CN112943687A - Impeller and automobile air conditioner blower - Google Patents
Impeller and automobile air conditioner blower Download PDFInfo
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- CN112943687A CN112943687A CN202110397523.4A CN202110397523A CN112943687A CN 112943687 A CN112943687 A CN 112943687A CN 202110397523 A CN202110397523 A CN 202110397523A CN 112943687 A CN112943687 A CN 112943687A
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- 239000004576 sand Substances 0.000 claims description 6
- 230000004323 axial length Effects 0.000 claims description 4
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 238000004364 calculation method Methods 0.000 claims description 3
- 238000004378 air conditioning Methods 0.000 abstract description 3
- 238000000465 moulding Methods 0.000 description 6
- 230000018109 developmental process Effects 0.000 description 5
- 238000005452 bending Methods 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 2
- 239000008358 core component Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 210000005069 ears Anatomy 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
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- 238000004088 simulation Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
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Abstract
本申请涉及空调设备技术领域，具体而言，涉及一种叶轮及汽车空调鼓风机，包括依次固定连接的轮盖、叶片和轮毂，以使在所述轮毂的轴向上所述叶片位于所述轮盖与所述轮毂之间，所述叶片为后弯叶片，且所述叶片具有前掠部；所述叶轮应用于汽车空调。本申请的目的在于针对目前叶轮内的流场结构比较复杂，传统的叶轮并不利于内部流场的发展，会造成一定的能量损失，从而降低鼓风机整体的效率的问题，提供一种叶轮及汽车空调鼓风机。
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.
Description
Technical Field
The application relates to the technical field of air conditioning equipment, in particular to an impeller and an automobile air conditioner blower.
Background
As a core component of the automobile air conditioner, optimization of the impeller structure of the blower has a key significance for improving the performance of the automobile air conditioner. With the gradual improvement of the requirements on the automobile air conditioner, the performance requirements on the blower are increasingly strict, and the impeller of the automobile air conditioner blower has the development trend of large air volume, high efficiency, low noise and small volume. The traditional automobile air conditioner adopts a centrifugal impeller with forward-bent blades, the molding line at the center of the blades is an arc curve, and the molding line is thickened and then is stretched to a certain length along the direction vertical to the molding surface to form the blades.
In the existing automobile air conditioner, blades of an impeller of the air blower are formed only after arc-shaped axial stretching, but in actual flow, a flow field structure in the impeller is complex, and the traditional impeller is not beneficial to development of an internal flow field and can cause certain energy loss, so that the overall efficiency of the air blower is reduced.
Disclosure of Invention
The utility model provides an aim at to the flow field structure in the present impeller is more complicated, and traditional impeller does not do benefit to the development in inside flow field, can cause certain energy loss to reduce the problem of the holistic efficiency of air-blower, provide an impeller and vehicle air conditioner air-blower.
In order to achieve the purpose, the following technical scheme is adopted in the application:
the impeller provided by the embodiment of the application comprises a shroud, blades and a hub which are sequentially and fixedly connected, so that the blades are positioned between the shroud and the hub in the axial direction of the hub, the blades are backward-bent blades, and the blades are provided with forward swept parts; the impeller is applied to an automobile air conditioner.
Optionally, the impeller is an axial-radial flow type closed impeller for guiding the airflow to enter axially and flow out radially.
Optionally, the forward sweep inclination angle of the forward sweep is γ, and 81 ° ≦ γ ≦ 86 °.
Optionally, the forward sweep inclination of the forward sweep is γ, and γ is 83 °.
Optionally, the blades have a blade exit angle β, and 60 ≦ β ≦ 70.
Optionally, the blades have a blade exit angle β, and β is 65 °.
Optionally, the blade root radius of the blade at the inlet is RhThe radius of the blade tip at the inlet is RsAnd R is 0.35. ltoreq. Rh/Rs≤0.4。
Optionally, the blade root radius of the blade at the inlet is RhThe radius of the blade tip at the inlet is RsAnd R ish/Rs＝0.37。
Optionally, an included angle between a tangential direction of a blade tip profile of the blade at the inlet and a rotation direction of the impeller at the blade tip is β1And beta is not more than 56 degrees1≤64°。
Optionally, an included angle between a tangential direction of a blade tip profile of the blade at the inlet and a rotation direction of the impeller at the blade tip is β1And β1＝62°。
Optionally, the impeller outlet width of the impeller is b2, and b2 is calculated by the formula (1), wherein the formula (1) is:
b2＝Q/(2π×R2×φ×u2) (1)；
wherein R is2Is the impeller exit radius of the impeller; u. of2Is the peripheral speed and phi is the flow coefficient at the impeller exit.
