Impeller unit of cross-flow wind wheel, cross-flow wind wheel and cross-flow fan

Abstract

The utility model relates to the technical field of draught fans, and discloses an impeller unit of a cross-flow wind wheel, the cross-flow wind wheel and a cross-flow draught fan, the impeller unit comprises an annular wheel disc and a plurality of blades, the diameter D of the annular wheel disc is larger than or equal to 85 mm, and the relation between the air volume change rate QDZ / QDave of the impeller unit of the cross-flow wind wheel and the blade number Z of the blades meets the formula: QDZ / QDave =-0.0057 Z < 2 > + 0.0487 Z + 0.9151; in the formula, QDZ represents the air volume under the conditions of the diameter D and the blade number Z, and QDave represents the diameter D and the average air volume under the condition that all the blade numbers are within the interval of 20-35; the blade number Z is larger than or equal to 26 and smaller than or equal to 32, and the air volume change rate QDZ / QDave is larger than or equal to 0.98 and smaller than or equal to 1.02. According to the cross-flow wind wheel, the relation between the air volume change rate of the impeller unit of the cross-flow wind wheel and the number of the blades is set, and the number of the blades is set to range from 26 to 32, so that the number of the blades of the impeller unit of the large-diameter cross-flow wind wheel can be reduced, cost is reduced, and meanwhile the air volume performance of the impeller unit of the cross-flow wind wheel is guaranteed.

Description

Technical Field

[0001] The utility model relates to the technical field of fans, in particular to an impeller unit of a cross-flow air wheel, a cross-flow air wheel and a cross-flow fan. Background Art

[0002] The cross-flow air wheel is mainly applied to related categories of cross-flow fans. As a core component, its cost and performance have an important impact on the sales volume of products.

[0003] Among them, for cross-flow air wheels with large diameters (the outer diameter of the annular disk is more than 85 mm), there is a problem of fixed blade numbers. For the existing large-diameter cross-flow air wheels on the market, the number of blades is generally 35. However, the fixed blade numbers will lead to the fixation of blade material costs, and the material cost of the cross-flow air wheel is relatively high, reducing the profit of the product. At the same time, the fixed number of blades may cause the air wheel and the air duct not to reach the best matching relationship. Therefore, the problem of blade fixation of large-diameter cross-flow air wheels needs to be solved urgently. Summary of the Utility Model

[0004] In view of this, the utility model provides an impeller unit of a cross-flow air wheel, a cross-flow air wheel and a cross-flow fan to solve the problems of fixed air wheel cost and reduced performance caused by the fixed number of blades of large-diameter cross-flow air wheels.

[0005] In the first aspect, the utility model provides an impeller unit of a cross-flow air wheel, including an annular disk and a plurality of blades. The diameter D of the annular disk is greater than or equal to 85 mm, and the plurality of blades are arranged at intervals in the circumferential direction of the annular disk. The air volume change rate Q DZ / Q Dave of the impeller unit of the cross-flow air wheel satisfies the following relationship with the number of blades Z of the blades:

[0006] Q DZ / Q Dave =-0.0057Z 2 +0.0487Z + 0.9151

[0007] In the formula, Q DZ —the air volume under the conditions of diameter D and the number of blades Z, Q Dave —the average air volume under the conditions of diameter D and all numbers of blades in the range of 20 - 35;

[0008] The number of blades Z satisfies 26 ≤ Z ≤ 32, and the air volume change rate Q DZ / Q Dave satisfies 0.98 ≤ Q DZ / Q Dave ≤ 1.02.

[0009] Beneficial effects: By setting the relationship between the air volume change rate of the impeller unit of the cross-flow air wheel and the number of blades of the blades, and setting the number of blades to be between 26 and 32, the number of blades of the impeller unit of the large-diameter cross-flow air wheel can be reduced, the cost is lowered, and at the same time, the air volume of the impeller unit of the cross-flow air wheel can basically reach the average air volume, and the air volume performance of the impeller unit of the cross-flow air wheel will not be reduced due to the reduction of the number of blades, ensuring the comprehensive performance of the cross-flow air wheel.

