A double-suction and double-direction fan system and air conditioner

Abstract

The application provides a double-suction bidirectional fan system and an air conditioner, the double-suction bidirectional fan system comprising: a fan blade and a first flow guide ring, the first flow guide ring being arranged on an axial side of the fan blade and located on an air inlet side of the fan blade, so that air flow first flows through the first flow guide ring and then reaches the fan blade, in an axial projection plane, a rotation center of the fan blade is point O, a center of the first flow guide ring is point P, point O and point P are not coincident and the distance between the two is k, a horizontal line passing through point O is H, the included angle between OP and H is beta, and beta is within the range of 85°<beta<95°, and 3mm<k<9mm, the diameter of the first flow guide ring is d2, and d2 is within the range of 210mm<d2<220mm. According to the application, the spatial position of the eccentric flow guide ring can be controlled, the pressure distribution of the air inlet is uniform, the resistance is reduced through pressure balance, the air flow is smoother, the air volume of the system is improved, and abnormal noise is weakened.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioners, and particularly relates to a double-suction and bidirectional fan system and an air conditioner. Background Art

[0002] With the development of the Internet and the upgrading of consumption, users' demands for the comfort of air conditioners have become increasingly strong. At present, the double-suction and bidirectional fan system can achieve shower cooling and carpet heating, which can better improve the indoor comfort of users. At present, the layout design of the guide ring of the double-suction and bidirectional fan system is unreasonable, the pressure distribution on both sides of the air inlet is uneven, and the air flow is not smooth, resulting in a reduction in the air volume of the air outlet and abnormal noise. The layout design of the volute tongue is unreasonable, resulting in air flow backflow, resulting in a reduction in the air volume of the air outlet and abnormal noise. At present, the system has problems such as insufficient air volume of the air outlet and poor sound quality, and cannot meet the needs of users. Therefore, it is urgent to optimize the fan system to increase the air volume of the air outlet and improve the sound quality.

[0003] Due to the technical problems such as insufficient air volume of the air outlet in the double-suction and bidirectional fan system in the prior art, the present invention researches and designs a double-suction and bidirectional fan system and an air conditioner. Summary of the Invention

[0004] Therefore, the technical problem to be solved by the present invention is to overcome the defect of insufficient air volume of the air outlet in the double-suction and bidirectional fan system in the prior art, so as to provide a double-suction and bidirectional fan system and an air conditioner.

[0005] To solve the above problems, the present invention provides a double-suction and bidirectional fan system, which includes:

[0006] A fan blade and a first guide ring, the first guide ring is arranged on one axial side of the fan blade and is located on the air inlet side of the fan blade, so that the air flow first passes through the first guide ring and then reaches the fan blade. In the axial projection plane, the rotation center of the fan blade is point O, the center of the first guide ring is point P, point O and point P do not coincide and the distance between them is k, the horizontal line passing through point O is H, the included angle between OP and H is β, and there is: the value range of the angle β is 85° < β < 95°, and 3mm < k < 9mm. The diameter of the first guide ring is d2, and its value range is 210mm < d2 < 220mm.

[0007] In some embodiments,

[0008] It further includes a second air deflector ring. The airfoil is a centrifugal airfoil. The second air deflector ring is arranged on the other axial side of the airfoil and is located on the air inlet side on the other side of the airfoil. The second air deflector ring has the same structure as the first air deflector ring. And in the axial projection plane, the center of the second air deflector ring coincides with the center of the first air deflector ring, both being point P. The diameter of the second air deflector ring is equal to the diameter of the first air deflector ring, both being d2.

[0009] In some embodiments,

[0010] It further includes a volute, an upper air duct and a lower air duct. The airfoil is arranged inside the volute. One end of the upper air duct is communicated with the upper outlet of the volute, and the upper air duct extends towards the upper part of the volute. One end of the lower air duct is communicated with the lower outlet of the volute, and the lower air duct extends towards the lower part of the volute. The volute has an upper volute tongue relatively close to the upper air duct side and a lower volute tongue relatively close to the lower air duct side.

