CN115479047A - Volute of centrifugal fan, centrifugal fan and air conditioner - Google Patents

Abstract

The invention discloses a volute of a centrifugal fan, a centrifugal fan and an air conditioner. The volute is formed with a first air inlet, a second air inlet, an air outlet and a centrifugal air duct, and the centrifugal air duct communicates with the first air inlet and the second air inlet. The air outlet and the air outlet, the first air inlet and the second air inlet are arranged oppositely at both ends of the volute in the axial direction, the centrifugal air duct is used to accommodate the centrifugal wind wheel, and the side of the volute is provided with the first air inlet It is used to install the motor, wherein the air inlet area of the first air inlet is larger than that of the second air inlet. In this embodiment, by increasing the area of the first air inlet on the motor side of the volute, the adverse effect caused by the installation of the motor on one air inlet side of the centrifugal fan is reduced, so that the two air inlets of the centrifugal fan The side air intake is more balanced, so that it still runs smoothly at high speeds and reduces wind noise.

Description

Centrifugal fan volute, centrifugal fan and air conditioner

technical field

The invention relates to the technical field of air conditioning, in particular to a volute of a centrifugal fan, a centrifugal fan and an air conditioner.

Background technique

The volute and wind wheel of the existing double-suction centrifugal fan for air-conditioning adopt a substantially symmetrical structure design, and the motor is installed on one of the two air inlet sides of the double-suction centrifugal fan.

Due to the existence of the motor and its installation structure on the air inlet side of the double-suction centrifugal fan, the air inlet effect on both sides of the double-suction centrifugal fan is different, which leads to the unstable operation of the double-suction centrifugal fan at high speed, and the airflow noise is relatively high. big.

Contents of the invention

The main purpose of the present invention is to provide a volute of a centrifugal fan, a centrifugal fan and an air conditioner, aiming at improving the difference in the air intake between the two air intake sides of the double-suction centrifugal fan and reducing airflow noise.

In order to achieve the above object, the present invention proposes a volute of a centrifugal fan,

The volute is formed with a first air inlet, a second air inlet, an air outlet and a centrifugal air channel, and the centrifugal air channel communicates with the first air inlet, the second air inlet and the air outlet, and the The first air inlet and the second air inlet are oppositely arranged at both ends of the volute in the axial direction;

The centrifugal air duct is used to accommodate the centrifugal wind wheel, and the side of the volute provided with the first air inlet is used to install the motor;

Wherein, the air inlet area of the first air inlet is larger than that of the second air inlet.

In one embodiment, both the first air inlet and the second air inlet are circular, and the diameter of the first air inlet is larger than that of the second air inlet.

In order to achieve the above object, the present invention also proposes a centrifugal fan, including:

the volute as above;

The centrifugal wind wheel is arranged in the centrifugal air duct, the centrifugal wind wheel includes a partition, and centrifugal blades arranged on both sides of the partition opposite to each other, and a driving installation part is provided on one side of the partition, The side of the baffle provided with the drive installation part faces the first air inlet, and the side of the baffle facing away from the drive installation part faces the second air inlet; and,

The motor is arranged on the side of the volute where the first air inlet is provided, and the motor is drivingly connected to the driving installation part for driving the centrifugal wind wheel to rotate.

In one embodiment, the centrifugal fan blade is a multi-blade centrifugal fan blade, the inner diameter of the centrifugal fan blade is d1, the outer diameter is d2, and the first air inlet and the second air inlet are circular shape, the diameter of the first air inlet is D1, the diameter of the second air inlet is D2, D1=d1+λ(d2-d1), D2=d1+b(d2-d1), where λ is greater than equal to 0.4 and less than or equal to 0.6, b less than or equal to 0.2.

In one embodiment, the centrifugal blades include a first blade set and a second blade set, the first blade set is arranged on the side of the partition plate where the driving installation part is provided, and the second blade assembled on the side of the partition facing away from the drive installation part;

The structures related to the air intake of the first blade set and the second blade set are set differently, so as to reduce the difference of the air intake between the first blade set and the second blade set.

In an embodiment, the first blade set includes a plurality of first blades arranged at intervals along the circumferential direction of the centrifugal rotor to form the cylindrical first blade set, and the plurality of first blades The blades are arranged around the driving installation part;

The second blade set includes a plurality of second blades arranged at intervals along the circumferential direction of the centrifugal rotor to form the cylindrical second blade set;

The inner diameter of the first vane set is larger than the inner diameter of the second vane set.

In one embodiment, the width of each of the first blades is smaller than the width of each of the second blades.

In one embodiment, the installation angle of each of the first blades is greater than the installation angle of each of the second blades.

In one embodiment, the inner diameter of the first vane set is d1, the inner diameter of the second vane set is d11, the outer diameters of the first vane set and the second vane set are d2, and the second vane set has an outer diameter of d2. Both the first air inlet and the second air inlet are circular, the diameter of the first air inlet is D1, the diameter of the second air inlet is D2, D1=d1+c(d2-d1), D2= d11+c(d2-d11), wherein, c is greater than or equal to 0.1 and less than or equal to 0.3.

In order to achieve the above object, the present invention also proposes an air conditioner, including the above-mentioned centrifugal fan.

