CN115479047A

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

Info

Publication number: CN115479047A
Application number: CN202110603556.XA
Authority: CN
Inventors: 吴鑫
Original assignee: GD Midea Air Conditioning Equipment Co Ltd; Guangzhou Hualing Refrigeration Equipment Co Ltd
Current assignee: GD Midea Air Conditioning Equipment Co Ltd; Guangzhou Hualing Refrigeration Equipment Co Ltd
Priority date: 2021-05-31
Filing date: 2021-05-31
Publication date: 2022-12-16

Abstract

The invention discloses a volute of a centrifugal fan, the centrifugal fan and an air conditioner. In this embodiment, the area of the first air inlet on one side of the motor of the volute is increased, and the adverse effect of one air inlet side of the centrifugal fan caused by the installation of the motor is reduced, so that the air inlets on the two air inlet sides of the centrifugal fan are more balanced, the centrifugal fan still runs stably during high-speed operation, and the air noise is reduced.

Description

Volute of centrifugal fan, 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, the centrifugal fan and an air conditioner.

Background

The volute and the impeller of the double-suction centrifugal fan for the existing air conditioner adopt a basically symmetrical structural design, and the motor is arranged on one of two air inlet sides of the double-suction centrifugal fan.

The air inlet side of the double-suction centrifugal fan provided with the motor has different air inlet effects due to the existence of the motor and the installation structure thereof, so that the double-suction centrifugal fan is unstable in operation during high-speed operation and has high airflow noise.

Disclosure of Invention

The invention mainly aims to provide a volute of a centrifugal fan, the centrifugal fan and an air conditioner, and aims to improve the air inlet difference of two air inlet sides of a double-suction centrifugal fan and reduce airflow noise.

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

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.

In an embodiment, the first air inlet and the second air inlet are both 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 further provides a centrifugal fan, including:

a volute as described above;

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 the number of the first and second groups,

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

In an embodiment, the centrifugal fan blade is a multi-blade centrifugal fan blade, the centrifugal fan blade 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), wherein 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.

In one embodiment, the centrifugal fan blade comprises a first blade group and a second blade group, the first blade group is arranged on one side of the partition plate, which is provided with the driving installation part, and the second blade group is arranged on one side of the partition plate, which faces away from the driving installation part;

the first blade group and the second blade group are arranged in a differentiated mode with air inlet quantity related structures, and therefore the air inlet quantity difference value between the first blade group and the second blade group is reduced.

In one embodiment, the first blade group includes a plurality of first blades arranged at intervals along the circumferential direction of the centrifugal wind wheel to form a cylindrical first blade group, and the plurality of first blades are arranged around the driving installation part;

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.

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

In an embodiment, the setting angle of each first blade is larger than the setting angle of each second blade.

In an embodiment, 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 both 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.

In order to achieve the above object, the present invention further provides an air conditioner, which includes the centrifugal fan as described above.

In the embodiment provided by the invention, the volute is provided with a first air inlet, a second air inlet, an air outlet and a centrifugal air channel, the centrifugal air channel is communicated with the first air inlet, the second air inlet and the air outlet, 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 channel is used for accommodating a centrifugal wind wheel, one side of the volute, which is provided with the first air inlet, is used for installing a motor, and the air inlet area of the first air inlet is larger than that of the second air inlet. Compared with the traditional double-suction centrifugal fan with basically identical air inlets at two sides, the centrifugal fan provided by the invention has the advantages that the area of the first air inlet at one side of the volute provided with the motor is increased, the adverse effects of reduction of air inlet area, increase of wind resistance and the like caused by installation of the motor at one air inlet side of the centrifugal fan are reduced, the air inlet amount at one side of the centrifugal fan provided with the motor tends to increase, the air inlet amount difference value of the two air inlet sides of the centrifugal fan is reduced, air inlet at two sides is more balanced, the centrifugal fan still runs stably during high-speed running, and the wind noise is reduced.