[0010] In an alternative embodiment, the number of blades Z satisfies 28 ≤ Z ≤ 32.

[0011] Beneficial effects: By setting the number of blades between 28 and 32, while reducing the cost, the air volume change rate Q DZ / Q Dave of the cross-flow air wheel is basically 1, the air volume of the impeller unit of the cross-flow air wheel can reach the average air volume, ensuring that the air volume of the impeller unit of the cross-flow air wheel is large, and the air volume performance of the impeller unit of the cross-flow air wheel reaches a better level.

[0012] In an alternative embodiment, the plurality of blades are arranged in a non-uniform pitch manner.

[0013] Beneficial effects: By arranging the plurality of blades in a non-uniform pitch manner, it is possible to prevent the same wind cutting frequency from being generated when the blades are evenly distributed, thereby causing wind frequency superposition, and preventing the noise superposition of the same frequency of the blades from increasing the resonance peak value and generating noise hazards.

[0014] In an alternative embodiment, the plurality of blades are arranged in a manner of sine frequency adjustment.

[0015] Beneficial effects: By arranging the plurality of blades in a manner of sine frequency adjustment, the non-uniform distribution can be formed into a specifically adjustable distribution manner, which is convenient for optimizing the specific parameters of the non-uniformity in subsequent R & D tests, so as to obtain the optimal solution.

[0016] In an alternative embodiment, the blades are bent. Taking the center O of the annular disk as the base point, a tangent is made to the arc close to the base point in the projection of each blade on the annular disk. Select one of the blades as the first blade, then the tangent point formed by the tangent of the base point and the arc of the first blade is A1, and the tangent point formed by the tangent of the base point and the arc of the i-th blade is A i , then the included angle ∠A1OA i = θ i-1 is the distribution angle of the (i - 1)-th blade, and the blade distribution angles of the plurality of blades are arranged in the manner of sine frequency adjustment.

[0017] Beneficial effects: Since multiple blades are circumferentially spaced on the annular disk, by setting the blade distribution angle formed by the projection of the blades on the annular disk in a sine frequency adjustment manner, it is convenient to arrange multiple blades on the annular disk.

[0018] In an alternative embodiment, the sine frequency adjustment manner of the blade distribution angle satisfies:

[0019] θ i = θ0×i + A×sin(S×θ0×i×π / 180)

[0020] In the formula, i - blade number, i ∈ [1, Z]; θ0 - blade spacing angle with multiple blades evenly distributed along the circumference, θ0 = 360 / Z; A - sine adjustment amplitude; S - sine adjustment times.

[0021] In an alternative embodiment, the sine adjustment amplitude A satisfies 1 ≤ A ≤ 4.

[0022] Beneficial effects: The sine adjustment amplitude mainly affects the upper and lower limit difference of the non-uniform blade distribution angle. By setting the sine adjustment amplitude to satisfy 1 ≤ A ≤ 4, it can prevent the comprehensive performance of the impeller unit of the cross-flow wind wheel from being affected by too large or too small sine adjustment amplitude, so as to ensure that the air volume and noise of the impeller unit of the cross-flow wind wheel can reach a better level.

[0023] In an alternative embodiment, the sine adjustment times S satisfies 1 ≤ S ≤ 5.

[0024] Beneficial effects: The sine adjustment times determines the number of cycle times of the blade distribution angle changing cyclically within the circumferential range, and also determines the number of non-uniformly distributed blades λ = Z / S within one cycle. If S takes too large a value, it will lead to too many cycle times of cyclic change, but the number of non-uniformly distributed blades within one cycle is small, resulting in more blades cutting the wind at the same frequency, weakening the noise reduction effect, and at the same time, the wind speed performance will also decay. By setting the sine adjustment times to satisfy 1 ≤ S ≤ 5, it can ensure that the air volume, wind speed and noise performance of the impeller unit of the cross-flow wind wheel all reach a better level.

[0025] In a second aspect, the present invention also provides a cross-flow wind wheel, including:

[0026] The above-mentioned impeller unit.