In the embodiment provided by the present invention, the volute is formed with a first air inlet, a second air inlet, an air outlet and a centrifugal air duct, the centrifugal air duct communicates with the first air inlet, the second air inlet and the air outlet, and the first air inlet It is opposite to the second air inlet and arranged at both ends of the volute in the axial direction. The centrifugal air duct is used to accommodate the centrifugal wind wheel. The side of the volute with the first air inlet is used to install the motor. The first The air inlet area of the air inlet is larger than that of the second air inlet. Compared with the traditional double-suction centrifugal fan with substantially the same air inlets on both sides, the centrifugal fan provided by the present invention reduces one air inlet side of the centrifugal fan by increasing the area of the first air inlet on the motor side of the volute. Due to the adverse effects such as the reduction of the air intake area and the increase of wind resistance caused by the installation of the motor, the air intake volume on the side of the centrifugal fan with the motor tends to increase, so that the difference in the air intake volume between the two air intake sides of the centrifugal fan decreases. , the air intake on both sides is more balanced, so that it still runs smoothly at high speeds and reduces wind noise.

Description of drawings

Fig. 1 is a side view of an embodiment of an air conditioner provided by the present invention;

Fig. 2 is an exploded schematic view of the air conditioner in Fig. 1;

The three-dimensional structural schematic diagram of the centrifugal fan in Fig. 3 Fig. 1;

Fig. 4 is a schematic diagram of the exploded three-dimensional structure of the centrifugal fan in Fig. 3;

Fig. 5 is a front view of the motor side of the centrifugal fan in Fig. 3;

Fig. 6 is the sectional view of A-A place in Fig. 5;

Fig. 7 is the sectional view of B-B place in Fig. 6;

Fig. 8 is a front view of the volute motor side in Fig. 3;

Fig. 9 is a front view of the side opposite to the motor side of the volute in Fig. 3;

Fig. 10 is a front view of an embodiment of the centrifugal wind wheel in Fig. 4;

Fig. 11 is a three-dimensional structural schematic diagram of another embodiment of the centrifugal wind wheel in Fig. 4;

Fig. 12 is a sectional view of the first blade group in Fig. 11;

Fig. 13 is a sectional view of the second blade group in Fig. 11;

Fig. 14 is a three-dimensional structural schematic diagram of another embodiment of the centrifugal wind wheel in Fig. 4;

Fig. 15 is a sectional view of the first blade group in Fig. 14;

Fig. 16 is a sectional view of the second blade group in Fig. 14;

Fig. 17 is a comparison chart of air volume-noise data between the centrifugal fan provided by the present invention and the existing centrifugal fan;

Fig. 18 is a λ-air volume curve diagram of an embodiment of a centrifugal fan provided by the present invention;

Fig. 19 is a comparison diagram of the air volume and flow field of the centrifugal fan provided by the present invention under different values of λ.

Explanation of reference numbers:

label name label name 100 centrifugal fan 30 motor 10 Centrifugal Wind Wheel 31 Motor mount 11 first blade set 32 Motor shaft 110 first blade 40 motor mount 12 second blade set 41 connecting plate 120 second blade 42 connecting rib 13 Partition 200 air conditioner 131 Driver Installation Department 201 shell 20 volute 202 heat exchange inlet twenty one first air inlet 203 heat exchange outlet twenty two Second air inlet 204 Heat Exchanger twenty three air outlet

The realization of the purpose of the present invention, functional characteristics and advantages will be further described in conjunction with the embodiments and with reference to the accompanying drawings.

detailed description

The following will clearly and completely describe the technical solutions in the embodiments of the present invention with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other embodiments obtained by persons of ordinary skill in the art without creative efforts fall within the protection scope of the present invention.

It should be noted that if there is a directional indication (such as up, down, left, right, front, back...) in the embodiment of the present invention, the directional indication is only used to explain the position in a certain posture (as shown in the accompanying drawing). If the specific posture changes, the directional indication will also change accordingly.

In addition, if there are descriptions involving "first", "second" and so on in the embodiments of the present invention, the descriptions of "first", "second" and so on are only for descriptive purposes, and should not be interpreted as indicating or implying Its relative importance or implicitly indicates the number of technical features indicated. Thus, the features defined as "first" and "second" may explicitly or implicitly include at least one of these features. In addition, the technical solutions of the various embodiments can be combined with each other, but it must be based on the realization of those skilled in the art. If there is, it is not within the protection scope of the present invention.

The present invention provides an air conditioner 200 . The air conditioner 200 can be an integrated air conditioner, a split type air conditioner, an air conditioner outdoor unit, or a cabinet type air conditioner indoor unit, a built-in air conditioner indoor unit, or a wall-mounted air conditioner indoor unit, etc. An air conditioner 100 with double-suction centrifugal wind wheels. Please refer to FIG. 1 and FIG. 2 , in this embodiment, the air conditioner 200 is a cabinet air conditioner indoor unit.

The volute and wind wheel of the existing double-suction centrifugal fan adopt a basically symmetrical structure design, and the motor is installed on one of the two air inlet sides of the double-suction centrifugal fan. The centrifugal fan in the double-suction centrifugal fan rotates under the drive of the motor, and the two air inlets located on both sides of the volute draw the air into the centrifugal air duct and send it out from the air outlet. The motor of the double-suction centrifugal fan is usually installed on one of the two air intake sides of the volute, resulting in a decrease in the air intake area of the air intake side, an increase in wind resistance, and a significant reduction in the air intake compared with the other air intake side. The difference between the air intake and the wind speed of the two air intake sides of the double-suction centrifugal fan is large, which leads to the unbalanced air intake of the two air intake sides of the double-suction centrifugal fan when the centrifugal fan is running at high speed, resulting in the centrifugal fan The operation is unstable, the wind noise is large, and the air supply volume is also affected and reduced.