Drawings

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

FIG. 2 is an exploded view of the air conditioner of FIG. 1;

FIG. 3 is a schematic perspective view of the centrifugal fan of FIG. 1;

FIG. 4 is an exploded perspective view of the centrifugal fan of FIG. 3;

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

FIG. 6 isbase:Sub>A cross-sectional view taken at A-A of FIG. 5;

FIG. 7 is a cross-sectional view taken at B-B of FIG. 6;

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

FIG. 9 is a front view of the side of the volute of FIG. 3 opposite the motor side;

figure 10 is a front view of an embodiment of the centrifugal wind rotor of figure 4;

FIG. 11 is a schematic perspective view of another embodiment of the centrifugal wind wheel of FIG. 4;

FIG. 12 is a cross-sectional view of the first vane pack of FIG. 11;

FIG. 13 is a cross-sectional view of the second blade set of FIG. 11;

figure 14 is a schematic perspective view of a further embodiment of the centrifugal rotor of figure 4;

FIG. 15 is a cross-sectional view of the first vane pack of FIG. 14;

FIG. 16 is a cross-sectional view of the second blade set of FIG. 14;

FIG. 17 is a comparison graph of air volume-noise data between a centrifugal fan according to the present invention and a conventional centrifugal fan;

FIG. 18 is a lambda-air volume curve of an embodiment of the centrifugal fan provided by the present invention;

fig. 19 is a comparison graph of air flow fields of the centrifugal fan provided by the invention under different values of lambda.

The reference numbers illustrate:

reference numerals	Name (R)	Reference numerals	Name (R)
				100	Centrifugal fan	30	Electric machine
10	Centrifugal wind wheel	31	Motor base
				11	First blade group	32	Motor shaft
110	First blade	40	Motor mounting part
				12	Second blade group	41	Connecting plate
120	Second blade	42	Connecting rib
				13	Partition plate	200	Air conditioner
131	Drive mounting part	201	Outer casing
				20	Spiral casing	202	Heat exchange air inlet
21	First air inlet	203	Heat exchange air outlet
				22	Second air inlet	204	Heat exchanger
23	Air outlet

The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

It should be noted that, if directional indications (such as up, down, left, right, front, back, 8230; etc.) are involved in the embodiment of the present invention, the directional indications are only used for explaining the relative positional relationship between the components, the motion situation, etc. in a specific posture (as shown in the figure), and if the specific posture is changed, the directional indications are correspondingly changed.

In addition, if there is a description of "first", "second", etc. in an embodiment of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, the technical solutions between the various embodiments may be combined with each other, but must be based on the realization of the present invention by those skilled in the art, and when existing, the technical solutions do not fall within the protection scope of the present invention.

The present invention provides an air conditioner 200. The air conditioner 200 may be an integrated air conditioner, a split air conditioner, an outdoor unit of an air conditioner, an indoor unit of a cabinet air conditioner, an indoor unit of an embedded air conditioner, an indoor unit of a wall-mounted air conditioner, or any other air conditioner 100 that can use a double suction centrifugal wind wheel. Referring to fig. 1 and 2, in the present embodiment, the air conditioner 200 is a cabinet air conditioner indoor unit.

The volute and the impeller of the existing double-suction centrifugal fan adopt a basically symmetrical structural design, and the motor is arranged on one of two air inlet sides of the double-suction centrifugal fan. The centrifugal wind wheel in the double-suction centrifugal fan is driven by the motor to rotate, and two air inlets respectively arranged at two sides of the volute suck airflow into the centrifugal air duct and send the airflow out from the air outlet. The motor of the double-suction centrifugal fan is usually arranged on one of two air inlet sides of the volute, so that the air inlet area of the air inlet side is reduced, the air resistance is increased, and the air inlet amount is obviously reduced compared with the other air inlet side. The air inlet difference and the air inlet speed difference of the two air inlet sides of the double-suction centrifugal fan are large, so that when the double-suction centrifugal fan runs at a high speed, the air inlets of the two air inlet sides are unbalanced, the centrifugal fan runs unstably, the air noise is large, and the air supply amount is also influenced and reduced.

To solve the above technical problem, please refer to fig. 3 to 9, the present invention provides a volute 20 of a centrifugal fan 100 and a centrifugal fan 100 including the centrifugal wind wheel 10.

Referring to fig. 3 and 4, in the present embodiment, a centrifugal fan 100 includes a volute 20, a centrifugal wind 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 is communicated with 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 two axial ends of the volute 20, the centrifugal wind wheel 10 is arranged at the centrifugal air duct, and the motor 30 is arranged at one side of the volute 20 where the first air inlet 21 is arranged and used for driving the centrifugal wind wheel 10 to rotate. When the centrifugal wind wheel 10 rotates, the air flow is sucked into the centrifugal wind channel from the first air inlet 21 and the second air inlet 22, and the air flow is sent out from the air outlet 23.

