Cross-flow wind wheel and air conditioner with same

Abstract

The cross-flow wind wheel comprises at least one wind wheel section, each wind wheel section comprises a partition plate and a plurality of blades arranged in the circumferential direction of the partition plate, the blades are distributed in the circumferential direction at unequal intervals, the central angle alpha between any two adjacent blades is divided into m groups clockwise, m is larger than or equal to 1, and m is larger than or equal to 1. The (T-1) th group of central angle data changes according to a first change trend, the Tth group of central angle data changes according to a second change trend, and the (T + 1) th group of central angle data changes according to a third change trend; at least one of the first change trend, the second change trend and the third change trend is oscillation rising or oscillation falling. Based on the technical scheme provided by the utility model, new distribution is designed mainly from non-periodic distribution in the circumferential direction of the blades, the impact strength and phase of each blade to the volute tongue when the blade passes through the volute tongue are different, mutual interference among harmonics is caused, the spectrum characteristic is discrete, and the working noise of the cross-flow wind wheel is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of air conditioning, in particular to an irrigation fan wheel and an air conditioner having the same. Background Art

[0002] The whistling sound in a wall-mounted unit is caused by the fan periodically impacting the volute, generating sound waves that radiate outward. A fan has N blades, for example 35. The airflow passing between each blade impacts the volute, generating sound waves. The superposition of these waves increases their amplitude, which in turn produces a sharp whistling sound similar to a whistle, significantly affecting the human ear.

[0003] Means to reduce whistling noise include non-periodic circumferential distribution of blades, certain angle distribution between different sections of the fan, and adding special structures to the volute tongue.

[0004] Different existing fans have a design with non-periodic circumferential distribution of blades, but the whistling sound is still obvious. Utility Model Content

[0005] The first aspect of the present invention aims to provide a crossflow impeller with low operating noise.

[0006] The second object of the present invention is to provide an air conditioner with low noise.

[0007] In particular, the present invention provides a crossflow impeller comprising:

[0008] It comprises at least one wind wheel segment, wherein the wind wheel segment comprises a partition and a plurality of blades arranged along the circumference of the partition, and is characterized in that:

[0009] The plurality of blades are unequally distributed along the circumferential direction, and the central angle α between any two adjacent blades is divided into m groups in a clockwise direction, wherein:

[0010] The T-1th group of central angle data changes with the first changing trend, the Tth group of central angle data changes with the second changing trend, and the T+1th group of central angle data changes with the third changing trend;

[0011] At least one of the first change trend, the second change trend, and the third change trend is an oscillating increase or an oscillating decrease.

[0012] Optionally, m≥6, where

[0013] The second set of central angle data changes in an oscillating downward trend, the third set of central angle data changes in an oscillating upward trend, and the fourth set of central angle data changes in an oscillating downward trend.

[0014] Optionally, the center angles of the circles are substituted into the following formula (1):

[0015]

[0016] Among them, X i is the degree of the i-th central angle, and n is the number of central angles;

[0017] Calculated

[0018] Optionally, the central angles are arranged in order from small to large or from large to small, and the specific central angle q is determined according to the following formula (2):

[0019]

[0020] Where n is the number of central angles;

[0021] 10°<q<11°.

[0022] Optionally, the center angles of the circles are substituted into the following formula (3):

[0023]

[0024] Among them, n is the number of central angles, X i is the angle of the center of the ith circle, is the average value of the central angle;

[0025] Calculation shows that 1<D(X)<2.

[0026] Optionally, the number of the blades is an odd number.

[0027] Optionally, the number of the blades is Y, 32<Y<38.

[0028] Optionally, a plurality of wind wheel segments are sequentially arranged along the axis direction of the crossflow wind wheel, wherein

[0029] The blades on adjacent wind wheel sections are arranged in a one-to-one correspondence; or

[0030] The blades on adjacent wind wheel sections are arranged staggered with each other; or

[0031] The blades on some of the wind rotor segments among the plurality of wind rotor segments are arranged in a one-to-one correspondence, and the blades on the remaining wind rotor segments are arranged in a staggered manner.

[0032] According to another aspect of the present invention, an air conditioner is provided, comprising the crossflow impeller as described in any one of the above items.

[0033] The crossflow wind wheel proposed in the present invention includes at least one wind wheel section, which includes a partition and multiple blades arranged circumferentially along the partition, wherein the multiple blades are unequally spaced along the circumferential direction, and the central angle α between any two adjacent blades is divided into m groups in a clockwise direction, wherein the central angle data of the T-1 group changes according to a first change trend, the central angle data of the T group changes according to a second change trend, and the central angle data of the T+1 group changes according to a third change trend; at least one of the first change trend, the second change trend, and the third change trend is an oscillating rise or an oscillating fall. Based on the technical solution proposed in the present invention, a new distribution is designed, mainly starting from the non-periodic distribution of the blades circumferentially. When each blade passes through the volute tongue, there are differences in the impact intensity and phase on the volute tongue, causing mutual interference between harmonics, and the spectrum characteristics are discrete, thereby reducing the operating noise of the crossflow wind wheel.

[0034] Lowered the whistle.

[0035] Furthermore, the number of blades is an odd number, for example, 33, 35, or 37. The odd number of blades can make the vibration frequency generated during the rotating air supply more mutually prime with other vibration frequencies in the surrounding environment, thereby reducing the resonance between the blades and the surrounding environment and further reducing the rotation noise of the crossflow impeller.

[0036] When the number of blades is 33, 35 or 39, the operating noise of the crossflow impeller is reduced.

[0037] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention, it can be implemented in accordance with the contents of the specification. In order to make the above and other purposes, features and advantages of the present invention more obvious and easy to understand, the specific implementation methods of the present invention are listed below.