Alternatively, u2The calculation is carried out by the formula (2), wherein the formula (2) is as follows:
u2＝2πR2n (2)；
wherein n is the impeller rotation speed.
Alternatively, 90mm ≦ R2Not more than 110mm and not more than 0.2 and not more than 0.3.
Optionally, the blade thickness at the inlet of the impeller is δ1，0.8mm≤δ1≤1.5mm。
Optionally, the blade thickness at the inlet of the impeller is δ1And δ1＝1.1mm。
Optionally, the blade thickness δ at the outlet of the impeller2And 1.3mm is not more than delta2≤2.5mm。
Optionally, the blade thickness δ at the outlet of the impeller2And δ2＝1.9mm。
Optionally, the number of blades is 19 or 23; the radius of the blade root of the blade at the inlet is 28.8 mm; the radius of the blade tip of the blade at the inlet is 72 mm; the blade angle at the blade tip of the blade at the inlet is 62 degrees, and the blade angle at the blade root of the blade at the inlet is 37 degrees; the width of an outlet of the impeller is 25mm, the angle of blades at the outlet of the impeller is 65 degrees, and the radius of the outlet of the impeller is 92.1 mm; the axial length of the impeller is 40.2 mm.
Another aspect of the present application provides a motor vehicle air conditioner blower including an impeller as provided herein.
The technical scheme provided by the application can achieve the following beneficial effects:
according to the impeller and the automobile air conditioner blower, the impeller is provided with the backward bent blades twisted in space, accelerated air enters the impeller and is higher in fit degree with the blades, energy added to airflow in the impeller is mainly changed into pressure energy, and the requirement for high efficiency is met; the forward swept portion of the blades at the inlet is beneficial to reducing aerodynamic noise generated after airflow impacts the impeller.
Additional features of the present application and advantages thereof will be set forth in the description which follows, or may be learned by practice of the present application.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings used in the description of the embodiments will be briefly described below. It should be apparent that the drawings in the following description are embodiments of the present application and that other drawings may be derived from those drawings by a person of ordinary skill in the art without inventive step.
Fig. 1 is a schematic perspective view of an embodiment of an impeller provided in an embodiment of the present application;
FIG. 2 is a schematic right-view structural diagram of an embodiment of an impeller provided in an example of the present application;
FIG. 3 is a schematic front view of an embodiment of an impeller provided in an embodiment of the present application;
FIG. 4 is a cross-sectional view taken at A-A of FIG. 3;
FIG. 5 is a schematic perspective view of a portion of an embodiment of an impeller provided in an example of the present application;
FIG. 6 is a partial front view schematic diagram of an embodiment of an impeller provided in an example of the present application;
FIG. 7 is a perspective view of an embodiment of a blade provided in accordance with an embodiment of the present disclosure;
FIG. 8 is a front view of a blade according to an embodiment of the present disclosure.
Reference numerals:
100-a hub;
200-blades;
210-forward sweep;
211-blade tip;
220-a blade root;
300-wheel cover;
400-shaft hole.
Detailed Description
The technical solutions of the present application will be described clearly and completely with reference to the accompanying drawings, and it should be understood that the described embodiments are only some embodiments of the present application, but not all 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 application.
In the description of the present application, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present application. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present application, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present application can be understood in a specific case by those of ordinary skill in the art.
As shown in fig. 1 to 8 and partial schematic structural views thereof, one aspect of the present application provides an impeller including a shroud 300, a blade 200 and a hub 100 fixedly connected in sequence, such that the blade 200 is located between the shroud 300 and the hub 100 in an axial direction of the hub 100, the blade 200 is a backward curved blade, and the blade 200 has a forward swept portion; the impeller is applied to an automobile air conditioner. A shaft hole 400 for connecting a driving shaft is formed on the front cover.
According to the impeller provided by the application, the impeller adopts the backward bent blades twisted in space, after accelerated air enters the impeller, the attachment degree of the accelerated air and the blades 200 is higher, the energy added to airflow in the impeller is mainly changed into pressure energy, and the requirement of high efficiency is ensured; the forward swept portion 210 of the blade 200 at the inlet helps to reduce aerodynamic noise generated after the airflow impacts the impeller.
Optionally, the impeller is an axial-radial flow type closed impeller for guiding the airflow to enter axially and flow out radially.
Optionally, the forward sweep inclination angle of the forward sweep 210 is γ, and 81 ° ≦ γ ≦ 86 °.
Alternatively, the forward sweep inclination of the forward sweep 210 is γ, and γ is 83 °.
