Impeller, fan and range hood

Abstract

The utility model relates to the technical field of impellers, and particularly discloses an impeller, a draught fan and a range hood, the impeller comprises a plurality of blades distributed in the circumferential direction of the impeller, the blades are in an arc shape, and the ratio of the chord length of the blades to half of the outer diameter of the impeller is 0.15-0.20; the inlet angle of the blade is an included angle between a vertical line of a connecting line between the starting end of the pressure surface of the blade and the center of the impeller and a tangent line of an arc at the starting end of the pressure surface, and the inlet angle is 72-78 degrees; an outlet angle of the blade is an included angle between a vertical line of a connecting line between the tail end of the pressure surface of the blade and the center of the impeller and a tangent line of an arc at the tail end of the pressure surface, and the outlet angle is 12-18 degrees; the inclination angle of the blade is an included angle between a connecting line between the tail end of the pressure face and the starting end of the pressure face and a connecting line between the tail end of the pressure face of the blade and the center of the impeller, and the inclination angle ranges from 26 degrees to 32 degrees. According to the scheme, air pressure and air volume of the fan can be improved, and fan performance is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of impellers, and in particular to an impeller, a fan and a range hood. Background Art

[0002] The impeller is an air supply device that inlets air axially and blows air radially. It is widely used in fans of various range hood extraction equipment. The air volume and air pressure of the fan are mainly affected by the parameters of the impeller. The air volume and air pressure of the current fan are relatively low, which leads to poor range hood extraction effect.

[0003] To address the above problems, no effective solution has been proposed yet. Utility Model Content

[0004] The embodiments of this specification provide an impeller, a fan and a range hood to solve the technical problem in the prior art that the air volume and air pressure of the fan are not high enough.

[0005] An embodiment of the present specification provides an impeller, the impeller comprising a plurality of blades distributed in the circumferential direction of the impeller, the blades being arc-shaped, the ratio between the chord length of the blade and half of the outer diameter of the impeller being 0.15 to 0.20; the chord length of the blade being the length of a line between the end of the pressure surface of the blade and the starting end of the pressure surface;

[0006] The blade has a preset inlet angle, a preset outlet angle and a preset inclination angle;

[0007] The preset inlet angle is the angle between the perpendicular line of the line between the starting end of the pressure surface of the blade and the center of the impeller and the tangent line of the arc at the starting end of the pressure surface, and the preset inlet angle is 72° to 78°;

[0008] The preset outlet angle is the angle between the perpendicular line of the line between the end of the pressure surface of the blade and the center of the impeller and the tangent line of the arc at the end of the pressure surface, and the preset outlet angle is 12° to 18°;

[0009] The preset inclination angle is the angle between the line between the end of the pressure surface and the starting end of the pressure surface and the line between the end of the pressure surface of the blade and the center of the impeller, and the preset inclination angle is 26° to 32°.

[0010] In one embodiment, the preset inlet angle of the blade is 74° to 76°;

[0011] The preset outlet angle of the blade is 14° to 16°;

[0012] The preset inclination angle of the blade is 29° to 31°.

[0013] In one embodiment, the ratio between the chord length of the blade and half of the outer diameter of the impeller is 0.16 to 0.18.

[0014] In one embodiment, the ratio between the crown height and the chord length of the blade is 0.20 to 0.27.

[0015] In one embodiment, the ratio between the crown height and the chord length of the blade is 0.23 to 0.25.

[0016] In one embodiment, the ratio of the distance between two adjacent blades among the plurality of blades to half of the outer diameter of the impeller is 0.035 to 0.06, and the distance between two adjacent blades is the shortest distance between the end of the pressure surface of one blade and the suction surface of another blade.

[0017] In one embodiment, a ratio of a distance between two adjacent blades of the plurality of blades to a half of an outer diameter of the impeller is 0.04 to 0.06.

[0018] The embodiment of this specification also provides a fan, the fan comprising a volute, an impeller as described in any of the above embodiments, the impeller being arranged in the volute;

[0019] a motor connected to the impeller to drive the impeller to rotate;

[0020] The motor is fixed on the volute or the motor is fixed on a wall.

[0021] In one embodiment, the volute profile expansion ratio of the volute and the circumferential angle of the volute satisfy the following relationship:

[0022] y=aθ+b;

[0023] Wherein, y is the volute profile expansion ratio of the volute, θ is the circumferential angle of the volute, a is the slope, a is 0.0019 to 0.0023, b is the intercept, b is 1.0 to 1.14; the volute includes a shroud arranged around the impeller, the volute profile expansion ratio is the ratio of the distance between a point on the shroud and the center of the impeller to half of the outer diameter of the impeller, and the circumferential angle is the angle between the line between the point on the shroud and the center of the impeller and the line between the starting end of the volute profile and the center of the impeller.

[0024] In one embodiment, a is 0.0020 to 0.0022, and b is 1.0 to 1.1.

[0025] In one embodiment, the volute comprises a first side plate and a second side plate which are arranged opposite to each other, and a surrounding plate located between the first side plate and the second side plate; the surrounding plate is respectively connected to the first side plate and the second side plate to form the volute; the surrounding plate is formed with a volute tongue at a position close to the air outlet of the volute;

[0026] The volute further comprises an oil-blocking member, which is located on a portion of the enclosure between the volute tongue and the air outlet and is used to prevent oil stains at the air outlet from flowing toward the volute tongue.

[0027] In one embodiment, the oil-blocking member is a baffle provided on the inner wall of the enclosure, and the baffle is located inside the volute or the baffle is provided close to the air outlet of the volute; or, the oil-blocking member is a groove opened on the inner wall of the enclosure; or, the oil-blocking member is a groove formed by the enclosure protruding in a direction away from the interior of the volute.

[0028] In one embodiment, the oil blocking member is further used to guide oil stains to the first side plate and / or the second side plate.