[0027] Beneficial effects: Since the cross-flow wind wheel includes the above-mentioned impeller unit, it has the same effects as the above-mentioned impeller unit, which will not be elaborated here.

[0028] In a third aspect, the present invention also provides a cross-flow fan, including:

[0029] A housing;

[0030] The above cross-flow impeller is rotatably arranged in the housing;

[0031] A driving device is connected to the cross-flow impeller and is used to drive the cross-flow impeller to rotate.

[0032] Beneficial effects: Since the cross-flow fan includes the above cross-flow impeller, it has the same effects as the above cross-flow impeller, which will not be elaborated here. Description of the Drawings

[0033] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following will briefly introduce the drawings required for the description of the specific embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0034] Figure 1 It is a schematic structural diagram of an impeller unit according to an embodiment of the present invention;

[0035] Figure 2 It is Figure 1 A schematic diagram of the projection of the blades of the impeller unit shown on the annular disk;

[0036] Figure 3 It is a graph showing the change trend of the air volume change rate of the impeller unit with the number of blades;

[0037] Figure 4 It is a schematic diagram of the blade distribution angle;

[0038] Figure 5 It is a schematic diagram of the blade spacing angle;

[0039] Figure 6 It is a schematic diagram of the change of the blade spacing angle with the sine adjustment amplitude;

[0040] Figure 7 It is a schematic diagram of the change of the blade spacing angle with the number of sine adjustments;

[0041] Figure 8 It is a broadband noise contour map of a cross-flow impeller in the prior art;

[0042] Figure 9 It is a broadband noise contour map of the cross-flow impeller in this embodiment.

[0043] Description of the reference numerals:

[0044] 1. Annular disk; 2. Blade. Detailed Embodiments

[0045] To make the objectives, technical solutions, and advantages of the embodiments of the present utility model clearer, the technical solutions in the embodiments of the present utility model will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present utility model. Apparently, the described embodiments are some, but not all, of the embodiments of the present utility model. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present utility model without creative efforts shall fall within the protection scope of the present utility model.

[0046] The inventor of the present utility model has counted the application specification diameter distribution of cross-flow fans in recent years and found that for cross-flow fans with large diameters (the outer diameter of the annular wheel disc is above 85 mm), there is a common problem of fixed blade numbers, and the number of blades is uniformly set to 35.

[0047] On the one hand, the fixed blade number will lead to the fixation of blade material costs. The material cost of the cross-flow fan is relatively high, reducing the product profit. On the other hand, the fixed number of blades will result in a non-optimal matching relationship between the wind wheel and the air duct. The number of blades will affect the distribution of the pressure gradient between the blades. If the number of blades is too many, the blade grid density is large, which will increase the frictional loss of the impeller channel of the cross-flow fan and reduce the performance. If the number of blades is too few, the gap of the blade flow channel will be increased, easily generating secondary eddies, causing energy loss and reducing the air volume.

[0048] Reducing the number of blades can reduce the material cost, but at the same time, it will also cause attenuation of the wind speed and air volume performance. Moreover, the number of blades will also affect the pressure pulsation on the surface of the cross-flow fan blades and the separation degree of the blade surface boundary layer, thus affecting the BPF (Blade Passing Frequency) noise of the cross-flow fan.

[0049] Therefore, to solve the above problems, the inventor of the present utility model has proposed an impeller unit of a cross-flow fan, a cross-flow fan, and a cross-flow blower.

[0050] The following combines Figures 1 to 9 , to describe the embodiments of the present utility model.

[0051] According to an embodiment of the present utility model, in a first aspect, an impeller unit of a cross-flow fan is provided, including an annular wheel disc 1 and a plurality of blades 2. The diameter D of the annular wheel disc 1 is greater than or equal to 85 mm. The plurality of blades 2 are spaced apart in the circumferential direction of the annular wheel disc 1. The air volume change rate Q DZ / Q Dave of the impeller unit of the cross-flow fan and the number Z of the blades 2 satisfy the following relationship:

[0052] Q DZ / Q Dave =-0.0057Z 2 +0.0487Z + 0.9151

[0053] In the formula, QDZ — Air volume under the conditions of diameter D and number of blades Z, Q Dave — Average air volume under the conditions of diameter D and the number of all blades in the range of 20 - 35;

[0054] When the number of blades Z satisfies 26 ≤ Z ≤ 32, the air volume change rate Q DZ / Q Dave satisfies 0.98 ≤ Q DZ / Q Dave ≤ 1.02.