[0038] Based on the following detailed description of specific embodiments of the present invention in conjunction with the accompanying drawings, those skilled in the art will become more aware of the above and other objects, advantages and features of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] Hereinafter, some specific embodiments of the present invention will be described in detail in an exemplary and non-limiting manner with reference to the accompanying drawings. The same reference numerals in the accompanying drawings indicate the same or similar components or parts. It should be understood by those skilled in the art that these drawings are not necessarily drawn to scale. In the accompanying drawings:

[0040] Figure 1 This is a first schematic diagram of a crossflow impeller according to an embodiment of the present invention;

[0041] Figure 2 is a second schematic diagram of a crossflow impeller according to an embodiment of the present invention;

[0042] Figure 3 This is a first schematic diagram of a disassembled crossflow impeller according to an embodiment of the present invention;

[0043] Figure 4 This is a second schematic diagram of a disassembled crossflow impeller according to an embodiment of the present invention;

[0044] Figure 5 This is a schematic structural diagram of a wind wheel section according to an embodiment of the present utility model;

[0045] Figure 6 is a top view of a wind wheel section according to one embodiment of the utility model;

[0046] Figure 7 This is a schematic diagram of the changing trend of the center angle between adjacent blades according to one embodiment of the present utility model;

[0047] Figure 8 This is a first schematic diagram of a crossflow wind wheel blade according to an embodiment of the present utility model;

[0048] Figure 9 This is a second schematic diagram of a crossflow wind wheel blade according to an embodiment of the present invention;

[0049] Figure 10 It is a schematic structural block diagram of an air conditioner according to an embodiment of the present utility model. DETAILED DESCRIPTION

[0050] Refer to the following Figures 1 to 10 The following describes a crossflow impeller according to an embodiment of the present invention and an air conditioner having the same. The directions or positional relationships indicated by terms such as "front," "rear," "upper," "lower," "inner," and "outer" are based on those shown in the accompanying drawings and are intended solely to facilitate and simplify the description of the present invention. They do not indicate or imply that the devices or components referred to must have, be constructed, or operate in a specific orientation, and are therefore not to be construed as limitations on the present invention.

[0051] The terms "first," "second," etc. are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, the definition of "first," "second," etc. may explicitly or implicitly include at least one of the features, that is, include one or more of the features. In the description of the present utility model, "plurality" means at least two, such as two, three, etc., unless otherwise specifically defined. When a feature "includes or contains" one or more of the features it covers, unless otherwise specifically described, this indicates that other features are not excluded and may further include other features.

[0052] In the description of the present embodiment, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any appropriate manner in any one or more embodiments or examples.

[0053] Unless otherwise defined, all terms (including technical terms and scientific terms) used in the description of the embodiments of the present invention have the same meaning as commonly understood by ordinary technicians in the technical field to which this application belongs.

[0054] The principle of unequal-distance noise reduction is as follows:

[0055] Blade rotation angular velocity: ω = n × 2π;

[0056] The rotation time interval between adjacent blades:

[0057] The noise frequency generated between adjacent blades:

[0058] For an equidistant wind wheel, the spacing between adjacent blades is the same, and the noise frequency f i This harmonic coherence enhances the pulsation intensity at the fundamental frequency, which appears as a prominent peak in the spectrum.

[0059] For unequally spaced wind rotors, the spacing between adjacent blades is different, which will weaken the fundamental frequency f1 when the blades are equally spaced to a distributed frequency (f2, f3), thereby reducing the rotational noise and weakening the peak of the equidistant wind rotor at the fundamental frequency to a smaller distributed value on the frequency spectrum.

[0060] Figure 1 This is a first schematic diagram of a crossflow impeller according to an embodiment of the present invention;

[0061] Figure 2 is a second schematic diagram of a crossflow impeller according to an embodiment of the present invention;

[0062] Figure 3 This is a first schematic diagram of a disassembled crossflow impeller according to an embodiment of the present invention;

[0063] Figure 4 This is a second schematic diagram of a disassembled crossflow impeller according to an embodiment of the present invention;

[0064] Figure 5This is a schematic structural diagram of a wind wheel section according to an embodiment of the present utility model;

[0065] Figure 6 is a top view of a wind wheel section according to one embodiment of the utility model;

[0066] Figure 7 The figure is a schematic diagram of the changing trend of the center angle between adjacent blades according to one embodiment of the present invention.

[0067] See also Figure 1-7 As shown, the utility model proposes a cross-flow wind wheel 1, which includes at least one wind wheel segment 10, and the wind wheel segment 10 includes a partition 12 and a plurality of blades 11 arranged circumferentially along the partition 12, wherein the plurality of blades 11 are unequally distributed along the circumferential direction, and the central angles between any two adjacent blades 11 are divided into m groups in a clockwise direction, wherein the T-1 group of central angle data changes with a first change trend, the T group of central angle data changes with a second change trend, and the T+1 group of central angle data changes with a third change trend, wherein at least one of the first change trend, the second change trend and the third change trend is an oscillating rise or an oscillating fall.

[0068] Among them, the partition 12 is annular, and the blades 11 are arranged along the circumference of the partition 12 and are not arranged at equal intervals, that is, any two adjacent blades 11 among all the blades 11 can form a central angle α, and these central angles α are not completely equal, and there is at least one central angle α that is different from the other central angles α.

[0069] Preferably, the degree of each central angle α is unequal, or several consecutive central angles α are equal, while the remaining central angles α are unequal. Central angle α is determined by connecting a line from a point on the side of the blade 11 closest to the axis of the crossflow rotor 1 to the center of the circle on which it lies. The center angle α is the distance between the two connecting lines. Determining central angle α does not necessarily require selecting a specific point; it is sufficient to connect each blade 11 from the same position to the center of the circle on which it lies.

[0070] In this embodiment, a new distribution is designed based on the circumferential non-periodic distribution of the blades 11, so that the impact intensity and phase of each blade 11 on the volute tongue are different when passing through the volute tongue, causing mutual interference between harmonics, and the spectrum characteristics are discrete, thereby reducing the working noise of the crossflow impeller 1.