[0011] In some embodiments,

[0012] In the axial projection plane, the minimum distance between the upper volute tongue and the airfoil is a, and 9mm < a < 14mm. The contour of the upper volute tongue is an arc structure, its radius is r1, and 16mm < r1 < 20mm. The width of the upper volute throat is g. The upper volute throat is the minimum distance formed between the horizontal line made at the upper volute tongue and the air duct wall opposite to the upper volute tongue, and 130mm < g < 140mm.

[0013] In some embodiments,

[0014] In the axial projection plane, the minimum distance between the lower volute tongue and the airfoil is b, and 11mm < b < 17mm. The contour of the lower volute tongue is an arc structure, its radius is r2, and 16mm < r2 < 20mm. The width of the lower volute throat is c. The lower volute throat is the minimum distance formed between the horizontal line made at the lower volute tongue and the air duct wall opposite to the lower volute tongue, and 120mm < c < 130mm.

[0015] In some embodiments,

[0016] It further includes a motor and a motor bracket. The motor is arranged on one side of the first air deflector ring and relatively far away from the second air deflector ring. The motor is axially connected to the airfoil to drive the airfoil to rotate. The motor is supported on the volute through the motor bracket.

[0017] In some embodiments,

[0018] The inner diameter of the centrifugal impeller is d1, and its value range is 200mm < d1 < 210mm; the outer diameter of the centrifugal impeller is d3, and its value range is 250mm < d3 < 270mm.

[0019] In some embodiments,

[0020] d1 < d2 < d3.

[0021] In some embodiments,

[0022] The axial gap between the centrifugal impeller and the first guide ring is f, and 9mm < f < 14mm. The axial gap between the centrifugal impeller and the second guide ring is e, and 9mm < e < 14mm. The axial height of the centrifugal impeller is h, and 140mm < h < 160mm.

[0023] The present invention also provides an air conditioner, which includes the aforementioned double-suction and bidirectional fan system.

[0024] A double-suction and bidirectional fan system and an air conditioner provided by the present invention have the following beneficial effects:

[0025] 1. In the present invention, by setting the included angle β between the line connecting the center P of the first guide ring and the center O point of the impeller and the horizontal line H passing through the O point to satisfy the value range of 85° < β < 95°, and setting the distance k between OP to satisfy 3mm < k < 9mm, and further setting the diameter d2 of the first guide ring to satisfy 210mm < d2 < 220mm. Through the combined action of these several parameter ranges, the spatial position of the eccentric guide ring can be effectively controlled, making the pressure distribution at the air inlet more uniform. By balancing the pressure, the resistance is reduced, the air resistance is smaller, the air flow is smoother, the air volume can be effectively increased, thereby improving the air volume of the system's air output and reducing abnormal noise. The present invention also sets a second guide ring on the other axial side of the impeller, and makes the structure of the second guide ring the same as that of the first guide ring. The centers of the two guide rings coincide in the axial end face and have equal diameters, making the inlet air pressure at the second guide ring also evenly distributed, reducing the air resistance, increasing the air volume while reducing the noise.

[0026] 2. The present invention also sets the minimum distance a between the upper volute tongue and the wind blade to satisfy 9 mm < a < 14 mm, sets the radius r1 of the upper volute tongue to satisfy 16 mm < r1 < 20 mm, and sets the width g of the upper volute throat to 130 mm < g < 140 mm. Through the combined action of these several parameter ranges, the key parameters in the upper volute tongue area are effectively controlled, the air flow reflux in the upper air duct volute tongue area is weakened, the air volume of the whole machine is increased, and the aerodynamic noise is reduced. The present invention sets the minimum distance b between the lower volute tongue and the wind blade to satisfy 11 mm < b < 17 mm, sets the radius r2 of the lower volute tongue to satisfy 16 mm < r2 < 20 mm, and sets the width c of the lower volute throat to satisfy 120 mm < c < 130 mm. Through the combined action of these several parameter ranges, the key parameters in the lower volute tongue area are effectively controlled, the air flow reflux in the lower air duct volute tongue area is weakened, the air volume of the whole machine is increased, and the aerodynamic noise is reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 is a three-dimensional structure diagram of the double-suction and two-way fan system of the present invention;

[0028] Figure 2 is Figure 1 the left view of

[0029] Figure 3 is Figure 1 the right view of

[0030] Figure 4 is a longitudinal sectional view of the air duct component of the double-suction and two-way fan system of the present invention;

