Low-noise efficient cross-flow wind wheel and air conditioner with same

Abstract

The cross-flow wind wheel comprises at least one wind wheel section, the wind wheel section comprises a partition plate and a plurality of blades arranged in the circumferential direction of the partition plate, the inscribed circle diameter of all the blades on the wind wheel section is d1, the circumscribed circle diameter of all the blades on the wind wheel section is d2, the chord length of each blade is L1, the number of the blades on the partition plate is Y, wherein in the # imgabs0 #, k2 is a constant, and k2lt is greater than 12; 13. Based on the technical scheme provided by the utility model, the influences of the inscribed circle diameter d1, the circumscribed circle diameter d2, the chord length L1 and the number Y of the blades on the noise and the air volume are associated with one another, and jointly determine the aerodynamic performance and the noise characteristic of the blades. The inscribed circle diameter d1 and the circumscribed circle diameter d2 of the cross-flow wind wheel, the number Y of the blades and the chord length L1 of the blades are reasonably set, so that the working noise of the cross-flow wind wheel is reduced, and meanwhile it is guaranteed that the air volume of the blades is not changed.

Description

Technical Field

[0001] The utility model relates to the technical field of air conditioners, in particular to a low-noise and high-efficiency cross-flow impeller and an air conditioner having the same. Background Art

[0002] The reason for the generation of the whistling sound of the wall-mounted machine is that the fan periodically impacts the volute tongue, generating sound waves and radiating outwards. The fan has N blades, such as 35 blades. The air flow passing between each blade will impact the volute tongue, thereby generating sound waves. After superposition, the amplitude increases, and it is manifested as a sharp whistling sound when transmitted to the human ear, similar to the sound of whistling, which greatly affects the ear feeling.

[0003] Means for reducing the whistling sound include non-periodic circumferential distribution of the blades, a certain angular distribution between different sections of the fan, and adding special structures to the volute tongue, etc.

[0004] Existing different fans have non-periodic circumferential distribution designs of the blades, but the whistling sound is still obvious. Summary of the Utility Model

[0005] An object of the utility model is to reduce the noise of the cross-flow impeller.

[0006] A further object of the utility model is to ensure that the air volume of the cross-flow impeller remains unchanged.

[0007] In particular, the utility model provides a low-noise and high-efficiency cross-flow impeller, including at least one impeller section. The impeller section includes a partition plate and a plurality of blades arranged circumferentially along the partition plate. Among them,

[0008] The inscribed circle diameter of all the blades on the impeller section is d1, the circumscribed circle diameter is d2, the chord length of the blade is L1, and the number of blades on the partition plate is Y. Among them,

[0009]

[0010] Among them, k2 is a constant, and 12 < k2 < 13.

[0011] Optionally, 71 mm < d1 < 73 mm.

[0012] Optionally, 101 mm < d2 < 103 mm.

[0013] Optionally, 12 mm < L1 < 13 mm.

[0014] Optionally, the number of blades is odd.

[0015] Optionally, 32 < Y < 38.

[0016] Optionally, at least one of the impeller sections is located between the driven shaft end cover and the driving shaft end cover which are oppositely arranged. Among them,

[0017] A rotating shaft is provided on the end cover of the driven shaft, and a motor shaft sleeve is provided on the driving end cover.

[0018] Optionally, the number of the wind wheel sections is any value from 9 to 13.

[0019] Optionally, a plurality of the wind wheel sections are sequentially arranged along the axial direction of the cross-flow wind wheel, wherein

[0020] the blades on adjacent wind wheel sections are arranged in one-to-one correspondence; or

[0021] the blades on adjacent wind wheel sections are staggered; or

[0022] the blades on some of the plurality of wind wheel sections are arranged in one-to-one correspondence, and the blades on the remaining wind wheel sections are staggered.

[0023] According to another aspect of the present invention, an air conditioner is further provided, which includes the low-noise and high-efficiency cross-flow wind wheel as described in any one of the above.

[0024] The low-noise and high-efficiency cross-flow wind wheel proposed by the present invention includes at least one wind wheel section. The wind wheel section includes a partition plate and a plurality of blades arranged circumferentially along the partition plate. Among them, the inscribed circle diameter of all the blades on the wind wheel section is d1, the circumscribed circle diameter is d2, the chord length of the blade is L1, and the number of blades on the partition plate is Y, wherein wherein, k2 is a constant, and 12 < k2 < 13. Based on the technical solution proposed by the present invention, the influence of the inscribed circle diameter d1, the circumscribed circle diameter d2, the chord length L1 of the blade, and the number Y of the blades on the noise and the air volume is mutually related, and they jointly determine the aerodynamic performance and the noise characteristics of the blade. By reasonably setting the inscribed circle diameter d1, the circumscribed circle diameter d2, the number Y of the blades, and the chord length L1 of the blade of the cross-flow wind wheel, the working noise of the cross-flow wind wheel is reduced while ensuring that the air volume of the blade remains unchanged.

[0025] The above description is only an overview of the technical solution of the present invention. In order to be able to understand the technical means of the present invention more clearly, it can be implemented according to the content of the description. And in order to make the above and other purposes, features and advantages of the present invention more obvious and understandable, the following specific embodiments of the present invention are specifically exemplified.