The centrifugal fan 100 in this embodiment is a double-suction centrifugal fan, and compared with a common centrifugal fan that generally sucks air flow from only one side, the double-suction centrifugal fan sucks air flow from both sides at the same time, which increases the air inlet area and thus has a larger air volume than the common centrifugal fan. However, as shown in this embodiment, the centrifugal fan 100 needs to install the motor 30 on one side of the volute 20 (the side of the centrifugal fan 100 where the motor 30 is installed is referred to as the motor side in the present invention), so that the air intake from the first air inlet 21 on the motor side of the centrifugal fan 100 is blocked by the motor 30, and compared with the air intake from the second air inlet 22 on the other side, the air intake volume is larger, and the air intake area is reduced, so that the air intake difference with the first air inlet 21 and the second air inlet 22 is larger, and the air intake on both sides of the centrifugal fan 100 is unbalanced.

Therefore, in the present embodiment, referring to fig. 5 to 8, a first air inlet 21, a second air inlet 22, an air outlet 23, and a centrifugal air duct are formed in the volute 20 of the centrifugal fan 100, the centrifugal air duct is communicated with 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 disposed at two ends of the volute 20 in the axial direction, the centrifugal air duct is used for accommodating the centrifugal wind wheel 10, and one side of the volute 20, where the first air inlet 21 is disposed, is used for mounting the motor 30. In addition, in the present embodiment, the air intake area of the first air intake opening 21 is larger than that of the second air intake opening 22.

It should be noted that, in the invention, the air intake area of the first air intake opening 21 or the second air intake opening 22 only considers the shape and size of the first air intake opening 21 and the second air intake opening 22 on the scroll casing 20. The influence of the shielding of the motor 30 or the structure of the internal centrifugal wind wheel 10 on the actual wind intake amount of the first wind inlet 21 and the second wind inlet 22 is not considered. Through the design of spiral case 20 in this embodiment, centrifugal fan 100 in this embodiment compares the two-sided air intake traditional double suction formula centrifugal fan that is the same basically, through the area that increases spiral case 20 and is equipped with first air intake 21 of motor 30 one side, reduce adverse effect such as the intake area that an air inlet side of centrifugal fan 100 brought owing to installing motor 30 reduces, windage increase, the intake of centrifugal fan 100 one side that is equipped with motor 30 has the increase trend, make the intake difference of two air inlets sides of centrifugal fan reduce, both sides air inlet is more balanced, thereby still operate steadily when high-speed operation, reduce wind and make an uproar.

The specific shape of the first air intake vent 21 and the second air intake vent 22 is not limited as long as it enables the air flow to be drawn into the centrifugal air duct therethrough. In this embodiment, referring to fig. 8 and 9, in order to reduce the wind resistance, the first wind inlet 21 and the second wind inlet 22 are both circular, the diameter of the first wind inlet 21 is D1, the diameter of the second wind inlet 22 is D2, and D1 is greater than D2. As such, in the present embodiment, the first air inlet 21 has a larger area than the second air inlet 22, and thus has a larger air inlet area than the second air inlet 22. When the centrifugal fan 100 is working, the air intake of the first air inlet 21 tends to increase. Therefore, adverse effects of reduction of air inlet area, increase of air resistance and the like caused by installation of the motor 30 on one air inlet side of the centrifugal fan 100 are reduced, so that the air inlet quantity difference value of the two air inlet sides of the centrifugal fan is reduced, air inlets on the two sides are more balanced, the centrifugal fan still runs stably during high-speed operation, and air noise is reduced.

