Impeller, fan and air processor

Abstract

The invention discloses an impeller, a fan and an air handler, the impeller comprises a first end plate, a second end plate and a plurality of blades, the second end plate and the first end plate are sequentially distributed at intervals in the air inlet direction of the impeller, and the second end plate is provided with an air inlet; the multiple blades are distributed in the circumferential direction of the impeller at intervals, the blades are connected with the first end plate and the second end plate, the first end plate comprises a first plate part and a second plate part annularly arranged on the periphery of the first plate part, and the second plate part obliquely extends in the air inlet direction in the direction away from the axis of the impeller. According to the technical scheme, the efficiency of the impeller can be improved.

Description

Technical Field

[0001] The present invention relates to the technical field of fans, and in particular to an impeller, a fan and an air handling unit. Background Art

[0002] The impeller used in the centrifugal fan usually includes two end plates arranged opposite to each other and a plurality of blades arranged between the two end plates, wherein the end plates are usually arranged in a flat plate structure, resulting in large flow loss and turning loss when the airflow enters the impeller, thereby resulting in low efficiency of the centrifugal fan. Summary of the invention

[0003] The main purpose of the present invention is to provide an impeller, aiming to improve the efficiency of the impeller.

[0004] To achieve the above object, the impeller proposed by the present invention comprises:

[0005] A first end plate and a second end plate, wherein the second end plate and the first end plate are sequentially spaced apart along an air inlet direction of the impeller, and the second end plate is provided with an air inlet; and

[0006] A plurality of blades are distributed at intervals along the circumference of the impeller, the blades connecting the first end plate and the second end plate, the first end plate comprising a first plate portion and a second plate portion arranged around the periphery of the first plate portion, the second plate portion extending obliquely in the direction away from the axis of the impeller in the air intake direction.

[0007] Optionally, the plate surface of the first plate portion is orthogonal to the axis of the impeller.

[0008] Optionally, the second end plate includes a third plate portion and a fourth plate portion arranged around the periphery of the third plate portion, and the fourth plate portion extends obliquely in the direction away from the axis of the impeller in the air intake direction.

[0009] Optionally, a first reference plane is defined to be perpendicular to the axis of the impeller, an angle γ between the second plate portion and the first reference plane is configured to be 10°≤γ≤40°, and / or an angle δ between the fourth plate portion and the first reference plane is configured to be 10°≤δ≤40°.

[0010] Optionally, an outer diameter of the first end plate is smaller than an outer diameter of the second end plate.

[0011] Optionally, a ratio of an outer diameter of the first end plate to an outer diameter of the second end plate is greater than or equal to 0.7.

[0012] Optionally, in the radial direction of the air inlet, a dimension between a projection line of the blade on the axial section of the air inlet and the axis of the air inlet gradually decreases along the air inlet direction.

[0013] Optionally, the blade has a first end and a second end that are sequentially distributed in the air inlet direction, and the second end extends outward in the radial direction of the impeller and exceeds the periphery of the first end plate.

[0014] Optionally, the trailing edge of the second end portion extends beyond the first end plate in the air intake direction; or, the trailing edge of the second end portion is provided with an outwardly convex transition fillet, and the transition fillet is connected to the edge of the first end plate.

[0015] Optionally, in the air intake direction, the trailing edge of the blade extends obliquely away from the rotation direction of the impeller.

[0016] Optionally, a second reference plane is defined to pass through the axis of the impeller and the center point of the trailing edge of the blade at the same time, and the angle between the trailing edge of the blade and the second reference plane is less than or equal to 45°.

[0017] Optionally, the blade has a first end and a second end that are sequentially distributed in the air inlet direction, and a periphery of the second end plate extends outward in the radial direction of the impeller and exceeds the first end.

[0018] Optionally, the outlet installation angle of the blade is less than 90°.

[0019] The present invention further provides a fan, comprising a motor and the aforementioned impeller, wherein the rotating shaft of the motor is arranged on a first end plate of the impeller.