[0029] In one embodiment, at least part of the oil blocking member is higher than a part of the oil blocking member close to the first side plate, and / or at least part of the oil blocking member is higher than a part of the oil blocking member close to the second side plate.

[0030] In one embodiment, the oil blocking member is partially or entirely inclined.

[0031] In one embodiment, the first side plate is used to mount the motor, and the oil blocking member is used to guide the oil to the second side plate; or, the second side plate is used to mount the motor, and the oil blocking member is used to guide the oil to the first side plate.

[0032] In one embodiment, a first end of the oil blocking member close to the first side plate is higher than other parts of the oil blocking member; or a second end of the oil blocking member close to the second side plate is higher than other parts of the oil blocking member.

[0033] In one embodiment, the oil blocking member is used to guide the oil to the second side plate, and the distance between the oil blocking member and the air outlet gradually increases from the first end of the oil blocking member close to the first side plate to the second end of the oil blocking member close to the second side plate; or,

[0034] The oil blocking member is used to guide oil to the first side plate, and the distance between the oil blocking member and the air outlet gradually decreases from a first end of the oil blocking member close to the first side plate to a second end of the oil blocking member close to the second side plate.

[0035] In one embodiment, the oil blocking member includes a first end close to the first side plate and a second end close to the second side plate; the impeller includes a first end surface close to the first side plate and a second end surface close to the second side plate;

[0036] The projection of the first end of the oil-blocking member in the axial direction of the impeller is located between the projection of the first end surface of the impeller in the axial direction of the impeller and the projection of the first side plate in the axial direction of the impeller; and / or,

[0037] The projection of the second end of the oil-blocking member in the axial direction of the impeller is located between the projection of the second end surface of the impeller in the axial direction of the impeller and the projection of the second side plate in the horizontal direction.

[0038] In one embodiment, one end of the oil-blocking member extends to the first side plate and is connected to the first side plate; and / or the other end of the oil-blocking member extends to the second side plate and is connected to the second side plate.

[0039] An embodiment of the present specification also provides a range hood, including: the fan described in any of the above embodiments.

[0040] The technical solution of this specification has the following significant beneficial effects:

[0041] The impeller in the embodiment of this specification includes a plurality of blades distributed in the circumference of the impeller. The ratio between the chord length of the blade and half of the outer diameter of the impeller, the inlet angle, outlet angle and inclination angle of the blade will affect the performance of the fan. If the ratio between the chord length of the blade and half of the outer diameter of the impeller is too large, the impeller air inlet will be too small, resulting in an increase in the air inlet resistance, which is not conducive to the air suction of the impeller. If the ratio between the chord length of the blade and half of the outer diameter of the impeller is too small, the working area of ​​the impeller blade will be too small, and the air volume cannot be effectively provided, and the static pressure will also be reduced. Therefore, the value of the ratio between the chord length of the blade and half of the outer diameter of the impeller needs to take into account the air inlet resistance of the impeller and the working area of ​​the impeller blade. If the inlet angle of the blade is too small, the impact of the airflow entering the impeller is large, which will lead to an increase in flow loss. If the inlet angle of the blade is too large, the airflow may not flow smoothly in the impeller, reducing the efficiency of the fan. Therefore, the value of the inlet angle of the blade needs to take into account the airflow loss and the smoothness of the airflow in the impeller. The outlet angle of the blade has a significant impact on the maximum static pressure. An outlet angle that is too large will reduce the maximum static pressure and expand the low-pressure area of ​​the flow; while an outlet angle that is too small will increase the flow resistance and affect the air volume. Therefore, the value of the outlet angle of the blade needs to take into account both the maximum static pressure and the airflow resistance. The inclination angle of the blade will affect the efficiency of the fan. A too small inclination angle will significantly increase the required power, while a too large inclination angle will cause flow turbulence and blade airflow separation, increase flow resistance, and thus affect the air volume and pressure. Therefore, the value of the inclination angle of the blade needs to take into account both the efficiency of the fan and the flow resistance of the fan. By comprehensively adjusting the ratio of the chord length of the blade to half the outer diameter of the impeller, the inlet angle, outlet angle and inclination angle of the blade, the ratio of the chord length of the blade to half the outer diameter of the impeller is set to 0.15 to 0.20, the preset inlet angle of the blade is set to 72° to 78°, the preset outlet angle of the blade is set to 12° to 18°, and the preset inclination angle of the blade is set to 26° to 32°. The wind pressure and air volume of the fan can be effectively increased, thereby improving the range hood extraction effect.

[0042] With reference to the following description and drawings, specific embodiments of the present invention are disclosed in detail, indicating the manner in which the principles of the present invention can be adopted. It should be understood that the embodiments of the present invention are not limited in scope. Features described and / or shown for one embodiment can be used in one or more other embodiments in the same or similar manner, combined with features in other embodiments, or replace features in other embodiments.

[0043] It should be emphasized that the term “include / comprises” when used herein refers to the presence of features, parts, steps or components, but does not exclude the presence or addition of one or more other features, parts, steps or components. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] The drawings described herein are only for explanation purposes and are not intended to limit the scope of the present invention in any way. In addition, the shapes and proportional dimensions of the components in the drawings are only for illustration purposes and are used to help understand the present invention. They do not specifically limit the shapes and proportional dimensions of the components of the present invention. Under the guidance of the present invention, those skilled in the art can select various possible shapes and proportional dimensions to implement the present invention according to specific circumstances. In the drawings:

[0045] Figure 1 A schematic diagram of the structure of an impeller in one embodiment of this specification is shown;

[0046] Figure 2 A cross-sectional view of an impeller in an embodiment of the present specification is shown;

[0047] Figure 3 A partial enlarged view of an impeller in an embodiment of the present specification is shown;

