and improves flow field stability. Uniform disturbances can more effectively break up large vortexes and reduce noise. The sharp edges of the equilateral triangle can improve the flow characteristics of the boundary layer and reduce airflow separation at the trailing edge. Reducing separation can reduce irregular motion of the airflow and reduce separation noise. The geometry of the equilateral triangle can smooth the flow field and reduce irregular motion of the airflow.

[0075] Of course, in other embodiments of the present application, in order to take into account other aspects of the performance of the impeller 100, such as wind pressure, wind volume, etc., other acute or obtuse triangles can also be used. The angles of each noise reduction tooth groove 137 can also be different.

[0076] In the embodiment, the plurality of noise reduction tooth grooves 137 are arranged in sequence and continuously, and a triangular convex tooth 138 is formed between two adjacent noise reduction tooth grooves 137. Such arrangement forms a sawtooth shape on the trailing edge curved surface 135 of the blade 130.

[0077] The plurality of noise reduction tooth grooves 137 are arranged continuously, so that by introducing a slight irregular structure at the trailing edge, the large vortex flow in the airflow can be dispersed and decomposed into smaller vortex flows. The small vortex flow has lower energy and produces less noise.

[0078] In the embodiment, the included angle between the two side walls of the noise reduction tooth groove 137 near the lower curved surface 134 is smaller than the included angle between the two side walls of the noise reduction tooth groove 137 near the upper curved surface 133.

[0079] The angle of the noise reduction tooth groove 137 in the upper region is large, and the angle of the noise reduction tooth groove 137 in the lower region is small. The noise reduction tooth groove 137 with a larger angle in the upper region can better guide the airflow to flow upward, and the noise reduction tooth groove 137 with a smaller angle in the lower region can better guide the airflow to flow downward. Overall, the distribution of the airflow at the trailing edge can be optimized, the generation of irregular vortex flow can be reduced, and the uniformity and stability of the flow field can be improved.

[0080] In the embodiment, the angle of the noise reduction tooth groove 137 in the lower region is an acute angle, and increases sequentially upward until the uppermost one is an obtuse angle. The included angle is in the range of 66° to 106°.

[0081] It should be noted that the two side surfaces of the noise reduction tooth groove 137 forming the included angle are spline surfaces, which can more smoothly guide the flow and further reduce the generation of noise.

[0082] In the embodiment, the depth of the noise reduction tooth groove 137 is in the range of 0.5mm to 1mm.

[0083] The depth of the noise reduction tooth groove 137 is set in the range of 0.5mm to 1mm. The aerodynamic performance of the blade 130 can be significantly improved and the noise can be reduced.

[0084] In the embodiment, the tooth tips of all the triangular convex teeth 138 are on a concave spline curve (as shown by the dashed line in Figure 8 Before the noise reduction tooth groove 137 is formed on the trailing edge curved surface 135, the blade 130 has a blade shape in which the middle region of the trailing edge curved surface 135 is a concave spline surface. Such arrangement can significantly improve the aerodynamic performance of the blade 130 and reduce noise. The concave design changes the flow characteristics of the airflow, reduces vortex generation and boundary layer separation, and thus achieves the purpose of optimizing performance.

[0085] Please refer to 1 to 10, in this embodiment, the specific heat insulation sheet 370 is mica sheet. A plurality of heat insulation sheets 370 are arranged along the circumference of the support seat 350 and are arranged in the support seat 350, the outer side of the support seat 350 and the inner wall of the shell 330 form a flow channel 348, the impeller 100 rotates the airflow flowing from the air inlet 333, which can flow forward through the flow channel 348. The length direction of the heat insulation sheet 370 is parallel to the axial direction of the support seat 350. The length of the heat insulation sheet 370 is negatively correlated with the depth of the noise reduction tooth groove 137.