[0020] Optionally, the fan also includes a guide cover, which is arranged upstream of the impeller and has a cross-sectional area that gradually decreases in the air intake direction. The guide cover has a guide end and a guide end distributed sequentially in the air intake direction, and the guide end extends into the air inlet of the second end plate.

[0021] Optionally, in the radial direction of the impeller, a gap d between the guide end and the edge of the air inlet is configured to be 4 mm ≤ d ≤ 10 mm.

[0022] Optionally, a depth H of the guide end extending into the air inlet is configured to be 5mm≤H≤15mm.

[0023] The present invention also provides an air handling unit, comprising the aforementioned impeller, or comprising the aforementioned fan.

[0024] In the technical solution of the present invention, by improving the structure of the first end plate facing the air inlet so that its second plate portion extends outwardly in an inclined manner in the air inlet direction, the turning degree of the airflow flowing in from the air inlet in the impeller can be reduced, thereby reducing the impact loss and turning loss of the airflow energy, thereby improving the efficiency of the impeller. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying creative work.

[0026] Figure 1 It is a structural schematic diagram of an impeller according to an embodiment of the present invention;

[0027] Figure 2 for Figure 1 a side view of the impeller shown;

[0028] Figure 3 for Figure 1 A cross-sectional view of the impeller shown, the section plane passing through the axis of the impeller;

[0029] Figure 4 is a cross-sectional view of another embodiment of an impeller of the present invention, wherein the cross-sectional plane passes through the axis of the impeller;

[0030] Figure 5 It is a structural schematic diagram of another embodiment of the impeller of the present invention;

[0031] Figure 6 for Figure 5 a side view of the impeller shown;

[0032] Figure 7 It is a structural schematic diagram of an embodiment of a fan of the present invention;

[0033] Figure 8 for Figure 7 A cross-sectional view of the fan shown, the section plane passing through the axis of the impeller;

[0034] Fig. 9 It is a structural schematic diagram of an embodiment of an air handling unit of the present invention;

[0035] Fig.10 for Fig. 9 The internal structure diagram of the air handling unit shown;

[0036] Fig.11 This is a comparison chart of the required speed of the impeller of this application and the impeller of the same diameter under the same efficiency and air volume;

[0037] Fig.12 This is a comparison chart of the efficiency of a fan using the impeller of the present application and a fan using a traditional impeller.

[0038] Description of Figure Numbers:

[0039]

[0040]

[0041] The realization of the purpose, functional features and advantages of the present invention will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0042] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0043] It should be noted that if the embodiments of the present invention involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative position relationship, movement status, etc. between the components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indication will also change accordingly.

[0044] In the present invention, unless otherwise clearly specified and limited, the terms "connection", "fixation", etc. should be understood in a broad sense. For example, "fixation" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0045] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present invention, the descriptions of "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In addition, the meaning of "and / or" appearing in the full text includes three parallel schemes. Taking "A and / or B" as an example, it includes scheme A, or scheme B, or a scheme that satisfies both A and B. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of ordinary technicians in the field to implement. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0046] The present invention provides an impeller, a fan and an air handling unit, wherein the impeller is applied to the fan, and the fan is applied to the air handling unit. Of course, the fan can also be applied to a ventilation system or other air conditioning systems.

[0047] Please refer to Figures 1 to 6 In some embodiments of the present invention, the impeller 10 includes a first end plate 11, a second end plate 12 and a blade group, the second end plate 12 and the first end plate 11 are spaced apart in sequence along the air intake direction of the impeller 10, and the second end plate 12 is provided with an air inlet 12a; the blade group includes a plurality of blades 13 spaced apart along the circumferential direction of the impeller 10, the blades 13 connect the first end plate 11 and the second end plate 12, the first end plate 11 includes a first plate portion 111 and a second plate portion 112 arranged around the periphery of the first plate portion 111, and the second plate portion 112 extends obliquely in the air intake direction in a direction away from the axis of the impeller 10.