[0026] Those skilled in the art will understand the above and other purposes, advantages and features of the present invention more clearly according to the following detailed description of the specific embodiments of the present invention in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Some specific embodiments of the present utility model will be described in detail hereinafter with reference to the accompanying drawings in an illustrative rather than restrictive manner. The same reference numerals in the drawings denote the same or similar components or parts. Those skilled in the art should understand that these drawings are not necessarily drawn to scale. In the drawings:

[0028] Figure 1 is the first schematic diagram of a low-noise and high-efficiency cross-flow impeller according to an embodiment of the present utility model;

[0029] Figure 2 is the second schematic diagram of a low-noise and high-efficiency cross-flow impeller according to an embodiment of the present utility model;

[0030] Figure 3 is the first schematic diagram of a disassembled low-noise and high-efficiency cross-flow impeller according to an embodiment of the present utility model;

[0031] Figure 4 is the second schematic diagram of a disassembled low-noise and high-efficiency cross-flow impeller according to an embodiment of the present utility model;

[0032] Figure 5 is the schematic structural diagram of an impeller section according to an embodiment of the present utility model;

[0033] Figure 6 is the top view of an impeller section according to an embodiment of the present utility model;

[0034] Figure 7 is the schematic diagram of the change trend of the central angle degree between adjacent blades according to an embodiment of the present utility model;

[0035] Figure 8 is the first schematic diagram of a blade of a low-noise and high-efficiency cross-flow impeller according to an embodiment of the present utility model;

[0036] Figure 9 is the second schematic diagram of a blade of a low-noise and high-efficiency cross-flow impeller according to an embodiment of the present utility model;

[0037] Figure 10 is the schematic structural block diagram of an air conditioner according to an embodiment of the present utility model. Specific Embodiments

[0038] The cross-flow impeller of the embodiment of the present utility model and the air conditioner having the same will be described below with reference to Figures 1 to 10 Among them, the orientation or positional relationship indicated by "front", "rear", "upper", "lower", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present utility model.

[0039] The terms "first", "second", etc. are only used for descriptive purposes and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first", "second", etc. may explicitly or implicitly include at least one such feature, that is, include one or more such features. In the description of the present utility model, the meaning of "a plurality" is at least two, such as two, three, etc., unless otherwise specifically defined. When a certain feature "includes or contains" a certain or certain features it covers, unless otherwise specifically described, this indicates that other features are not excluded and other features may be further included.

[0040] In the description of this embodiment, the description referring to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples", etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present utility model. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0041] Unless otherwise limited, all terms (including technical terms and scientific terms) used in the description of the embodiments of the present utility model have the same meaning as commonly understood by those of ordinary skill in the technical field to which this application belongs.

[0042] The principle of non-uniform noise reduction is as follows:

[0043] Angular velocity of blade rotation: ω = n×2π;

[0044] Rotation time interval between adjacent blades:

[0045] Noise frequency generated between adjacent blades:

[0046] For an equidistant wind wheel, the distance between adjacent blades is the same, and the generated noise frequency f i is all equal. This harmonic coherence enhances the pulsation intensity at the fundamental frequency, and on the spectrum, it shows prominent spikes.

[0047] For a non-uniform wind wheel, the distances between adjacent blades are different, which weakens the fundamental frequency f1 at equidistant time to a distributed frequency (f2, f3), thereby reducing the rotational noise, and weakening the peak value of the equidistant wind wheel at the fundamental frequency to a smaller distributed value on the frequency spectrum.

[0048] Figure 1 is the first schematic diagram of a cross-flow wind wheel according to an embodiment of the present utility model;

[0049] Figure 2 is the second schematic diagram of a cross-flow impeller according to an embodiment of the present utility model;

[0050] Figure 3 is the first schematic diagram of a disassembled cross-flow impeller according to an embodiment of the present utility model;

[0051] Figure 4 is the second schematic diagram of a disassembled cross-flow impeller according to an embodiment of the present utility model;

[0052] Figure 5 is the structural schematic diagram of a wind wheel section according to an embodiment of the present utility model;

[0053] Figure 6 is the top view of a wind wheel section according to an embodiment of the present utility model;

[0054] Figure 7 is the schematic diagram of the changing trend of the central angle degree between adjacent blades according to an embodiment of the present utility model.

[0055] See Figures 1 - 7 As shown, the present utility model provides a cross-flow impeller 1, which includes at least one wind wheel section 10. The wind wheel section 10 includes a partition plate 12 and a plurality of blades 11 arranged circumferentially along the partition plate 12. Among them, the plurality of blades 11 are unevenly distributed in the circumferential direction. The central angle between any two adjacent blades 11 is divided into m groups in the clockwise direction. Among them, the central angle data of the (T - 1)th group changes in a first changing trend, the central angle data of the Tth group changes in a second changing trend, and the central angle data of the (T + 1)th group changes in a third changing trend. Among them, at least one of the first changing trend, the second changing trend, and the third changing trend is an oscillating increase or an oscillating decrease.

[0056] Among them, the partition plate 12 is annular, and the blades 11 are arranged circumferentially along the partition plate 12 and are unevenly arranged. 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 at least one central angle α is not equal to the other central angles α.

[0057] Preferably, the degrees of each central angle α are not equal, or several consecutive central angles α are equal, and the remaining central angles α are not equal. The determination method of the central angle α is to connect the center of the circle on the circumference where a point on the side of the blade 11 close to the axis of the cross-flow impeller 1 is located. The angle between the two connections is the central angle α. When determining the central angle α, it is not necessarily to select a specific point for determination, as long as each blade 11 is connected to the center of the circle on its circumference from the same position.

[0058] In this embodiment, starting from the circumferential aperiodic distribution of the blades 11, a new distribution is designed, so that when each blade 11 passes through the volute tongue, the impact intensity and phase on the volute tongue are different, causing mutual interference between harmonics, and the spectral characteristics are discrete, reducing the working noise of the cross-flow impeller 1.