[0055] By setting the relationship between the air volume change rate of the impeller unit of the cross-flow air wheel and the number of blades of blade 2, and setting the number of blades between 26 and 32, it is possible to reduce the number of blades of the impeller unit of the large-diameter cross-flow air wheel, reduce the cost. At the same time, the air volume of the impeller unit of the cross-flow air wheel can basically reach the average air volume, and the air volume performance of the impeller unit of the cross-flow air wheel will not be reduced due to the reduction of the number of blades, ensuring the comprehensive performance of the cross-flow air wheel.

[0056] The impeller unit in this embodiment is applicable to a large-diameter cross-flow air wheel. The annular wheel disc 1 of the large-diameter cross-flow air wheel is circular, that is, the diameter of the annular wheel disc 1 of the impeller unit (i.e., the outer diameter of the annular wheel disc 1) D is greater than or equal to 85 mm. The upper end surface of the annular wheel disc 1 is provided with blades 2 with the number of blades Z at intervals along the circumference, as Figure 1 shown. As an alternative implementation, it can also be that the annular wheel disc 1 of the large-diameter cross-flow air wheel has other shapes, and the diameter of the annular wheel disc 1 refers to the diameter of its circumscribed circle.

[0057] Among them, a plurality of blades 2 are integrally injection-molded on the annular wheel disc 1. As an alternative implementation, it can also be that the blades 2 are fixedly connected to the annular wheel disc 1 by other means, such as welding, etc., and no more restrictions are made here.

[0058] The diameters D of the annular wheel discs 1 of the existing large-diameter cross-flow air wheels on the market mainly have several specifications such as 85 mm, 98 mm, 102 mm, 108 mm, and 120 mm, etc. The inventor of the present utility model analyzed the variation law of the air volume performance of several mainstream large-diameter cross-flow air wheels on the existing market with the change of the number of blades, and fitted the relational expression of the influence of the number of blades on the air volume change rate through software, and found that the air volume change rate Q DZ / Q Dave has the same influence trend with the number of blades Z, and all show a quadratic polynomial parabola trend, as Figure 3 shown.

[0059] Specifically, the variation trend of the air volume change rate Q DZ / Q Dave with the number of blades Z satisfies Q DZ / Q Dave= -0.0057Z 2 +0.0487Z + 0.9151, and the inventor of the present utility model has verified that the degree of fit between this change trend and the performance curve of the cross-flow fan can reach 0.9493. The closer the degree of fit between the change trend and the performance curve is to 1, the closer it is to the actual change law.

[0060] As Figure 3 shown, when the number of blades Z < 26, the air volume performance drops sharply. When the number of blades Z satisfies 26 ≤ Z ≤ 32, the air volume performance reaches a relatively optimal level, enabling the air volume of the cross-flow fan to basically reach the average air volume when the number of all blades is in the range of 20 - 35.

[0061] In one embodiment, the number of blades Z satisfies 28 ≤ Z ≤ 32. By setting the number of blades between 28 and 32, while reducing costs, it can ensure that the air volume of the impeller unit of the cross-flow fan is large and at the same order of magnitude. As Figure 3 shown, it makes the air volume change rate Q DZ / Q Dave basically 1, and the air volume of the impeller unit of the cross-flow fan can reach the average air volume, and the performance reaches a relatively optimal level. As an alternative implementation, it can also be that the number of blades Z is between 26 and 28.

[0062] In actual setting, for the impeller unit with a diameter D greater than or equal to 85 mm, regardless of the specific specification of the diameter D, such as 85 mm or 120 mm, the number of blades thereon can be selected between 26 and 32 to ensure that the air volume performance of the cross-flow fan reaches a relatively optimal level.