In order to solve the above technical problems, please refer to FIG. 3 to FIG. 9 , the present invention provides a volute 20 of a centrifugal fan 100 and a centrifugal fan 100 including the centrifugal fan 10 .

Please refer to FIG. 3 and FIG. 4 , in this embodiment, the centrifugal fan 100 includes a volute 20 , a centrifugal fan wheel 10 and a motor 30 . The volute 20 is formed with a first air inlet 21, a second air inlet 22, an air outlet 23 and a centrifugal air duct, the centrifugal air duct communicates with the first air inlet 21, the second air inlet 22 and the air outlet 23, and the first air inlet 21 The second air inlet 22 is oppositely arranged at both ends of the volute 20 in the axial direction, the centrifugal wind wheel 10 is arranged in the centrifugal air duct, and the motor 30 is arranged on the side of the volute 20 provided with the first air inlet 21. To drive the centrifugal wind wheel 10 to rotate. When the centrifugal wind wheel 10 rotates, the airflow is sucked into the centrifugal air channel from the first air inlet 21 and the second air inlet 22 , and the airflow is sent out from the air outlet 23 .

The centrifugal fan 100 in this embodiment is a double-suction centrifugal fan. Compared with a common centrifugal fan that generally only sucks airflow from one side, the double-suction centrifugal fan sucks airflow from both sides at the same time, increasing the air intake area. Therefore, it has a larger air volume than ordinary centrifugal fans. However, as shown in this embodiment, the centrifugal fan 100 needs to install the motor 30 on one side of the volute 20 (in the present invention, the side where the motor 30 is installed on the centrifugal fan 100 is called the motor side), resulting in the centrifugal fan 100 motor side The first air inlet 21 of the first air inlet 21 is blocked by the motor 30. Compared with the second air inlet 22 on the other side, the air intake air volume and wind resistance are larger, and the air inlet area is reduced, so that it is different from the first air inlet 21 and the second air inlet. The air intake of the tuyere 22 is quite different, and the air intake on both sides of the centrifugal fan 100 is unbalanced.

For this reason, in this embodiment, please refer to Fig. 5 to Fig. 8, the volute 20 of centrifugal blower 100 is formed with first air inlet 21, second air inlet 22, air outlet 23 and centrifugal air channel, and centrifugal air channel communicates The first air inlet 21, the second air inlet 22 and the air outlet 23, the first air inlet 21 and the second air inlet 22 are oppositely arranged at the two ends of the volute 20 in the axial direction, and the centrifugal air duct is used to accommodate the centrifugal fan. The side of the wind wheel 10 and the volute 20 provided with the first air inlet 21 is used for installing the motor 30 . Moreover, in this embodiment, the air intake area of the first air inlet 21 is larger than that of the second air inlet 22 .

It should be noted that, in the invention, the air inlet area of the first air inlet 21 or the second air inlet 22 only considers the shape and size of the first air inlet 21 and the second air inlet 22 on the volute 20 . The influence of the shielding of the motor 30 or the structure of the internal centrifugal rotor 10 on the actual air intake volumes of the first air inlet 21 and the second air inlet 22 is not considered. Through the design of the volute 20 in this embodiment, the centrifugal fan 100 in this embodiment is compared with the traditional double-suction centrifugal fan whose air inlets on both sides are basically the same. The area of the air inlet 21 reduces the air intake side of the centrifugal fan 100. Due to the adverse effects such as the reduction of the air intake area and the increase of the wind resistance caused by the installation of the motor 30, the air intake of the centrifugal fan 100 is provided with the motor 30 side. The increasing trend reduces the air intake difference between the two air intake sides of the centrifugal fan, and the air intake on both sides is more balanced, so that the operation is still stable at high speed and the wind noise is reduced.

The specific shapes of the first air inlet 21 and the second air inlet 22 are not limited, as long as the airflow can be sucked into the centrifugal air duct therefrom. In this embodiment, please refer to FIG. 8 and FIG. 9 , in order to reduce wind resistance, the first air inlet 21 and the second air inlet 22 are circular, the diameter of the first air inlet 21 is D1, and the diameter of the second air inlet 22 is The diameter is D2, and D1 is larger than D2. Thus, in this embodiment, the area of the first air inlet 21 is larger than that of the second air inlet 22 , thus having a larger air inlet area than the second air inlet 22 . When the centrifugal fan 100 is working, the air intake volume of the first air inlet 21 tends to increase. In this way, the adverse effects such as the reduction of the air intake area and the increase of wind resistance caused by the installation of the motor 30 on one of the air intake sides of the centrifugal fan 100 are reduced, so that the difference in the air intake volume of the two air intake sides of the centrifugal fan is reduced, and the two The side air intake is more balanced, so that it still runs smoothly at high speeds and reduces wind noise.

The structure and size of the centrifugal wind wheel 10 are not limited, as long as it is suitable for the centrifugal wind wheel 10 of the double-suction centrifugal fan 100 and can suck wind from both sides simultaneously. In one embodiment, please refer to FIG. 5 to FIG. 7 , the centrifugal wind wheel 10 includes a partition 13 , and centrifugal blades disposed opposite to each other on both sides of the partition 13 , and one side of the partition 13 is provided with a driving installation portion 131 , the driving installation part 131 is used for transmission cooperation with the motor 30 , so that the motor 30 drives the centrifugal wind wheel 10 to rotate.