[0031] Figure 5 is of the present invention Figure 3 partial enlarged parameter schematic diagram (non-motor side);

[0032] Figure 6 is Figure 5 a further enlarged view at the central position of

[0033] Figure 7 is of the present invention Figure 2 partial enlarged parameter schematic diagram (motor side);

[0034] Figure 8 is a longitudinal sectional parameter schematic diagram of the air duct component of the double-suction and two-way fan system of the present invention;

[0035] Figure 9 is a parameter schematic diagram of the vertical section (axial projection plane) of the air duct component of the double-suction and two-way fan system of the present invention;

[0036] Figure 10 is the inlet air pressure distribution diagram on the motor side of the present invention (i.e., the first guide ring side);

[0037] Figure 11 This is the non-motor side air inlet pressure distribution diagram of the present invention (i.e., the second guide ring side);

[0038] Figure 12 This is a velocity vector diagram of the upper cochlear tongue region of the present invention;

[0039] Figure 13 This is a velocity vector diagram of the lower cochlear tongue region of the present invention.

[0040] The attached figures are labeled as follows:

[0041] 1. Fan blade; 2. First guide ring; 3. Second guide ring; 4. Volute; 5. Upper air duct; 6. Lower air duct; 7. Upper volute tongue; 8. Lower volute tongue; 9. Motor; 10. Motor bracket; 11. Electric heating element. Detailed Implementation

[0042] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0043] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0044] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0045] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0046] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0047] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0048] like Figure 1-13As shown in the figure, the present invention provides a double-suction and bidirectional fan system, which includes:

[0049] A wind blade 1 and a first guide ring 2, the first guide ring 2 is arranged on one axial side of the wind blade 1 and is located on the air inlet side of the wind blade 1, so that the air flow first passes through the first guide ring 2 and then reaches the wind blade 1. In the axial projection plane, the rotation center of the wind blade 1 is point O, the center of the first guide ring 2 is point P, the point O does not coincide with the point P and the distance between the two is k. The horizontal line passing through point O is H, and the included angle between OP and H is β, and there is: the value range of the angle β is 85° < β < 95°, and 3mm < k < 9mm. The diameter of the first guide ring 2 is d2, and its value range is 210mm < d2 < 220mm.

[0050] By setting the included angle β between the connection line between the center P of the first guide ring and the center O point of the wind blade and the horizontal line H passing through point O to satisfy the value range of 85° < β < 95°, and setting the distance k between OP to satisfy 3mm < k < 9mm, and also setting the diameter d2 of the first guide ring to satisfy 210mm < d2 < 220mm. Through the combined action of these several parameter ranges, the spatial position of the eccentric guide ring can be effectively controlled, making the pressure distribution at the air inlet more uniform, reducing the resistance through pressure balance, having a smaller air resistance, making the air flow smoother, effectively improving the air volume, and thus enhancing the air volume of the system's air outlet and weakening abnormal noise.

[0051] The present invention proposes a parametric design method for an efficient double-suction and bidirectional fan system. The uneven pressure at the air inlets on both sides of the air duct of the double-suction fan system and the existence of backflow at the volute tongue lead to unpleasant aerodynamic noise and insufficient air volume at the air outlet. By adopting this design method, the spatial position of the eccentric guide ring can be controlled, making the pressure distribution at the air inlet more uniform, the air flow smoother, and the air resistance smaller, thereby enhancing the air volume of the system's air outlet and weakening abnormal noise. Further, by controlling the key parameters in the volute tongue area, the air flow backflow in the volute tongue area of the upper air duct is weakened and the backflow at the volute tongue of the lower air duct is eliminated, enhancing the air volume of the system's air outlet and reducing aerodynamic noise. After the parameter design according to the first inventive point (the design of the guide ring) and the second inventive point (the design of the volute tongue), according to the experimental test, after the improvement according to the above parameters, the air volume of the double-suction and bidirectional fan system is increased by about 5% - 9%, and the on-site experience has a better sound quality.

[0052] The present invention solves the following problems:

[0053] 1) Solved the problem of insufficient air volume at the air outlet of the double-suction and bidirectional fan system.

[0054] 2) Solved the problem of abnormal sound quality of the double-suction and bidirectional fan system.