[0048] In the technical solution of the present invention, by improving the structure of the first end plate 11 facing the air inlet 12a so that its second plate portion 112 extends outwardly in an inclined manner in the air inlet direction, the turning degree of the airflow flowing in from the air inlet 12a in the impeller 10 can be reduced, thereby reducing the impact loss and turning loss of the airflow energy, thereby improving the efficiency of the impeller 10.

[0049] It should be noted that the circumferential direction of the impeller 10 refers to the circumferential direction around the axis of the impeller 10 , and the radial direction of the impeller 10 refers to any direction radiating from the axis of the impeller 10 to the surroundings on a plane perpendicular to the axis of the impeller 10 .

[0050] In the embodiment of the present application, the outlet installation angle of the blade 13 is less than 90°, that is, the impeller 10 of the present application is configured as a centrifugal impeller 10 with backward blades 13, so that the fan can have higher efficiency and larger flow. Of course, in other embodiments, the outlet installation angle of the blade 13 can also be greater than or equal to 90°, that is, it can also be configured as a forward blade 13 or a radial blade 13.

[0051] Please refer to Figure 7 and Figure 8 In one embodiment of the fan of the present invention, the fan includes a motor, a guide cover 31 and the aforementioned impeller 10. The rotating shaft 21 of the motor is installed on the first end plate 11 of the impeller 10 to drive the first end plate 11 and the entire impeller 10 to rotate. The guide cover 31 is arranged upstream of the impeller 10. The cross-sectional area of ​​the guide cover 31 gradually decreases in the air intake direction, and has a guide end and a guide end sequentially distributed in the air intake direction. The guide end is installed in the air duct 41 and the guide end extends into the air inlet 12a of the second end plate 12, and plays the role of introducing the air in the air duct 41 located upstream of the impeller 10 into the air inlet 12a of the second end plate 12. Of course, in other embodiments, the fan may not be provided with a guide cover 31.

[0052] Specifically, optionally, the first plate portion 111 is provided with a mounting hole 11a, the end of the motor shaft 21 extends into the mounting hole 11a, and a flange 22 is provided on the outer circumferential surface of the shaft 21, and the flange 22 is screwed to the first plate portion 111. In this way, the installation reliability and convenience of the motor shaft 21 can be improved. Of course, in other embodiments, the first end plate 11 may not be provided with a mounting hole 11a, and the motor shaft 21 is directly fixed on the outer side surface of the first end plate 11, or the motor shaft 21 is fixed to the first end plate 11 by riveting, clamping or bonding.

[0053] Please refer to Figure 3 and Figure 4 In some embodiments, the plate surface of the first plate portion 111 is orthogonal to the axis of the impeller 10. In this way, the straight first plate portion 111 and the inclined second plate portion 112 cooperate to guide the airflow flowing in from the air inlet 12a, thereby reducing the turning loss without significantly reducing the pressure lift effect of the impeller. It should be noted that orthogonal refers to a vertical or nearly vertical state. Of course, in other embodiments, the first plate portion 111 can also be arranged to extend obliquely like the second plate portion 112.

[0054] Please refer to Figure 7 and Figure 8 In some embodiments, in the radial direction of the impeller 10, the gap d between the guide end and the edge of the air inlet 12a is configured to be 4mm≤d≤10mm. It can be understood that if the gap d is too small, the second end plate 12 is prone to motion interference and collision with the air guide cover 31 during the rotation of the second end plate 12 relative to the air guide cover 31; if the gap d is too large, the air in the air duct 41 is prone to enter the air inlet 12a of the impeller 10 through the gap, and constitute an obvious useless circulating airflow. The gas in the circulating airflow enters the air inlet 12a from the gap, and after flowing out of the impeller 10, it turns around the second end plate 12 and flows back to the gap, and enters the air inlet 12a again from the gap. Therefore, by limiting the gap d to within 10mm, the useless circulating airflow is weakened, thereby improving the efficiency of the impeller 10.

[0055] In some embodiments, the depth H of the guide end extending into the air inlet 12a is configured to be 5mm≤H≤15mm. It can be understood that if the depth H is too small, the matching gap between the guide end and the air inlet 12a is too short, and the obstruction effect on the circulating airflow is too small; if the depth H is too large, the size and volume of the guide end are too large, and the manufacturing cost is high.