It should be noted that, in this embodiment, the partition 13 mainly plays the role of cooperating with the motor 30 , and the driving connection between the motor 30 and the centrifugal wind wheel 10 is realized through the driving installation part 131 provided on the partition 13 . The rotating action of the motor 30 can be transmitted to the centrifugal wind wheel 10, thereby driving the centrifugal wind wheel 10 to rotate, generating centrifugal force, driving airflow to be sucked into the centrifugal air duct from the first air inlet 21 and the second air inlet 22, and then from the outlet Tuyere 23 sends out. In addition, the partition 13 can also play a role in blocking the airflow. It can be understood that in this embodiment, the first air inlet 21 and the second air inlet 22 are sucked into the centrifugal wind from two directions opposite to the axial direction of the centrifugal fan wheel 10. That is to say, the direction of the intake airflow of the first air inlet 21 and the second air inlet 22 is opposite. If there is no partition 13 to block it, it is easy for the two intake airflows to collide with each other and cancel each other, resulting in the blowing of the centrifugal fan 100. The air volume is reduced. Therefore, in this embodiment, the baffle 13 plays a role in blocking the airflow, so that the airflow entering the centrifugal air duct from the first air inlet 21 is blocked by the baffle 13, and is transported to the air outlet 23 under the centrifugal action of the centrifugal fan blades. At the same time, the airflow entering the centrifugal air duct from the second air inlet 22 is blocked by the partition plate 13, and is transported to the air outlet 23 under the centrifugal action of the centrifugal fan blades. For this reason, the separator 13 is preferably a circular plate-shaped structure matching the centrifugal air duct, and preferably does not have a hollow structure as a whole to avoid cross-flow.

In this embodiment, the side of the partition 13 provided with the driving installation portion 131 is facing the first air inlet 21 , and the side of the partition 13 facing away from the driving installation portion 131 is facing the second air inlet. The specific structure of the driving installation part 131 is not limited, for example, it may be a transmission shaft, a shaft hole and other structures keyed to the motor 30 . In this embodiment, referring to FIG. 6 , the mounting part of the motor 30 is a motor 30 mounting shaft hole formed in the center of the partition 13 for axial connection with the motor shaft 32 of the motor 30, so that the partition 13 plays a role in the motor 30. Rotate down, and drive the centrifugal fan blades on both sides of the dividing plate 13 to rotate thereupon, generate centrifugal force to drive the airflow to flow along the air delivery direction of the centrifugal air duct.

In one embodiment, please refer to FIG. 10 , the centrifugal blades of the centrifugal rotor 10 are multi-bladed centrifugal blades, and the centrifugal blades on both sides of the partition have substantially the same inner diameter and outer diameter. Specifically, the inner diameter of the centrifugal fan blade is d1, the outer diameter of the centrifugal fan blade is d2, the first air inlet 21 and the second air inlet 22 are circular, the diameter of the first air inlet 21 is D1, and the second air inlet The diameter of 22 is D2, and the values of D1 and D2 are as follows: D1=d1+λ(d2-d1), D2=d1+b(d2-d1).

In the prior art, the value ranges of λ and b are both about 0.2, which means that D1 and D2 are basically the same or similar, so the air intake areas of the first air inlet 21 and the second air inlet 22 are basically the same. As a result, the air intake on both sides of the centrifugal fan 100 is unbalanced, and the wind noise is relatively large. In this embodiment, the value of λ is greater than b, so that D1 is greater than D2, that is to say, the diameter of the first air inlet 21 is larger than that of the second air inlet 22, and the air inlet area of the first air inlet 21 is therefore larger than that of the second air inlet. Tuyere 22.

In this embodiment, b is less than or equal to 0.2, preferably b is equal to 0.2. It can be understood that the larger the value of λ, the larger the air intake area of the first air inlet 21 is larger than that of the second air inlet 22 , and the more favorable the actual air intake volume of the first air inlet 21 is closer to the second air inlet 22 . If the value of λ is too small, the air intake area of the first air inlet 21 cannot be significantly increased to achieve the purpose of balancing the air intake on both sides of the centrifugal fan 100 . However, if the value of λ is too large, it may also cause adverse effects of sudden decrease in air volume and increase in noise. For this reason, considering comprehensively the extent to which the first air inlet 21 is blocked by the installation of the motor 30, as well as factors such as reducing noise and increasing the air output of the centrifugal fan 100, the value of λ can be appropriately increased to increase the first air inlet 21. The diameter of air inlet 21.

Specifically, according to the air flow field simulation experiment, the λ-air flow curve shown in Figure 18 can be obtained. It can be seen from the figure that the value of λ is in the range of 0.1 to 0.4, and the air output of the centrifugal fan 100 does not change much. , the value of λ is in the range of 0.4 to 0.6, the air output of the centrifugal fan 100 is increased, and when the value of λ is greater than 0.6, the air output of the centrifugal fan 100 is obviously reduced. Please refer to FIG. 19 , which shows a comparison diagram of air volume and flow field under different values of λ. In Figure 19, the value of λ in the left figure is 0.1, the value of λ in the middle figure is 0.5, and the value of λ in the right figure is 0.8. It can be seen from the figure that when the value of λ is 0.5, the distribution effect of the air volume flow field is the best, and the air volume is the largest. Therefore, in this embodiment, λ is greater than or equal to 0.4 and less than or equal to 0.6.