[0086] The length of the heat insulation sheet 370 determines the size of the along-the-way loss of the airflow and the development degree of the vortex structure in the flow channel 348. However, the flow guiding effect of the heat insulation sheet 370 that is too short on the airflow is limited, which causes the airflow to still have a relatively large circumferential velocity. The length of the heat insulation sheet 370 that is too large causes the vortex structure in the flow channel 348 to develop obviously in the flow direction. According to the vortex size caused by the concave structure at the trailing edge of the blade 130, a suitable length of the heat insulation sheet 370 corresponding to the vortex size is matched, so as to ensure the operation efficiency of the hair dryer 300.

[0087] Specifically, the length of the heat insulation sheet 370 is inversely proportional to the depth of the noise reduction tooth groove 137. The length of the heat insulation sheet 370 is in the range of 33 mm to 40 mm. Such setting and value can better improve the fluid dynamics performance and noise reduction performance of the hair dryer 300.

[0088] Please refer to Figures 6 to 10 In this embodiment, the value range of the inlet angle at any point on the leading edge line 136 is -45° to -7°, and the value range of the outlet angle is 15° to 30°.

[0089] In this embodiment, the value range of the inlet angle at any point on the leading edge line 136 of the blade 130 of the impeller 100 is set to -45° to -7°, and the value range of the outlet angle is set to 15° to 30°. Through flow field analysis, it can be obtained that the improved impeller 100 not only suppresses the vortex structure on the surface of the blade 130, but also weakens the axial movement of the airflow at the top of the blade 130, thereby enhancing the axial doing function of the impeller 100 on the airflow.

[0090] It should be noted that the inlet angle and the outlet angle of each point on the leading edge line 136 are important parameters for describing the geometric characteristics and fluid flow characteristics of the blade 130. These angles directly affect the aerodynamic performance and efficiency of the blade 130. The inlet angle refers to the angle of the fluid entering the leading edge of the blade 130 relative to the tangent direction of the leading edge line 136 of the blade 130. The inlet angle can be measured by the included angle between the fluid velocity vector and the tangent direction of the leading edge line 136. The inlet angle directly affects the flow conditions when the fluid enters the blade 130, and the optimization of the inlet angle helps to smooth the incoming airflow and reduce turbulence and resistance. The outlet angle refers to the angle of the fluid leaving the trailing edge of the blade 130 relative to the tangent direction of the trailing edge line of the blade 130. The outlet angle can be measured by the included angle between the fluid velocity vector and the tangent direction of the trailing edge line.

[0091] Please refer to Figure 11 and Figure 12 , Figure 11 is a fluid simulation diagram of the blade 130 before the range of values of the inlet angle and the outlet angle of each point on the leading edge line 136 of the blade 130 is optimized. Figure 12 is a fluid simulation diagram of the blade 130 after the range of values of the inlet angle and the outlet angle of each point on the leading edge line 136 of the blade 130 is optimized. Compared with Figure 1 and Figure 2 , it can be clearly seen that the optimized blade 130 has fewer vortexes on the surface and the axial movement of the airflow at the top of the blade 130 is weakened, thereby enhancing the axial work function of the impeller 100 on the airflow.

[0092] Please refer to Figures 6 to 10 , specifically, in the height direction of the blade 130, the leading edge line 136 has a first control point 139, a second control point 141, a third control point 142, a fourth control point 143, a fifth control point 144 and a sixth control point 145 arranged in sequence from low to high. At the first control point 139, the range of values of the inlet angle is -45° to -40°, and the range of values of the outlet angle is 15° to 20°. At the second control point 141, the range of values of the inlet angle is -35° to -30°, and the range of values of the outlet angle is 18° to 23°. At the third control point 142, the range of values of the inlet angle is -34° to -32°, and the range of values of the outlet angle is 19° to 22°. At the fourth control point 143, the range of values of the inlet angle is -23° to -28°, and the range of values of the outlet angle is 21° to 24°. At the fifth control point 144, the range of values of the inlet angle is -17° to -13°, and the range of values of the outlet angle is 23° to 28°. At the sixth control point 145, the range of values of the inlet angle is -10° to -7°, and the range of values of the outlet angle is 25° to 30°.

