WO2022217956A1

WO2022217956A1 - Impeller and vehicle air conditioner blower

Info

Publication number: WO2022217956A1
Application number: PCT/CN2021/138411
Authority: WO
Inventors: 杨云; 宋婷婷; 张邢; 赵林林
Original assignee: 浙江银轮机械股份有限公司
Priority date: 2021-04-13
Filing date: 2021-12-15
Publication date: 2022-10-20
Also published as: CN112943687A

Abstract

An impeller and a vehicle air conditioner blower, relating to the technical field of air conditioning devices, and comprising a cover (300), blades (200), and a hub (100) which are fixedly connected in sequence, so that the blades (200) are located between the cover (300) and the hub (100) in the axial direction of the hub (100). The blades (200) are backward-curved blades, and each blade (200) is provided with a forward-swept portion (210); the impeller is applied to a vehicle air conditioner. The purpose of the solution is to provide an impeller and a vehicle air conditioner blower in view of the problem of reduction of the overall efficiency of blowers due to energy loss caused by the flow field structures in current impellers being complex and conventional impellers being not conducive to development of internal flow fields.

Description

Impeller and car air conditioner blower

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the priority of the Chinese patent application with the application number 202110397523.4 and the title of "Impeller and Automobile Air Conditioning Blower" filed with the State Intellectual Property Office of China on April 13, 2021, the entire contents of which are incorporated into this application by reference.

technical field

The present application relates to the technical field of air-conditioning equipment, and in particular, to an impeller and an automotive air-conditioning blower.

Background technique

As the core component of automotive air conditioners, the optimization of the blower impeller structure is of critical significance to the performance improvement of automotive air conditioners. With the gradual improvement of the requirements for automobile air conditioners, the performance requirements of blowers are becoming more and more demanding. Large air volume, high efficiency, low noise and small size have gradually become the development trend of automobile air conditioner blower impellers. Traditional automotive air conditioners generally use centrifugal impellers with forward-bending blades. The center molding line of the blade is an arc curve. After the molding line is thickened, it is stretched to a certain length in the direction perpendicular to the molding surface, that is, the blade is formed.

In the current automobile air conditioner, the blades of the blower impeller are only formed by arc-shaped axial stretching, but in actual flow, the flow field structure in the impeller is relatively complex, and the traditional impeller is not conducive to the development of the internal flow field. It will cause a certain amount of energy loss, thereby reducing the overall efficiency of the blower.

SUMMARY OF THE INVENTION

At least in view of the fact that the current structure of the flow field in the impeller is relatively complex, the traditional impeller is not conducive to the development of the internal flow field, and will cause a certain amount of energy loss, thereby reducing the overall efficiency of the blower. The application provides an impeller and an automotive air-conditioning blower. .

In an impeller provided by an embodiment of the present application, the impeller may include a wheel cover, a blade and a wheel hub that are fixedly connected in sequence, so that the blades are located between the wheel cover and the wheel hub in the axial direction of the wheel hub. Meanwhile, the blade may be a backward curved blade, and the blade may have a forward swept portion; the impeller may be applied to an automobile air conditioner.

Optionally, the impeller may be an axial-radial flow closed impeller that guides airflow to enter axially and to flow radially out.

Optionally, the swept angle of the swept portion may be γ, and 81°≤γ≤86°.

Optionally, the swept angle of the swept portion may be γ, and γ is 83°.

Optionally, the blade outlet angle of the blade may be β, and 60°≤β≤70°.

Optionally, the blade outlet angle of the blade may be β, and β is 65°.

Optionally, the blade root radius of the blade at the inlet may be R _h , the blade tip radius at the inlet may be R _s , and 0.35≦R _h /R _s ≦0.4.

Optionally, the root radius of the blade at the inlet may be _Rh , the tip radius at the inlet may be R _s , and _Rh /R _s =0.37.

Optionally, the angle between the tangential direction of the blade shape of the blade tip of the blade at the inlet and the rotation direction of the impeller at the blade tip may be β ₁ , and 56°≤β ₁ ≤64°.

Optionally, the angle between the tangential direction of the blade shape of the blade tip of the blade at the inlet and the rotation direction of the impeller at the blade tip may be β ₁ , and β ₁ =62°.

Optionally, the impeller outlet width of the impeller can be b2, and b2 can be calculated by formula (1), and the formula (1) is:

Among them, R ₂ is the impeller outlet radius of the impeller; u ₂ is the peripheral speed,

is the flow coefficient at the impeller outlet.