The centrifugal wind wheel 10 is not limited in structure and size as long as it can simultaneously suck wind from both sides as long as it is applicable to the centrifugal wind wheel 10 of the double suction centrifugal fan 100. In an embodiment, referring to fig. 5 to 7, the centrifugal wind wheel 10 includes a partition plate 13 and centrifugal blades oppositely disposed on two sides of the partition plate 13, one side of the partition plate 13 is provided with a driving installation portion 131, and the driving installation portion 131 is configured to be in transmission fit 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 functions to cooperate with the motor 30, and the driving connection between the motor 30 and the centrifugal wind wheel 10 is realized through the driving installation portion 131 provided on the partition 13. So that the rotation of the rotating shaft 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, and driving the air flow to be sucked into the centrifugal air duct from the first air inlet 21 and the second air inlet 22, and then to be sent out from the air outlet 23. In addition, the partition plate 13 can also function to block the air flow, and it can be understood that, in this embodiment, the first air inlet 21 and the second air inlet 22 are sucked into the centrifugal air duct from two opposite directions in the axial direction of the centrifugal wind wheel 10, that is, the air inlet air flow directions of the first air inlet 21 and the second air inlet 22 are opposite, and if no partition plate 13 blocks the air inlet, the two air inlet air flows are likely to collide and offset each other, which results in the reduction of the air output of the centrifugal fan 100. Therefore, in this embodiment, the partition plate 13 plays a role of blocking the airflow, so that the airflow entering the centrifugal air duct from the first air inlet 21 is blocked by the partition plate 13 and is delivered to the air outlet 23 under the centrifugal action of the centrifugal fan blade, and meanwhile, the airflow entering the centrifugal air duct from the second air inlet 22 is blocked by the partition plate 13 and is delivered to the air outlet 23 under the centrifugal action of the centrifugal fan blade. For this purpose, the partition 13 is preferably a disk-like structure matching the centrifugal air duct, and preferably has no hollow structure as a whole, so as to avoid streaming.

In this embodiment, the side of the partition plate 13 provided with the driving installation portion 131 faces the first air inlet 21, and the side of the partition plate 13 facing away from the driving installation portion 131 faces the second air inlet. The specific structure of the driving mounting portion 131 is not limited, and may be other structures such as a transmission shaft and a shaft hole that are connected to the motor 30. In this embodiment, referring to fig. 6, the mounting portion of the motor 30 is a mounting shaft hole of the motor 30 formed at the center of the partition 13, and is used for being connected to a motor shaft 32 of the motor 30, so that the partition 13 rotates under the action of the motor 30 and drives the centrifugal blades at two sides of the partition 13 to rotate along with the motor shaft, and centrifugal force is generated to drive airflow to flow along the air feeding direction of the centrifugal air duct.

In an embodiment, referring to fig. 10, the centrifugal blades of the centrifugal wind wheel 10 are multi-blade centrifugal blades, and the centrifugal blades on both sides of the partition have substantially the same inner diameter and outer diameter. Specifically, the internal diameter of centrifugal fan blade is D1, and the external diameter of centrifugal fan blade is D2, and first air intake 21 and second air intake 22 all are circular, and the diameter of first air intake 21 is D1, and the diameter of second air intake 22 is D2, and the value of D1 and D2 is 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, that is, D1 and D2 are substantially the same or similar, so the air intake areas of the first air intake 21 and the second air intake 22 are substantially the same. Resulting in unbalanced air intake at both sides of the centrifugal fan 100 and large wind noise. In this embodiment, the value of λ is greater than b, so that D1 is greater than D2, that is, the diameter of the first air inlet 21 is greater than that of the second air inlet 22, and the air inlet area of the first air inlet 21 is greater than that of the second air inlet 22.

In the present embodiment, b is 0.2 or less, preferably 0.2 or less. It can be understood that the larger the value of λ is, the larger the air intake area of the first air intake 21 is than that of the second air intake 22, which is also beneficial to the closer the actual air intake of the first air intake 21 is to the second air intake 22. If the value of λ is too small, the air intake area of the first air intake 21 cannot be significantly increased, so as to achieve the purpose of balancing the air intake on both sides of the centrifugal fan 100. However, too large a value of λ may cause an adverse effect of a sudden decrease in air volume and an increase in noise. Therefore, the value of λ can be increased properly to increase the diameter of the first air inlet 21 by comprehensively considering the degree of shielding the first air inlet 21 by the motor 30, reducing noise, increasing the air output of the centrifugal fan 100, and the like.

Specifically, a λ -air volume curve shown in fig. 18 can be obtained according to an air volume flow field simulation experiment, and it can be seen in the graph that the value of λ is in the range of 0.1 to 0.4, the air volume of the centrifugal fan 100 does not change greatly, the value of λ is in the range of 0.4 to 0.6, the air volume of the centrifugal fan 100 is increased, and when the value of λ is greater than 0.6, the air volume of the centrifugal fan 100 is significantly reduced. Referring to fig. 19, fig. 19 shows a comparison graph of air flow fields of λ at different values. In fig. 19, λ in the left graph is 0.1, λ in the middle graph is 0.5, and λ in the right graph is 0.8. It can be seen from the figure that when the value of lambda is 0.5, the distribution effect of the air flow field is best, and the air output is maximum. Therefore, in the present embodiment, λ is 0.4 or more and 0.6 or less.