[0063] Since the setting of the number of blades in this embodiment is reduced compared to the number of blades of the existing large-diameter cross-flow fan, it may increase the flow channel gap of blade 2, easily generate secondary eddy currents, causing energy loss, and the number of blades will also affect the pressure pulsation on the surface of the cross-flow fan and the separation degree of the blade surface boundary layer, thus affecting the BPF noise of the cross-flow fan. Therefore, if blade 2 is evenly distributed in the circumferential direction of the annular wheel disc 1, during actual operation, the noise superposition of the same components and frequencies will increase the resonance peak value, generating noise hazards.

[0064] For this reason, multiple blades 2 in this embodiment are arranged in a non-equidistant manner to prevent the noise superposition caused by the equal-distance setting of blade 2 and the same blade shape of blade 2, thereby increasing the resonance peak value, and reducing the noise hazards of the cross-flow fan.

[0065] Specifically, multiple blades 2 in this embodiment are arranged in a manner of sine frequency adjustment. By arranging multiple blades 2 in a manner of sine frequency adjustment, a non-equidistant distribution can be formed into a specifically adjustable distribution method, which is convenient for optimizing the specific parameters of the non-equidistance during subsequent R & D tests, so as to obtain the optimal solution.

[0066] The blade 2 in this embodiment is bent, as Figure 4 shown. Taking the center O of the annular disk 1 as the base point, tangent lines are made to the arc close to the base point in the projection of each blade 2 on the annular disk 1. Select one of the blades 2 as the first blade, then the tangent point formed by making a tangent line between the base point and the arc of the first blade is A1, and the tangent point formed by making a tangent line between the base point and the arc of the i-th blade is A i , then the included angle ∠A1OA formed by the three points i =θ i-1 is the distribution angle of the (i - 1)-th blade, and the distribution angles of multiple blades 2 are set in the way of sine frequency adjustment.

[0067] In this embodiment, tangent lines are made to the arc close to the base point in the projection of each blade 2 on the annular disk 1. Here, the arc refers to the arc starting from the center O that can only form a tangent line with the projection of each blade 2 on the annular disk 1, excluding the arc starting from the center O that can both form a tangent line with the projection of each blade 2 on the annular disk 1 and intersect with the projection, as Figure 4 shown, that is, the rightmost arc in the projection of each blade 2 on the annular disk 1.

[0068] Since multiple blades 2 are arranged at intervals in the circumferential direction of the annular disk 1, by setting the distribution angles of the blades 2 formed by the projections of the blades 2 on the annular disk 1 in the way of sine frequency adjustment, it is convenient to arrange multiple blades 2 on the annular disk 1.

[0069] Specifically, the sine frequency adjustment method of the blade distribution angle in this embodiment satisfies:

[0070] θ i =θ0×i + A×sin(S×θ0×i×π / 180)

[0071] In the formula, i - blade 2 number, i ∈ [1, Z]; θ0 - the interval angle of blades 2 evenly distributed in the circumferential direction, θ0 = 360 / Z; A - sine adjustment amplitude; S - sine adjustment times.

[0072] On this basis, the interval angle Δθ between adjacent blades 2 is set i , as Figure 5 shown, the blade interval angle satisfies:

[0073] Δθ1 = θ1, Δθ i =θ i -θ i-1 (2 ≤ i ≤ Z)

[0074] Same as the blade distribution angle, the blade interval angle in this embodiment is also set in the way of sine frequency adjustment, and the specific trend curve is asFigure 6 and Figure 7 as shown

[0075] In this embodiment, the sine-adjusted amplitude A satisfies 1 ≤ A ≤ 4.

[0076] As Figure 6 shown, the sine-adjusted amplitude A mainly affects the difference between the upper and lower limits of the non-uniform blade distribution angle. By setting the sine-adjusted amplitude A to satisfy 1 ≤ A ≤ 4, it is possible to prevent the sine-adjusted amplitude A from being set too large or too small, which may affect the comprehensive performance of the impeller unit of the cross-flow fan, so as to ensure that both the air volume and noise of the impeller unit of the cross-flow fan can reach a better level.