[0071]

[0072]

[0073] Table 1 Central angle table

[0074] Figure 7The change trend of the central angle α shown is obtained by plotting the central angle α data shown in Table 1 above.

[0075] See also Figure 7 As shown, in some preferred or alternative embodiments according to the present invention, the central angle α is divided into groups m≥6, preferably 6 groups, wherein the second group of central angle α data changes in an oscillating downward trend, the third group of central angle α data changes in an oscillating upward trend, and the fourth group of central angle α data changes in an oscillating downward trend.

[0076] Among them, the three adjacent groups of central angle α data change in an oscillating upward or oscillating downward trend, which further makes the impact intensity and phase of each blade 11 on the volute tongue different when passing through the volute tongue, causing mutual interference between harmonics, and the spectrum characteristics are discrete, thereby achieving the effect of further reducing the working noise intensity of the blade 11.

[0077] In some preferred or alternative embodiments of the present invention, 8°<α<13°.

[0078] During the operation of the crossflow impeller 1, the noise generated includes not only the pulsating pressure on the surface of the blades 11, but also the pulsating pressure on the surface of the stationary volute wall and the rear volute wall. The blades 11 are arranged in an unequal spacing structure, resulting in differences in the impact intensity and phase of each blade 11 on the volute tongue when passing through the volute tongue. Its frequency spectrum characteristics are discrete, and the noise between different frequencies interferes with each other, making resonance less likely to occur, thereby effectively reducing the noise intensity.

[0079] In some preferred or alternative embodiments of the present invention, each central angle α is substituted into the following formula (1):

[0080]

[0081] Among them, X i is the angle of the i-th central angle α, and n is the number of central angles α;

[0082] Calculated

[0083] In a specific embodiment, according to the data in Table 1 above,

[0084] In some preferred or alternative embodiments of the present invention, the central angles are arranged in order from small to large or from large to small, and the specific central angle q is determined according to the following formula (2):

[0085]

[0086] Where n is the number of central angles;

[0087] 10°<q<11°.

[0088] In a specific embodiment, according to the data in Table 1 above, the degree of the specific central angle q is 10.2031°.

[0089] In some preferred or alternative embodiments of the present invention, the degrees of the center angles of each circle are substituted into the following formula (3):

[0090]

[0091] Among them, n is the number of central angles, X i is the angle of the center of the ith circle, is the average value of the central angle;

[0092] Calculation shows that 1<D(X)<2.

[0093] In a specific embodiment, according to the data in Table 1 above, D(X) is 1.4174.

[0094] In some preferred or alternative embodiments according to the present invention, the number of blades 11 is an odd number.

[0095] Among them, the number of blades 11 is an odd number, the number of blades 11 is Y, 32<Y<38, preferably 33, 35 or 37 blades. The odd number of blades 11 can make the frequency of the vibration generated during the rotation and air supply more mutually prime with the frequency of other vibrations in the surrounding environment, reduce the resonance between the blades 11 and the surrounding environment, and reduce the rotation noise of the cross-flow impeller 1.

[0096] In some preferred or alternative embodiments of the present invention, a plurality of wind wheel segments 10 are sequentially arranged along the axis of the cross-flow wind wheel, wherein

[0097] The blades 11 on adjacent wind wheel segments 10 are arranged in a one-to-one correspondence; or

[0098] The blades 11 on adjacent wind wheel segments 10 are arranged staggered with each other; or

[0099] The blades 11 on some of the wind rotor segments 10 among the multiple wind rotor segments 10 are arranged in a one-to-one correspondence, and the blades 11 on the remaining wind rotor segments 10 are arranged in a staggered manner.

[0100] The blades 11 on two adjacent rotor segments 10 are arranged in a one-to-one correspondence, meaning that after the crossflow rotor 1 is installed, no blades 11 are misaligned on its surface. In another preferred alternative embodiment, the blades 11 on adjacent rotor segments 10 are staggered, or the blades 11 on some of the multiple rotor segments 10 are arranged in a one-to-one correspondence, while the blades 11 on the remaining rotor segments 10 are staggered, which can further reduce discrete frequency noise.

[0101] In some preferred or alternative embodiments of the present invention, at least one wind wheel section 10 is located between the oppositely arranged driven shaft end cover 30 and the driving end cover 20, wherein the driven shaft end cover 30 is provided with a rotating shaft 50, and the driving end cover 20 is provided with a motor shaft sleeve 40.

[0102] Multiple rotor segments 10 are fixedly arranged along the axis of the crossflow rotor 1 between the driven shaft end cap 30 and the driving end cap 20. The number of rotor segments 10 is selected from 9 to 13, preferably 11. A rotating shaft 50 is provided on the driven shaft end cap 30. The rotating shaft 50 rotates along with the rotor segments 10 driven by the motor. The rotating shaft 50 not only provides support but also serves to mount the crossflow rotor 1 as a whole within the housing of the air conditioning and ventilation system. The driven shaft end cap 30 also has multiple, preferably six, ribs 60 on its inner side. These ribs 60 are triangular, plate-like structures of equal thickness, forming a hexagram shape. One end of each rib 60 intersects the axis of the driven shaft end cap 30. The driving end cap 20 is located on the motor side. A motor sleeve 40 is provided on its outer wall. The motor sleeve 40 is connected to the motor to transmit power from the motor to the rotor segments 10, driving their rotation. Both the driving end cover 20 and the driven shaft end cover 30 can block the airflow inside the noise-reducing wind wheel 1 from moving along the axial direction of the noise-reducing wind wheel 1 .

[0103] In addition, the diameter of the steel shaft disc is selected from any value between 2 mm and 4 mm, preferably 3 mm.

[0104] In some preferred or alternative embodiments of the present invention, the inclination angle of the blade 11 is θ, the height of the blade 11 is h, and the number of blades 11 on the partition 12 is Y, wherein,

[0105]

[0106] Wherein, k1 is a constant, 2<k1<12.