[0056] Please refer to Fig. 9 and Fig.10In one embodiment of the air handling unit of the present invention, the air handling unit includes an air duct 41, a heat exchanger 42 and the aforementioned fan, wherein the heat exchanger 42 and the fan are both installed in the air duct 41, and the heat exchanger 42 is located upstream of the fan, and the heat exchanger 42 is used to heat or cool the air in the air duct 41. The air guide cover 31 of the fan is fixed to the air duct 41 through a mounting plate 43, the motor is fixed to the air duct 41 through a mounting bracket, and the rotating shaft 21 of the motor extends toward the air guide cover 31 and is equipped with an impeller 10. Of course, in other embodiments, the air handling unit may not be provided with a heat exchanger 42, or the heat exchanger 42 may be provided downstream of the fan.

[0057] In addition, according to the requirements of year-round air conditioning, the air handling unit may also include at least one component of a humidifier, a filter, etc. In this way, the clean air is sent to the cooler or heater through the fan to be cooled or heated to reach the required temperature, and then sent to the required place. Since the air handling unit mainly processes the state of indoor circulating air, and after using the above-mentioned fan, the air volume is large and the air quality is high, it is particularly suitable for ventilation and air exchange in large spaces and places with large traffic, such as computer rooms, shopping malls, exhibition halls, airports, etc.

[0058] The technical solution of the present invention, under the limitation of system equipment size, can reduce the speed of the impeller 10 as much as possible by maximizing the load of the impeller 10 and reducing the turning loss of the airflow energy while meeting the same pressure rise requirement, thereby significantly improving the rotation noise of the impeller 10 and improving the efficiency, thereby achieving the quiet and efficient design purpose of the fan. On the other hand, the structural design without a volute can significantly improve the dynamic and static interference noise, thereby further improving the quiet effect of the whole machine.

[0059] To further improve the efficiency of the impeller 10, please refer to Figures 1 to 6 In some embodiments, the second end plate 12 includes a third plate portion 121 and a fourth plate portion 122 arranged around the periphery of the third plate portion 121, and the fourth plate portion 122 extends obliquely in the direction away from the axis of the impeller 10 in the air intake direction. That is, the fourth plate portion 122 extends in the same direction as the second plate portion 112, and also extends obliquely outward in the air intake direction. The fourth plate portion 122 can guide the airflow, and together with the second plate portion 112, guide the airflow to the side and rear of the impeller 10, thereby further reducing the impact loss and turning loss of the airflow energy, and improving the efficiency of the impeller 10. On the other hand, the fourth plate portion 122 is arranged to extend obliquely, which can also reduce the degree of vortex generated by the airflow falling off the inner wall surface of the fourth plate portion 122, and improve the flow field inside the impeller 10, thereby reducing the flow loss of the airflow energy.

[0060] In some embodiments, the first reference plane is defined to be perpendicular to the axis of the impeller 10, and the angle γ between the second plate portion 112 and the first reference plane is configured to be 10°≤γ≤40°. That is, the inclination angle of the second plate portion 112 relative to the plane where the air inlet 12a is located is limited. It can be understood that if the inclination angle of the second plate portion 112 is too small, the effect of reducing the degree of turning of the airflow is insufficient, resulting in an insignificant effect on the reduction of the impact loss and turning loss of the airflow energy; if the inclination angle of the second plate portion 112 is too large, most of the airflow hardly turns and flows out along the axial direction of the impeller 10, resulting in a weakening of the pressure rise of the airflow when it flows through the impeller 10.

[0061] Please refer to Figure 2 and Figure 4 In some embodiments, the angle δ between the fourth plate portion 122 and the first reference plane is configured to be 10°≤δ≤40°. That is, the inclination angle of the fourth plate portion 122 relative to the plane where the air inlet 12a is located is limited. It can be understood that if the inclination angle of the fourth plate portion 122 is too small, the effect of reducing the degree of turning of the airflow is insufficient, resulting in an insignificant effect on reducing the impact loss of airflow energy and the turning loss; if the inclination angle of the fourth plate portion 122 is too large, most of the airflow hardly turns and flows out along the axial direction of the impeller 10, resulting in a weakening of the pressure rise of the airflow when it flows through the impeller 10.