In an embodiment, please refer to FIG. 11 to FIG. 16 , the centrifugal fan includes a first blade set 11 and a second blade set 12 . Moreover, the first vane set 11 is disposed on a side of the partition 13 where the driving installation portion 131 is disposed, and the second vane set 12 is disposed on a side of the partition 13 facing away from the driving installation portion 131 . The first blade set 11 and the second blade set 12 have different structures related to the air intake to reduce the air intake difference between the first blade set 11 and the second blade set 12 due to the influence of the motor 30 .

The specific forms of the first blade set 11 and the second blade set 12 are also not limited, for example, they may be multi-blade centrifugal rotors or wind wheel centrifugal rotors. In this embodiment, please refer to FIG. 11 , the structure of the first blade group 11 and the second blade group 12 related to the air intake is differentiated, so as to reduce the influence of the first blade group 11 from the influence of the motor 30 and the second blade group. The air intake difference between 12.

In this embodiment, there is no limit to the specific implementation of the structural differentiation of the first blade group 11 and the second blade group 12, as long as it can reduce the air inlet side of the centrifugal fan 100 due to the installation of the motor 30. Adverse effects such as reduced wind area and increased wind resistance are sufficient. In this embodiment, through the differentiated structural design of the first blade group 11 and the second blade group 12 of the centrifugal fan 10, the air intake corresponding to the first blade group 11 can be increased, so that the two air inlet sides of the centrifugal fan 100 The difference in air intake is reduced, and the air intake on both sides is more balanced, so that it still runs smoothly at high speeds and reduces wind noise.

In this embodiment, please continue to refer to FIG. 11 to FIG. 16 , the centrifugal rotor 10 is a multi-blade centrifugal rotor. Specifically, the first blade set 11 includes a plurality of first blades 110 arranged at intervals along the circumferential direction of the centrifugal fan 10 to form a cylindrical first blade set 11 , and the plurality of first blades 110 surround the driving installation part 131 set up. In this way, in this embodiment, please refer to FIG. 6 , the motor 30 may be at least partially installed in the hollow space of the first blade set 11 , so as to reduce the overall volume of the centrifugal fan 100 . The second blade set 12 includes a plurality of second blades 120 arranged at intervals along the circumferential direction of the centrifugal fan 10 to form a cylindrical second blade set 12 . The extension directions of each first blade 110 and each second blade 120 extend along the axial direction of the centrifugal fan 10 . It can be understood that the first blade set 11 and the second blade set 12 should have similar or even substantially the same outer diameter, so as to adapt to the basic structure of the centrifugal air duct and ensure the air supply effect of the centrifugal fan 100 . In this embodiment, the outer diameters of the first blade group 11 and the second blade group 12 are both d2, and at the same time, the inner diameter d1 of the first blade group 11 is greater than the inner diameter d11 of the second blade group 12, that is, the first blade group The maximum inner diameter of 11 in the radial direction is greater than the maximum inner diameter of the second blade set 12 in the radial direction.

Thus, in this embodiment, the first blade group 11 has a larger air intake area than the second blade group 12, thereby making up for the fact that the centrifugal fan 100 motor 30 side is installed with the motor 30 on the first blade group 11. coming adverse effects. Please refer to FIG. 7 for details. In the first blade group 11, if the inner diameters of the first blade group 11 and the second blade group 12 are the same, the air intake corresponding to the first blade group 11 will be much smaller than that of the second blade group 12. In this embodiment, due to the relative increase of the inner diameter of the first blade group 11, the distance L between the inner diameter of the first blade group 11 and the motor seat 31 of the motor 30 tends to increase, thereby making the periphery of the motor seat 31 larger. The air intake area of the first blade group 11 has a tendency to increase, reaching the same or close to the air intake volume of the second blade group 12, or although the air intake volume is smaller than the second blade group 12, it is at least the same as the second blade group 12. The air intake difference of the blade group 12 is reduced. In this way, in this embodiment, the first blade set 11 is designed to have a larger inner diameter than the second blade set 12, which can increase the air intake corresponding to the first blade set 11, and reduce the first blade set 11 due to the motor 30. The air intake difference between the second blade group 12 and the second blade group 12 caused by the installation reduces the air intake difference between the two air intake sides of the centrifugal fan 100, and the air intake on both sides is more balanced, so that the operation is still stable at high speed. Reduce wind noise.

There are many ways to realize that the inner diameter of the first vane set 11 is larger than the inner diameter of the second vane set 12 . In an embodiment, please refer to FIG. 11 to FIG. 13 , and the width of each of the first blades 110 is smaller than the width of each of the second blades 120 . In this embodiment, the width of each blade specifically refers to the width value of each blade from the outermost peripheral side to the innermost peripheral side in the radial direction. As shown in Figure 12, the width of each of the first blades 110 of the first blade group 11 is h1, as shown in Figure 13, the width of each of the first blades 110 of the second blade group 12 is h2, h1 is greater than h2, so that the inner diameter d1 of the first vane set 11 is greater than the inner diameter d11 of the second vane set 12 . In this embodiment, the first blade 110 and the second blade 120 preferably have the same or similar installation angles, and the inner diameter d1 of the first blade group 11 is realized only by adjusting the profile and width of the first blade 110 and the second blade 120 greater than the inner diameter d11 of the second vane set 12 . Of course, it is also possible that the first blade set 11 and the second blade set 12 have different installation angles and different blade widths, so that the inner diameter d1 of the first blade set 11 is larger than the inner diameter d11 of the second blade set 12 .