Optionally, the blade 200 has a blade exit angle β, and 60 ≦ β ≦ 70.
Optionally, the blade 200 has a blade exit angle β, and β is 65 °.
The blade has a blade tip 211 and a blade root 220, optionally the blade 200 at the inlet has a root radius RhThe radius of the blade tip at the inlet is RsAnd R is 0.35. ltoreq. Rh/RsLess than or equal to 0.4. The inlet in the embodiments of the present application refers to the inlet of the impeller.
Optionally, the blade 200 at the inlet has a root radius RhThe radius of the blade tip at the inlet is RsAnd R ish/Rs＝0.37。
Optionally, an included angle between a tangential direction of a blade tip profile of the blade 200 at the inlet and a rotation direction of the impeller at the blade tip is β1And beta is not more than 56 degrees1≤64°。
Optionally, an included angle between a tangential direction of a blade tip profile of the blade 200 at the inlet and a rotation direction of the impeller at the blade tip is β1And β1＝62°。
Optionally, the impeller outlet width of the impeller is b2, and b2 is calculated by the formula (1), wherein the formula (1) is:
b2＝Q/(2π×R2×φ×u2) (1)；
wherein R is2Is the impeller exit radius of the impeller; u. of2Is the peripheral speed and phi is the flow coefficient at the impeller exit.
Alternatively, u2The calculation is carried out by the formula (2), wherein the formula (2) is as follows:
u2＝2πR2n (2)；
wherein n is the impeller rotation speed.
Alternatively, 90mm ≦ R2Not more than 110mm and not more than 0.2 and not more than 0.3.
Optionally, the blades 200 at the inlet of the impeller have a thickness δ1，0.8mm≤δ1≤1.5mm。
Optionally, the blades 200 at the inlet of the impeller have a thickness δ1And δ1＝1.1mm。
Optionally, the blade 200 at the outlet of the impeller has a thickness δ2And 1.3mm is not more than delta2≤2.5mm。
Optionally, the blade 200 at the outlet of the impeller has a thickness δ2And δ2＝1.9mm。
Optionally, the number of the blades 200 is 19 or 23; the root radius of the blade 200 at the inlet is 28.8 mm; the radius of the tip of the blade 200 at the inlet is 72 mm; the blade angle at the tip of the blade 200 at the inlet is 62 degrees, and the blade angle at the root of the blade 200 at the inlet is 37 degrees; the width of an outlet of the impeller is 25mm, the angle of blades at the outlet of the impeller is 65 degrees, and the radius of the outlet of the impeller is 92.1 mm; the axial length of the impeller is 40.2 mm.
Another aspect of the present application provides a blower for a vehicle air conditioner including an impeller as provided by embodiments of the present application.
According to the impeller and the automobile air conditioner blower, the impeller is the backward bent blades twisted in space, after accelerated air enters the impeller, the attachment degree of the accelerated air and the blades 200 is high, energy added to airflow in the impeller is mainly changed into pressure energy, and the requirement for high efficiency is met; the forward swept portion 210 of the blade 200 at the inlet helps to reduce aerodynamic noise generated after the airflow impacts the impeller.
To further explain the impeller and the automobile air conditioner blower provided by the application, the application also provides an application example of the impeller and the automobile air conditioner blower:
as a core component of the automobile air conditioner, optimization of the impeller structure of the blower has a key significance for improving the performance of the automobile air conditioner.
With the gradual improvement of the requirements on the automobile air conditioner, the performance requirements on the blower are increasingly strict, and the impeller of the automobile air conditioner blower has the development trend of large air volume, high efficiency, low noise and small volume. The traditional automobile air conditioner adopts a centrifugal impeller with forward-bent blades, the molding line at the center of the blades is an arc curve, and the molding line is thickened and then is stretched to a certain length along the direction vertical to the molding surface to form the blades. In the existing automobile air conditioner, blades of an impeller of the air blower are formed only by stretching a circular arc along the axial direction, but in actual flow, the structure of a flow field in the impeller is complex, the traditional impeller is not beneficial to the development of an internal flow field, and certain energy loss can be caused, so that the overall efficiency of the air blower is reduced, and in order to meet the requirement of the air quantity of the automobile air conditioner, the axial size of the impeller of the air blower is large, so that the occupied space of a matched volute and the like is large, and the miniaturization of the automobile and the automobile air conditioner is not facilitated.