In an embodiment, referring to fig. 11 to 16, the centrifugal fan includes a first blade set 11 and a second blade set 12. The first blade group 11 is provided on the side of the partition plate 13 where the driving attachment portion 131 is provided, and the second blade group 12 is provided on the side of the partition plate 13 facing away from the driving attachment portion 131. The first blade group 11 and the second blade group 12 are arranged in a differentiated manner with respect to the air intake, so that the air intake difference between the first blade group 11 and the second blade group 12 due to the influence of the motor 30 is reduced.

The specific form of the first blade group 11 and the second blade group 12 is also not limited, and may be, for example, a multi-wing centrifugal rotor or a wind-wheel centrifugal rotor. In the embodiment, referring to fig. 11, the first blade group 11 and the second blade group 12 are arranged differently according to the structure related to the intake air amount, so as to reduce the intake air amount difference between the first blade group 11 and the second blade group 12 due to the influence of the motor 30.

In this embodiment, the specific implementation manner of the structure differentiation setting of the first blade group 11 and the second blade group 12 is not limited, as long as the adverse effects of the reduction of the air inlet area, the increase of the wind resistance and the like caused by the installation of the motor 30 on one air inlet side of the centrifugal fan 100 can be reduced. In this embodiment, through the differentiated structural design of the first blade group 11 and the second blade group 12 of the centrifugal wind wheel 10, the air intake rate corresponding to the first blade group 11 can be increased, so that the air intake rate difference between the two air intake sides of the centrifugal fan 100 is reduced, and the air intake at the two sides is more balanced, so that the centrifugal fan still operates stably during high-speed operation, and the wind noise is reduced.

In the present embodiment, please continue to refer to fig. 11 to fig. 16, the centrifugal wind wheel 10 is a multi-wing centrifugal wind wheel. Specifically, the first blade group 11 includes a plurality of first blades 110 disposed at intervals in a circumferential direction of the centrifugal wind rotor 10 to form a cylindrical first blade group 11, and the plurality of first blades 110 are disposed around the driving mount portion 131. Thus, in the present embodiment, referring to fig. 6, the motor 30 may be at least partially disposed in the hollow space of the first blade group 11, so as to reduce the overall volume of the centrifugal fan 100. The second blade group 12 includes a plurality of second blades 120 arranged at intervals along the circumferential direction of the centrifugal wind wheel 10 to form a cylindrical second blade group 12. Each of the first blades 110 and each of the second blades 120 extends in the axial direction of the centrifugal wind rotor 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 to adapt to the basic structure of the centrifugal air duct and ensure the air supply effect of the centrifugal fan 100. In the present embodiment, the outer diameters of the first blade group 11 and the second blade group 12 are both d2, and meanwhile, the inner diameter d1 of the first blade group 11 is larger than the inner diameter d11 of the second blade group 12, that is, the maximum inner diameter of the first blade group 11 in the radial direction is larger than the maximum inner diameter of the second blade group 12 in the radial direction.

In this way, in the present embodiment, the first blade group 11 has a larger air intake area than the second blade group 12, so as to compensate for the adverse effect of the motor 30 installed at the motor 30 side of the centrifugal fan 100 on the intake of the first blade group 11. Referring to fig. 7, 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 intake air amount corresponding to the first blade group 11 is greatly smaller than that of the second blade group 12, and in the embodiment, because the inner diameter of the first blade group 11 is relatively increased, the distance L between the inner diameter of the first blade group 11 and the motor base 31 of the motor 30 tends to be increased, so that the periphery of the motor base 31 has a larger intake air area, and the intake air amount of the first blade group 11 tends to be increased, which is the same as or close to the intake air amount of the second blade group 12, or although the intake air amount is smaller than that of the second blade group 12, the intake air difference with the second blade group 12 is at least reduced. So, in this embodiment, adopt first blade group 11 to compare the design that second blade group 12 has bigger internal diameter, can increase the intake that first blade group 11 corresponds, reduce first blade group 11 because the installation of motor 30 lead to with the intake difference between second blade group 12 for the intake difference of two air inlet sides of centrifugal fan 100 reduces, and both sides air inlet is more balanced, thereby still operates steadily when high-speed operation, reduces wind and makes an uproar.