[0107] like Figure 6 As shown, the top and bottom ends of the blade 11 close to the axis of the crossflow impeller 1 are connected to the center of the circle on which they are located, and the distance between the two connecting lines is the inclination angle, h is the vertical height h of the blade 11, and is also the distance between adjacent partitions 12.

[0108] Changes in the inclination angle will change the flow path and speed of the air between the blades 11, thereby affecting the stability of the airflow. Unstable airflow is prone to turbulence and vortices. A moderate inclination angle of the blades 11 helps reduce the instability of the airflow, thereby reducing noise. The number of blades 11 directly affects the air supply and wind pressure of the fan. At the same time, the number of blades 11 also determines the number of times the airflow is divided and reorganized inside the fan, which affects the generation of noise. Under the same fan size and speed, the more blades 11 there are, the less air each blade 11 pushes, which helps to reduce the noise generated by a single blade 11. However, an increase in the number of blades 11 will also increase the overall noise level of the fan, because more blades 11 mean more airflow disturbances and collisions. Therefore, it is necessary to find a balance between the number of blades 11 and the noise level. The height h of the blades 11, that is, the distance between adjacent partitions 12, mainly affects the flow space of the airflow inside the fan. A smaller distance between the partitions 12 can restrict airflow, causing turbulence and eddies between the partitions 12; a larger distance can overly disperse the airflow, reducing fan efficiency. Properly setting the distance between partitions is crucial for reducing fan noise. Too small a distance between partitions can increase noise, as airflow is more likely to generate turbulence and eddies within a confined space. Too large a distance between partitions can reduce fan efficiency and fail to effectively reduce noise.

[0109] When the number of blades 11 is small, particularly when the number is less than 10, the fan's air volume increases significantly with the number of blades 11, and this relationship is approximately linear. As the number of blades 11 increases further, to between 10 and 39, the air volume growth trend slows, but still maintains growth. However, when the number of blades 11 exceeds 39, the air volume may decrease as the number of blades 11 increases. This is because an excessive number of blades 11 increases air flow resistance, resulting in a decrease in air volume. Within the range of available dimensions, increasing the height h of blades 11 generally leads to an increase in air volume. This is because taller blades 11 more effectively propel air flow, generating greater air volume. However, if the height h of blades 11 is too high, it may lead to unstable air flow and increased wind resistance, which in turn affects air volume output. The pitch angle of blades 11 is a key factor influencing fan air volume. When the pitch angle of blades 11 is small, the air flow generated is primarily driven by the air moving through the rotating fan blades, resulting in slower air flow and lower air volume. As the inclination angle of the blades 11 increases, the air is forced to accelerate when passing through the fan blades, forming a stronger airflow, thereby increasing the air volume. However, too large an inclination angle may also cause the wind direction to change or backflow, affecting the fan performance.

[0110] The effects of blade 11 height h, blade 11 pitch angle, and number of blades 11 on noise and airflow are interrelated, and together determine the aerodynamic performance and noise characteristics of blade 11. This embodiment effectively reduces the operating noise of the crossflow impeller 1 while maintaining the airflow of blades 11 by rationally setting the blade 11 pitch angle, number of blades 11, and distance between baffles 12.

[0111] In some preferred or alternative embodiments of the present invention, 6°<θ<7°.

[0112] In some preferred or alternative embodiments of the present invention, 55 mm < h < 65 mm.

[0113] In some preferred or alternative embodiments of the present invention, at least one wind wheel segment 10 is located between the driven shaft end cover 30 and the driving end cover 20 that are oppositely disposed, wherein:

[0114] The height h of the blade 11 of the wind rotor segment 10 closest to the driving end cover 20 is h1, 63mm

[0115] The height h of the blades 11 of the remaining wind wheel segments 10 is h2, and 55 mm < h2 < 57 mm.

[0116] In a specific embodiment, the inclination angle θ of the blade 11 is 6.72°, the height h of the blade 11 is 56 mm, the number Y of the blades 11 is 35, and k1 is 8.2.

[0117] In another specific embodiment, the inclination angle θ of the blade 11 is 6.72°, the height h of the blade 11 is 64 mm, the number Y of the blades 11 is 35, and k1 is 2.8.

[0118] In some preferred or alternative embodiments of the present invention, the inscribed circle diameter of all blades 11 on the wind rotor section 10 is d1, the circumscribed circle diameter is d2, and the chord length is L1, wherein,

[0119]

[0120] Among them, k2 is a constant, 12<k2<13.

[0121] Figure 8 FIG1 is a first schematic diagram of a crossflow wind wheel blade 11 according to an embodiment of the present invention. Figure 6 、 8 As shown, the inscribed circle diameter d1 is the diameter of the circle formed by connecting a point on the side of all blades 11 close to the central axis of the crossflow wind wheel 1; the circumscribed circle diameter d2 is the diameter of the circle formed by connecting a point on the side of all blades 11 away from the central axis of the crossflow wind wheel 1; the chord length L1 of the blade 11 is the distance between the center of the leading edge and the center of the trailing edge of the blade 11.​

[0122] Among them, the size of the inscribed circle diameter d1 affects the airflow velocity and pressure distribution inside the wind rotor 1. A smaller inscribed circle diameter d1 may lead to a narrow airflow channel, increase airflow turbulence and vortexes, and thus generate more aerodynamic noise. Aerodynamic noise is one of the main components of crossflow fan noise, so changes in the inscribed circle diameter d1 will directly affect the noise level. Increasing the circumscribed circle diameter d2 will increase the area of ​​the wind rotor 1, thereby theoretically increasing the air volume and wind pressure. However, an excessively large circumscribed circle diameter d2 may also cause the gap between the wind rotor 1 and surrounding components (such as the volute) to decrease, increasing noise. Changes in the chord length L1 of the blade 11 will directly affect the shape and area of ​​the blade 11, and thus affect the aerodynamic performance of the wind rotor 1. A longer chord length L1 may increase the stiffness of the blade 11, reducing vibration and noise; however, an excessively long chord length L1 may also increase the weight of the blade 11, increasing the load and noise of the motor. Changes in the chord length L1 will also affect the frequency characteristics of the noise. Generally speaking, a longer chord length L1 may shift the frequency of the noise toward low frequencies, while a shorter chord length L1 may shift the frequency of the noise toward high frequencies.