[0062] Please refer to Figure 2 and Figure 4 , further optionally, the angle δ between the fourth plate portion 122 and the first reference plane is greater than the angle γ between the second plate portion 112 and the first reference plane. That is, along the extension direction of the air outlet channel formed by the interval between two adjacent blades 13, the spacing between the second plate portion 112 and the fourth plate portion 122 gradually decreases in the direction away from the axis of the impeller 10, so that the airflow can be more smoothly guided to the side and rear of the impeller 10, thereby reducing the flow loss of the airflow and improving the efficiency of the impeller 10. Of course, in other embodiments, the angle δ may be less than or equal to the angle γ.

[0063] Please refer to Figure 2 and Figure 4 In order to further reduce the impact loss of airflow energy, in some embodiments, the outer diameter D1 of the first end plate 11 is smaller than the outer diameter D2 of the second end plate 12. In this way, the first end plate 11 with a smaller size can further reduce the impact loss and turning loss of airflow energy and improve the efficiency of the impeller 10. Of course, in other embodiments, the outer diameter D1 of the first end plate 11 may be greater than or equal to the outer diameter D2 of the second end plate 12.

[0064] It should be noted that, in the embodiment of the present application, the outer contours of the first end plate 11 and the second end plate 12 are optionally configured as circular or substantially circular features, and therefore, the outer diameters of the first end plate 11 and the second end plate 12 refer to the diameters of the circles in which their outer contours are located. Of course, in embodiments where the outer contours of the first end plate 11 and the second end plate 12 are other shapes, such as when the outer contours are rectangular, polygonal or irregular curves, their outer diameters refer to the diameters of the circumscribed circles tangent to the outer contours. That is, the orthographic projection of the second end plate 12 on the first reference plane falls within the region of the orthographic projection of the first end plate 11 on the first reference plane.

[0065] In some embodiments, the ratio of the outer diameter D1 of the first end plate 11 to the outer diameter D2 of the second end plate 12 is greater than or equal to 0.7, that is, D1 / D2≥0.7. It can be understood that if the ratio of the outer diameter D1 of the first end plate 11 to the outer diameter D2 of the second end plate 12 is too small, it means that the size of the first end plate 11 is too small, and most of the airflow flows out along the axis direction of the impeller 10 without turning, resulting in a weakened pressure rise of the airflow when it flows through the impeller 10.

[0066] In some embodiments, multiple blades 13 are connected between the first end plate 11 and the second end plate 12, and are arranged around the axis of the air inlet 12a, and an air outlet is formed between the first end plate 11 and the second end plate 12. In the axial direction of the air inlet 12a, the diameters of the circles enclosed by the blades 13 are different. When the impeller is applied to a fan, the load of the impeller can be maximized within the size limit of the air duct of the fan, and then the speed can be reduced as much as possible while meeting the pressure rise requirement, thereby improving noise and the loss of airflow under the action of the impeller, thereby improving efficiency.

[0067] Specifically, when the impeller is used in a fan, the airflow will be transformed from radial flow to flow along the impeller axis through cooperation with the air duct. Since in the axial direction of the air inlet 12a, the diameters of the circles enclosed by the blades 13 are not equal, that is, based on the specific structure of the blades 13, the diameters of the circles can gradually decrease in the direction from the second end plate 12 to the first end plate 11, or the diameters of the circles can first increase and then decrease, or the diameters of the circles can first decrease and then increase. At this time, the impeller formed by the connection between the first end plate 11 and the second end plate 12 is a non-equal diameter impeller. Such a setting can effectively reduce the rotation speed, improve noise, and effectively reduce the loss during turning, thereby improving efficiency.