There are various ways to achieve a larger inner diameter of the first blade set 11 than the second blade set 12. In an embodiment, please refer to fig. 11 to 13, and the width of each first blade 110 is smaller than the width of each second blade 120. In the present embodiment, the width of each blade specifically refers to a width value from one side of the outermost periphery to one side of the innermost periphery of each blade in the radial direction. As shown in fig. 12, each of the first blades 110 of the first blade group 11 has a width h1, and as shown in fig. 13, each of the first blades 110 of the second blade group 12 has a width h2, and h1 is greater than h2, so that the inner diameter d1 of the first blade group 11 is greater than the inner diameter d11 of the second blade group 12. In the present embodiment, the first blade 110 and the second blade 120 preferably have the same or similar installation angle, and the inner diameter d1 of the first blade group 11 is larger than the inner diameter d11 of the second blade group 12 only by adjusting the blade profile and the width of the first blade 110 and the second blade 120. Of course, the first blade group 11 and the second blade group 12 may have different installation angles and different blade widths, and the inner diameter d1 of the first blade group 11 may be larger than the inner diameter d11 of the second blade group 12.

So, in this embodiment, adopt first blade group 11 to compare the design that second blade group 12 has bigger internal diameter, can increase the intake that first blade group 11 corresponds, reduce first blade group 11 because the motor 30 installation lead to with the second blade group 12 between the air inlet difference for the intake difference of two air inlet sides of centrifugal fan 100 reduces, the both sides air inlet is more balanced, thereby still operates steadily when high-speed operation, reduces wind and makes an uproar. Preferably, the first blade 110 and the second blade 120 have the same installation angle, so as to reduce the difficulty of assembly.

In another embodiment, referring to fig. 14-16, the stagger angle of each first blade 110 is greater than the stagger angle of each second blade 120. In the present embodiment, referring to fig. 15 and 16, the installation angle of the blade specifically refers to the included angle between the tangent of the curved inner edge of each blade and the tangent of the outer periphery of the blade group on the cross section of the cylindrical blade group. As shown in fig. 15, the installation angle of each first blade 110 is a1, and as shown in fig. 16, the installation angle of each second blade 120 is a2, and a1> a2, so that the inner diameter d1 of the first blade group 11 is larger than the inner diameter d11 of the second blade group 12. In the present embodiment, the first blade 110 and the second blade 120 preferably have the same or similar blade profiles, and the inner diameter d1 of the first blade group 11 is larger than the inner diameter d11 of the second blade group 12 only by adjusting the blade installation angles of the first blade 110 and the second blade 120. Of course, the first blade group 11 and the second blade group 12 may have different blade profiles and different installation angles, and the inner diameter d1 of the first blade group 11 may be larger than the inner diameter d11 of the second blade group 12.

So, in this embodiment, adopt first blade group 11 to compare the design that second blade group 12 has bigger internal diameter, can increase the intake that first blade group 11 corresponds, reduce first blade group 11 because the installation of motor 30 lead to with the intake difference between second blade group 12 for the intake difference of two air inlet sides of centrifugal fan 100 reduces, and both sides air inlet is more balanced, thereby still operates steadily when high-speed operation, reduces wind and makes an uproar. Preferably, the first blade 110 and the second blade 120 have the same profile, thereby reducing the manufacturing cost.

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 diameters of the first blade group and the second blade group are D2, the first air inlet 21 and the second air inlet 22 are both 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), where c is greater than or equal to 0.1 and less than or equal to 0.3, and 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 greater than the second air inlet 22, so that the centrifugal fan 100 in this embodiment, compared with a conventional double-suction centrifugal fan with substantially the same air inlets on both sides, reduces adverse effects such as reduction of the air inlet area and increase of the wind resistance on one air inlet side of the centrifugal fan 100 due to installation of the motor 30 by increasing the area of the first air inlet 21 on the side of the volute 20 where the motor 30 is disposed, and increases the air inlet volume on the side of the centrifugal fan 100 where the motor 30 is disposed, so that the difference between the air inlet volumes on the two air inlet sides of the centrifugal fan is reduced, the air inlets on both sides are more balanced, and thus the centrifugal fan can still operate stably at high speed, and reduce wind noise.