[0123] If the inscribed circle diameter d1 is too small, the blade 11 may lack structural strength, affecting the fan's reliability and lifespan. If it is too large, it may increase the resistance of the blade 11 and reduce airflow. The circumscribed circle diameter d2 directly affects the fan's swept area—the area covered by the blade 11 during rotation. A larger swept area theoretically moves more air, thereby increasing airflow. However, an increase in the circumscribed circle diameter d2 also results in greater resistance and higher energy consumption. Therefore, a balance between airflow, resistance, and energy consumption is necessary during design. Increasing the chord length L1 can improve the uniformity of load distribution on the blade 11 and reduce its drag coefficient, thereby increasing airflow to a certain extent. This is because a longer chord length L1 more effectively utilizes wind energy and improves wind energy conversion efficiency. However, an excessively long chord length L1 can also increase the cost and weight of the blade 11, reduce the fan's speed and power, and thus potentially affect airflow. Therefore, the selection of the chord length L1 requires careful consideration based on the specific usage environment and requirements.

[0124] The inscribed diameter d1, circumscribed diameter d2, chord length L1 of blades 11, and the number Y of blades 11 have an interrelated impact on noise and airflow, collectively determining the aerodynamic performance and noise characteristics of blades 11. This embodiment, by rationally setting the inscribed diameter d1, circumscribed diameter d2, number Y of blades 11, and chord length L1 of the crossflow rotor, further reduces the operating noise of the crossflow rotor 1 while maintaining the airflow of blades 11.

[0125] In some preferred or alternative embodiments of the present invention, 71 mm < d1 < 73 mm.

[0126] In some preferred or alternative embodiments of the present invention, 101 mm < d2 < 103 mm.

[0127] In some preferred or alternative embodiments of the present invention, 12 mm < L < 13 mm.

[0128] In a specific embodiment, the inscribed circle diameter d1 is 72 mm, the circumscribed circle diameter d2 is 102 mm, the number Y of blades 11 is 35, the chord length L1 of the blade 11 is 12.363 mm, and k2 is 12.34.

[0129] See also Figure 5 As shown, in some preferred or alternative embodiments according to the present invention, the blade 11 has a relative suction side and a pressure side, wherein,

[0130] The suction surface of the blade 11 comprises a first arc segment a, a second arc segment b and a third arc segment c which are connected in sequence;

[0131] The pressure surface of the blade 11 has a third arc segment c, a fourth arc segment d and a fifth arc segment e which are connected in sequence;

[0132] The arc length of the first arc segment a is S1, the arc length of the second arc segment b is S2, and the arc length of the third arc segment c is S3;

[0133] The arc length of the fourth arc segment d is S4, the arc length of the fifth arc segment e is S5, and the arc length of the sixth arc segment f is S6; wherein,

[0134] 0.3<S1 / S4<0.4, 2.8<S2 / S5<2.9, 0.2<S3 / S6<0.3.

[0135] See also Figure 6 As shown, the suction surface of the blade 11 is the convex arc surface of the blade 11, the pressure surface of the blade 11 is the concave arc surface of the blade 11, the first arc segment a, the second arc segment b and the third arc segment c are arranged in sequence from the leading edge to the trailing edge of the blade 11 and are arc transitions, and the fourth arc segment d, the fifth arc segment e and the sixth arc segment f are arranged in sequence from the leading edge to the trailing edge of the blade 11 and are arc transitions.

[0136] The suction surface of the blade 11 is the side of the blade 11 where the airflow velocity is higher and the pressure is lower, and is usually located on the leeward side of the blade 11. On this side, the airflow is guided by the shape of the blade 11, resulting in a specific flow pattern and pressure distribution, which have an important impact on the generation and propagation of noise. The arc length of each section of the suction surface of the blade 11 will directly affect the flow path and velocity distribution of the airflow. Changes in arc length may cause separation of the airflow on the surface of the blade 11, the generation of vortices or other unsteady flow phenomena, all of which will increase the generation of noise. In addition, changes in arc length will also affect the pressure distribution on the suction surface of the blade 11. Different arc lengths may cause changes in the pressure gradient, thereby affecting the stability of the airflow and generating noise.

[0137] The pressure surface of the blade 11 is the side of the blade 11 where the airflow velocity is lower and the pressure is higher, and is usually located on the windward side of the blade 11. On this side, the airflow is blocked and compressed by the blade 11, resulting in a specific flow pattern and pressure distribution, which have an important impact on the generation and propagation of noise. The arc length of each section of the pressure surface of the blade 11 will directly affect the flow stability of the airflow. Changes in arc length may cause the flow of air on the surface of the blade 11 to become unstable, generating turbulence or vortices, thereby increasing the generation of noise. In addition, changes in arc length will also affect the pressure distribution on the pressure surface of the blade 11. Different arc lengths may cause changes in the pressure gradient, which in turn affects the stability of the airflow and the generation of noise.

[0138] The design of the suction surface arc length directly affects the attachment of the airflow to the surface of the blade 11. A longer suction surface arc length helps the airflow to remain attached to the blade 11 for a longer time, reducing premature separation and the formation of vortices. This can improve the flow efficiency of the airflow, thereby increasing the wind volume. On the contrary, if the suction surface arc length is too short, the airflow may separate rapidly near the leading edge of the blade 11, forming vortices and turbulence, increasing resistance and reducing wind volume. Changes in the suction surface arc length will affect the lift coefficient of the blade 11. A reasonable arc length design can optimize the lift coefficient, allowing the blade 11 to more effectively capture and push air during rotation, thereby increasing wind volume. By reducing the formation of vortices and turbulence, a longer suction surface arc length can improve the aerodynamic efficiency of the blade 11, reduce energy loss, and further increase wind volume.