[0068] The outer diameter of the first end plate 11 is smaller than the outer diameter of the second end plate 12. Since the second end plate 12 can guide the airflow to the blades 13, the first end plate 11 can make the airflow flow to the air outlet along a certain angle and flow out from the air outlet. The setting of this angle not only assists the flow of the airflow, but also facilitates the change of the flow direction when cooperating with the air duct. At the same time, the outer diameter of the second end plate 12 is limited to be larger than the outer diameter of the first end plate 11, so as to form a bladeless expansion zone between the second end plate 12 and the wall of the air duct, reduce the ineffective work when the airflow passes through the impeller, further improve the static pressure efficiency, and improve the noise.

[0069] Therefore, in the axial direction of the air inlet 12a, the diameters of the circles enclosed by the blades 13 are designed to be unequal, and the outer diameter of the first end plate 11 is set to be smaller than the outer diameter of the second end plate 12. When the impeller is applied to the fan, the load of the impeller can be maximized within the size limit of the air duct of the fan, and the speed can be reduced as much as possible while meeting the pressure rise requirement, thereby effectively improving noise and the loss of airflow under the action of the impeller, thereby improving efficiency.

[0070] Please refer to Figure 2 and Figure 4 In the radial direction of the air inlet 12a, the dimension between the projection line of the blade 13 on the axial section of the air inlet 12a and the axis of the air inlet 12a gradually decreases along the air inlet direction. That is, the cross-sectional shape 13a of the blade 13 on the axial section of the impeller 10 extends obliquely toward the axis of the impeller 10 in the air inlet direction. Specifically, Figure 2 and Figure 4 In the illustrated embodiment, the axial section of the impeller 10 intercepts three blade 13 positions, and the cross-sectional shapes 13a of the three blades 13 are all roughly rectangular, and the cross-sectional shapes 13a of each blade 13 are inclined and extended in the air intake direction toward the axis direction close to the impeller 10. In this way, on the one hand, the cross-sectional area of ​​the air outlet channel can be increased under the condition of the same size, which is conducive to converting the kinetic energy of the airflow into static pressure energy, thereby improving the pressure rise effect of the impeller 10. On the other hand, along the direction from the second end plate 12 to the first end plate 11, the projection line gradually approaches the axis of the air inlet 12a, or the diameter of the circumference formed by each blade 13 gradually decreases. At this time, the impeller formed by the connection of the first end plate 11 and the second end plate 12 is a non-uniform impeller, and the restrictions such as D2 is less than D1, 0.7≤D1 / D2<1, etc. are conducive to further reliably reducing the speed, improving noise, reducing the loss during turning, and improving efficiency.

[0071] Of course, in other embodiments, the cross-sectional shape 13a of the blade 13 on the axial section of the impeller 10 may extend along the axial direction of the impeller 10, or extend obliquely away from the axial direction of the impeller 10 in the air intake direction.

[0072] In some embodiments, the blade 13 has a first end 131 and a second end 132 which are sequentially distributed in the air inlet direction, and the second end 132 extends outward in the radial direction of the impeller 10 and exceeds the periphery of the first end plate 11. That is, the outer diameter D1 of the first end plate 11 is smaller than the maximum outer diameter D4 of the blade group at one end close to the first end plate 11. In this way, the flow loss of the airflow is weakened by reducing the outer contour size of the first end plate 11. On this basis, the second end 132 of the blade 13 which exceeds the first end plate 11 and extends outward can still guide the airflow, thereby increasing the effective length of the air outlet channel to a certain extent, so as to improve the efficiency of the impeller 10. Of course, in other embodiments, the second end 132 may be flush with the periphery of the first end plate 11 in the radial direction of the impeller 10, or the periphery of the first end plate 11 may exceed the second end 132.

[0073] Specifically, the blade 13 has a leading edge 133 close to the air inlet 12a and a trailing edge 134 away from the air inlet 12a. There are many ways for the second end 132 to protrude outward, for example, please refer to Figure 1 and Figure 3 In one embodiment, the trailing edge 134 of the second end portion 132 exceeds the first end plate 11 in the air intake direction. In this way, the second end portion 132 not only exceeds the boundary of the first end plate 11 in the radial direction of the impeller 10, but also exceeds the boundary of the first end plate 11 in the air intake direction, thereby further improving the efficiency of the impeller 10.