[0048] Figure 4 A schematic diagram of the structure of a fan in an embodiment of this specification is shown;

[0049] Figure 5 A front view of a volute in an embodiment of the present specification is shown;

[0050] Figure 6 A schematic diagram of the structure of a volute in an embodiment of the present specification is shown;

[0051] Figure 7 A schematic diagram of the structure of a volute in an embodiment of the present specification is shown;

[0052] Figure 8 A schematic diagram of the structure of a volute in an embodiment of the present specification is shown;

[0053] Fig. 9 A cross-sectional view of a portion of the enclosure between the volute tongue and the air outlet in an embodiment of the present specification is shown;

[0054] Fig.10 A front view of a portion of the enclosure between the volute tongue and the air outlet in an embodiment of the present specification is shown;

[0055] Fig.11 A front view of a portion of the enclosure between the volute tongue and the air outlet in an embodiment of the present specification is shown;

[0056] Fig.12 A front view of a portion of the enclosure between the volute tongue and the air outlet in an embodiment of the present specification is shown.

[0057] Reference numerals of the above drawings:

[0058] 1. Fan; 10. Impeller; 20. Volute; 30. Motor; 11. Blades; 110. Pressure surface; 1101. Starting end; 1102. End; 111. Suction surface; 21. First side panel; 22. Second side panel; 23. Enclosure; 24. Air outlet; 25. Volute tongue; 26. Oil stopper; 261. First end; 262. Second end; O. Impeller center; L. Blade chord length; R. Half of the impeller outer diameter; H. Blade arch height; d. Distance between two adjacent blades; α. Blade inlet angle; β. Blade outlet angle; γ. Blade inclination angle; θ. Circumferential angle of volute profile. DETAILED DESCRIPTION

[0059] The principles and spirit of this specification will be described below with reference to several exemplary embodiments. It should be understood that these embodiments are provided only to enable those skilled in the art to better understand and implement this specification, and are not intended to limit the scope of this specification in any way. On the contrary, these embodiments are provided to make this specification more thorough and complete, and to fully convey the scope of this disclosure to those skilled in the art.

[0060] Those skilled in the art will appreciate that the embodiments of this specification may be implemented as a system, device, method, or computer program product. Therefore, this specification may be implemented in the following forms: complete hardware, complete software (including firmware, resident software, microcode, etc.), or a combination of hardware and software.

[0061] In combination with the accompanying drawings and the description of the specific embodiments of the present invention, the details of the present invention can be more clearly understood. However, the specific embodiments of the present invention described herein are only used to explain the purpose of the present invention and cannot be understood as limiting the present invention in any way. Under the guidance of the present invention, technicians can conceive of any possible variations based on the present invention, which should be regarded as belonging to the scope of the present invention. It should be noted that when an element is referred to as "disposed on" another element, it can be directly on the other element or there can also be a central element. When an element is considered to be "connected" to another element, it can be directly connected to the other element or there may be a central element at the same time. The terms "installed", "connected" and "connected" should be understood in a broad sense, for example, it can be a mechanical connection or an electrical connection, or it can be the internal communication of two elements, it can be directly connected, or it can be indirectly connected through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to the specific circumstances. The terms "vertical", "horizontal", "up", "down", "left", "right" and similar expressions used herein are only for illustrative purposes and do not represent the only implementation method.

[0062] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art to which this specification belongs. The terms used herein in this specification are only for the purpose of describing specific embodiments and are not intended to limit this specification. The term "and / or" used herein includes any and all combinations of one or more of the related listed items.

[0063] This specification provides an impeller. Figure 1 and Figure 2 , showing a structural schematic diagram and a cross-sectional view of an impeller in one embodiment of the present specification. Figure 2 It is a cross-sectional view obtained by cutting along the radial direction of the impeller. Figure 1 and Figure 2 As shown, the impeller 10 may include a plurality of blades 11 distributed in a circumferential direction of the impeller 10 .

[0064] Please refer to Figure 3 , showing Figure 2 A partial enlarged view of the cross-section of the impeller in FIG. Figure 2 and Figure 3 As shown, when the impeller 10 is cut along the radial direction, the blade 11 is arc-shaped and has a certain thickness. In one embodiment, the arc shape of the blade can include a single arc, a double arc or multiple arcs. The specific form of the blade arc can refer to the existing arc form. This application does not limit this.

[0065] like Figure 3As shown, the two sides of the blade 11 are respectively a pressure surface 110 and a suction surface 111. The suction surface 111 of the impeller 10 refers to the curved surface where the fluid impacts the blade 11 due to pressure reduction. The pressure surface 110 refers to the curved surface where the blade 11 applies pressure to the fluid due to pressure increase. The ratio L / R between the chord length L of the blade 11 and the half R of the outer diameter of the impeller 10 is 0.15 to 0.20. The chord length L of the blade 11 refers to the length of the line between the end 1102 of the pressure surface 110 of the blade 11 and the starting end 1101 of the pressure surface 110. The half R of the outer diameter of the impeller 10 refers to the length of the line between the end 1102 of the pressure surface 110 and the center O of the impeller 10. If the ratio L / R between the chord length L of the blade 11 and the half R of the outer diameter of the impeller 10 is too large, the air inlet of the impeller 10 will be too small, thereby increasing the air inlet resistance, which is not conducive to the air suction of the impeller 10. If the ratio L / R between the chord length L of the blade 11 and the half R of the outer diameter of the impeller 10 is too small, the working area of ​​the blade 11 of the impeller 10 will be too small, and the air volume cannot be effectively provided, and the static pressure will also be reduced. By setting the ratio L / R between the chord length L of the blade 11 and the half R of the outer diameter of the impeller 10 to 0.15 to 0.20, the air inlet resistance of the impeller 10 can be reduced, and the working area of ​​the blade 11 of the impeller 10 can be increased.