[0055] In some embodiments,

[0056] It further includes a second air deflector ring 3. The wind blade 1 is a centrifugal wind blade. The second air deflector ring 3 is arranged on the other axial side of the wind blade 1 and is located on the air inlet side on the other side of the wind blade 1. The second air deflector ring 3 has the same structure as the first air deflector ring 2. And in the axial projection plane, the center of the second air deflector ring 3 coincides with the center of the first air deflector ring 2, both being point P. The diameter of the second air deflector ring 3 is equal to the diameter of the first air deflector ring 2, both being d2.

[0057] The present invention also arranges a second air deflector ring on the other axial side of the wind blade, and makes the second air deflector ring have the same structure as the first air deflector ring. The centers of the two air deflector rings coincide in the axial end face and have equal diameters, so that the air inlet pressure at the second air deflector ring is also evenly distributed, reducing the wind resistance, increasing the air volume and weakening the noise while increasing the air volume.

[0058] To improve the pressure distribution of the two side air inlets, the present invention parametrically designs the air deflector ring area. Point P is the center of the air deflector ring. The first air deflector ring and the second air deflector ring have the same diameter (d2), and its value range is 210mm < d2 < 220mm, and preferably d2 = 216mm. The distance from point O to point P is k, and its value range is 3mm < k < 9mm, and preferably k = 6mm. H is a horizontal line, and the value range of the angle β is 85° < β < 95°, and preferably β = 92°. After strictly controlling the above parameters, an eccentric air deflector ring arrangement can be formed, making the pressure distribution of the two side air inlets more uniform, the air flow smoother, the air resistance smaller, effectively increasing the air volume and reducing the pneumatic noise, as shown in Figure 10 and 11 .

[0059] The present invention makes the pressure distribution of the air inlet more uniform by controlling the position of the air deflector ring. When the air inlet pressure is not balanced, eddy currents or air flow collisions are likely to form at the air inlet. Through the above parameters, the spatial position of the eccentric air deflector ring is controlled, and the simulation data at this position is as shown in Figure 10 and 11 . When the eccentric air deflector ring is arranged, the pressure distribution of the two side air inlets is more uniform, the air flow is smoother, the air resistance is smaller, effectively increasing the air volume and reducing the pneumatic noise. Supported by simulation data ( Figure 10 and 11 ).

[0060] When the present invention adopts this parameter design method, an eccentric air deflector ring arrangement can be formed, the air inlet pressure distribution is more uniform, the air flow is smoother, the air resistance is smaller, effectively increasing the air volume and reducing the pneumatic noise. Further defining the relevant design parameters of the volute tongue area weakens the air flow reflux in the volute tongue area of the upper air duct and eliminates the reflux at the volute tongue of the lower air duct, improving the air volume of the whole machine's air outlet and reducing the pneumatic noise. According to experimental tests, after improving according to the above parameters, the air volume of the double-suction and two-way fan system is increased by about 5% - 9%, and the on-site experience has better sound quality.

[0061] In some embodiments,

[0062] It further includes a volute 4, an upper air duct 5 and a lower air duct 6. The air blade 1 is arranged inside the volute 4. One end of the upper air duct 5 is communicated with the upper outlet of the volute 4, and the upper air duct 5 extends upward toward the volute 4. One end of the lower air duct 6 is communicated with the lower outlet of the volute 4, and the lower air duct 6 extends downward toward the volute 4. The volute 4 has an upper volute tongue 7 relatively close to one side of the upper air duct 5 and a lower volute tongue 8 relatively close to one side of the lower air duct 6.

[0063] This is a further preferred structural form of the double-suction and two-way fan of the present invention. The volute can accommodate the air blade therein. The upper air duct and the lower air duct are respectively communicated with the upper and lower air outlets of the volute to guide the air flow entrained and output by the air blade inside the volute and transport it to a designated area in the space, achieving the purpose and effect of upper and lower air outlet and forming two-way air outlet.

[0064] In some embodiments,

[0065] In the axial projection plane, the minimum distance between the upper volute tongue 7 and the air blade 1 is a, and 9 mm < a < 14 mm. The contour of the upper volute tongue 7 is an arc structure, and its radius is r1, and 16 mm < r1 < 20 mm. The width of the upper volute throat is g. The upper volute throat is the minimum distance formed by making a horizontal line at the upper volute tongue and intersecting with the air duct wall opposite to the upper volute tongue, and 130 mm < g < 140 mm.