[0093] The embodiment can improve the vortex problem to improve the axial work function of the impeller 100 on the air flow by optimizing the value range of the inlet angle and the outlet angle at different control points.

[0094] In the embodiment, the first control point 139, the second control point 141, the third control point 142, the fourth control point 143, the fifth control point 144 and the sixth control point 145 are arranged at equal intervals.

[0095] The embodiment arranges the control points at equal intervals, so that the vortex problem can be improved to improve the axial work function of the impeller 100 on the air flow, and the air volume and air pressure can be improved.

[0096] Please refer to Figures 6 to 10 , in detail, the blade 130 further comprises an upper curved surface 133 and a lower curved surface 134, the upper end of the pressure curved surface 132 and the suction curved surface 131 intersects with the upper curved surface 133, and the lower end of the pressure curved surface 132 and the suction curved surface 131 intersects with the lower curved surface 134. The first control point 139 is the intersection of the leading edge line 136 and the lower curved surface 134, and the sixth control point 145 is the intersection of the leading edge line 136 and the upper curved surface 133. The second control point 141, the third control point 142, the fourth control point 143 and the fifth control point 144 are arranged at equal intervals from bottom to top on the leading edge line 136.

[0097] It can be understood that the first control point 139 and the sixth control point 145 are two end points of the leading edge line 136. The second control point 141, the third control point 142, the fourth control point 143 and the fifth control point 144 divide the leading edge line 136 into five equal length segments.

[0098] It should be noted that the leading edge line 136 is curved in three-dimensional space. The leading edge line 136 can be obtained by connecting the first control point 139, the second control point 141, the third control point 142, the fourth control point 143 and the fifth control point 144 in turn. The upper curved surface 133 corresponds to the blade tip of the blade 130, and the lower curved surface 134 corresponds to the blade root of the blade 130.

[0099] Please refer to Figures 6 to 10 , in a side view, it can be seen that the leading edge line 136 extends reversely curved from low to high in the height direction of the blade 130 to the trailing edge. It can be seen that the lower part area is slightly concave, and the upper part area is convex. The bottom of the leading edge line 136 is directly connected with the hub 110.

[0100] In some embodiments of the present application, the first control point 139, the second control point 141, the third control point 142, the fourth control point 143, the fifth control point 144 and the sixth control point 145 are the intersection points of the cross section at 0%, 20%, 40%, 60%, 80%, 100% of the height direction of the blade 130 and the leading edge line 136 respectively.

[0101] Optionally, the inlet angle at the first control point 139 is -43°, and the outlet angle is 17°. The inlet angle at the second control point 141 is -34°, and the outlet angle is 18°. The inlet angle at the third control point 142 is -33.1°, and the outlet angle is 19.2°. The inlet angle at the fourth control point 143 is -25.5°, and the outlet angle is 21.7°. The inlet angle at the fifth control point 144 is -16°, and the outlet angle is 23.5°. The inlet angle at the sixth control point 145 is -9.1°, and the outlet angle is 26°.

[0102] In this embodiment, the angles of the controls are optimized by being arranged at equal intervals in the height direction of the blade 130, so that the problem of vortex can be further improved, the axial working capacity of the impeller 100 on the airflow is improved, and the air volume and air pressure are further improved.

[0103] Optionally, the inlet angle at the first control point 139 is -42°, and the outlet angle is 18°. The inlet angle at the second control point 141 is -33.5°, and the outlet angle is 19.5°. The inlet angle at the third control point 142 is -33°, and the outlet angle is 20.7°. The inlet angle at the fourth control point 143 is -27°, and the outlet angle is 22.4°. The inlet angle at the fifth control point 144 is -15.5°, and the outlet angle is 24.5°. The inlet angle at the sixth control point 145 is -8°, and the outlet angle is 27.5°.