In this way, in this embodiment, the first blade set 11 is designed to have a larger inner diameter than the second blade set 12, which can increase the air intake corresponding to the first blade set 11, and reduce the first blade set 11 due to the motor 30. The air intake difference between the second blade group 12 and the second blade group 12 caused by the installation reduces the air intake difference between the two air intake sides of the centrifugal fan 100, and the air intake on both sides is more balanced, so that the operation is still stable at high speed. Reduce wind noise. Preferably, the installation angles of the first blade 110 and the second blade 120 are the same to reduce assembly difficulty.

In another embodiment, please refer to FIG. 14 to FIG. 16 , the installation angle of each first blade 110 is larger than the installation angle of each second blade 120 . In this embodiment, please refer to FIG. 15 and FIG. 16 , the installation angle of the blades specifically refers to the angle between the tangent line of the curved inner edge of each blade and the tangent line of the outer periphery of the blade group on the section of the cylindrical blade group. As shown in Figure 15, the installation angle of each first blade 110 is a1, as shown in Figure 16, the installation angle of each of the second blades 120 is a2, a1>a2 makes the inner diameter d1 of the first blade group 11 larger than the second The inner diameter d11 of the vane set 12 . In this embodiment, the first blade 110 and the second blade 120 preferably have the same or similar airfoil shape, and the inner diameter d1 of the first blade group 11 is greater than The inner diameter d11 of the second vane set 12 . Of course, it is also possible that the first blade set 11 and the second blade set 12 have different blade shapes and different installation angles, so that the inner diameter d1 of the first blade set 11 is larger than the inner diameter d11 of the second blade set 12 .

In this way, in this embodiment, the first blade set 11 is designed to have a larger inner diameter than the second blade set 12, which can increase the air intake corresponding to the first blade set 11, and reduce the first blade set 11 due to the motor 30. The air intake difference between the second blade group 12 and the second blade group 12 caused by the installation reduces the air intake difference between the two air intake sides of the centrifugal fan 100, and the air intake on both sides is more balanced, so that the operation is still stable at high speed. Reduce wind noise. Preferably, the first vane 110 and the second vane 120 have the same airfoil shape to reduce manufacturing costs.

Based on the above embodiment, the inner diameter of the first blade group is d1, the inner diameter of the second blade group is d11, the outer diameter of the first blade group and the second blade group is d2, and the first air inlet 21 and the second air inlet 22 are both It is circular, the diameter of the first air inlet 21 is D1, the diameter of the second air inlet 22 is D2, D1=d1+c(d2-d1), D2=d11+c(d2-d11), wherein, c is greater than equal to 0.1 and less than or equal to 0.3, preferably c is equal to 0.2.

In this embodiment, since d1 is greater than d11, the diameter D1 of the first air inlet 21 is greater than the diameter D2 of the second air inlet 22, and the air inlet area of the first air inlet 21 is larger than that of the second air inlet 22, so that in this embodiment Compared with the traditional double-suction centrifugal fan with substantially the same air inlets on both sides, the centrifugal fan 100 in the centrifugal fan 100 reduces the area of the first air inlet 21 on the side of the motor 30 on the volute 20, thereby reducing one inlet of the centrifugal fan 100. On the wind side, due to the adverse effects such as the reduction of the air intake area and the increase of wind resistance caused by the installation of the motor 30, the air intake volume on the side of the centrifugal fan 100 provided with the motor 30 tends to increase, so that the air intake of the two air intake sides of the centrifugal fan 100 tends to increase. The difference in air volume is reduced, and the air intake on both sides is more balanced, so that it still runs smoothly at high speeds and reduces wind noise.

The technical effects brought about by applying the volute 20 provided in this embodiment to the centrifugal fan 100 will be described below in combination with the prior art. In the prior art, the air intake areas of the air inlets on both sides of the double-suction centrifugal fan are basically the same, but in the centrifugal fan 100 in this embodiment, the air intake area of the first air inlet 21 is larger than that of the second air inlet.

Please refer to FIG. 17 . FIG. 17 shows a schematic diagram of air volume-noise data comparison between the centrifugal fan 100 provided by the present invention and the existing centrifugal fan. In Fig. 17, the volute 1 is the volute of the centrifugal fan 100 in this embodiment, and the volute 2 is the volute in the prior art. The abscissa in the figure indicates the working air volume (m3/h) of the centrifugal fan 100 using the volute 1, and the ordinate indicates the noise level (dB) generated when the centrifugal fan 100 works with different working air volumes. It can be seen from the figure that no matter it is the volute 1 or the volute 2, the noise of the centrifugal fan 100 during operation increases with the increase of the air volume. And when the air volume is low, that is, the air volume is less than 1160m3/h, the noise of the volute 1 is greater than that of the volute 2, but as the air volume increases, the noise gap between the two gradually narrows. In the case of high air volume, that is, the air volume is greater than or equal to 1160m3/h, the noise of the volute 1 is lower than that of the volute 2, and with the increase of the wind wheel, the noise gap between the two gradually increases. As shown in FIG. 17 , when the working air volume of the centrifugal fan 100 is 1200m3/h, the noise value of the volute 1 is 0.5dB lower than that of the volute 2 . That is to say, the slope of the increase of the noise of the volute 1 with the increase of the air volume is smaller than the slope of the increase of the noise of the volute 2 with the increase of the air volume. In the air conditioner 200 using the double-suction centrifugal fan 100, its normal working air volume is usually greater than 1200m3/h, that is to say, the air conditioner 200 using the centrifugal fan 100 provided by this embodiment has the same air volume , its working noise is smaller, which can bring users a more comfortable experience.