[0066] like Figure 2 and Figure 3 As shown, the blade 11 has a preset inlet angle α, a preset outlet angle β and a preset inclination angle γ.

[0067] The preset inlet angle α is the angle between the perpendicular line of the line between the starting end 1101 of the pressure surface 110 of the blade 11 and the center O of the impeller 10 and the tangent line of the arc at the starting end 1101 of the pressure surface 110. The preset inlet angle α is 72° to 78°. If the inlet angle α of the blade is too small, the impact of the airflow when entering the impeller 10 is large, which will cause increased flow losses. If the inlet angle α of the blade is too large, the airflow may not flow smoothly in the impeller 10, reducing the efficiency of the fan. By setting the inlet angle α of the blade to 72° to 78°, the airflow loss can be reduced, while ensuring that the airflow flows more smoothly in the impeller 10.

[0068] The preset outlet angle β is the angle between the perpendicular line of the line between the end 1102 of the pressure surface 110 of the blade 11 and the center O of the impeller 10 and the tangent line of the arc of the end 1102 of the pressure surface 110. The preset outlet angle β is 12° to 18°. The outlet angle β of the blade has a significant effect on the maximum static pressure. An outlet angle β that is too large will reduce the maximum static pressure and expand the low-pressure area of ​​the flow; while an outlet angle β that is too small will increase the flow resistance and affect the air volume. By setting the outlet angle β of the blade to 12° to 18°, a higher maximum static pressure and a lower airflow resistance can be ensured at the same time.

[0069] The preset inclination angle γ is the angle between the line between the end 1102 of the pressure surface 110 of the blade 11 and the starting end 1101 of the pressure surface 110 and the line between the end 1102 of the pressure surface 110 of the blade 11 and the center O of the impeller 10. The preset inclination angle γ is 26° to 32°. The inclination angle γ of the blade affects the efficiency of the fan. A too small inclination angle γ will significantly increase the required power, while a too large inclination angle γ will cause flow turbulence and blade airflow separation, increase flow resistance, and further affect air volume and wind pressure. By setting the inclination angle γ of the blade to 26° to 32°, higher fan efficiency and lower flow resistance can be ensured.

[0070] In this embodiment, the impeller 10 includes a plurality of blades 11 distributed in the circumferential direction of the impeller 10. By comprehensively adjusting the factors including the ratio L / R between the chord length L of the blade 11 and half the outer diameter R of the impeller, the inlet angle α, the outlet angle β and the inclination angle γ of the blade, the ratio L / R between the chord length L of the blade 11 and half the outer diameter R of the impeller 10 is set to 0.15 to 0.20, the preset inlet angle α of the blade 11 is set to 72° to 78°, the preset outlet angle β of the blade 11 is set to 12° to 18°, and the preset inclination angle γ of the blade 11 is set to 26° to 32°. This can effectively increase the wind pressure and air volume of the fan, improve the operating performance of the fan, and thus improve the fume extraction effect of the range hood.

[0071] In some embodiments of the present specification, the preset inlet angle α of the blade 11 is 74° to 76°. Preferably, the preset inlet angle α of the blade 11 is 75°.

[0072] In some embodiments of the present specification, the preset outlet angle β of the blade 11 is 14° to 16°. Preferably, the preset outlet angle β of the blade 11 is 15°.

[0073] In some embodiments of the present specification, the preset inclination angle γ of the blade 11 is 29° to 31°. Preferably, the preset inclination angle γ of the blade 11 is 30°.

[0074] In some embodiments of the present specification, L / R is 0.16 to 0.18. Preferably, L / R is 0.171.

[0075] In some embodiments of the present specification, the ratio H / L between the arch height H and the chord length L of the blade 11 is 0.20 to 0.27. The arch height H of the blade 11 refers to the maximum distance between a point on the pressure surface 110 of the blade 11 and the line between the end 1102 of the pressure surface 110 of the blade 11 and the starting end 1101 of the pressure surface 110. The chord length L of the blade 11 refers to the length of the line between the end 1102 of the pressure surface 110 of the blade 11 and the starting end 1101 of the pressure surface 110. If the ratio H / L between the arch height H and the chord length L of the blade 11 is too large, the throat size between the blades will be too small. If the ratio H / L between the arch height H and the chord length L of the blade 11 is too small, the efficiency of the fan will be reduced. By setting the ratio H / L between the arch height H and the chord length L of the blade 11 to 0.20 to 0.27, the noise can be reduced without increasing the flow resistance.

[0076] In some embodiments of the present specification, H / L is 0.23 to 0.25. Preferably, H / L is 0.237.

[0077] In some embodiments of the present specification, the ratio d / R between the distance d between two adjacent blades 11 in the plurality of blades 11 and half R of the outer diameter of the impeller 10 is 0.035 to 0.06. Figure 3 As shown, the distance d between two adjacent blades 11 is the shortest distance between the end 1102 of the pressure surface 110 of one blade 11 and the suction surface 111 of another blade 11. The ratio d / R between the distance d between two adjacent blades 11 and half R of the outer diameter of the impeller 10 will affect the sparseness of the blades 11 of the impeller 10. The density of the blades 11 will affect the efficiency and fluidity of the fan, especially the efficiency at the limit air volume. If d / R is too small (too dense), the manufacturing cost will increase, and the flow resistance at the limit air volume will increase and the power will increase, thereby reducing the efficiency of the fan. If d / R is too large (too sparse), the air volume will be too small at the same speed, and large vortices will be generated between the blades 11, which will increase the noise. By setting the ratio d / R between the distance d between two adjacent blades 11 and half R of the outer diameter of the impeller 10 to 0.035 to 0.06, the fan can be ensured to operate at a higher fan efficiency while reducing noise.

[0078] In some embodiments of the present specification, d / R is 0.04 to 0.06. Preferably, d / R is 0.05.