[0104] In this embodiment, the angles of the controls are optimized by being arranged at equal intervals in the height direction of the blade 130, so that the problem of vortex can be further improved, the axial working capacity of the impeller 100 on the airflow is improved, and the air volume and air pressure are further improved.

[0105] Optionally, the inlet angle at the first control point 139 is -40°, and the outlet angle is 19.7°. The inlet angle at the second control point 141 is -31.3°, and the outlet angle is 21.5°. The inlet angle at the third control point 142 is -32.5°, and the outlet angle is 22°. The inlet angle at the fourth control point 143 is -23°, and the outlet angle is 23.8°. The inlet angle at the fifth control point 144 is -13°, and the outlet angle is 26°. The inlet angle at the sixth control point 145 is -7°, and the outlet angle is 29°.

[0106] The embodiment optimizes the controlled angles arranged at equal intervals in the height direction of the blade 130, thereby further improving the vortex problem, improving the axial working capacity of the impeller 100 on the airflow, and further improving the air volume and air pressure.

[0107] In the embodiment, the center line length of the blade 130 is 24.15 mm at the first control point 139. The center line length of the blade 130 is 22.25 mm at the second control point 141. The center line length of the blade 130 is 20.41 mm at the third control point 142. The center line length of the blade 130 is 19.58 mm at the fourth control point 143. The center line length of the blade 130 is 19.32 mm at the fifth control point 144. The center line length of the blade 130 is 19.1 mm at the sixth control point 145.

[0108] The embodiment sets the center line length of the blade 130 at the corresponding control point to the corresponding value described above, thereby further improving the vortex problem, improving the axial working capacity of the impeller 100 on the airflow, and further improving the air volume and air pressure.

[0109] Please refer to Figures 6 to 10 In the embodiment, the hub 110 is provided with a conical surface 111 on one side, and the blade 130 includes nine blades 130 arranged at equal intervals on the conical surface 111, and the lower curved surface 134 is coplanar with the conical surface 111.

[0110] The embodiment sets the one side of the hub 110 provided with the blade 130 as the conical surface 111, thereby reducing the turbulence and resistance of the airflow. The blade 130 is provided with nine blades, thereby providing greater air pressure.

[0111] It can be understood that the lower curved surface 134 is coplanar with the conical surface 111, which means that the blade 130 is intercepted by the conical surface 111 of the hub 110, forming the lower curved surface 134 of the blade 130.

[0112] Further, the upper curved surface 133 extends downwardly and curvedly from a section connected with the leading edge of the blade 130 to an end connected with the trailing edge of the blade 130. The downwardly and curvedly extending upper curved surface 133 of the blade 130 can improve the fluid flow efficiency, reduce flow separation, optimize pressure distribution, improve the lift and thrust of the blade 130, reduce vibration and noise, and improve structural strength.

[0113] In one view of the impeller 100, the upper curved surface 133 is a three-dimensional curved surface of a spiral shape, and the curvature gradually decreases in the direction of the trailing edge. That is, the portion of the upper curved surface 133 close to the leading edge is more curved, and the portion close to the trailing edge is more smooth. In addition, the portion of the upper curved surface 133 close to the leading edge has a slight inclination toward one side of the pressure curved surface 132, and the inclination angle in this direction gradually decreases in the manner toward the trailing edge.

[0114] Further, the blade 130 is a three-dimensional twisted shape of a backward bending type. The provision of the blade 130 in the three-dimensional twisted shape of the backward bending type in the embodiment can improve the efficiency, increase the flow rate, improve the flow stability, and reduce the noise.

[0115] In the embodiment, the trailing edge of the blade 130 is concave to form a curved surface, which can reduce the noise.

[0116] Please refer to Figure 13 , Figure 13 The test characteristic curve comparison diagram of the impeller 100 of the traditional structure and the impeller 100 improved in the embodiment of the utility model is shown in FIG. 5. In FIG. 5, Figure 5 the horizontal axis in FIG. 5 is the rotating speed of the impeller 100, the right vertical axis is the air volume of the blower 300, and the left vertical axis is the air pressure.