[0074] Of course, the second end portion 132 may also be protruded outward in other ways, for example, please refer to Figure 5 and Figure 6 In another embodiment, the trailing edge 134 of the second end portion 132 may be provided with an outwardly convex transition fillet 135, and the transition fillet 135 is connected to the edge of the first end plate 11. In this way, not only the efficiency of the impeller 10 can be improved, but also the trailing edge 134 of the blade 13 can be smoothly connected to the first end plate 11 by utilizing the feature of the transition fillet 135, thereby avoiding the problem of insufficient local structural strength of the trailing edge 134 of the blade 13.

[0075] In some embodiments, the blade 13 has a first end 131 and a second end 132 which are sequentially distributed in the air inlet direction, and the periphery of the second end plate 12 extends outward in the radial direction of the impeller 10 and exceeds the first end 131. That is, the outer diameter D2 of the second end plate 12 is greater than the maximum outer diameter D3 of the blade group at one end close to the second end plate 12. In this way, the distance between the periphery of the second end plate 12 and the inner wall surface of the air duct 41 can be shortened, and a bladeless expansion area is formed between the second end plate 12 and the air duct 41, thereby improving the static pressure energy and static pressure efficiency of the impeller 10. On the other hand, by shortening the distance between the periphery of the second end plate 12 and the inner wall surface of the air duct 41, and the guiding effect of the fourth plate portion 122, it is possible to prevent the gas flowing out of the impeller 10 from bypassing the second end plate 12 and flowing back to the air inlet 12a, thereby weakening the circulating gas doing useless work, thereby improving the efficiency of the impeller 10. Of course, in other embodiments, the outer diameter of the second end plate 12 may be equal to or smaller than the outer diameter of the end of the blade assembly close to the second end plate 12 .

[0076] Without loss of generality, the performance of the mixed flow impeller is mainly reflected in the air volume and noise control. The air volume and noise level are interrelated. Generally, the larger the air volume, the higher the noise, and the smaller the air volume, the lower the noise. The air volume is proportional to the rotation speed.

[0077] Combined with the parameter design of 0.7≤D1 / D2<1, D1>D4 and D2>D3, and the diameter of each circle formed by each blade 13 in the axial direction of the air inlet is gradually reduced, the impeller is configured as a non-uniform diameter impeller, such as Fig.11 As shown in the figure, under the same air volume and efficiency conditions, the speed required by the non-equal diameter impeller is significantly lower than that required by the equal diameter impeller. Therefore, the fan with non-equal diameter impeller can effectively increase the load and significantly reduce the speed while ensuring efficiency and air volume. For specific speed value comparison, please refer to the table below.

[0078]

[0079] In some embodiments, in the air intake direction, the trailing edge 134 of the blade 13 extends obliquely away from the rotation direction of the impeller 10. That is, the trailing edge 134 of the blade 13 extends obliquely in the air intake direction, and in the rotation direction of the impeller 10, the end of the trailing edge 134 close to the second end plate 12 is located upstream of the end of the trailing edge 134 close to the first end plate 11. In this way, the flow field at the tail end of the air outlet channel can be improved, so that the flow field has a phase difference in the air intake direction, thereby improving the aerodynamic noise. Specifically, optionally, a second reference plane is defined to pass through the axis of the impeller 10 and the center point of the trailing edge 134 of the blade 13 at the same time, and the angle α between the trailing edge 134 of the blade 13 and the second reference plane is configured to be α≤45°, that is, 0<α≤45°. Of course, in other embodiments, the trailing edge 134 of the blade 13 may extend obliquely toward the rotation direction of the impeller 10 in the air intake direction, or the trailing edge 134 of the blade 13 may extend along the axis direction of the impeller 10.

[0080] It is worth mentioning that through the design of the shape, size and other structural parameters of the above structure, the performance of the impeller of the present application is significantly improved compared with the traditional equal-diameter impeller. When used on a fan, the efficiency of the fan using the non-equal-diameter impeller of the present solution is greatly improved compared with the efficiency of the fan of the traditional solution. For specific efficiency comparison, please refer to Fig.12 And the table below.