[0079] The present specification also provides a fan. Figure 4 , shows a schematic diagram of the structure of the fan in the embodiment of this specification. Figure 4 As shown, the fan 1 may include a volute 20, an impeller 10 and a motor 30. The impeller 10 may be the impeller 10 described in any of the above embodiments.

[0080] like Figure 4 As shown, the impeller 10 can be disposed in the volute 20. The motor 30 can be connected to the impeller 10 to drive the impeller 10 to rotate. In one embodiment, the motor 30 can be fixed on the volute 20. In another embodiment, the motor 30 can be fixed on the wall.

[0081] Please refer to Figure 5 , shows a front view of the volute in the embodiment of this specification. Figure 5 As shown, the volute 20 has a volute profile l. In some embodiments of the present specification, the expansion ratio of the volute profile l of the volute 20 and the circumferential angle θ of the volute 20 satisfy the following relationship:

[0082] y=aθ+b.

[0083] Wherein, y is the expansion ratio of the volute profile line l of the volute 20, θ is the circumferential angle of the volute 20, a is the slope, a is 0.0019 to 0.0023, b is the intercept, b is 1.0 to 1.14. The volute 20 includes a shroud 23 arranged around the impeller 10, the expansion ratio y of the volute profile line l is the ratio of the distance between a point on the shroud 23 and the center O of the impeller 10 to half R of the outer diameter of the impeller 10, and the circumferential angle θ is the angle between the line between the point on the shroud 23 and the center O of the impeller 10 and the line between the starting end of the volute profile line l and the center O of the impeller 10. The circumferential angle θ ranges from 0° to 270°. The starting end of the volute profile line l is the intersection with the volute 20 when extending upward from the center O of the impeller 10 in the vertical direction.

[0084] If the intercept b is too large, the distance between the volute 20 and the impeller 10 is too large, the pressure diffusion capacity decreases, and insufficient static pressure occurs; if the intercept b is too small, the high-speed rotation of the impeller 10 will interfere with the volute tongue 25 to produce abnormal noise, affecting the normal operation of the fan 1. If the slope a is too small, the volute 20 cannot effectively increase the pressure, which will cause the performance of the fan 1 to fail to reach the best according to the blade shape design; and if the slope a is too large, the size of the volute will increase, requiring a larger space to install the fan, and too large an oblique flow will cause the fan to produce unstable airflow and whirring sound when running at a low speed. By comprehensively setting the slope a and the intercept b, setting the slope a to 0.0019 to 0.0023 and the intercept b to 1.0 to 1.14, sufficient static pressure can be ensured and noise can be reduced.

[0085] In some embodiments of the present specification, a is 0.0020 to 0.0022. Preferably, a is 0.0021.

[0086] In some embodiments of the present specification, b is 1.0 to 1.1. Preferably, b is 1.053.

[0087] Please refer to Figures 6 to 8 , shows a schematic diagram of the structure of the volute in the embodiment of this specification. Figures 6 to 8 As shown, in some embodiments of the present specification, the volute 20 includes a first side plate 21, a second side plate 22 and a surrounding plate 23 that are arranged opposite to each other. The surrounding plate 23 is located between the first side plate 21 and the second side plate 22. The surrounding plate 23 is connected to the first side plate 21 and the second side plate 22 to form the volute 20. The surrounding plate 23 is formed with a volute tongue 25 at a position close to the air outlet 24 of the volute 20.

[0088] like Figures 5 to 8 As shown, the volute 20 may further include an oil blocking member 26. The oil blocking member 26 is located on a portion of the enclosure 23 between the volute tongue 25 and the air outlet 24. The oil blocking member 26 may be used to prevent oil stains at the air outlet 24 from flowing toward the volute tongue 25.

[0089] In this embodiment, an oil-blocking member 26 is provided on a portion of the enclosure 23 between the volute tongue 25 and the air outlet 24 to prevent oil stains at the air outlet 24 from flowing toward the volute tongue 25, thereby preventing the volute tongue 25 from being attached to oil. On the one hand, the blades 11 of the impeller 10 can be prevented from contacting the oil attached to the volute tongue 25 to produce abnormal noise, thereby reducing the noise during the operation of the fan 1. On the other hand, the blades 11 of the impeller 10 can be prevented from contacting the oil attached to the volute tongue 25 to affect the rotation speed of the blades 11, thereby improving the operating performance of the fan 1 and improving the user experience.

[0090] like Figure 5 and Figure 6 As shown, in some embodiments of the present specification, the oil blocking member 26 is a groove formed by the surrounding plate 23 protruding in a direction away from the interior of the volute 20 .

[0091] In some embodiments of the present specification, the oil blocking member 26 is a groove formed on the inner wall of the enclosure 23. The inner wall of the enclosure 23 may be concave to form a groove.

[0092] In the above embodiment, by providing a groove on a portion of the enclosure 23 between the air outlet 24 and the volute tongue 25 , oil flowing from the air outlet 24 toward the volute tongue 25 can be stored, thereby avoiding or delaying the oil from flowing to the volute tongue 25 .

[0093] like Figure 7 and Figure 8 As shown, in some embodiments of the present specification, the oil blocking member 26 is a baffle disposed on the inner wall of the enclosure 23. Figure 7 As shown, the baffle can be arranged near the air outlet 24 of the volute 20. In other words, the baffle can be arranged on the enclosure 23 at the air outlet 24. Figure 8 As shown, the baffle may be located inside the volute 20 .

[0094] In the above embodiment, by providing a baffle on the enclosure between the air outlet 24 and the volute tongue 25 , the oil stains at the air outlet can be blocked from flowing toward the volute tongue 25 .