[0117] As can be seen from FIG. 5, Figure 13 the air volume and the air pressure of the blower 300 provided in the embodiment are obviously greater than those of the blower 300 using the traditional impeller 100 at the same rotating speed. Although the air pressure and the air volume of the blower 300 provided in the embodiment are greatly improved compared with those of the blower 300 using the traditional impeller 100, the noise of the blower 300 provided in the embodiment is not greatly increased compared with that of the traditional blower 300. In particular, as the rotating speed increases, the difference between the two in terms of noise gradually decreases and even becomes the same. It can be seen that the impeller 100 provided in the embodiment has the effect of reducing noise.

[0118] It should be noted that the air pressure and the air volume of the blower 300 are important indicators for measuring the performance of the blower 300, and the noise is one of the key factors affecting the user experience. The increase in the air pressure and the air volume is often accompanied by an increase in the noise, because the increase in the air pressure and the air volume usually requires a higher rotating speed and a stronger airflow. The air volume of the blower 300 provided in the embodiment is better than 5 or so, and the air pressure is better than 4 or so, and the noise is the same when the rotating speed of the impeller 100 is 20000 rpm. It can be seen that the comprehensive performance of the blower 300 provided in the embodiment is stronger.

[0119] Please refer to Figure 14 , Figure 14is the inlet angle and the outlet angle of each control point of the blade 130 of the impeller 100 of the hair dryer 300, and the test characteristic curve of the hair dryer 300 provided by the structure of the present embodiment is compared. Among them, Figure 6 The horizontal axis in is the rotating speed of the impeller 100, the right vertical axis is the air volume of the hair dryer 300, and the left vertical axis is the air pressure and the noise. From Figure 6 It can be seen that, at any rotating speed, the air volume and the air pressure of the hair dryer 300 provided by the present embodiment are superior to those of the hair dryer 300 of the structure not within the parameter range, and the noise of the hair dryer 300 provided by the present embodiment is also smaller at the same rotating speed.

[0120] It should be noted that the structure not within the parameter range means that the value range of the inlet angle of any point on the leading edge line 136 of the blade 130 of the impeller 100 is not within-45° to-7°, and the value range of the outlet angle is not within 15°-30°. In the case that the other structures of the blade 130 are basically the same.

[0121] It can be understood that the impeller 100 provided by the present embodiment can also be applied in other household appliances or devices in other fields to make air supply. The present application does not limit that the impeller 100 can only be applied in the hair dryer 300.

[0122] In summary, the impeller 100 and the hair dryer 300 provided by the present embodiment set the plurality of noise reduction tooth grooves 137 inwardly concave on the trailing edge curved surface 135 of the blade 130, which can reduce the vortex generation at the trailing edge of the blade, change the frequency of the vortex, and reduce the separation of the boundary layer when the impeller 100 operates, so as to make the flow field relatively smooth, thereby reducing the noise when the impeller 100 operates and improving the fluid dynamics performance of the impeller 100.

[0123] The above is only a specific embodiment of the present application, but the protection scope of the present application is not limited to this. Any person skilled in the art can easily think of changes or replacements within the technical range disclosed by the present application, which should be covered within the protection scope of the present application.

Claims

1. An impeller, characterized by, The hub (110) and a plurality of blades (130) arranged on one side of the hub (110); The shape of the blade (130) is a three-dimensional twisted structure; The blade (130) comprises a suction surface (131), a pressure surface (132), an upper surface (133), a lower surface (134) and a trailing edge surface (135); The pressure surface (132) and the suction surface (131) intersect with the upper surface (133) at the top end of the blade (130); the pressure surface (132) and the suction surface (131) intersect with the lower surface (134) at the bottom end of the blade (130); the pressure surface (132) and the suction surface (131) intersect at the leading edge of the blade (130) to form a leading edge line (136); the pressure surface (132) and the suction surface (131) intersect with the trailing edge surface (135) at the trailing edge of the blade (130); The trailing edge surface (135) of the blade (130) is concavely provided with a plurality of noise reduction tooth grooves (137).