The technical effect of the volute 20 provided by the present embodiment when applied to the centrifugal fan 100 will be described below in conjunction with the comparison of the prior art. In the prior art, the air inlet areas of the air inlets on both sides of the double-suction centrifugal fan are substantially the same, and in the centrifugal fan 100 in this embodiment, the air inlet area of the first air inlet 21 is larger than that of the second air inlet.

Referring to fig. 17, fig. 17 is a schematic diagram showing a comparison between air volume-noise data of the centrifugal fan 100 according to the present invention and that of a conventional centrifugal fan. In fig. 17, a scroll casing 1 is a scroll casing of a centrifugal fan 100 in the present embodiment, and a scroll casing 2 is a scroll casing in the related art. In the figure, the abscissa represents the operating air volume (m 3/h) of the centrifugal fan 100 to which the volute 1 is applied, and the ordinate represents the noise level (dB) generated when the centrifugal fan 100 operates corresponding to different operating air volumes. As can be seen from the figure, the noise of the centrifugal fan 100 in operation increases with the increase of the air volume, regardless of the scroll 1 or the scroll 2. And under the condition of low air volume, namely the air volume is less than 1160m3/h, the noise of the volute 1 is greater than that of the volute 2, but the noise difference between the volute and the volute is gradually reduced along with the increase of the air volume. And under the condition of high air volume, namely the air volume is more than or equal to 1160m3/h, the noise of the volute 1 is less than that of the volute 2, and the noise difference between the volute and the wind wheel is gradually increased along with the increase of the wind wheel. As shown in fig. 17, when the operating 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, the slope of the noise increase of the volute 1 with the air volume increase is smaller than that of the volute 2 with the air volume increase. In the air conditioner 200 using the double-suction centrifugal fan 100, the normal operation air volume is usually larger than 1200m3/h, that is, the air conditioner 200 using the centrifugal fan 100 provided by the embodiment has smaller operation noise under the condition of the same air volume, and can bring more comfortable use experience to users.

Based on the above embodiment, it can be understood that the purpose of reducing the adverse effect of the installation of the motor 30 on 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 the present embodiment, referring to fig. 3 to 5, the centrifugal fan 100 further includes a motor mounting member 40. The motor 30 is disposed in the volute casing 20 and at least partially 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 to the volute casing 20 through a motor mounting member 40 and is spaced apart from the volute casing 20, and the motor shaft 32 extends from the motor base 31 to the partition 13 and is drivingly connected to the driving mounting portion 131.

In this embodiment, the motor 30 is substantially accommodated in the air inlet duct corresponding to the first blade group 11, that is, substantially accommodated in the volute 20, so as to reduce the overall volume of the centrifugal fan 100, so that the centrifugal fan 100 has a compact structure and is easy to install. Meanwhile, the motor base 31 is connected with the volute casing 20 through the motor mounting part 40, the motor base 31 is arranged at an interval with the volute casing 20, a gap is formed between the motor base 31 and the inner side wall of the first air inlet 21, inlet airflow flows into the centrifugal air duct from the gap between the motor base 31 and the inner side wall of the first air inlet 21, preferably, the motor base 31 is correspondingly arranged at the center of the first air inlet 21, airflow flowing into the middle of the first vane assembly 11 from the first air inlet 21 is more balanced, air inlet is smooth, wind resistance is reduced, and the air inlet amount corresponding to the first vane assembly 11 is increased. By combining the 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 inlet amount corresponding to the first blade group 11 can be increased, and the air inlet difference between the first blade group 11 and the second blade group 12 caused by the installation of the motor 30 is reduced, so that the air inlet amount difference between the two air inlet sides of the centrifugal fan 100 is reduced, air inlets on the two sides are more balanced, and the centrifugal fan still runs stably during high-speed running and reduces wind noise. Preferably, the first blade 110 and the second blade 120 have the same installation angle, so that the assembly difficulty is reduced.

On the basis of the above embodiment, in order to more stably mount the motor 30, the motor mount 40 is provided in plurality, the plurality of motor mounts 40 are distributed at intervals along the circumferential direction of the first air inlet 21, each motor mount 40 extends along the radial direction of the first air inlet 21, and one end of each motor mount 40 is connected to the scroll 20, and the other end of each motor mount is connected to the motor base 31. In this way, providing support for motor mount 31 from multiple orientations provides for a reasonable force on motor mount 31. And each installed part is the design of long and narrow shape for the installed part is little in the area occupied of air inlet direction, reduces the occupation to the air inlet area, increases the intake.