[0095] Please refer to Fig. 9 , showing a cross-sectional view of part of the enclosure between the volute tongue and the air outlet in an embodiment of this specification. Fig. 9 The cross-sectional view in FIG. 1 is obtained by cutting along the radial direction of the impeller 10 . Fig. 9 The right side of the panel is the side close to the snail tongue. Fig. 9 As shown in (a), the oil blocking member 26 is a groove formed by the enclosing plate 23 protruding in a direction away from the interior of the volute 20. Fig. 9 As shown in (b) and (c), the oil blocking member 26 is a baffle disposed on the inner wall of the enclosure 23. Fig. 9 As shown in (b), the baffle is located inside the volute 20. Fig. 9 As shown in (c), the baffle is disposed near the air outlet 24 of the volute 20. Fig. 9 As shown in (d), the oil blocking member 26 is a groove opened on the inner wall of the enclosure 23.

[0096] Please refer to Figures 10 to 12 , shows a front view of a portion of the enclosure between the volute tongue and the air outlet in the embodiment of this specification. The two sides of the enclosure 23 are the first side plate 21 and the second side plate 22. Fig.10 As shown, the oil blocking member 26 can be used to guide the oil dirt to the first side plate 21. Fig.11 As shown, the oil blocking member 26 can be used to guide the oil dirt to the second side plate 22. Fig.12 As shown, the oil blocking member 26 can be used to guide the oil to the first side plate 21 and the second side plate 22 .

[0097] like Fig.10 As shown, in some embodiments of the present specification, at least part of the oil blocking member 26 is higher than the part of the oil blocking member 26 close to the first side plate 21. By setting at least part of the oil blocking member 26 to be higher than the part of the oil blocking member 26 close to the first side plate 21, oil can be directed to the first side plate 21.

[0098] like Fig.11 As shown, in some embodiments of the present specification, at least part of the oil blocking member 26 is higher than the part of the oil blocking member 26 close to the second side plate 22. By setting at least part of the oil blocking member 26 to be higher than the part of the oil blocking member 26 close to the second side plate 22, oil can be directed to the second side plate 22.

[0099] like Fig.12As shown, in some embodiments of the present specification, at least part of the oil blocking member 26 is higher than the part of the oil blocking member 26 close to the first side plate 21 and higher than the part of the oil blocking member 26 close to the second side plate 22. By setting at least part of the oil blocking member 26 to be higher than the part of the oil blocking member 26 close to the first side plate 21 and higher than the part of the oil blocking member 26 close to the second side plate 22, oil stains can be directed to the first side plate 21 and the second side plate 22.

[0100] like Fig.10 (b) Fig.11 (b) and Fig.12 As shown in (b), in some embodiments of the present specification, the oil blocking member 26 is partially tilted.

[0101] like Fig.10 (a) and (c) Fig.11 (a) and (c) and Fig.12 As shown in (a) and (c), in some embodiments of the present specification, the oil blocking member 26 is arranged to be tilted as a whole.

[0102] In the above embodiment, by arranging the oil blocking member 26 to be partially inclined or entirely inclined, the oil stains can be guided to the first side plate 21 and / or the second side plate 22 .

[0103] In some embodiments of the present specification, the second side plate 22 is used to install the motor 30. Fig.10 As shown, when the second side plate 22 is used to install the motor 30 , the oil blocking member 26 can be used to guide the oil to the first side plate 21 .

[0104] In some embodiments of the present specification, the first side plate 21 is used to install the motor 30. Fig.11 As shown, when the first side plate 21 is used to install the motor 30 , the oil blocking member 26 can be used to guide the oil to the second side plate 22 .

[0105] In the above embodiment, by directing the oil to the side plate away from the side where the motor 30 is installed, the oil can be prevented from flowing to the motor 30, thereby preventing the oil from affecting the normal operation of the motor 30.

[0106] like Fig.10 As shown, in some embodiments of the present specification, the first end 261 of the oil blocking member 26 close to the first side plate 21 is higher than other parts of the oil blocking member 26. In this embodiment, by setting the first end 261 of the oil blocking member 26 close to the first side plate 21 to be higher than other parts of the oil blocking member 26, oil pollution can be prevented from flowing to the first side plate 21.

[0107] like Fig.11As shown, in some embodiments of the present specification, the second end 262 of the oil blocking member 26 close to the second side plate 22 is higher than other parts of the oil blocking member 26. In this embodiment, by setting the second end 262 of the oil blocking member 26 close to the second side plate 22 to be higher than other parts of the oil blocking member 26, oil pollution can be prevented from flowing to the second side plate 22.

[0108] like Fig.10 As shown in (a) and (c), in some embodiments of the present specification, the oil blocking member 26 is used to guide the oil to the first side plate 21, and the distance between the oil blocking member 26 and the air outlet 24 gradually decreases from the first end 261 to the second end 262.

[0109] like Fig.11 As shown in (a) and (c), in some embodiments of the present specification, the oil blocking member 26 is used to guide the oil to the second side plate 22, and the distance between the oil blocking member 26 and the air outlet 24 gradually increases from the first end 261 to the second end 262.

[0110] In some embodiments of the present specification, the oil blocking member 26 includes a first end 261 close to the first side plate 21 and a second end 262 close to the second side plate 22. The impeller 10 includes a first end surface close to the first side plate 21 and a second end surface close to the second side plate 22.

[0111] In some embodiments of the present specification, the projection of the first end 261 of the oil blocking member 26 in the axial direction of the impeller 10 is located between the projection of the first end surface of the impeller 10 in the axial direction of the impeller 10 and the projection of the first side plate 21 in the axial direction of the impeller 10. By arranging the first end 261 of the oil blocking member 26 to be located in the gap between the first end surface of the impeller 10 and the first side plate 21 of the volute 20 in the axial direction, it is possible to prevent the oil flowing out of the first end 261 of the oil blocking member 26 from contacting the blades 11 of the impeller 10 after reaching the volute tongue 25.