2. The impeller of claim 1, wherein The noise reduction tooth grooves (137) are triangular.

3. The impeller of claim 2, wherein A plurality of noise reduction tooth grooves (137) are sequentially and continuously arranged, and a triangular convex tooth (138) is formed between two adjacent noise reduction tooth grooves (137).

4. The impeller of claim 3, wherein The included angle between the two side walls of the noise reduction tooth groove (137) near the lower surface (134) is smaller than the included angle between the two side walls of the noise reduction tooth groove (137) near the upper surface (133); And / or, The depth of the noise reduction tooth groove (137) ranges from 0.5mm to 1mm; And / or, The tooth tips of all the triangular convex teeth (138) are on a concave spline curve.

5. The impeller of any one of claims 1-4, wherein, The inlet angle at any point on the leading edge line (136) ranges from -45° to -7°, and the outlet angle ranges from 15° to 30°.

6. The impeller of claim 5, wherein In the height direction of the blade (130), the leading edge line (136) has a first control point (139), a second control point (141), a third control point (142), a fourth control point (143), a fifth control point (144) and a sixth control point (145) arranged in sequence at equal intervals from low to high; At the first control point (139), the inlet angle ranges from -45° to -40°, and the outlet angle ranges from 15° to 20°; at the second control point (141), the inlet angle ranges from -35° to -30°, and the outlet angle ranges from 18° to 23°; at the third control point (142), the inlet angle ranges from -34° to -32°, and the outlet angle ranges from 19° to 22°; at the fourth control point (143), the inlet angle ranges from -23° to -28°, and the outlet angle ranges from 21° to 24°; at the fifth control point (144), the inlet angle ranges from -17° to -13°, and the outlet angle ranges from 23° to 28°; at the sixth control point (145), the inlet angle ranges from -10° to -7°, and the outlet angle ranges from 25° to 30°.

7. The impeller of claim 6, wherein The first control point (139) is the intersection of the leading edge line (136) and the lower curved surface (134), and the sixth control point (145) is the intersection of the leading edge line (136) and the upper curved surface (133). The second control point (141), the third control point (142), the fourth control point (143), and the fifth control point (144) are arranged in an equal interval from bottom to top on the leading edge line (136).

8. A hair dryer characterized by The hair dryer comprises a motor (310), a shell (330), and the impeller according to any one of claims 1-7. The shell (330) is provided with a cavity (331), an air inlet (333), and an air outlet (335) which are in communication with the cavity (331). The motor (310) is installed in the cavity (331) and fixed to the shell (330), and the hub (110) is fixedly connected to the output shaft of the motor (310). The motor (310) can drive the impeller to rotate to suck external air into the cavity (331) through the air inlet (333) and send the air out through the air outlet (335).

9. The hair dryer of claim 8, wherein, The hair dryer further comprises a support seat (350), an electric heating wire, and a plurality of heat insulation sheets (370). The support seat (350) is arranged in the cavity (331), and a plurality of the heat insulation sheets (370) are arranged in an interval along the circumferential direction of the support seat (350), and a flow channel (348) is formed between the outer side of the support seat (350) and the inner wall of the shell (330). The length direction of the heat insulation sheet (370) is parallel to the axial direction of the support seat (350). The electric heating wire is wound around the outer periphery of the heat insulation sheet (370). The length of the heat insulation sheet (370) is negatively correlated with the depth of the noise reduction tooth groove (137).

10. The hair dryer of claim 9, wherein, The length of the heat insulation sheet (370) is inversely proportional to the depth of the noise reduction tooth groove (137). And / or, The length of the heat insulation sheet (370) ranges from 33mm to 40mm.

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