[0077] If the sine-adjusted amplitude A is too large, it will cause a large difference in the non-uniform distribution angle of the blades 2. The excessive upper limit spacing will increase the flow channel clearance of the blades 2, easily generate secondary eddy currents, cause energy loss, and reduce the air volume. At the lower limit of the spacing, the small spacing of the blades 2 will lead to a large blade row density, increase the frictional loss of the impeller, and also reduce the performance. If the sine-adjusted amplitude A is too small, the non-uniform change amount of the blades 2 will be small, and the purpose of reducing the resonant noise by staggering cannot be achieved.

[0078] According to the data in Table 1 below, the performance of the impeller unit changes with the sine-adjusted amplitude A. When the value of A satisfies A ≥ 5, the air volume decays and the noise peak value rises significantly. By setting the sine-adjusted amplitude A to satisfy 1 ≤ A ≤ 4, the performance of the impeller unit can reach a better level. Therefore, the range setting of the sine-adjusted amplitude A in this embodiment can ensure the better performance of the cross-flow fan.

[0079] Table 1 Performance of the impeller unit changes with the sine-adjusted amplitude A

[0080] Sine-adjusted amplitude A <![CDATA[Air volume (m 3 / h)]]> Noise (dB) 1 360.42 58.3 3 358.6 59.4 4 355.49 57.6 5 355 60.9 6 353.18 61.7

[0081] As Figure 7 shown, the sine-adjusted number of times S in this embodiment satisfies 1 ≤ S ≤ 5.

[0082] The sine-adjusted number of times S determines the number of cycle times of the blade distribution angle changing cyclically within the circumferential range, and also determines the number of non-uniformly distributed blades λ = Z / S within one cycle. If the value of S is too large, it will lead to too many cycle times of cyclic change, but the number of non-uniformly distributed blades 2 within one cycle is small, resulting in more blades cutting the wind at the same frequency, weakening the noise reduction effect, and at the same time, the wind speed performance will also decay. By setting the sine-adjusted number of times S to satisfy 1 ≤ S ≤ 5, it is possible to ensure that the air volume, wind speed and noise performance of the impeller unit of the cross-flow fan all reach a better level.

[0083] According to the data in Table 2 below, the performance of the impeller unit changes with the number of sine regulations S. When the value of S satisfies S≥6, the air volume and air velocity performance decay and the noise peak value increases significantly. While setting the number of sine regulations S to satisfy 1≤S≤5 can make the performance of the cross-flow wind turbine with fewer blades reach an optimal level. Therefore, the setting range of the number of sine regulations S in this embodiment can ensure the optimal performance of the cross-flow wind turbine.

[0084] Table 2 Variation of impeller unit performance with the number of sine regulations S

[0085] Sine-adjusted number of times S <![CDATA[Air volume (m 3 / h)]]> Noise (dB) Outlet air velocity (m / s) 1 364.82 58.8 5.7 3 361.58 58.1 5.64 5 360.29 58.3 5.6 6 359.2 60.2 5.43 7 356.7 61.3 5.37

[0086] According to an embodiment of the present invention, in a second aspect, a cross-flow wind turbine is further provided, including:

[0087] The impeller unit of the above cross-flow wind turbine.

[0088] A general cross-flow wind turbine is composed of several impeller units. The cross-flow wind turbine in this embodiment includes multiple impeller units. The specific number of impeller units of the cross-flow wind turbine can be set according to actual needs and will not be limited here too much.

[0089] Since the cross-flow wind turbine in this embodiment includes the above impeller unit, although the number of blades of the cross-flow wind turbine is reduced, the air volume performance and noise reduction performance of the cross-flow wind turbine can both reach an optimal level. At the same time, due to the reduction of the number of blades, the cost can also be reduced and the profit value of the product can be improved.

[0090] Such as Figure 8 and Figure 9 As shown, compared with the large-diameter cross-flow wind turbine with 35 blades in the prior art, the total noise value in the broadband noise cloud map of the cross-flow wind turbine in this embodiment is significantly reduced, and the distribution of the inter-blade noise gradient (the white area of the cloud map) decreases significantly. Therefore, although the number of blades of the cross-flow wind turbine in this embodiment is reduced, it still has a significant noise reduction effect.