[0066] The present invention also effectively controls the key parameters of the upper volute tongue region by setting the minimum distance a between the upper volute tongue and the air blade to satisfy 9 mm < a < 14 mm, setting the radius r1 of the upper volute tongue to satisfy 16 mm < r1 < 20 mm, and setting the width g of the upper volute throat to 130 mm < g < 140 mm. Through the combined action of these parameter ranges, the air flow backflow in the upper volute tongue region of the upper air duct is weakened, the air output volume of the whole machine is increased, and the pneumatic noise is reduced.

[0067] To weaken the air flow backflow of the upper volute tongue, the present invention conducts parametric design on the upper volute tongue region. Such as Figure 9 , the radius of the upper volute tongue is r1, 16 mm < r1 < 20 mm, and preferably r1 = 18 mm. The minimum distance between the upper volute tongue and the air blade is a, 9 mm < a < 14 mm, and preferably a = 11 mm. The width of the upper volute throat is g, 130 mm < g < 140 mm, and preferably g = 135 mm. By strictly controlling the above parameters, the layout of the upper volute tongue region is made more reasonable, the air flow backflow in the upper volute tongue region of the upper air duct is weakened, the air flow is smoother, the impact of the air flow on the volute tongue is weakened, thereby further increasing the air output volume of the whole machine and reducing the pneumatic noise. See Figure 12 。

[0068] In some embodiments,

[0069] In the axial projection plane, the minimum distance between the lower volute tongue 8 and the wind blade 1 is b, and 11 mm < b < 17 mm. The contour of the lower volute tongue 8 is an arc structure with a radius of r2, and 16 mm < r2 < 20 mm. The width of the lower volute throat is c. The lower volute throat is the minimum distance formed by making a horizontal line at the lower volute tongue and intersecting the air duct wall opposite the lower volute tongue, and 120 mm < c < 130 mm.

[0070] In the present invention, by setting the minimum distance b between the lower volute tongue and the wind blade to satisfy 11 mm < b < 17 mm, setting the radius r2 of the lower volute tongue to satisfy 16 mm < r2 < 20 mm, and setting the width c of the lower volute throat to satisfy 120 mm < c < 130 mm, through the combined action of these parameter ranges, the key parameters in the lower volute tongue area are effectively controlled, the air flow reflux in the lower air duct volute tongue area is weakened, the air output volume of the whole machine is increased, and the pneumatic noise is reduced.

[0071] To eliminate the air flow reflux at the lower volute tongue, the present invention conducts parametric design on the lower volute tongue area. The radius of the lower volute tongue is r2, 16 mm < r2 < 20 mm, and preferably r2 = 18 mm. The minimum distance between the lower volute tongue and the wind blade is b, 11 mm < b < 17 mm, and preferably b = 14 mm. The width of the lower volute throat is c, 120 mm < c < 130 mm, and preferably c = 123 mm. By strictly controlling the above parameters, the internal layout of the lower air duct is made more reasonable, the reflux at the lower air duct volute tongue is eliminated, the air flow becomes smoother, thereby further increasing the air output volume of the whole machine and reducing the pneumatic noise, see Figure 13 。

[0072] In the present invention, by strictly controlling the radius r1 of the upper volute tongue, the minimum distance a between the upper volute tongue and the wind blade, and the width g of the upper volute throat, the layout of the upper volute tongue area is made more reasonable, the air flow reflux in the upper air duct volute tongue area is weakened, the air flow is smoother, and the impact of the air flow on the volute tongue is weakened, thereby further increasing the air output volume of the whole machine and reducing the pneumatic noise, see Figure 12 。By strictly controlling the radius r2 of the lower volute tongue, the minimum distance b between the lower volute tongue and the wind blade, and the width c of the lower volute throat, the internal layout of the lower air duct is made more reasonable, the reflux at the lower air duct volute tongue is eliminated, the air flow becomes smoother, thereby further increasing the air output volume of the whole machine and reducing the pneumatic noise, see Figure 13 。Through simulation data support ( Figure 12 and 13 ).