[0059]

[0060]

[0061] Table 1 Central Angle Degree Table

[0062] Figure 7 The shown change trend of the central angle α is obtained by plotting according to the central angle α data shown in Table 1 above.

[0063] See Figure 7 As shown, in some preferred or alternative embodiments according to the present invention, the central angle α is divided into m≥6 groups, preferably 6 groups. Among them, the central angle α data of the second group changes in an oscillating downward trend, the central angle α data of the third group changes in an oscillating upward trend, and the central angle α data of the fourth group changes in an oscillating downward trend.

[0064] Among them, the central angle α data of adjacent three groups change in an oscillating upward or oscillating downward trend respectively, further making 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 spectral characteristics are discrete, thereby achieving the effect of further reducing the working noise intensity of the blade 11.

[0065] In some preferred or alternative embodiments according to the present invention, 8° < α < 13°.

[0066] During the operation of the cross-flow impeller 1, the generated noise not only includes the pulsating pressure on the surface of the blade 11, but also includes the pulsating pressure on the surfaces of the stationary volute wall and the rear volute wall. The blades 11 are arranged in a non-uniform spacing structure, resulting in different impact intensities and phases of each blade 11 on the volute tongue when passing through the volute tongue. Its spectral characteristics are discrete, and the noise between frequencies interferes with each other, and resonance is not likely to occur, effectively reducing the noise intensity.

[0067] In some preferred or alternative embodiments according to the present invention, substitute the central angle α values into the following formula (1):

[0068]

[0069] Among them, X i is the central angle α value of the i-th one, and n is the number of central angle α;

[0070] Calculate to obtain

[0071] In a specific embodiment, it is obtained according to the data in Table 1 above

[0072] In some preferred or alternative embodiments according to the present utility model, the central angles are arranged in ascending or descending order, and a specific central angle q is determined according to the following formula (2):

[0073]

[0074] where n is the number of central angles;

[0075] 10° < q < 11°.

[0076] In a specific embodiment, the degree of the specific central angle q obtained according to the data in Table 1 above is 10.2031°.

[0077] In some preferred or alternative embodiments according to the present utility model, the degrees of each central angle are substituted into the following formula (3):

[0078]

[0079] where n is the number of central angles, X i is the degree of the i-th central angle, is the average value of the central angle degrees;

[0080] It is calculated that 1 < D(X) < 2.

[0081] In a specific embodiment, D(X) obtained according to the data in Table 1 above is 1.4174.

[0082] In some preferred or alternative embodiments according to the present utility model, the number of blades 11 is odd.

[0083] where the number of blades 11 is odd, the number of blades 11 is Y, 32 < Y < 38, preferably 33, 35 or 37. The odd number of blades 11 can make the frequency of the vibration generated during rotational air supply more co-prime with the frequencies of other vibrations in the surrounding environment, reduce the resonance between the blades 11 and the surrounding environment, and reduce the rotational noise of the cross-flow impeller 1.

[0084] In some preferred or alternative embodiments according to the present utility model, a plurality of impeller sections 10 are arranged in sequence along the axis direction of the cross-flow impeller, where

[0085] the blades 11 on adjacent impeller sections 10 are arranged in one-to-one correspondence; or

[0086] the blades 11 on adjacent impeller sections 10 are arranged staggeredly; or

[0087] The blades 11 on some of the multiple wind wheel sections 10 are arranged in one-to-one correspondence, and the blades 11 on the remaining wind wheel sections 10 are arranged staggeredly.

[0088] Among them, the blades 11 on two adjacent wind wheel sections 10 are arranged in one-to-one correspondence, that is, after the cross-flow wind wheel 1 is installed, there will be no misalignment of the blades 11 on its surface. In another preferred alternative embodiment, the blades 11 on adjacent wind wheel sections 10 are arranged staggeredly, or some of the multiple wind wheel sections 10 have the blades 11 arranged in one-to-one correspondence, and the blades 11 on the remaining wind wheel sections 10 are arranged staggeredly, which can further reduce the discrete frequency noise.

[0089] In some preferred or alternative embodiments according to the present invention, at least one wind wheel section 10 is located between the relatively arranged driven shaft end cover 30 and the drive end cover 20. Among them, a rotating shaft 50 is provided on the driven shaft end cover 30, and a motor shaft sleeve 40 is provided on the drive end cover 20.

[0090] Among them, a plurality of wind wheel sections 10 are fixedly arranged in sequence along the axis direction of the cross-flow wind wheel 1 between the driven shaft end cover 30 and the drive end cover 20. The number of wind wheel sections 10 is selected from any value between 9 and 13 sections, preferably 11 sections. Among them, a rotating shaft 50 is provided on the driven shaft end cover 30, and the rotating shaft 50 rotates together with the wind wheel section 10 under the drive of the motor. In addition, while the rotating shaft 50 plays a supporting role, it is also used to install the cross-flow wind wheel 1 as a whole in the housing of the air-conditioning ventilation system. A plurality of ribs 60 are further provided on the inner side of the driven shaft end cover 30, preferably six. The ribs 60 are triangular plate-like structures with equal thickness and are star-shaped as a whole. One end of the plurality of ribs 60 intersects on the axis of the driven shaft end cover 30. The drive end cover 20 is located on the motor side, and a motor shaft sleeve 40 is provided on the outer wall of the drive end cover 20. The motor shaft sleeve 40 is connected to the motor to transmit the power of the motor to the wind wheel section 10 and drive the wind wheel section 10 to rotate. Both the drive end cover 20 and the driven shaft end cover 30 can prevent the airflow inside the noise-reducing wind wheel 1 from moving axially along the noise-reducing wind wheel 1.