Optionally, u ₂ can be calculated by formula (2), and the formula (2) is:

u ₂ =2πR ₂ n (2);

Among them, n is the impeller speed.

Optionally, _{90mm≤R2≤110mm} , and

Optionally, the thickness of the blade at the inlet of the impeller may be δ ₁ , where 0.8mm≦δ ₁ ≦1.5mm.

Optionally, the blade thickness at the inlet of the impeller may be δ ₁ , and δ ₁ =1.1 mm.

Optionally, the thickness of the blades at the outlet of the impeller may be δ ₂ , and 1.3 mm≤δ ₂ ≤2.5 mm.

Optionally, the blade thickness at the outlet of the impeller may be δ ₂ , and δ ₂ =1.9 mm.

Optionally, the number of the blades may be 19 or 23; the blade root radius of the blades at the inlet may be 28.8 mm; the tip radius of the blades at the inlet may be 72 mm; The blade angle at the tip of the blade can be 62°, and the blade angle at the root of the blade at the inlet can be 37°; the impeller outlet width of the impeller can be 25mm, and the impeller outlet blade angle of the impeller can be 65°, the impeller outlet radius of the impeller may be 92.1 mm; the axial length of the impeller may be 40.2 mm.

Other embodiments of the present application provide an automotive air-conditioning blower, and the automotive air-conditioning blower may include an impeller as provided in the present application.

The technical solution provided by this application can achieve at least the following beneficial effects:

In the impeller and the air-conditioning blower for automobiles provided by the present application, the impeller adopts space-distorted backward curved blades. After the accelerated air enters the impeller, the degree of fit with the blades is relatively high, and the energy added to the airflow in the impeller is mainly converted into pressure energy, ensuring that The high-efficiency requirements are met; the swept part of the blade at the inlet is beneficial to reduce the aerodynamic noise generated after the airflow hits the impeller.

Additional technical features and advantages of the present application will be more apparent in the following description, or can be learned through the specific practice of the present application.

Description of drawings

In order to illustrate the technical solutions of the specific embodiments of the present application more clearly, the accompanying drawings that need to be used in the description of the specific embodiments will be briefly introduced below. Obviously, the drawings in the following description are some embodiments of the present application, and for those of ordinary skill in the art, other drawings can also be obtained from these drawings without creative effort.

FIG. 1 is a schematic three-dimensional structure diagram of an embodiment of an impeller provided in an embodiment of the present application;

Fig. 2 is a right side structural schematic diagram of an embodiment of the impeller provided by the embodiment of the present application;

3 is a schematic front view structure diagram of an embodiment of the impeller provided in the embodiment of the present application;

Fig. 4 is the sectional view at A-A place in Fig. 3;

Fig. 5 is a partial three-dimensional structural schematic diagram of an embodiment of the impeller provided in the embodiment of the present application;

FIG. 6 is a partial front structural schematic diagram of an embodiment of the impeller provided in the embodiment of the present application;

FIG. 7 is a schematic three-dimensional structural diagram of an embodiment of the blade provided by the embodiment of the application;

FIG. 8 is a schematic front view structure diagram of an embodiment of the blade provided in the embodiment of the present application.

Reference number:

100 - hub;

200 - leaves;

210 - swept part;

211 - leaf tip;

220 - leaf root;

300-wheel cover;

400-shaft hole.

Detailed ways

The technical solutions of the present application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are part of the embodiments of the present application, but not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present application.

In the description of this application, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. The indicated orientation or positional relationship is based on the orientation or positional relationship shown in the accompanying drawings, which is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the indicated device or element must have a specific orientation or a specific orientation. construction and operation, and therefore should not be construed as limitations on this application. Furthermore, the terms "first", "second", and "third" are used for descriptive purposes only and should not be construed to indicate or imply relative importance.

In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installed", "connected" and "connected" should be understood in a broad sense, for example, it may be a fixed connection or a detachable connection Connection, or integral connection; can be mechanical connection, can also be electrical connection; can be directly connected, can also be indirectly connected through an intermediate medium, can be internal communication between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood in specific situations.

As shown in FIGS. 1 to 8 , the impeller and its partial structure diagrams, some embodiments of the present application provide an impeller, which may include a wheel cover 300 , blades 200 and a hub 100 that are fixedly connected in sequence, so that the blades 200 Located between the wheel cover 300 and the hub 100 in the axial direction of the hub 100, the blade 200 may be a backward curved blade, and the blade 200 may have a forward sweep; the impeller may be applied to Car Air Conditioner. A shaft hole 400 for connecting the drive shaft may be formed on the front cover.