[0112] In some embodiments of the present specification, the projection of the second end 262 of the oil blocking member 26 in the axial direction of the impeller 10 is located between the projection of the second end surface of the impeller 10 in the axial direction of the impeller 10 and the projection of the second side plate 22 in the horizontal direction. By arranging the second end 262 of the oil blocking member 26 to be located in the gap between the second end surface of the impeller 10 and the second side plate 22 of the volute 20 in the axial direction, it is possible to prevent the oil flowing out of the second end 262 of the oil blocking member 26 from contacting the blades 11 of the impeller 10 after reaching the volute tongue 25.

[0113] In some embodiments of the present specification, the projection of the first end 261 of the oil blocking member 26 in the axial direction of the impeller 10 is located between the projection of the first end surface of the impeller 10 in the axial direction of the impeller 10 and the projection of the first side plate 21 in the axial direction of the impeller 10, and the projection of the second end 262 of the oil blocking member 26 in the axial direction of the impeller 10 is located between the projection of the second end surface of the impeller 10 in the axial direction of the impeller 10 and the projection in the horizontal direction of the second side plate 22. By arranging the two ends of the oil blocking member 26 in the axial direction to be located in the gap between the end surface of the impeller 10 and the side plate of the volute 20, it is possible to prevent the oil flowing out from the two ends of the oil blocking member 26 from contacting the blades 11 of the impeller 10 after reaching the volute tongue 25.

[0114] In some embodiments of the present specification, one end of the oil blocking member 26 extends to the first side plate 21 and is connected to the first side plate 21. By setting one end of the oil blocking member 26 to extend to the first side plate 21 and be connected to the first side plate 21, the oil blocked by the oil blocking member 26 can flow to the first side plate 21, thereby preventing or reducing the oil from flowing to the volute tongue 25.

[0115] In some embodiments of the present specification, the other end of the oil blocking member 26 extends to the second side plate 22 and is connected to the second side plate 22. By setting one end of the oil blocking member 26 to extend to the second side plate 22 and be connected to the second side plate 22, the oil blocked by the oil blocking member 26 can flow to the second side plate 22, thereby preventing or reducing the oil from flowing to the volute tongue 25.

[0116] like Fig.10 (c) Fig.11 (c) and Fig.12 As shown in (c), in some embodiments of the present specification, one end of the oil blocking member 26 extends to the first side plate 21 and is connected to the first side plate 21, and the other end of the oil blocking member 26 extends to the second side plate 22 and is connected to the second side plate 22. By arranging the two ends of the oil blocking member 26 to extend to the first side plate 21 and the second side plate 22 respectively, the oil blocked by the oil blocking member 26 can flow to the first side plate 21 and / or the second side plate 22, thereby avoiding or reducing the oil flowing to the volute tongue 25.

[0117] The description of the oil-blocking member in the above embodiment is an improvement on the volute in the fan. It can be understood that the improvement on the volute in the above embodiment is not limited to the improvement on the impeller in the above embodiment. That is to say, the improvement on the volute and the improvement on the impeller can be independent of each other.

[0118] In some embodiments of the present specification, a volute is also provided. The volute includes a first side plate and a second side plate arranged opposite to each other, and a surrounding plate located between the first side plate and the second side plate; the surrounding plate is respectively connected to the first side plate and the second side plate to form the volute; the surrounding plate is formed with a volute tongue at a position close to the air outlet of the volute; the volute also includes an oil blocking member, which is located on a portion of the surrounding plate between the volute tongue and the air outlet, and is used to prevent oil stains at the air outlet from flowing toward the volute tongue. The implementation of the volute in this embodiment can refer to the above implementation of the volute in the fan, and the repeated parts will not be repeated.

[0119] The embodiments of the present specification also provide a fan, comprising: a volute in any of the above embodiments; an impeller, the impeller being arranged in the volute; a motor, the motor being connected to the impeller to drive the impeller to rotate; the motor being fixed on the volute or the motor being fixed on a wall.

[0120] The embodiments of this specification also provide a range hood, comprising the fan in any of the above embodiments.

[0121] Each embodiment in this specification is described in a progressive manner, and the same or similar parts between the embodiments can be referred to each other, and each embodiment focuses on the differences from other embodiments. For details, please refer to the description of the above-mentioned related processing related embodiments, and no further description is given here.

[0122] The above is a description of a specific embodiment of the specification. Other embodiments are within the scope of the appended claims. In some cases, the actions or steps recorded in the claims can be performed in an order different from that in the embodiments and still achieve the desired results. In addition, the processes depicted in the drawings do not necessarily require the specific order or continuous order shown to achieve the desired results. In some embodiments, multitasking and parallel processing are also possible or may be advantageous.

[0123] It should be understood that the above description is for illustration and not for limitation. Many embodiments and many applications beyond the examples provided will be apparent to those skilled in the art upon reading the above description. Therefore, the scope of this specification should not be determined with reference to the above description, but should be determined with reference to the preceding claims and the full scope of equivalents to which these claims belong.

[0124] The above description is only the preferred embodiment of this specification and is not intended to limit this specification. For those skilled in the art, the embodiments of this specification may have various changes and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of this specification shall be included in the protection scope of this specification.

Claims

1. An impeller, characterized in that: The impeller comprises a plurality of blades distributed in the circumferential direction of the impeller, the blades are arc-shaped, and the ratio between the chord length of the blade and half of the outer diameter of the impeller is 0.15 to 0.20; the chord length of the blade is the length of the line between the end of the pressure surface of the blade and the starting end of the pressure surface; The blade has a preset inlet angle, a preset outlet angle and a preset inclination angle; The preset inlet angle is the angle between the perpendicular line of the line between the starting end of the pressure surface of the blade and the center of the impeller and the tangent line of the arc at the starting end of the pressure surface, and the preset inlet angle is 72° to 78°; The preset outlet angle is the angle between the perpendicular line of the line between the end of the pressure surface of the blade and the center of the impeller and the tangent line of the arc at the end of the pressure surface, and the preset outlet angle is 12° to 18°; The preset inclination angle is the angle between the line between the end of the pressure surface and the starting end of the pressure surface and the line between the end of the pressure surface of the blade and the center of the impeller, and the preset inclination angle is 26° to 32°.