[0091] In addition, the diameter of the steel shaft disc is selected from any value between 2 mm and 4 mm, preferably 3 mm.

[0092] In some preferred or alternative embodiments according to 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 plate 12 is Y. Among them,

[0093]

[0094] Among them, k1 is a constant, and 2 < k1 < 12.

[0095] Such as Figure 6As shown, the top and bottom of the blade 11 near the axis of the cross-flow impeller 1 are respectively connected to the center of the circle on its circumference. The inclination angle is the angle between the two connecting lines. h is the vertical height h of the blade 11 and also the distance between adjacent partitions 12.

[0096] The change in the angle of the inclination angle will change the flow path and speed of the air between the blades 11, thereby affecting the stability of the air flow. Unstable air flow is prone to generate turbulence and eddy currents. An appropriate inclination angle of the blade 11 helps to reduce the instability of the air flow, thereby reducing noise. The number of blades 11 directly affects the air volume and air pressure of the fan. At the same time, the number of blades 11 also determines the number of times the air flow is divided and recombined inside the fan, which will affect the generation of noise. At the same fan size and rotational speed, the more the number of blades 11, the less the amount of air pushed by each blade 11, which helps to reduce the noise generated by a single blade 11. However, the increase in the number of blades 11 will also increase the overall noise level of the fan because more blades 11 mean more air flow disturbances and collisions. Therefore, a balance needs to be found between the number of blades 11 and the noise level. The height h of the blade 11, that is, the distance between adjacent partitions 12, mainly affects the flow space of the air flow inside the fan. A smaller distance between the partitions 12 may limit the flow of the air flow, resulting in turbulence and eddy currents of the air flow between the partitions 12; while a larger distance between the partitions 12 may make the air flow too dispersed, reducing the air supply efficiency of the fan. The reasonable setting of the distance between the partitions is crucial for reducing the noise of the fan. An overly small distance between the partitions will increase the generation of noise because the air flow is more likely to generate turbulence and eddy currents in a restricted space; while an overly large distance between the partitions 12 may reduce the air supply efficiency of the fan and cannot effectively reduce the noise either.

[0097] When the number of blades 11 is small, especially when the number of blades 11 is less than 10, the air volume of the fan increases significantly with the increase in the number of blades 11, and this relationship is approximately linear. When the number of blades 11 further increases and is between 10 and 39, the growth trend of the air volume gradually slows down but still remains increasing. However, when the number of blades 11 exceeds 39, the air volume may decrease with the increase in the number of blades 11. This is because too many blades 11 will increase the resistance to air flow, resulting in a decrease in the air volume. Within the optional size range, an increase in the height h of the blades 11 generally leads to an increase in the air volume. This is because higher blades 11 can more effectively push the air flow, thus generating a larger air volume. However, if the height h of the blades 11 is too high, it may cause unstable air flow and an increase in wind resistance, which instead affects the output of the air volume. The inclination angle of the blades 11 is one of the key factors affecting the air volume of the fan. When the inclination angle of the blades 11 is small, the generated air flow is mainly formed by the air driven by the rotation of the fan blades. At this time, the air flow speed is slow and the air volume is small. As the inclination angle of the blades 11 increases, the air is forced to accelerate when passing through the fan blades, forming a stronger air flow, thereby increasing the air volume. However, too large an inclination angle may also cause a change in the wind direction or a back-blow phenomenon, affecting the performance of the fan.

[0098] The effects of the height h of the blades 11, the inclination angle of the blades 11, and the number of blades 11 on the noise and air volume are interrelated, and they jointly determine the aerodynamic performance and noise characteristics of the blades 11. In this embodiment, by reasonably setting the inclination angle of the blades 11, the number of blades 11, and the distance between the partition plates 12, the working noise of the cross-flow impeller 1 is effectively reduced while ensuring that the air volume of the blades 11 remains unchanged.

[0099] In some preferred or alternative embodiments according to the present invention, 6° < θ < 7°.

[0100] In some preferred or alternative embodiments according to the present invention, 55 mm < h < 65 mm.

[0101] In some preferred or alternative embodiments according to the present invention, at least one wind wheel section 10 is located between the relatively arranged driven shaft end covers 30 and the driving end cover 20, wherein,

[0102] The height h of the blades 11 of the wind wheel section 10 closest to the driving end cover 20 is h1, and 63 mm < h1 < 65 mm; and / or

[0103] The height h of the blades 11 of the remaining wind wheel sections 10 is h2, and 55 mm < h2 < 57 mm.

[0104] In a specific embodiment, the inclination angle θ of the blades 11 is 6.72°, the height h of the blades 11 is 56 mm, the number Y of the blades 11 is 35, and k1 is 8.2.

[0105] In another specific embodiment, the tilt 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.

[0106] In some preferred or alternative embodiments according to the present invention, for the inscribed circle diameter d1, the circumscribed circle diameter d2, and the chord length L1 of all the blades 11 on the cross-flow impeller section 10, where,

[0107]

[0108] where k2 is a constant, and 12 < k2 < 13.

[0109] Figure 8 is the first schematic diagram of the cross-flow impeller blade 11 according to an embodiment of the present invention. Refer to Figure 6 、 8 As shown, the inscribed circle diameter d1 is the diameter of the circle formed by connecting the points on one side of all the blades 11 close to the central axis of the cross-flow impeller 1; the circumscribed circle diameter d2 is the diameter of the circle formed by connecting the points on the side of all the blades 11 far from the central axis of the cross-flow impeller 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.