Based on the above embodiments, it can be understood that the purpose of reducing the adverse effect of the installation of the motor 30 on the air intake at the air intake side of the centrifugal fan 100 can also be achieved by improving the installation structure of the motor 30 . For this reason, in this embodiment, referring to FIGS. 3 to 5 , the centrifugal fan 100 further includes a motor mounting part 40 . The motor 30 is arranged on the volute 20, and is at least partly located in the centrifugal air duct between the first air inlet 21 and the partition 13. The motor 30 includes a motor base 31 and a motor shaft 32. The motor base 31 is mounted on the motor mount 40. The volute 20 is spaced apart from the volute 20 , the motor shaft 32 extends from the motor base 31 to the partition 13 , and is drivingly connected to the driving installation part 131 .

In this implementation, the motor 30 is basically accommodated in the air inlet duct corresponding to the first blade set 11, that is, basically accommodated in the volute 20, thereby reducing the overall volume of the centrifugal fan 100, making the centrifugal fan 100 compact in structure, Easy to install. Simultaneously, the motor base 31 is connected and installed with the volute 20 through the motor mounting part 40, and the motor base 31 and the volute 20 are arranged at intervals, so that there is a gap between the motor base 31 and the inner sidewall of the first air inlet 21, and the air intake air flows from the motor base. The gap between 31 and the inner side wall of the first air inlet 21 flows into the centrifugal air duct, preferably the motor base 31 is correspondingly arranged at the center of the first air inlet 21, so that the first air inlet 21 flows into the airflow in the middle of the first blade group 11 More balanced and smooth air intake is beneficial to reduce wind resistance and increase the air intake corresponding to the first blade set 11 . Combined with the above-mentioned design that the inner diameter of the first blade group 11 is larger than the inner diameter of the second blade group 12, the air intake corresponding to the first blade group 11 can be increased, and the gap between the first blade group 11 and the second blade group 12 caused by the installation of the motor 30 can be reduced. The air intake difference between the two air intake sides of the centrifugal fan 100 is reduced, and the air intake on both sides is more balanced, so that the operation is still stable at high speed and the wind noise is reduced. Preferably, the installation angles of the first blade 110 and the second blade 120 are the same to reduce assembly difficulty.

On the basis of the previous embodiment, in order to install the motor 30 more stably, a plurality of motor mounting parts 40 are provided, and the plurality of motor mounting parts 40 are distributed at intervals along the circumferential direction of the first air inlet 21, and each motor mounting part 40 is respectively Extending along the radial direction of the first air inlet 21 , one end is connected to the volute 20 and the other end is connected to the motor base 31 . In this way, the motor base 31 is supported from multiple directions, so that the force on the motor base 31 is reasonable. In addition, each mounting piece is designed in a narrow and long shape, so that the mounting piece occupies a small area in the air inlet direction, reduces the occupation of the air inlet area, and increases the air inlet volume.

The specific structure of each motor mounting part 40 is not limited, as long as the motor 30 can be reliably fixed so that the motor 30 is stably installed on the volute 20 . In this embodiment, please refer to FIG. 3 to FIG. 5 , each motor mount 40 includes a connecting plate 41 connected to the motor base 31 and a plurality of connecting ribs 42 extending from the connecting plate 41 to the volute 20 , each phase There is a gap between two adjacent connecting ribs 42 . In this embodiment, the motor mounting part 40 has a hollowed out structure, so that the air intake air can flow into the centrifugal air duct from the gap formed between a plurality of connecting ribs 42 in the motor mounting part 40, further reducing the impact of the mounting part on the air intake. Covering, increasing the air intake of the first air inlet 21, and fixing the motor base 31 through the connecting plate 41 is also easy to assemble. Preferably, as shown in Figure 3, the size of each connecting rib 42 in the axial direction is greater than the size in the radial direction, that is, the windward side of each connecting rib 42 has a smaller size, and has a larger size in the direction of airflow delivery. The size is like this, while ensuring the rigidity of the connecting rib 42 and the strength of the motor mounting part 40, it reduces the resistance of the motor mounting part 40 to the airflow and increases the air intake.

Please refer to FIG. 1 to FIG. 2 , the centrifugal fan 100 and the centrifugal fan 10 provided in this embodiment are applied to an air conditioner 200 , and the air conditioner 200 is a cabinet type air conditioner indoor unit. In this embodiment, the air conditioner 200 includes a casing 201 , a heat exchanger 204 and a centrifugal fan 100 . Please continue to refer to Fig. 2, the casing 201 can include the chassis that is located at the lower end of the air conditioner 200, the bottom casing that extends upwards from the chassis, and the panel that is located at the front side of the bottom casing. The heat exchange air duct formed by the common enclosure, the lower end of the shell 201 is provided with two heat exchange air inlets 202, the upper end of the shell 201 is provided with a heat exchange air outlet 203, and the heat exchange air duct is connected to the two heat exchange air inlets 202 and the heat exchange air duct. Air outlet 203. The two heat exchange air inlets 202 are both arranged on the bottom shell, and are arranged on opposite sides of the bottom shell. The first air inlet 21 on the volute 20 corresponds to one of the two heat exchange air inlets 202, and the second air inlet 22 on the volute 20 of the centrifugal fan 100 corresponds to the other of the two heat exchange air inlets 202. The tuyere 23 is set corresponding to the heat exchange air outlet 203 . Driven by the centrifugal fan 100, the indoor air flows into the heat exchange air channel from the two heat exchange air inlets 202, and exchanges heat through the heat exchanger 204 in the heat exchange air channel to obtain the air after heat exchange, and the air after heat exchange automatically The heat exchange air outlet 203 is sent out to realize the adjustment of the indoor temperature by the air conditioner 200 .