The specific structure of each motor mount 40 is not limited as long as the motor 30 can be reliably fixed such that the motor 30 is stably mounted to the scroll casing 20. In the present embodiment, referring to fig. 3 to 5, each of the motor mounting members 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 scroll casing 20, and a gap is formed between every two adjacent connecting ribs 42. In this embodiment, the motor mounting member 40 has a hollow structure, so that the intake air can flow into the centrifugal air duct from the gap formed between the plurality of connecting ribs 42 in the motor mounting member 40, the shielding of the mounting member on the intake air is further reduced, the intake volume of the first air inlet 21 is increased, and the motor base 31 is easily assembled by the connecting plate 41. Preferably, as shown in fig. 3, the dimension of each connecting rib 42 in the axial direction is larger than that in the radial direction, that is, the windward side of each connecting rib 42 has a smaller dimension and a larger dimension in the airflow conveying direction, so that the blocking of the airflow by the motor mount 40 is reduced and the intake air amount is increased while the rigidity of the connecting ribs 42 and the strength of the motor mount 40 are ensured.

Referring to fig. 1 to 2, the centrifugal fan 100 and the centrifugal wind wheel 10 provided in the present embodiment are applied to an air conditioner 200, and the air conditioner 200 is a cabinet type air conditioner indoor unit. In the present embodiment, the air conditioner 200 includes a casing 201, a heat exchanger 204, and a centrifugal fan 100. Referring to fig. 2, the casing 201 may include a bottom chassis disposed at a lower end of the air conditioner 200, a bottom chassis extending upward from the bottom chassis, and a panel disposed at a front side of the bottom chassis, a heat exchange air duct formed by the bottom chassis, and the panel being enclosed together is formed in the casing 201, two heat exchange air inlets 202 are disposed at a lower end of the casing 201, a heat exchange air outlet 203 is disposed at an upper end of the casing 201, and the heat exchange air duct communicates the two heat exchange air inlets 202 and the heat exchange air outlet 203. The two heat exchange air inlets 202 are disposed on the bottom case, and disposed on two opposite sides of the bottom case, the heat exchanger 204 is disposed on the heat exchange air duct, the centrifugal fan 100 is disposed on the heat exchange air duct, the first air inlet 21 on the volute 20 of the centrifugal fan 100 is disposed corresponding to one of the two heat exchange air inlets 202, the second air inlet 22 on the volute 20 of the centrifugal fan 100 is disposed corresponding to the other one of the two heat exchange air inlets 202, and the air outlet 23 is disposed corresponding to the heat exchange air outlet 203. Under the driving of the centrifugal fan 100, indoor air flows into the heat exchange air duct from the two heat exchange air inlets 202, exchanges heat through the heat exchanger 204 in the heat exchange air duct to obtain heat-exchanged air, and the heat-exchanged air is sent out from the heat exchange air outlet 203, so that the air conditioner 200 adjusts the indoor temperature.

In the present embodiment, the air conditioner 200 employs the double-suction centrifugal fan 100 provided in the above-described embodiment, and in the double-suction centrifugal fan 100, the scroll 20 provided in the present embodiment is employed. In this embodiment, through the design of the volute 20 in this embodiment, compared with a conventional double-suction centrifugal fan with substantially the same air inlets at two sides, the centrifugal fan 100 provided by the present invention reduces adverse effects of a reduction in air inlet area, an increase in air resistance, and the like caused by the installation of the motor 30 at one air inlet side of the centrifugal fan 100 by increasing the area of the first air inlet 21 at the side of the volute 20 where the motor 30 is disposed, so that the difference between the air inlets at the two air inlet sides of the centrifugal fan is reduced, the air inlets at the two sides are more balanced, and the centrifugal fan 100 can still run stably at high speed (when the air volume of the air conditioner 200 is greater than 1200m 3/h) and reduces the air noise.

Thus, compared with the air conditioner 200 using the conventional centrifugal fan 100, the air conditioner 200 in the embodiment has smaller working noise under the condition of the same air supply amount, and can improve the use experience of a user. And under the condition that the rotating speed of the centrifugal wind wheel 10 is the same, the air supply quantity is larger, the heat exchange efficiency can be improved, and indoor refrigeration or heating is faster.

The above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention, and all equivalent structural changes made by using the contents of the present specification and the drawings, or any other related technical fields, which are directly or indirectly applied to the present invention, are included in the scope of the present invention.

Claims

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

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;

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.