[0110] Among them, the size of the inscribed circle diameter d1 will affect the air flow velocity and pressure distribution inside the impeller 1. A smaller inscribed circle diameter d1 may lead to a narrow air flow channel, increasing air flow turbulence and eddy currents, thus generating more aerodynamic noise. Aerodynamic noise is one of the main components of the cross-flow fan noise. Therefore, the change of the inscribed circle diameter d1 will directly affect the noise level. The increase of the circumscribed circle diameter d2 will increase the area of the impeller 1, thus theoretically improving the air volume and air pressure. However, an overly large circumscribed circle diameter d2 may also lead to a reduction in the gap between the impeller 1 and the surrounding components (such as the volute), increasing the noise. The change of 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 impeller 1. A longer chord length L1 may increase the stiffness of the blade 11, reducing vibration and noise; but an overly long chord length L1 may also cause an increase in the weight of the blade 11, increasing the load and noise of the motor. The change of 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 towards the low-frequency direction, while a shorter chord length L1 may shift the frequency of the noise towards the high-frequency direction.

[0111] If the inscribed circle diameter d1 is too small, it may lead to insufficient structural strength of the blade 11, affecting the reliability and lifespan of the fan. If it is too large, it may increase the resistance of the blade 11 and reduce the air volume. The circumscribed circle diameter d2 directly affects the swept area of the fan, that is, the area that can be covered when the blade 11 rotates. The larger the swept area, the more air can be driven theoretically, thus increasing the air volume. However, increasing the circumscribed circle diameter d2 will also bring greater resistance and higher energy consumption. Therefore, when designing, it is necessary to balance the relationship among air volume, resistance, and energy consumption. Increasing the chord length L1 can improve the uniformity of the load distribution of the blade 11 and reduce the resistance coefficient of the blade 11, thereby improving the air volume to a certain extent. This is because a longer chord length L1 can utilize wind energy more effectively and improve the conversion efficiency of wind energy. However, an overly long chord length L1 will also increase the cost and weight of the blade 11, reduce the rotational speed and power of the fan, and may thus affect the air volume. Therefore, when selecting the chord length L1, it is necessary to balance according to the specific usage environment and requirements.

[0112] The inscribed circle diameter d1, circumscribed circle diameter d2, chord length L1 of the blade 11, and the number Y of the blades 11 are interrelated in their effects on noise and air volume, and they jointly determine the aerodynamic performance and noise characteristics of the blade 11. In this embodiment, by reasonably setting the inscribed circle diameter d1, circumscribed circle diameter d2, the number Y of the blades 11, and the chord length L1 of the blade 11 of the cross-flow impeller, the working noise of the cross-flow impeller 1 is further reduced while ensuring that the air volume of the blade 11 remains unchanged.

[0113] In some preferred or alternative embodiments according to the present invention, 71 mm < d1 < 73 mm.

[0114] In some preferred or alternative embodiments according to the present invention, 101 mm < d2 < 103 mm.

[0115] In some preferred or alternative embodiments according to the present invention, 12 mm < L < 13 mm.

[0116] In a specific embodiment, the inscribed circle diameter d1 is 72 mm, the circumscribed circle diameter d2 is 102 mm, the number Y of the blades 11 is 35, the chord length L1 of the blade 11 is 12.363 mm, and k2 is 12.34.

[0117] See Figure 5 As shown, in some preferred or alternative embodiments according to the present invention, the blade 11 has a relative suction surface and pressure surface, wherein,

[0118] The suction surface of the blade 11 has a first arc segment a, a second arc segment b, and a third arc segment c connected in sequence;

[0119] The pressure surface of the blade 11 has a third arc segment c, a fourth arc segment d, and a fifth arc segment e that are connected in sequence;

[0120] 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;

[0121] 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; where,

[0122] 0.3 < S1 / S4 < 0.4, 2.8 < S2 / S5 < 2.9, 0.2 < S3 / S6 < 0.3.

[0123] See 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 in arc transition, 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 in arc transition.

[0124] The suction surface of the blade 11 is the side of the blade 11 where the air flow velocity is relatively large and the pressure is relatively low, and is usually located on the leeward side of the blade 11. On this side, the air flow is guided by the shape of the blade 11 to generate specific flow patterns and pressure distributions, all of which have important effects on the generation and propagation of noise. The arc lengths of each segment of the suction surface of the blade 11 will directly affect the flow path and velocity distribution of the air flow. Changes in the arc length may cause the separation, vortex, or other unsteady flow phenomena of the air flow on the surface of the blade 11, all of which will increase the generation of noise. In addition, changes in the arc length will also affect the pressure distribution on the suction surface of the blade 11. Different arc lengths may lead to changes in the pressure gradient, thereby affecting the stability of the air flow and generating noise.

[0125] The pressure surface of the blade 11 is the side of the blade 11 where the air flow velocity is relatively small and the pressure is relatively high, and is usually located on the windward side of the blade 11. On this side, the air flow is blocked and compressed by the blade 11 to generate specific flow patterns and pressure distributions, all of which have important effects on the generation and propagation of noise. The arc lengths of each segment of the pressure surface of the blade 11 will directly affect the flow stability of the air flow. Changes in the arc length may cause the flow of the air flow on the surface of the blade 11 to become unstable, generating turbulence or vortices, thereby increasing the generation of noise. In addition, changes in the arc length will also affect the pressure distribution on the pressure surface of the blade 11. Different arc lengths may lead to changes in the pressure gradient, thereby affecting the stability of the air flow and the generation of noise.