The purpose of this application example is to design a radial-axial flow closed impeller for vehicle air conditioner air-blower, and the blade is the space distortion back bend blade. The required target air volume can be achieved through the smaller axial size of the impeller, meanwhile, under the operation working condition, the flow field in the impeller is guaranteed to be more stable, the overall efficiency of the automobile air conditioner blower is improved, and the noise of the automobile air conditioner assembly is reduced.
The specific principle is as follows:
the invention relates to an impeller for an automobile air conditioner blower, which is of an axial-radial flow closed structure. The sweepforward blade structure ensures that the air flow enters the impeller more uniformly and stably before the air flow enters the impeller; because the blades are backward bent blades with twisted space, the air flow in the impeller flow channel is enabled to be attached to the blades; when the airflow flows to the outlet of the impeller, the stability of the flow field at the outlet of the impeller is improved due to the backward bending structure of the blades. And the turning loss of the airflow in the backward-bent impeller is relatively small, and the efficiency of the whole impeller is improved.
In the automobile air conditioner, the axial-radial flow closed backward-bending impeller in the application example is adopted, the required air volume can be completely achieved according to general design working conditions, meanwhile, the working efficiency is improved, the backward-bending impeller also widens the flow range of normal operation, and the internal flow field can be optimized, so that the effect of reducing noise is achieved.
The blower impeller for the automobile air conditioner comprises a hub, blades and a wheel cover. The blade and the wheel cover are of an integral structure and are fixed together with the hub through the blade. The hub is provided with a shaft hole for installing the motor and is fixedly connected with a motor shaft. The axial-radial flow type closed impeller structure for guiding airflow to axially enter and radially flow out is characterized in that the main structural parameter selection relation is as follows:
the blades at the inlet of the impeller are of a forward-swept structure, so that the air flow is guided to enter in a preset direction with minimum impact lossThe impeller has a forward sweep inclination angle gamma of 81-86 degrees, the impeller body is a backward bending blade, and the blade outlet angle beta is 60-70 degrees. Root radius at inlet of RhThe radius of the blade tip at the inlet is RsEnsuring that R is not less than 0.35h/RsLess than or equal to 0.4; the included angle beta between the tangential direction of the blade profile at the blade tip and the circumferential direction of the impeller156-64 degrees; thickness delta of blade at inlet10.8mm to 1.5 mm. At the outlet of the impeller, the requirements of envelope, pressure rise of the impeller, efficiency and the like are comprehensively considered, and the radius R of the outlet of the impeller is more than or equal to 90mm2Less than or equal to 110mm, the flow coefficient at the outlet is phi 0.2-0.3, and the peripheral speed u is2＝2πR2n; width b of impeller outlet2According to b2＝Q/(2π×R2×φ×u2) Selecting, at the outlet, the thickness delta of the blade1＝1.3mm～2.5mm。
According to specific requirements: maximum flow Q of 580m for air conditioner3H, analyzing the pressure rise of 1000Pa at the outlet of the impeller, the rotating speed n of the impeller is about 4000rpm, and the temperature T0298K, and 101300Pa, and designing an impeller structure as follows:
the reasonable selection of the structural strength and the blocking coefficient of the impeller and the axial dimension L of the impeller is considered, and the number of the blades is 19 or 23 according to the sensitivity of human ears in an automobile air conditioner to noise; the radius of the blade root at the inlet of the impeller is R designed according to boundary conditionsh28.8mm, tip radius RsThe blade angle at the blade tip is 62 degrees and the blade angle at the blade root is 37 degrees, which is 72 mm.
At the outlet of the impeller, the width of the outlet is 25mm, the angle of the blade at the outlet of the impeller is 65 degrees, and the radius of the outlet is 92.1 mm; the axial length of the impeller is 40.2 mm.
After the airflow enters the impeller designed according to the parameters, the efficiency can reach more than 80% under the designed working condition, meanwhile, the efficiency is kept more than 79% under the working condition of 0.4Q-1.2Q under different flow rates through simulation analysis, and the pressure rise can completely meet the requirement of 1000Pa under each working condition. Therefore, the air volume adjusting device is arranged in the automobile air conditioner, and can meet the requirement of air volume of the air conditioner for passengers in the automobile.
Finally, it should be noted that: the above embodiments are only used for illustrating the technical solutions of the present application, and not for limiting the same; although the present application has been described in detail with reference to the foregoing embodiments, it should be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present application.
Claims (19)
1. The impeller is characterized by comprising a shroud, blades and a hub which are fixedly connected in sequence, so that the blades are positioned between the shroud and the hub in the axial direction of the hub, the blades are backward-bent blades, and the blades are provided with forward swept parts; the impeller is applied to an automobile air conditioner.