[0139] Variations in the arc length of the blade's pressure surface also affect the drag coefficient of blade 11. While the pressure surface primarily bears pressure, an excessively long arc length can increase the drag and weight of blade 11, adversely affecting airflow. Therefore, a balance must be found between arc length that maintains low drag and ensures smooth airflow.

[0140] The effects of the arc lengths of the suction and pressure side segments of blade 11 on noise and airflow are interrelated, and together they determine the aerodynamic performance and noise characteristics of blade 11. This embodiment further reduces the operating noise of the crossflow impeller 1 while maintaining airflow by rationally setting the arc lengths of the suction and pressure side segments.

[0141] In some preferred or alternative embodiments according to the present invention,

[0142] 1mm<S1<2mm; and / or

[0143] 9mm<S2<10mm; and / or

[0144] 2mm<S3<3mm; and / or

[0145] 3mm<S4<4mm; and / or

[0146] 3mm<S5<4mm; and / or

[0147] 8mm<S6<10mm.

[0148] In a specific embodiment, S1 is 1.2756 mm, S2 is 9.8703 mm, S3 is 2.4990 mm, S4 is 3.3923 mm, S5 is 3.4454 mm, S6 is 8.9609 mm, S1 / S4=0.38, S2 / S5=2.86, S3 / S6=0.28.

[0149] In some preferred or alternative embodiments of the present invention, the radius of the first arc segment a is r1, the radius of the second arc segment b is r2, and the radius of the third arc segment c is r3;

[0150] The radius of the fourth arc segment d is r4, the radius of the fifth arc segment e is r5, and the radius of the sixth arc segment f is r6;

[0151] 0.3<r1 / r4<0.4, 0.8<r2 / r5<0.9, 0.9<r3 / r6<1.

[0152] The change in the radius of each section of the suction surface of the blade 11 will directly affect the flow path and velocity distribution of the airflow. As the radius increases, the airflow velocity may increase, causing the flow to become more complex, generating unstable flow phenomena such as vortices and turbulence, thereby increasing the generation of noise. In addition, the change in radius will also affect the pressure distribution on the suction surface of the blade 11. At a larger radius, due to the increase in airflow velocity, the pressure may decrease, forming a low-pressure area, which may cause the airflow to separate or reattach in this area, thereby generating noise. In addition, the noise generated by the suction surface of the blade 11 will radiate and propagate outward in the form of sound waves. The intensity and frequency of the noise source at different radii may be different, resulting in superposition and interference of sound waves during propagation, further affecting the distribution and intensity of the noise.

[0153] The change in the radius of each section of the pressure surface of the blade 11 will directly affect the pressure distribution. As the radius increases, the compression effect of the airflow on the blade 11 increases, and the pressure gradient may change, which in turn affects the stability of the airflow and the generation of noise. In addition, the change in radius will also affect the flow characteristics of the airflow. At a larger radius, the airflow velocity may increase, causing the flow to become more complex, and may produce unstable flow phenomena such as vortices and turbulence, thereby increasing noise. In addition, the noise generated by the pressure surface of the blade 11 will also radiate and propagate outward in the form of sound waves. The intensity and frequency of the noise source at different radii may be different, resulting in superposition and interference of sound waves during propagation, further affecting the distribution and intensity of the noise.

[0154] Changes in the suction surface radius of blade 11 directly affect the length of airflow attached to the surface of blade 11. A larger suction surface radius can allow the airflow to remain attached for a longer distance, reducing the generation of vortices and turbulence, thereby improving the flow efficiency of the airflow. Changes in the suction surface radius also affect the separation point of the airflow. A smaller radius may cause the airflow to separate prematurely, forming vortices and turbulence, reducing aerodynamic efficiency and air volume. However, an appropriate radius design can delay the separation of the airflow, allowing more air to be effectively captured and pushed.

[0155] Changes in the radius of the pressure surface of the blade 11 will directly affect the pressure distribution on the surface of the blade 11. As the radius increases, the pressure gradient on the pressure surface may change, thereby affecting the flow characteristics of the airflow. Appropriate pressure surface radius design helps to maintain the stability of the airflow and reduce the generation of vortices and turbulence. This helps to improve the flow efficiency of the airflow, thereby increasing the wind volume. Although the pressure surface mainly bears pressure, changes in its radius will still have a certain impact on the lift. A reasonable pressure surface radius design can optimize the lift coefficient, allowing the blade 11 to capture and push air more effectively during rotation. A pressure surface radius that is too large may increase the resistance of the blade 11, resulting in increased energy loss. Therefore, it is necessary to find a balance between lift and resistance during the design process to ensure that the wind volume is maximized.

[0156] The influence of the suction and pressure surface radii of blade 11 on noise and airflow is interrelated, and together they determine the aerodynamic performance and noise characteristics of blade 11. This embodiment further reduces the operating noise of crossflow impeller 1 by rationally setting the suction and pressure surface radii, while maintaining airflow.

[0157] In some preferred or alternative embodiments according to the present invention,

[0158] 7mm<r1<8mm; and / or

[0159] 12mm<r2<13mm; and / or

[0160] 9mm<r3<10mm; and / or

[0161] 19mm<r4<20mm; and / or

[0162] 15mm<r5<16mm; and / or

[0163] 9mm<r6<11mm.

[0164] In a specific embodiment, r1 is 7.2 mm, r2 is 12.2 mm, r3 is 9.1 mm, r4 is 19.7 mm, r5 is 15.2 mm, r6 is 10.0 mm, r1 / r4=0.37, r2 / r5=0.8, r3 / r6=0.91.