[0126] The design of the suction surface arc length directly affects the attachment of the airflow to the surface of blade 11. A longer suction surface arc length helps the airflow to remain attached to 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 air volume. On the contrary, if the suction surface arc length is too short, the airflow may separate rapidly near the leading edge of blade 11, forming vortices and turbulence, increasing the resistance and reducing the air volume. The change in the suction surface arc length affects the lift coefficient of blade 11. A reasonable arc length design can optimize the lift coefficient, enabling blade 11 to capture and push air more effectively during rotation, thereby increasing the air volume. By reducing the formation of vortices and turbulence, a longer suction surface arc length can improve the aerodynamic efficiency of blade 11, reduce energy losses, and further increase the air volume.

[0127] The change in the pressure surface arc length of the blade also affects the drag coefficient of blade 11. Although the pressure surface mainly bears pressure, an overly long arc length may increase the drag and weight of blade 11, having an adverse effect on the increase in air volume. Therefore, it is necessary to find a balance point such that the arc length can maintain a low drag while ensuring the smooth flow of the airflow.

[0128] The arc lengths of each section of the suction surface and each section of the pressure surface of blade 11 are interrelated in their effects on noise and air volume, and they jointly determine the aerodynamic performance and noise characteristics of blade 11. In this embodiment, by reasonably setting the arc lengths of each section of the suction surface and each section of the pressure surface, the working noise of the cross-flow fan 1 is further reduced without affecting the air volume.

[0129] In some preferred or alternative embodiments according to the present utility model,

[0130] 1 mm < S1 < 2 mm; and / or

[0131] 9 mm < S2 < 10 mm; and / or

[0132] 2 mm < S3 < 3 mm; and / or

[0133] 3 mm < S4 < 4 mm; and / or

[0134] 3 mm < S5 < 4 mm; and / or

[0135] 8 mm < S6 < 10 mm.

[0136] 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.

[0137] In some preferred or alternative embodiments of the present utility model, 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;

[0138] 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;

[0139] 0.3 < r1 / r4 < 0.4, 0.8 < r2 / r5 < 0.9, 0.9 < r3 / r6 < 1.

[0140] The change in the radius of each segment of the suction surface of the blade 11 will directly affect the flow path and velocity distribution of the air flow. As the radius increases, the air flow velocity may increase, resulting in a more complex flow, generating unstable flow phenomena such as vortices and turbulence, thereby increasing the generation of noise. In addition, the change in the radius will also affect the pressure distribution on the suction surface of the blade 11. At a larger radius, due to the increase in the air flow velocity, the pressure may decrease, forming a low-pressure area, which may cause the air flow to separate or reattach in this area, and thus generate 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 noise source intensity and frequency at different radii may be different, resulting in the superposition and interference of sound waves during the propagation process, further affecting the distribution and intensity of the noise.

[0141] The change in the radius of each segment of the pressure surface of the blade 11 will directly affect the pressure distribution. As the radius increases, the compression effect of the air flow on the blade 11 is enhanced, and the pressure gradient may change, thereby affecting the stability of the air flow and the generation of noise. In addition, the change in the radius will also affect the flow characteristics of the air flow. At a larger radius, the air flow velocity may increase, resulting in a more complex flow, and may generate unstable flow phenomena such as vortices and turbulence, thereby increasing the 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 noise source intensity and frequency at different radii may be different, resulting in the superposition and interference of sound waves during the propagation process, further affecting the distribution and intensity of the noise.

[0142] The change in the radius of the suction surface of the blade 11 will directly affect the attachment length of the air flow on the surface of the blade 11. A larger suction surface radius may keep the air flow attached for a longer distance, reducing the generation of vortices and turbulence, thereby improving the flow efficiency of the air flow. The change in the suction surface radius will also affect the separation point of the air flow. A smaller radius may cause the air flow to separate prematurely, forming vortices and turbulence, reducing the aerodynamic efficiency and the air volume. And an appropriate radius design can delay the separation of the air flow, enabling more air to be effectively captured and pushed.

[0143] The change in the pressure surface radius 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 air flow. Appropriate design of the pressure surface radius helps to maintain the stability of the air flow and reduce the generation of vortices and turbulence. This helps to improve the flow efficiency of the air flow, thereby increasing the air volume. Although the pressure surface mainly bears pressure, the change in its radius will still have a certain impact on the generation of lift. Reasonable design of the pressure surface radius can optimize the lift coefficient, enabling the blade 11 to more effectively capture and push air during rotation. An overly large pressure surface radius 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 the maximization of the air volume.

[0144] The influence of the radius of each section of the suction surface and the radius of each section of the pressure surface of the blade 11 on noise and air volume is interrelated, and they jointly determine the aerodynamic performance and noise characteristics of the blade 11. In this embodiment, by reasonably setting the radius of each section of the suction surface and the radius of each section of the pressure surface, the working noise of the cross-flow fan 1 is further reduced without affecting the air volume.

[0145] In some preferred or alternative embodiments according to the present invention,

[0146] 7 mm < r1 < 8 mm; and / or

[0147] 12 mm < r2 < 13 mm; and / or

[0148] 9 mm < r3 < 10 mm; and / or

[0149] 19 mm < r4 < 20 mm; and / or

[0150] 15 mm < r5 < 16 mm; and / or

[0151] 9 mm < r6 < 11 mm.

[0152] 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.

[0153] In some preferred or alternative embodiments according to 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;

[0154] 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;

[0155] 0.3 < P1 / P4 < 0.4, 2.7 < P2 / P5 < 2.8, 0.4 < P3 / P6 < 0.5.