In the impeller provided by the present application, the impeller adopts space-distorted backward-curved blades. After the accelerated air enters the impeller, it has a high degree of fit with the blade 200. The energy added to the airflow in the impeller is mainly converted into pressure energy, which ensures high efficiency. Requirements: The swept portion 210 of the blade 200 at the inlet is beneficial to reduce the aerodynamic noise generated after the airflow hits the impeller.

Optionally, the forward sweep angle of the forward sweep portion 210 may be γ, and 81°≤γ≤86°.

Optionally, the forward sweep angle of the forward sweep portion 210 may be γ, and γ may be 83°.

Optionally, the blade outlet angle of the blade 200 may be β, and 60°≤β≤70°.

Optionally, the blade outlet angle of the blade 200 may be β, and β may be 65°.

The blade may have a blade tip 211 and a blade root 220. Optionally, the blade root radius of the blade 200 at the inlet may be R _h , and the blade tip radius at the inlet may be R _s , and 0.35≦R _h /R _s≤0.4 . The inlet mentioned in the embodiments of the present application refers to the inlet of the impeller.

Optionally, the root radius of the blade 200 at the inlet may be _Rh , the tip radius at the inlet may be R _s , and _Rh /R _s =0.37.

Optionally, the angle between the tangential direction of the blade shape of the blade tip of the blade 200 at the inlet and the rotation direction of the impeller at the blade tip may be β ₁ , and 56°≤β ₁ ≤64°.

Optionally, the angle between the tangential direction of the blade shape of the blade tip of the blade 200 at the inlet and the rotation direction of the impeller at the blade tip may be β ₁ , and β ₁ =62°.

is the flow coefficient at the impeller outlet.

Optionally, u ₂ can be calculated by formula (2), and the formula (2) is:

u ₂ =2πR ₂ n (2);

Among them, n is the impeller speed.

Optionally, _{90mm≤R2≤110mm} , and

Optionally, the thickness of the blade 200 at the inlet of the impeller may be δ ₁ , and 0.8mm≦δ ₁ ≦1.5mm.

Optionally, the thickness of the blade 200 at the inlet of the impeller may be δ ₁ , and δ ₁ =1.1 mm.

Optionally, the thickness of the blade 200 at the outlet of the impeller may be δ ₂ , and 1.3 mm≤δ ₂ ≤2.5 mm.

Optionally, the thickness of the blade 200 at the outlet of the impeller may be δ ₂ , and δ ₂ =1.9 mm.

Optionally, the number of the blades 200 may be 19 or 23; the blade root radius of the blades 200 at the inlet may be 28.8 mm; the tip radius of the blades 200 at the inlet may be 72 mm; The blade angle at the tip of the blade 200 may be 62°, and the blade angle at the root of the blade 200 at the inlet may be 37°; the impeller outlet width of the impeller may be 25mm, and the impeller of the impeller The outlet blade angle may be 65°, the impeller outlet radius of the impeller may be 92.1 mm, and the axial length of the impeller may be 40.2 mm.

Other embodiments of the present application provide an automobile air conditioner blower, and the automobile air conditioner blower may include the impeller provided in the embodiments of the present application.

In the impeller and the air-conditioning blower for automobiles provided by the present application, the impeller adopts space-distorted backward-curved blades. After the accelerated air enters the impeller, the degree of fit with the blade 200 is relatively high, and the energy added to the airflow in the impeller mainly becomes pressure energy. The requirement of high efficiency is ensured; the swept part 210 of the blade 200 at the inlet is beneficial to reduce the aerodynamic noise generated after the airflow hits the impeller.

In order to describe the impeller and the automobile air-conditioning blower provided by the application, the application also provides an application example of the impeller and the automobile air-conditioning blower:

As the core component of automotive air conditioners, the optimization of the blower impeller structure is of critical significance to the performance improvement of automotive air conditioners.

With the gradual improvement of the requirements for automobile air conditioners, the performance requirements of blowers are becoming more and more demanding. Large air volume, high efficiency, low noise and small size have gradually become the development trend of automobile air conditioner blower impellers. Traditional automotive air conditioners generally use centrifugal impellers with forward-bending blades. The center molding line of the blade is an arc curve. After the molding line is thickened, it is stretched to a certain length in the direction perpendicular to the molding surface, that is, the blade is formed. In the current automobile air conditioner, the blades of the blower impeller are only formed by stretching the circular arc in the axial direction. However, in the actual flow, the flow field structure in the impeller is relatively complex, and the traditional impeller is not conducive to the development of the internal flow field. , will cause a certain amount of energy loss, thereby reducing the overall efficiency of the blower, and in order to meet the requirements of the air volume of the car air conditioner, the axial size of the blower impeller is large, resulting in a large space for the matching volute, which is not conducive to the operation of the car and the car air conditioner. miniaturization.