[0165] In some preferred or alternative embodiments of the present invention, the chord length of the first arc segment a is P1, the chord length of the second arc segment b is P2, and the chord length of the third arc segment c is P3;

[0166] The chord length of the fourth arc segment d is P4, the chord length of the fifth arc segment e is P5, and the chord length of the sixth arc segment f is P6;

[0167] 0.3<P1 / P4<0.4, 2.7<P2 / P5<2.8, 0.4<P3 / P6<0.5.

[0168] In some preferred or alternative embodiments according to the present invention,

[0169] 1mm<P1<2mm; and / or

[0170] 9mm<P2<10mm; and / or

[0171] 2mm<P3<3mm; and / or

[0172] 3mm<P4<4mm; and / or

[0173] 3mm<P5<4mm; and / or

[0174] 5mm<P6<6mm.

[0175] In a specific embodiment, P1 is 1.2739 mm, P2 is 9.6042 mm, P3 is 2.4911 mm, P4 is 3.3881 mm, P5 is 3.4381 mm, P6 is 5.4466 mm, P1 / P4=0.38, P2 / P5=2.79, P3 / P6=0.46.

[0176] In some preferred or alternative embodiments according to the present invention,

[0177] The leading edge diameter d3 of the blade 11 is selected from any value between 0.5 mm and 1 mm; and / or

[0178] The trailing edge diameter d4 of the blade 11 is selected from any value between 1 mm and 2 mm.

[0179] In a specific embodiment, the diameter d3 of the leading edge of the blade 11 is 0.8 mm, and the diameter d4 of the trailing edge of the blade 11 is 1.5 mm.

[0180] The leading edge of a blade 11 is the first part of the blade where air first contacts it. Changes in its diameter directly affect the pattern and velocity of airflow. A larger leading edge diameter can lead to more intense air turbulence and vortices, thereby increasing aerodynamic noise. Furthermore, changes in leading edge diameter can affect the boundary layer properties on the blade 11 surface, such as its stability and transition point, further impacting noise generation and propagation.

[0181] The trailing edge of blade 11 is the primary area of ​​interaction between wake vortex shedding and the turbulent boundary layer, and contributes significantly to trailing edge noise. Changes in the trailing edge diameter directly affect the frequency and intensity of wake vortex shedding, thereby changing the characteristics of trailing edge noise. In addition, changes in the trailing edge diameter may also have a combined impact on aerodynamic noise and mechanical noise. A larger trailing edge diameter may increase the resistance to air flow, resulting in more energy dissipation and noise generation. At the same time, it may also change the vibration characteristics and bearing load of blade 11, thereby affecting mechanical noise.

[0182] The effects of the leading edge diameter d3 of blade 11 and the trailing edge diameter d4 of blade 11 on noise are interrelated, and together they determine the aerodynamic performance and noise characteristics of blade 11. This embodiment further reduces the operating noise of the crossflow impeller 1 by optimizing the leading edge diameter d3 and the trailing edge diameter d4 of blade 11.

[0183] See also Figure 8 As shown, in some preferred or alternative embodiments according to the present invention, the thickness t of the thickest part of the blade 11 is selected from any value between 1 mm and 2 mm.

[0184] In a specific embodiment, the maximum thickness t of the blade 11 is 1.6 mm.

[0185] The thickness of blade 11 affects its interaction with the air. Thicker blades 11 may generate greater air disturbances and vortices during rotation. The interaction and energy transfer of these vortices can increase aerodynamic noise. In particular, as blade 11 thickness increases, friction and impact between the blade edge and the air increase, further exacerbating aerodynamic noise.

[0186] This embodiment further reduces the operating noise of the crossflow impeller 1 by optimizing the thickness of the blades 11 .

[0187] Figure 9 This is a second schematic diagram of a crossflow wind wheel blade according to an embodiment of the present invention.

[0188] See also Figure 9 As shown, in some preferred or alternative embodiments according to the present invention,

[0189] The inlet angle of the blade 11 is β, and the outlet angle of the blade 11 is γ, wherein,

[0190] 0.3<β / γ<0.4.

[0191] See also Figure 9As shown, the distance between the distal end of blade 11 and the axis is r7, the distance between the proximal end of blade 11 and the axis is r8, the tangent line of the representative cross section of blade 11 at the distal end is the first tangent line L2, the tangent line of the mid-arc of the representative cross section at the proximal end is the second tangent line L3, the perpendicular line to the line connecting the distal end and the axis is the first perpendicular line L4, the perpendicular line to the line connecting the proximal end and the axis is the second perpendicular line L5, the angle β between the first perpendicular line and the first tangent is the inlet angle, and the angle γ between the second perpendicular line and the second tangent is the outlet angle. By selecting reasonable values ​​for the inlet and outlet angles, the crossflow blade can ensure better aerodynamic performance and improve airflow efficiency.

[0192] The inlet angle of blade 11 directly affects the initial impact of the airflow on blade 11. When the inlet angle is too large or too small, the airflow may experience strong impact and separation on the surface of blade 11, forming vortices and turbulence, which in turn increases aerodynamic noise. A suitable inlet angle helps maintain stable airflow, reduces flow separation and vortex generation, and thus reduces aerodynamic noise. Conversely, an inappropriate inlet angle may lead to unstable flow and increase noise.

[0193] The size of the outlet angle of blade 11 affects the shedding pattern and frequency of the wake vortex. A larger outlet angle may cause the wake vortex to shed more violently and frequently, generating stronger wake vortex noise. At the same time, the interaction and energy transfer between the wake vortices may also increase aerodynamic noise. A suitable outlet angle helps to smoothly diffuse the airflow and reduce the generation of vortices and turbulence. Conversely, an excessively large outlet angle may lead to uneven airflow diffusion and increase aerodynamic noise.