[0156] In some preferred or alternative embodiments according to the present utility model,

[0157] 1 mm < P1 < 2 mm; and / or

[0158] 9 mm < P2 < 10 mm; and / or

[0159] 2 mm < P3 < 3 mm; and / or

[0160] 3 mm < P4 < 4 mm; and / or

[0161] 3 mm < P5 < 4 mm; and / or

[0162] 5 mm < P6 < 6 mm.

[0163] 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.

[0164] In some preferred or alternative embodiments according to the present utility model,

[0165] The leading edge diameter d3 of the blade 11 is selected from any value between 0.5 mm and 1 mm; and / or

[0166] The trailing edge diameter d4 of the blade 11 is selected from any value between 1 mm and 2 mm.

[0167] In a specific embodiment, the leading edge diameter d3 of the blade 11 is 0.8 mm, and the trailing edge diameter d4 of the blade 11 is 1.5 mm.

[0168] The leading edge of the blade 11 is the part where the air first contacts the blade 11, and the change in its diameter will directly affect the pattern and speed of air flow. A larger leading edge diameter may cause stronger air disturbances and vortex generation, thereby increasing the aerodynamic noise. Additionally, the change in the leading edge diameter may also affect the boundary layer characteristics on the surface of the blade 11, such as the stability of the boundary layer and the position of the transition point, and further affect the generation and propagation of noise.

[0169] The trailing edge of the blade 11 is the main area where the interaction between the wake shedding and the turbulent boundary layer occurs, and it contributes significantly to the trailing edge noise. The change in the trailing edge diameter will directly affect the frequency and intensity of the wake shedding, thereby changing the characteristics of the trailing edge noise. In addition, the change in the trailing edge diameter may also have a comprehensive impact on the aerodynamic noise and mechanical noise. A larger trailing edge diameter may increase the resistance of the air flow, resulting in more energy dissipation and noise generation. At the same time, it may also change the vibration characteristics of the blade 11 and the bearing load, thereby affecting the mechanical noise.

[0170] The influence of the leading edge diameter d3 of the blade 11 and the trailing edge diameter d4 of the blade 11 on the noise is interrelated, and they jointly determine the aerodynamic performance and noise characteristics of the blade 11. In this embodiment, the working noise of the cross-flow fan 1 is further reduced by optimizing the leading edge diameter d3 of the blade 11 and the trailing edge diameter d4 of the blade 11.

[0171] See Figure 8 As shown, in some preferred or alternative embodiments according to the present invention, the thickness t at the thickest part of the blade 11 is selected from any value between 1 mm and 2 mm.

[0172] In a specific embodiment, the maximum thickness t of the blade 11 is 1.6 mm.

[0173] Among them, the thickness of the blade 11 will affect its interaction with the air. A thicker blade 11 may generate greater air disturbances and vortices during rotation, and the interaction and energy transfer of these vortices will increase the aerodynamic noise. Especially when the thickness of the blade 11 increases, the friction and impact between the edge of the blade 11 and the air will also increase, further exacerbating the generation of aerodynamic noise.

[0174] In this embodiment, the working noise of the cross-flow fan 1 is further reduced by optimizing the thickness of the blade 11.

[0175] Figure 9 is the second schematic diagram of the cross-flow fan blade according to an embodiment of the present invention.

[0176] See Figure 9 As shown, in some preferred or alternative embodiments according to the present invention,

[0177] The inlet angle of the blade 11 is β, and the outlet angle of the blade 11 is γ, where,

[0178] 0.3 < β / γ < 0.4.

[0179] See Figure 9As shown, the distance between the distal end of the blade 11 and the axis is r7, the distance between the proximal end of the blade 11 and the axis is r8. The tangent line at the distal end of the representative cross-section of the blade 11 is the first tangent line L2, and the tangent line of the mid-arc line of the representative cross-section at the proximal end is the second tangent line L3. The perpendicular line to the connecting line between the distal end and the axis is the first perpendicular line L4, and the perpendicular line to the connecting line between the proximal end and the axis is the second perpendicular line L5. The angle β between the first perpendicular line and the first tangent line is the inlet angle, and the angle γ between the second perpendicular line and the second tangent line is the outlet angle. By reasonably setting the values of the inlet angle and the outlet angle, it is possible to ensure that the cross-flow fan blade has better aerodynamic performance and improve the air outlet efficiency.

[0180] The magnitude of the inlet angle of the blade 11 directly affects the initial impact of the air flow on the blade 11. When the inlet angle is too large or too small, it may cause strong impact and separation of the air flow on the surface of the blade 11, thereby forming vortices and turbulence, and increasing the aerodynamic noise. A suitable inlet angle helps to maintain the stable flow of the air flow, reduce the generation of flow separation and vortices, and thus reduce the aerodynamic noise. On the contrary, an inappropriate inlet angle may lead to unstable flow and increase the noise.

[0181] The magnitude of the outlet angle of the blade 11 affects the shedding mode and frequency of the wake vortices. A larger outlet angle may cause more intense and frequent shedding of the wake vortices, generating stronger wake vortex noise. At the same time, the interaction and energy transfer of the wake vortices may also increase the aerodynamic noise. A suitable outlet angle helps the smooth diffusion of the air flow and reduces the generation of vortices and turbulence. On the contrary, an excessive outlet angle may lead to uneven diffusion of the air flow and increase the aerodynamic noise.