In this application example, an axial-radial closed impeller for automobile air-conditioning blower is designed, and the blades are space-distorted backward-curved blades. The required target air volume can be achieved through the smaller axial size of the impeller, and at the same time, under the operating conditions, the flow field in the impeller is guaranteed to be more stable, the overall efficiency of the automotive air-conditioning blower is improved, and the noise of the automotive air-conditioning assembly is reduced.

Specific principle:

The impeller used in the automobile air-conditioning blower involved in the present application is of an axial radial flow closed structure. The impeller includes a wheel cover, blades and a wheel hub, and the blades are arranged between the wheel cover and the wheel hub. Before the incoming air enters the impeller, the forward-swept blade structure ensures that the airflow enters the impeller more uniformly and stably; because the blades are space-distorted backward-curved blades, the airflow in the impeller channel is urged to fit with the blades; the airflow flows to the impeller At the outlet, the stability of the flow field at the outlet of the impeller is improved due to the backward curved structure of the blade. In addition, the turning loss of the airflow in the backward curved impeller is relatively small, and the efficiency of the entire impeller is also improved.

In the automotive air conditioner, the axial-radial closed back-curved impeller in this application example can fully achieve the required air volume according to the general design conditions, and at the same time improve the work efficiency, and the back-curved impeller also widens the flow range of normal operation. , can optimize the internal flow field, so as to achieve the effect of reducing noise.

This application example provides a blower impeller for an automotive air conditioner, including a hub, a blade and a wheel cover. The blade and the wheel cover are an integral structure, and the blade and the hub are fixed together. A shaft hole for installing the motor is arranged on the wheel hub for fixed connection with the motor shaft. The impeller of the blower for automobile air conditioner is an axial-radial closed impeller structure that guides the airflow to enter in the axial direction and flow out radially. The selection relationship of the main structural parameters is as follows:

The blades at the inlet of the impeller are of forward-swept structure, which ensures that the airflow can be guided into the impeller in the predetermined direction with the minimum impact loss. ~70°. The radius of the blade root at the inlet is R _h , the radius of the blade tip at the inlet is R _s , and 0.35≤R _h /R _s ≤0.4 is guaranteed; the angle between the tangential direction of the blade tip at the blade tip and the circumferential direction of the impeller is β ₁ =56°～64 °; the thickness of the blade at the inlet is δ ₁ =0.8mm～1.5mm. At the outlet of the impeller, considering the requirements of the envelope, the pressure rise of the impeller, and the efficiency, the outlet radius of the impeller is 90mm≤R ₂ ≤110mm, and the flow coefficient at the outlet is taken as

Then the peripheral speed u ₂ =2πR ₂ n; the impeller outlet width b ₂ is based on

Select, the thickness of the blade at the outlet δ ₁ =1.3mm～2.5mm.

According to specific requirements: the air-conditioning box requires the maximum flow Q=580m ³ /h, the pressure rise of the impeller outlet is 1000Pa and the impeller speed n=4000rpm, the temperature _T0 =298K, and the pressure P=101300Pa. Design an impeller structure as follows:

Considering the structural strength of the impeller, the clogging factor and the reasonable selection of the axial dimension L of the impeller, and referring to the sensitivity of the human ear in the automobile air conditioner to noise, the number of blades is 19 or 23; an impeller inlet is designed according to the boundary conditions. , the blade root radius is R _h = 28.8mm, the blade tip radius is R _s = 72mm, the blade angle at the blade tip is 62°, and the blade angle at the blade root is 37°.

At the outlet of the impeller, the outlet width is 25mm, the blade angle of the impeller outlet is 65°, and the outlet radius is 92.1mm; the axial length of the impeller is 40.2mm.

After the airflow enters the impeller designed according to the above parameters, the efficiency can reach more than 80% under the design conditions. At the same time, the working conditions of 0.4Q ~ 1.2Q under different flow rates are simulated and analyzed, and the efficiency remains above 79%. The pressure rise under each working condition It can also fully meet the requirements of 1000Pa. Therefore, it is arranged in the air conditioner of the car, which can also meet the requirements of the passengers in the car for the air volume of the air conditioner.

Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present application, but not to limit them; although the present application has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that: The technical solutions described in the foregoing embodiments can still be modified, or some or all of the technical features thereof can be equivalently replaced; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the technical solutions of the embodiments of the present application. scope.