2. The impeller of claim 1, wherein the impeller is an axial-radial shrouded impeller that directs the flow of gas axially in and radially out.
3. The impeller according to claim 1, characterized in that the forward sweep inclination of the forward sweep is γ, and 81 ° ≦ γ ≦ 86 °.
4. The impeller according to claim 1, characterized in that the forward-sweep inclination of said forward-sweep portion is γ, and γ is 83 °.
5. The impeller according to claim 1, characterized in that the blade outlet angle of the blade is β, and 60 ° ≦ β ≦ 70 °.
6. The impeller according to claim 1, characterized in that the blade exit angle of the blade is β, and β is 65 °.
7. The impeller according to claim 1, characterized in that the root radius of the blade at the inlet is RhThe radius of the blade tip at the inlet is RsAnd R is 0.35. ltoreq. Rh/Rs≤0.4。
8. The impeller according to claim 1, characterized in that the root radius of the blade at the inlet is RhThe radius of the blade tip at the inlet is RsAnd R ish/Rs＝0.37。
9. The impeller as claimed in claim 1, wherein the angle between the tangential direction of the blade tip profile of said blade at the inlet and the direction of rotation of the impeller at the blade tip is β1And beta is not more than 56 degrees1≤64°。
10. The impeller as claimed in claim 1, wherein the angle between the tangential direction of the blade tip profile of said blade at the inlet and the direction of rotation of the impeller at the blade tip is β1And β1＝62°。
11. The impeller of claim 1, wherein the impeller has an impeller exit width of b2, and b2 is calculated by equation (1) where:
b2＝Q/(2π×R2×φ×u2) (1)；
wherein R is2Is the impeller exit radius of the impeller; u. of2Is the peripheral speed and phi is the flow coefficient at the impeller exit.
12. The impeller of claim 11, wherein u is2The calculation is carried out by the formula (2), wherein the formula (2) is as follows:
u2＝2πR2n (2)；
wherein n is the impeller rotation speed.
13. The impeller according to claim 11, characterized in that 90mm ≦ R2Not more than 110mm and not more than 0.2 and not more than 0.3.
14. The impeller according to claim 1, characterized in that the blade thickness at the inlet of the impeller is δ1，0.8mm≤δ1≤1.5mm。
15. The impeller according to claim 1, characterized in that the blade thickness at the inlet of the impeller is δ1And δ1＝1.1mm。
16. The impeller according to any one of claims 1 to 15, characterized in that the blade thickness δ at the outlet of the impeller2And 1.3mm is not more than delta2≤2.5mm。
17. The impeller according to claim 1, characterized in that the blade thickness δ at the outlet of the impeller2And δ2＝1.9mm。
18. The impeller according to claim 1, characterized in that said blades number 19 or 23; the radius of the blade root of the blade at the inlet is 28.8 mm; the radius of the blade tip of the blade at the inlet is 72 mm; the blade angle at the blade tip of the blade at the inlet is 62 degrees, and the blade angle at the blade root of the blade at the inlet is 37 degrees; the width of an outlet of the impeller is 25mm, the angle of blades at the outlet of the impeller is 65 degrees, and the radius of the outlet of the impeller is 92.1 mm; the axial length of the impeller is 40.2 mm.
19. A motor vehicle air conditioner blower, characterized in that it comprises an impeller according to any one of claims 1 to 18.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110397523.4A CN112943687A (en) | 2021-04-13 | 2021-04-13 | Impeller and automobile air conditioner blower |
| PCT/CN2021/138411 WO2022217956A1 (en) | 2021-04-13 | 2021-12-15 | Impeller and vehicle air conditioner blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110397523.4A CN112943687A (en) | 2021-04-13 | 2021-04-13 | Impeller and automobile air conditioner blower |
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| Publication Number | Publication Date |
|---|---|
| CN112943687A true CN112943687A (en) | 2021-06-11 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110397523.4A Pending CN112943687A (en) | 2021-04-13 | 2021-04-13 | Impeller and automobile air conditioner blower |
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| CN (1) | CN112943687A (en) |
| WO (1) | WO2022217956A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022217956A1 (en) * | 2021-04-13 | 2022-10-20 | 浙江银轮机械股份有限公司 | Impeller and vehicle air conditioner blower |
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| JPS62267597A (en) * | 1986-05-15 | 1987-11-20 | Ebara Res Co Ltd | Centrifugal impeller |
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| WO2022217956A1 (en) * | 2021-04-13 | 2022-10-20 | 浙江银轮机械股份有限公司 | Impeller and vehicle air conditioner blower |
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| WO2022217956A1 (en) | 2022-10-20 |
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