[0182] The inlet angle refers to the angle when the air flow enters the blade 11, which determines whether the air flow can smoothly enter the blade passage. When the inlet angle matches the air flow direction, the air flow can enter the blade 11 more smoothly, reducing impact and eddies, thereby increasing the air volume. If the inlet angle is too small or too large, it may cause the air flow to generate impact when entering the blade 11, increasing the energy loss and reducing the air volume. The inlet angle also affects the generation of lift of the blade 11. An appropriate inlet angle can enable the blade 11 to capture the air flow more effectively and generate lift, thereby pushing more air through the fan or wind turbine. The design of the inlet angle has an important impact on the aerodynamic efficiency. The optimized inlet angle can improve the aerodynamic efficiency, reduce the energy loss, and thus increase the air volume.

[0183] The outlet angle refers to the angle at which the air flow leaves the blade 11, which determines the acceleration and diffusion of the air flow after leaving the blade 11. A larger outlet angle can enable the air flow to obtain a greater acceleration when leaving the blade 11, but it may also cause the air flow to diffuse too quickly, reducing the air volume. An appropriate outlet angle can balance the requirements of air flow acceleration and diffusion, enabling the air flow to maintain a high speed and pressure after leaving the blade 11, thereby increasing the air volume. The change in the outlet angle also affects the pressure distribution on the surface of the blade 11. A reasonable outlet angle design can optimize the pressure distribution, reduce the generation of vortices and turbulence, improve the stability of the air flow, and thus increase the air volume.

[0184] The influence of the inlet angle and outlet angle of the blade 11 on the noise and air volume is interrelated. They jointly determine the aerodynamic performance and noise characteristics of the blade 11. In this embodiment, by making the ratio of the inlet angle to the outlet angle within a reasonable range, the working noise of the cross-flow impeller 1 is further reduced and the air volume is ensured.

[0185] In some preferred or alternative embodiments according to the present invention, 26° < β < 27°.

[0186] In some preferred or alternative embodiments according to the present invention, 83° < γ < 84°

[0187] In a specific embodiment, β is 26.62°, γ is 83.69°, and β / γ = 0.32.

[0188] Figure 10 It is a schematic structural block diagram of an air conditioner according to an embodiment of the present invention. Refer to 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.

[0189] The present invention proposes a low-noise and high-efficiency cross-flow impeller 1 and an air conditioner 2 having the same. The low-noise and high-efficiency cross-flow impeller 1 includes at least one impeller section 10. The cross-flow impeller 1 includes at least one impeller section 10. The impeller section 10 includes a partition 12 and a plurality of blades 11 arranged circumferentially along the partition 12. Among them, the inscribed circle diameter of all the blades 11 on the impeller section 10 is d1, the circumscribed circle diameter is d2, the chord length of the blade 11 is L1, and the number of blades on the partition is Y. Among them, Among them, k2 is a constant, 12 < k2 < 13. Based on the technical solution proposed by the present invention, the influence of the inscribed circle diameter d1, circumscribed circle diameter d2, chord length L1 and the number of blades Y of the blade on the noise and air volume is interrelated. They jointly determine the aerodynamic performance and noise characteristics of the blade. By reasonably setting the inscribed circle diameter d1, circumscribed circle diameter d2, the number of blades Y and the chord length L1 of the cross-flow impeller, the working noise of the cross-flow impeller is reduced while ensuring that the air volume of the blade remains unchanged.

[0190] Up to this point, those skilled in the art should recognize that although multiple exemplary embodiments of the present utility model have been shown and described in detail herein, many other variations or modifications that conform to the principles of the present utility model can still be directly determined or derived based on the content disclosed in the present utility model without departing from the spirit and scope of the present utility model. Therefore, the scope of the present utility model should be understood and determined to cover all these other variations or modifications.

Claims

1. A low-noise and high-efficiency crossflow wind wheel, comprising at least one wind wheel section, wherein the wind wheel section comprises a partition and a plurality of blades arranged along the circumference of the partition, characterized in that: The inscribed circle diameter of all blades on the wind wheel section is d1, the circumscribed circle diameter is d2, the chord length of the blade is L1, and the number of blades on the partition is Y, where: Among them, k2 is a constant, 12<k2<13.

2. The low-noise and high-efficiency crossflow impeller according to claim 1 is characterized in that: 71mm<d173mm.

3. The low-noise and high-efficiency crossflow impeller according to claim 1 is characterized in that: 101mm<d2<103mm.

4. The low-noise and high-efficiency crossflow impeller according to claim 1 is characterized in that: 12mm<L1<13mm.

5. The low-noise and high-efficiency crossflow impeller according to claim 1 is characterized in that: The number of blades is an odd number.

6. The low-noise and high-efficiency crossflow impeller according to claim 5, characterized in that: 32＜Y＜38。 7. The low-noise and high-efficiency crossflow impeller according to claim 1, characterized in that: At least one of the wind wheel sections is located between the driven shaft end cover and the driving end cover which are arranged opposite to each other, wherein: The driven shaft end cover is provided with a rotating shaft, and the driving end cover is provided with a motor shaft sleeve.

8. The low-noise and high-efficiency crossflow impeller according to claim 1, characterized in that: The number of wind wheel sections is any value between 9 and 13 sections.

9. The low-noise and high-efficiency crossflow impeller according to claim 1, characterized in that: A 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 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 nodes among the plurality of wind rotor nodes are arranged in one-to-one correspondence, and the blades on the remaining wind rotor nodes are arranged in a staggered manner.

10. An air conditioner, characterized in that: It comprises a low-noise and high-efficiency crossflow impeller as described in any one of claims 1 to 9.

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