[0081]

[0082] The above descriptions are only optional embodiments of the present invention, and are not intended to limit the patent scope of the present invention. All equivalent structural changes made using the contents of the present invention's specification and drawings, or directly / indirectly applied in other related technical fields, are included in the patent protection scope of the present invention.

Claims

1. An impeller, characterized in that: include: A first end plate and a second end plate, wherein the second end plate and the first end plate are sequentially spaced apart along the air inlet direction of the impeller, and the second end plate is provided with an air inlet; as well as A plurality of blades are distributed at intervals along the circumference of the impeller, the blades connecting the first end plate and the second end plate, the first end plate comprising a first plate portion and a second plate portion arranged around the periphery of the first plate portion, the second plate portion extending obliquely in the direction away from the axis of the impeller in the air intake direction.

2. The impeller according to claim 1, characterized in that The second end plate includes a third plate portion and a fourth plate portion arranged around the periphery of the third plate portion, and the fourth plate portion extends obliquely in the direction away from the axis of the impeller in the air intake direction.

3. The impeller according to claim 2, characterized in that A first reference plane is defined to be perpendicular to the axis of the impeller, an angle γ between the second plate portion and the first reference plane is configured to be 10°≤γ≤40°, and / or an angle δ between the fourth plate portion and the first reference plane is configured to be 10°≤δ≤40°.

4. The impeller according to claim 2, characterized in that An outer diameter of the first end plate is smaller than an outer diameter of the second end plate.

5. The impeller according to claim 4, characterized in that The ratio of the outer diameter of the first end plate to the outer diameter of the second end plate is greater than or equal to 0.7; And / or, in the radial direction of the air inlet, the dimension between the projection line of the blade on the axial section of the air inlet and the axis of the air inlet gradually decreases along the air inlet direction.

6. The impeller according to claim 4, characterized in that The blade has a first end and a second end which are sequentially distributed in the air inlet direction, and the second end extends outward in the radial direction of the impeller and exceeds the periphery of the first end plate.

7. The impeller according to claim 6, characterized in that The trailing edge of the second end portion extends beyond the first end plate in the air intake direction; or, the trailing edge of the second end portion is provided with an outwardly convex transition fillet, and the transition fillet is connected to the edge of the first end plate.

8. The impeller according to claim 1, characterized in that In the air inlet direction, the trailing edge of the blade extends obliquely away from the rotation direction of the impeller.

9. The impeller according to claim 8, characterized in that A second reference plane is defined to pass through the axis of the impeller and the center point of the trailing edge of the blade at the same time, and the angle between the trailing edge of the blade and the second reference plane is less than or equal to 45°.

10. The impeller according to claim 1, characterized in that The blade has a first end and a second end that are sequentially distributed in the air inlet direction, and the periphery of the second end plate extends outward in the radial direction of the impeller and exceeds the first end; and / or, the outlet installation angle of the blade is less than 90°; And / or, the plate surface of the first plate portion is orthogonal to the axis of the impeller.

11. A fan, characterized in that: It comprises a motor and an impeller as claimed in any one of claims 1 to 10, wherein the rotating shaft of the motor is arranged on the first end plate of the impeller.

12. The fan according to claim 11, characterized in that The fan also includes a guide cover, which is arranged upstream of the impeller and has a cross-sectional area that gradually decreases in the air intake direction. The guide cover has a guide end and a guide end that are sequentially distributed in the air intake direction, and the guide end extends into the air inlet of the second end plate.

13. The fan according to claim 12, characterized in that: In the radial direction of the impeller, the gap d between the guide end and the edge of the air inlet is configured to be 4 mm ≤ d ≤ 10 mm; And / or, the depth H of the guide end extending into the air inlet is configured to be 5mm≤H≤15mm.

14. An air handling unit, characterized in that: It comprises the impeller according to any one of claims 1 to 10, or it comprises the fan according to any one of claims 11 to 13.

Images