In this embodiment, the air conditioner 200 uses the double-suction centrifugal fan 100 provided in the above embodiments, and the double-suction centrifugal fan 100 uses the volute 20 provided in this embodiment. In this embodiment, through the design of the volute 20 in this embodiment, the centrifugal fan 100 provided by the present invention is compared with the traditional double-suction centrifugal fan with substantially the same air inlet on both sides, and the motor 30 is provided by enlarging the volute 20 The area of the first air inlet 21 on one side reduces the disadvantageous effects such as the reduction of the air intake area and the increase of wind resistance caused by the installation of the motor 30 on one air inlet side of the centrifugal fan 100. The centrifugal fan 100 is provided with a motor 30- The air intake on the side tends to increase, so that the difference between the two air intake sides of the centrifugal fan decreases, and the air intake on both sides is more balanced, so that when the air conditioner 200 is running at a high speed (when the air volume of the air conditioner 200 is greater than 1200m3/h) Smooth operation and reduced wind noise.

In this way, compared with the air conditioner 200 using the traditional centrifugal fan 100 , the air conditioner 200 in this embodiment has lower working noise under the condition of the same air supply volume, which can improve user experience. And in the case of the same rotational speed of the centrifugal wind wheel 10, it has a larger air supply volume, which can improve the heat exchange efficiency, and can cool or heat the room faster.

The above is only a preferred embodiment of the present invention, and does not limit the patent scope of the present invention. Under the inventive concept of the present invention, the equivalent structural transformation made by using the description of the present invention and the contents of the accompanying drawings, or direct/indirect use All other relevant technical fields are included in the patent protection scope of the present invention.

Claims (10)

1. A volute of a centrifugal fan is characterized in that,

the volute is provided with a first air inlet, a second air inlet, an air outlet and a centrifugal air duct, the centrifugal air duct is communicated with the first air inlet, the second air inlet and the air outlet, and the first air inlet and the second air inlet are oppositely arranged at two ends of the volute in the axial direction;

the centrifugal air duct is used for accommodating a centrifugal wind wheel, and one side of the volute, which is provided with the first air inlet, is used for installing a motor;

the air inlet area of the first air inlet is larger than that of the second air inlet.

2. The volute of a centrifugal fan of claim 1, wherein the first inlet and the second inlet are circular, and wherein the first inlet has a larger diameter than the second inlet.

3. A centrifugal fan, comprising:

a volute according to claim 1 or 2;

the centrifugal wind wheel is arranged in the centrifugal air duct and comprises a partition plate and centrifugal wind blades oppositely arranged on two sides of the partition plate, a driving installation part is arranged on one side of the partition plate, which is provided with the driving installation part, faces the first air inlet, and one side of the partition plate, which is back to the driving installation part, faces the second air inlet; and (c) a second step of,

the motor is arranged on one side of the first air inlet, and the motor is in driving connection with the driving installation part and used for driving the centrifugal wind wheel to rotate.

4. The centrifugal fan as claimed in claim 3, wherein the centrifugal fan is a multi-blade centrifugal fan, the centrifugal fan has an inner diameter D1 and an outer diameter D2, the first air inlet and the second air inlet are both circular, the diameter of the first air inlet is D1, the diameter of the second air inlet is D2, D1= D1+ λ (D2-D1), D2= D1+ b (D2-D1), λ is greater than or equal to 0.4 and less than or equal to 0.6, and b is less than or equal to 0.2.

5. The centrifugal fan as claimed in claim 3, wherein the centrifugal fan blade includes a first blade group and a second blade group, the first blade group is disposed on the side of the partition plate where the driving installation portion is disposed, and the second blade group is disposed on the side of the partition plate opposite to the driving installation portion;

the first blade group and the second blade group are arranged in a differentiated mode with air inlet volume related structures, so that air inlet volume difference values between the first blade group and the second blade group are reduced.

6. The centrifugal fan as claimed in claim 5, wherein the first blade group includes a plurality of first blades arranged at intervals in a circumferential direction of the centrifugal wind wheel to form the first blade group in a cylindrical shape, the plurality of first blades being arranged around the drive mounting portion;

the second blade group comprises a plurality of second blades which are arranged at intervals along the circumferential direction of the centrifugal wind wheel so as to form a cylindrical second blade group;

the inner diameter of the first blade group is larger than that of the second blade group.

7. The centrifugal fan of claim 6, wherein each first blade has a width less than a width of each second blade.

8. The centrifugal fan of claim 6 wherein each first blade has a stagger angle greater than each second blade.

9. The centrifugal fan as claimed in claim 6, wherein the inner diameter of the first blade group is D1, the inner diameter of the second blade group is D11, the outer diameters of the first blade group and the second blade group are D2, the first air inlet and the second air inlet are circular, the diameter of the first air inlet is D1, the diameter of the second air inlet is D2, D1= D1+ c (D2-D1), D2= D11+ c (D2-D11), and c is greater than or equal to 0.1 and less than or equal to 0.3.

10. An air conditioner characterized by comprising the centrifugal fan according to any one of claims 3 to 9.

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