2. The impeller according to claim 1, characterized in that: The preset inlet angle of the blade is 74° to 76°; The preset outlet angle of the blade is 14° to 16°; The preset inclination angle of the blade is 29° to 31°.

3. The impeller according to claim 1, characterized in that: The ratio between the chord length of the blade and half of the outer diameter of the impeller is 0.16 to 0.

18.

4. The impeller according to claim 1, characterized in that: The ratio between the crown height and the chord length of the blade is 0.20 to 0.

27.

5. The impeller according to claim 4, characterized in that: The ratio between the crown height and the chord length of the blade is 0.23 to 0.

25.

6. The impeller according to claim 1, characterized in that The ratio of the distance between two adjacent blades among the plurality of blades to half of the outer diameter of the impeller is 0.035 to 0.06, and the distance between two adjacent blades is the shortest distance between the end of the pressure surface of one blade and the suction surface of another blade.

7. The impeller according to claim 5, characterized in that A ratio of a distance between two adjacent blades of the plurality of blades to a half of an outer diameter of the impeller is 0.04 to 0.

06.

8. A fan, characterized in that: The fan comprises a volute, an impeller according to any one of claims 1 to 7, wherein the impeller is arranged in the volute; a motor connected to the impeller to drive the impeller to rotate; The motor is fixed on the volute or the motor is fixed on a wall.

9. The fan according to claim 8, characterized in that: The following relationship is satisfied between the volute profile expansion ratio of the volute and the circumferential angle of the volute: y=aθ+b; Wherein, y is the volute profile expansion ratio of the volute, θ is the circumferential angle of the volute, a is the slope, a is 0.0019 to 0.0023, b is the intercept, b is 1.0 to 1.14; the volute includes a shroud arranged around the impeller, the volute profile expansion ratio is the ratio of the distance between a point on the shroud and the center of the impeller to half of the outer diameter of the impeller, and the circumferential angle is the angle between the line between the point on the shroud and the center of the impeller and the line between the starting end of the volute profile and the center of the impeller.

10. The fan according to claim 9, characterized in that: a is 0.0020 to 0.0022, and b is 1.0 to 1.

1.

11. The fan according to claim 8, characterized in that: The volute comprises a first side plate and a second side plate which are arranged opposite to each other, and a surrounding plate located between the first side plate and the second side plate; the surrounding plates are respectively connected with the first side plate and the second side plate to form the volute; the surrounding plate is formed with a volute tongue at a position close to the air outlet of the volute; The volute further comprises an oil-blocking member, which is located on a portion of the enclosure between the volute tongue and the air outlet and is used to prevent oil stains at the air outlet from flowing toward the volute tongue.

12. The fan according to claim 11, characterized in that: The oil-blocking member is a baffle arranged on the inner wall of the enclosure, and the baffle is located inside the volute or the baffle is arranged close to the air outlet of the volute; or, the oil-blocking member is a groove opened on the inner wall of the enclosure; or, the oil-blocking member is a groove formed by the enclosure protruding in a direction away from the interior of the volute.

13. The fan according to claim 11, characterized in that: The oil blocking member is also used to guide oil dirt to the first side plate and / or the second side plate.

14. The fan according to claim 13, characterized in that: At least part of the oil-blocking member is higher than a part of the oil-blocking member close to the first side plate, and / or at least part of the oil-blocking member is higher than a part of the oil-blocking member close to the second side plate.

15. The fan according to claim 13, characterized in that: The oil blocking member is partially or entirely inclined.

16. The fan according to claim 13, characterized in that: The first side plate is used for mounting the motor, and the oil blocking member is used for directing oil to the second side plate; or, the second side plate is used for mounting the motor, and the oil blocking member is used for directing oil to the first side plate.

17. The fan according to claim 16, characterized in that: A first end of the oil-blocking member close to the first side plate is higher than other parts of the oil-blocking member; or a second end of the oil-blocking member close to the second side plate is higher than other parts of the oil-blocking member.

18. The fan according to claim 13, characterized in that: The oil blocking member is used to guide the oil to the second side plate, and the distance between the oil blocking member and the air outlet gradually increases from the first end of the oil blocking member close to the first side plate to the second end of the oil blocking member close to the second side plate; or, The oil blocking member is used to guide oil to the first side plate, and the distance between the oil blocking member and the air outlet gradually decreases from a first end of the oil blocking member close to the first side plate to a second end of the oil blocking member close to the second side plate.

19. The fan according to claim 11, characterized in that: The oil blocking member includes a first end close to the first side plate and a second end close to the second side plate; the impeller includes a first end surface close to the first side plate and a second end surface close to the second side plate; The projection of the first end of the oil-blocking member in the axial direction of the impeller is located between the projection of the first end surface of the impeller in the axial direction of the impeller and the projection of the first side plate in the axial direction of the impeller; and / or, The projection of the second end of the oil-blocking member in the axial direction of the impeller is located between the projection of the second end surface of the impeller in the axial direction of the impeller and the projection of the second side plate in the horizontal direction.

20. The fan according to claim 11, characterized in that: One end of the oil-blocking member extends to the first side plate and is connected to the first side plate; and / or the other end of the oil-blocking member extends to the second side plate and is connected to the second side plate.

21. A range hood, characterized in that: A wind turbine comprising any one of claims 8 to 20.

Images