[0073] In some embodiments,

[0074] It further includes a motor 9 and a motor bracket 10. The motor 9 is arranged on one side of the first guide ring 2 and relatively far from the second guide ring 3. The motor 9 is axially connected to the wind blade 1 to drive the wind blade 1 to rotate, and the motor 9 is supported on the volute 4 through the motor bracket 10.

[0075] This is a further preferred structural form of the present invention. The motor can provide a driving force for the wind blade to drive its rotation. The motor bracket can effectively mount the motor on the volute. The motor is preferably mounted on one side of the first guide ring, so that the side of the second guide ring is the non-motor side.

[0076] In some embodiments,

[0077] The inner diameter of the centrifugal wind blade is d1, and its value range is 200 mm < d1 < 210 mm. Preferably, d1 = 208 mm. The outer diameter of the centrifugal wind blade is d3, and its value range is 250 mm < d3 < 270 mm. Preferably, d3 = 260 mm. This is a preferred structural form of the centrifugal wind blade of the present invention, which can make d1 < d2 < d3, so that the range of the guide ring is between the inner and outer diameters of the wind blade, and can effectively play the role and effect of guiding the airflow through the guide ring.

[0078] A schematic diagram of the air duct component of the present invention is shown in Figures 1-4 . The air duct component includes a volute 4, a wind blade 1, a motor bracket 10, a motor 9, an electric heating component 11, a first guide ring 2 and a second guide ring 3. The volute, the wind blade, the motor bracket, the motor, the electric heating, the first guide ring and the second guide ring are fixed by screws or snap-fasteners. As Figure 5 , Figure 6 and Figure 7 , O is the rotation center of the wind blade. The inner diameter of the wind blade is d1, and its value range is 200 mm < d1 < 210 mm. Preferably, d1 = 208 mm. The outer diameter of the wind blade is d3, and its value range is 250 mm < d3 < 270 mm. Preferably, d3 = 260 mm.

[0079] In some embodiments,

[0080] d1 < d2 < d3. Through such a design (d1 < d2 < d3), it can make the range of the guide ring be between the inner and outer diameters of the wind blade, and can effectively play the role and effect of guiding the airflow through the guide ring.

[0081] In some embodiments,

[0082] The axial clearance between the centrifugal impeller and the first flow guide ring 2 is f, where 9 mm < f < 14 mm, preferably f = 11 mm. The axial clearance between the centrifugal impeller and the second flow guide ring 3 is e, where 9 mm < e < 14 mm, preferably e = 11.5 mm. The axial height of the centrifugal impeller is h, where 140 mm < h < 160 mm, preferably h = 153 mm.

[0083] As Figure 8 , in the present invention, the clearance between the impeller and the first flow guide ring is f, where 9 mm < f < 14 mm, preferably f = 11 mm. The clearance between the impeller and the second flow guide ring is e, where 9 mm < e < 14 mm, preferably e = 11.5 mm. The height of the impeller is h, where 140 mm < h < 160 mm, preferably h = 153 mm. By controlling the above parameters, while ensuring the air volume of the whole machine, the noise during the operation of the whole machine can be effectively reduced, and the sound quality in the on-site experience is better.

[0084] The present invention also provides an air conditioner, which includes the aforementioned double-suction and bidirectional fan system.

[0085] The present invention proposes a parametric design method for an efficient double-suction and bidirectional fan system. The uneven pressure at the air inlets on both sides of the air duct of the double-suction fan system and the existence of backflow at the volute tongue result in unpleasant aerodynamic noise and insufficient air volume at the air outlet. By adopting this design method, the spatial position of the eccentric flow guide ring can be controlled, making the pressure distribution at the air inlets more uniform, the air flow smoother, and the air resistance smaller, thereby improving the air volume at the air outlet of the system and reducing abnormal noise. Further, by controlling the key parameters in the volute tongue area, the air flow backflow in the volute tongue area of the upper air duct is reduced and the backflow at the volute tongue of the lower air duct is eliminated, improving the air volume at the air outlet of the system and reducing aerodynamic noise.

[0086] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the present invention. The above is only the preferred implementation manner of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the technical principle of the present invention, several improvements and variations can still be made, and these improvements and variations should also be regarded as within the protection scope of the present invention.