[0194] The inlet angle refers to the angle of the airflow when it enters the blade 11, which determines whether the airflow can smoothly enter the blade channel. When the inlet angle matches the direction of the airflow, the airflow can enter the blade 11 more smoothly, reducing impact and vortex, thereby increasing the air volume. If the inlet angle is too small or too large, it may cause the airflow to impact when entering the blade 11, increase energy loss, and reduce air volume. The inlet angle also affects the lift generation of the blade 11. The appropriate inlet angle can enable the blade 11 to more effectively capture the airflow and generate lift, thereby pushing more air through the fan or wind turbine. The design of the inlet angle has an important impact on aerodynamic efficiency. The optimized inlet angle can improve aerodynamic efficiency, reduce energy loss, and thereby increase air volume.

[0195] The outlet angle refers to the angle of the airflow when it leaves the blade 11, which determines the acceleration and diffusion of the airflow after leaving the blade 11. A larger outlet angle can make the airflow obtain greater acceleration when leaving the blade 11, but it may also cause the airflow to diffuse too quickly, reducing the air volume. An appropriate outlet angle can balance the needs of airflow acceleration and diffusion, so that the airflow maintains a higher speed and pressure after leaving the blade 11, thereby increasing the air volume. Changes in the outlet angle will also affect the pressure distribution on the surface of the blade 11. Reasonable outlet angle design can optimize the pressure distribution, reduce the generation of vortices and turbulence, improve the stability of the airflow, and thus increase the air volume.

[0196] The effects of the inlet and outlet angles of blades 11 on noise and airflow are interrelated. Together, they determine the aerodynamic performance and noise characteristics of blades 11. This embodiment further reduces the operating noise of the crossflow impeller 1 while ensuring adequate airflow by ensuring the ratio of the inlet and outlet angles is within a reasonable range.

[0197] In some preferred or alternative embodiments of the present invention, 26°<β<27°.

[0198] In some preferred or alternative embodiments of the present invention, 83°<γ<84°

[0199] In a specific embodiment, β is 26.62°, γ is 83.69°, and β / γ=0.32.

[0200] Figure 10 This is a schematic structural block diagram of an air conditioner according to an embodiment of the present invention. Figure 10 As shown, based on the same inventive concept, the present invention also proposes an air conditioner, which includes the cross-flow impeller 1 in any of the above embodiments.

[0201] The utility model proposes a cross-flow wind wheel 1 and an air conditioner 2 having the same, the cross-flow wind wheel 1 includes at least one wind wheel section 10, the wind wheel section 10 includes a partition 12 and a plurality of blades 11 arranged circumferentially along the partition 12, wherein the plurality of blades 11 are unequally distributed along the circumferential direction, and the central angle α between any two adjacent blades 11 is divided into m groups in a clockwise direction, wherein the central angle α data of the T-1th group changes with a first change trend, the central angle α data of the Tth group changes with a second change trend, and the central angle α data of the T+1th group changes with a third change trend; at least one of the first change trend, the second change trend and the third change trend is an oscillating rise or an oscillating fall, based on the technical solution proposed by the utility model, mainly starting from the circumferential non-periodic distribution of the blades 11, a new distribution is designed, when each blade passes through the volute tongue, there are differences in the impact strength and phase of the volute tongue, which causes mutual interference between harmonics, and the spectrum characteristics are discrete characteristics, thereby reducing the working noise of the cross-flow wind wheel.

[0202] At this point, those skilled in the art should recognize that, although multiple exemplary embodiments of the present invention have been shown and described in detail herein, many other variations or modifications consistent with the principles of the present invention can be directly determined or deduced from the contents disclosed herein without departing from the spirit and scope of the present invention. Therefore, the scope of the present invention should be understood and deemed to cover all such other variations or modifications.

Claims

1. A crossflow wind wheel, comprising at least one wind wheel segment, wherein the wind wheel segment comprises a partition and a plurality of blades arranged along the circumference of the partition, characterized in that: The plurality of blades are unequally distributed along the circumferential direction, and the central angle α between any two adjacent blades is divided into m groups in a clockwise direction, wherein: The T-1th group of central angle data changes with the first changing trend, the Tth group of central angle data changes with the second changing trend, and the T+1th group of central angle data changes with the third changing trend; At least one of the first change trend, the second change trend, and the third change trend is an oscillating rise or an oscillating fall; Arrange the central angles of the circle in order from small to large or from large to small, and determine the specific central angle q according to the following formula (2): Where n is the number of central angles; 10°＜q＜11°。 2. The crossflow impeller according to claim 1, characterized in that: m≥6, where The second group of central angle data changes in an oscillating downward trend, the third group of central angle data changes in an oscillating upward trend, and the fourth group of central angle data changes in an oscillating downward trend.

3. The crossflow impeller according to claim 1, characterized in that: 8°＜α＜13°。 4. The crossflow impeller according to claim 1, characterized in that: Substitute the central angles of each circle into the following formula (1): Among them, X i is the degree of the i-th central angle, and n is the number of central angles; Calculated 5. The crossflow impeller according to claim 1, characterized in that: Substitute the central angles of each circle into the following formula (3): Among them, n is the number of central angles, X i is the angle of the center of the ith circle, is the average value of the central angle; Calculation shows that 1<D(X)<2.

6. The crossflow impeller according to claim 1, characterized in that: The number of the blades is an odd number.

7. The crossflow impeller according to claim 6, characterized in that: The number of the blades is Y, 32<Y<38.

8. The crossflow impeller according to claim 1, characterized in that: The plurality of wind wheel segments are sequentially arranged along the axis direction of the crossflow wind wheel, wherein The blades on adjacent wind wheel sections are arranged in a one-to-one correspondence; or The blades on adjacent wind wheel sections are arranged staggered with each other; or The blades on some of the wind rotor segments among the plurality of wind rotor segments are arranged in a one-to-one correspondence, and the blades on the remaining wind rotor segments are arranged in a staggered manner.

9. An air conditioner, characterized in that: It comprises the crossflow impeller as described in any one of claims 1 to 8.

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