Industrial Applicability

The present application relates to the technical field of air-conditioning equipment, and in particular, to an impeller and an automotive air-conditioning blower, comprising a wheel cover, a blade and a hub that are fixedly connected in sequence, so that the blade is positioned on the wheel in the axial direction of the hub. Between the cover and the hub, the blade is a backward curved blade, and the blade has a forward swept portion; the impeller is applied to an automobile air conditioner. The purpose of the present application is to provide an impeller and a vehicle for the problem that the current structure of the flow field in the impeller is relatively complex, the traditional impeller is not conducive to the development of the internal flow field, and will cause a certain energy loss, thereby reducing the overall efficiency of the blower. Air conditioner blower.

Furthermore, it will be appreciated that the impeller and automotive air conditioner blower of the present application is reproducible and can be used in a variety of industrial applications. For example, the impeller and the automotive air-conditioning blower of the present application can be applied to the technical field of air-conditioning equipment, such as the field of automotive air-conditioning equipment.

Claims

The impeller is characterized in that it includes a wheel cover, a blade and a wheel hub that are fixedly connected in sequence, so that the blade is located between the wheel cover and the wheel hub in the axial direction of the wheel hub, and the blade is a backward curved blade , and the blade has a forward swept portion; the impeller is used in automobile air conditioners.
The impeller according to claim 1, wherein the impeller is an axial-radial flow closed impeller that guides airflow to enter axially and to flow radially out.
The impeller according to claim 1 or 2, wherein the swept angle of the swept part is γ, and 81°≤γ≤86°.
The impeller according to claim 1 or 2, wherein the swept angle of the swept portion is γ, and γ is 83°.
The impeller according to any one of claims 1 to 4, wherein the blade outlet angle of the blades is β, and 60°≤β≤70°.
The impeller according to any one of claims 1 to 4, wherein the blade outlet angle of the blade is β, and β is 65°.
The impeller according to any one of claims 1 to 6, wherein the blade root radius of the blade at the inlet is R h , the blade tip radius at the inlet is R s , and 0.35≤R h /R s ≤ 0.4.
The impeller according to any one of claims 1 to 6, wherein the blade root radius of the blade at the inlet is R h , the blade tip radius at the inlet is R s , and R h / R s =0.37.
The impeller according to any one of claims 1 to 8, wherein the included angle between the tangential direction of the blade shape of the blade tip of the blade at the inlet and the rotation direction of the impeller at the blade tip is β 1 , and 56°≤β 1 ≤64°.
The impeller according to any one of claims 1 to 8, wherein the included angle between the tangential direction of the blade shape of the blade tip of the blade at the inlet and the rotation direction of the impeller at the blade tip is β 1 , and β 1 =62°.
The impeller according to any one of claims 1 to 10, wherein the impeller outlet width of the impeller is b2, and b2 is calculated by formula (1), and the formula (1) is:

Among them, R 2 is the impeller outlet radius of the impeller; u 2 is the peripheral speed,
is the flow coefficient at the impeller outlet.
The impeller according to claim 11, wherein u 2 is calculated by formula (2), and the formula (2) is:

u 2 =2πR 2 n (2);

Among them, n is the impeller speed.
The impeller according to claim 11 or 12, wherein 90mm≤R2≤110mm , and
The impeller according to any one of claims 1 to 13, wherein the blade thickness at the inlet of the impeller is δ 1 , and 0.8mm≤δ 1 ≤1.5mm.
The impeller according to any one of claims 1 to 13, wherein the blade thickness at the inlet of the impeller is δ 1 , and δ 1 =1.1 mm.
The impeller according to any one of claims 1 to 15, wherein the blade thickness at the outlet of the impeller is δ 2 , and 1.3mm≤δ 2 ≤2.5mm.
The impeller according to any one of claims 1 to 15, wherein the blade thickness at the outlet of the impeller is δ 2 , and δ 2 =1.9 mm.
The impeller according to any one of claims 1 to 17, wherein the number of the blades is 19 or 23; the blade root radius of the blades at the inlet is 28.8 mm; The tip radius of the blade is 72mm; the blade angle at the tip of the blade at the inlet is 62°, and the blade angle at the root of the blade at the inlet is 37°; the impeller outlet width of the impeller is 25mm, The impeller outlet blade angle of the impeller is 65°, the impeller outlet radius of the impeller is 92.1 mm, and the axial length of the impeller is 40.2 mm.
The automobile air-conditioning blower is characterized in that, the automobile air-conditioning blower comprises the impeller according to any one of claims 1 to 18.