Claims

1. A dual-suction, bidirectional fan system, characterized in that: include: The fan blade (1) and the first guide ring (2) are arranged on one side of the axial direction of the fan blade (1) and located on the air inlet side of the fan blade (1), so that the airflow first flows through the first guide ring (2) and then reaches the fan blade (1). In the axial projection plane, the rotation center of the fan blade (1) is point O, and the center of the first guide ring (2) is point P. Point O and point P do not coincide and the distance between them is k. The horizontal line passing through point O is H, and the angle between OP and H is β. The value range of angle β is 85°. β 95°, and 3mm k The diameter of the first guide ring (2) is d2, which ranges from 210 mm to 9 mm. d2 220mm; It also includes a volute (4) and an upper air duct (5), the fan blade (1) is disposed inside the volute (4), one end of the upper air duct (5) is connected to the upper outlet of the volute (4), the upper air duct (5) extends toward the upper part of the volute (4), and the volute (4) has an upper volute tongue (7) relatively close to the side of the upper air duct (5). In the axial projection plane, the minimum distance between the upper volute tongue (7) and the fan blade (1) is a, and it is 9mm. a The upper volute tongue (7) has an arc-shaped outline with a radius of r1 and a diameter of 16mm. r1 The width of the upper volute throat is 20mm, and the upper volute throat is g. The upper volute throat is the minimum distance formed between the horizontal line drawn at the upper volute tongue and the air duct wall opposite to the upper volute tongue, and is 130mm. g 140mm.

2. The dual-suction bidirectional fan system according to claim 1, characterized in that: It also includes a second guide ring (3). The fan blade (1) is a centrifugal fan blade. The second guide ring (3) is located on the other side of the axial direction of the fan blade (1) and on the air inlet side of the other side of the fan blade (1). The second guide ring (3) has the same structure as the first guide ring (2). In the axial projection plane, the center of the second guide ring (3) coincides with the center of the first guide ring (2), both being point P. The diameter of the second guide ring (3) is equal to the diameter of the first guide ring (2), both being d2.

3. The dual-suction bidirectional fan system according to claim 2, characterized in that: It also includes a downdraft (6), one end of which is connected to the lower outlet of the volute (4), the downdraft (6) extending downward toward the volute (4), and the volute (4) also having a lower volute tongue (8) relatively close to the side of the downdraft (6).

4. The dual-suction bidirectional fan system according to claim 3, characterized in that: In the axial projection plane, the minimum distance between the lower volute tongue (8) and the fan blade (1) is b, and has a spacing of 11 mm. b The lower volute tongue (8) has an arc-shaped outline with a radius of r2 and a diameter of 17mm. r2 The width of the lower volute is 20mm, and the lower volute throat is c. The lower volute throat is the minimum distance formed between the horizontal line drawn at the lower volute tongue and the air duct wall opposite to the lower volute tongue, and has a width of 120mm. c 130mm.

5. The dual-suction bidirectional fan system according to any one of claims 3-4, characterized in that: It also includes a motor (9) and a motor bracket (10). The motor (9) is located on one side of the first guide ring (2) and relatively far away from the second guide ring (3). The motor (9) is connected to the shaft of the fan blade (1) to drive the fan blade (1) to rotate. The motor (9) is supported on the volute (4) by the motor bracket (10).

6. The dual-suction bidirectional fan system according to claim 2, characterized in that: The inner diameter of the centrifugal fan blade is d1, and its value ranges from 200 mm. d1 210mm; the outer diameter of the centrifugal fan blade is d3, which ranges from 250mm. d3 270mm.

7. The dual-suction bidirectional fan system according to claim 6, characterized in that: d1 d2 d3.

8. The dual-suction bidirectional fan system according to claim 2, characterized in that: The axial clearance between the centrifugal fan blade and the first guide ring (2) is f, and has a length of 9mm. f The axial clearance between the centrifugal fan blade and the second guide ring (3) is 14mm, and the clearance is 9mm. e The centrifugal fan blade has an axial height of 140mm and a diameter of 140mm. h 160mm.

9. An air conditioner, characterized in that: Includes the dual-suction bidirectional fan system as described in any one of claims 1-8.

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