[0091] According to an embodiment of the present invention, in a third aspect, a cross-flow fan is further provided, including:

[0092] A housing;

[0093] The above cross-flow wind turbine, rotatably arranged in the housing;

[0094] A driving device, connected to the cross-flow wind turbine for driving the cross-flow wind turbine to rotate.

[0095] Specifically, the driving device is a motor, which is arranged outside the housing. The output shaft of the motor is fixedly connected to the cross-flow impeller. In this way, when the motor works, the output shaft of the motor rotates, driving the cross-flow impeller to rotate synchronously to achieve the air outlet of the cross-flow fan. As an alternative embodiment, the driving device may specifically be other devices capable of providing power, and the specific installation position of the driving device can be adjusted according to actual needs, and no further limitations are imposed here.

[0096] Although the embodiments of the present invention have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of the present invention, and such modifications and variations fall within the scope defined by the appended claims.

Claims

1. An impeller unit of a crossflow impeller, comprising an annular wheel disc (1) and a plurality of blades (2), wherein the diameter D of the annular wheel disc (1) is greater than or equal to 85 mm, and the plurality of blades (2) are arranged at intervals in the circumferential direction of the annular wheel disc (1), characterized in that: The air volume change rate Q of the impeller unit of the crossflow wind wheel DZ / Q Dave The relationship with the number Z of blades (2) satisfies: Q DZ / Q Dave =-0.0057Z 2 +0.0487Z+0.9151 In the formula, Q DZ —Air volume under the condition of diameter D and number of blades Z, Q Dave —Average air volume when the diameter D and the number of blades are between 20 and 35; The number of blades Z satisfies 26≤Z≤32, and the air volume change rate Q DZ / Q Dave Satisfy 0.98≤Q DZ / Q Dave ≤1.

02.

2. The impeller unit of the crossflow impeller according to claim 1, characterized in that: The number of blades Z satisfies 28≤Z≤32.

3. The impeller unit of the crossflow impeller according to claim 1 or 2, characterized in that: The plurality of blades (2) are arranged at unequal distances.

4. The impeller unit of the crossflow impeller according to claim 3, characterized in that: The plurality of blades (2) are arranged in a sinusoidal frequency adjustment manner.

5. The impeller unit of the crossflow impeller according to claim 4, characterized in that: The blades (2) are arranged in a curved manner, with the center O of the annular wheel disc (1) as the base point, and a tangent line is drawn to the arc of each blade (2) in the projection on the annular wheel disc (1) close to the base point. One of the blades (2) is selected as the first blade, and the tangent point formed by the tangent line between the base point and the arc of the first blade is A1, and the tangent point formed by the tangent line between the base point and the arc of the i-th blade is A i , then the angle ∠A1OA formed by the three points i =θ i-1 That is, the i-1th blade distribution angle, and the blade distribution angles of the plurality of blades (2) are set in the manner of sinusoidal frequency regulation.

6. The impeller unit of the crossflow impeller according to claim 5, characterized in that: The sinusoidal frequency adjustment method of the blade distribution angle satisfies: i i =θ0×i+A×sin(S×θ0×i×π / 180) Where, i—blade (2) number, i∈[1,Z]; θ0—the interval angle of the blades (2) uniformly distributed along the circumferential direction, θ0=360 / Z; A—sine adjustment amplitude; S—sine adjustment times.

7. The impeller unit of the crossflow impeller according to claim 6, characterized in that: The sinusoidal adjustment amplitude A satisfies 1≤A≤4.

8. The impeller unit of the crossflow impeller according to claim 6, characterized in that: The sinusoidal adjustment times S satisfies 1≤S≤5.

9. A crossflow impeller, characterized in that: include: The impeller unit according to any one of claims 1 to 8.

10. A crossflow fan, characterized in that: include: case; The crossflow impeller of claim 9 is rotatably disposed in the housing; A driving device is connected to the crossflow wind wheel and is used for driving the crossflow wind wheel to rotate.

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