WO2022217957A1

WO2022217957A1 - Axial radial flow blower and air conditioning device

Info

Publication number: WO2022217957A1
Application number: PCT/CN2021/138418
Authority: WO
Inventors: 杨云; 钟学伟; 杨家政; 冉亚楠
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: CN112943657A

Abstract

An axial radial flow blower and an air conditioning device, the axial radial flow blower comprising: a motor (30), centrifugal impellers (20) and a machine housing (10). The machine housing (10) comprises a front housing body (11) and a rear housing body (12) which are connected to one another; the front housing body (11) is provided with an air inlet, the rear housing body (12) is provided with an air outlet (14), and the gas circulation cross-section of the air inlet (13) and the gas circulation cross-section of the air outlet (14) intersectingly provided with the axis direction of the centrifugal impellers (20); and the front housing body (11) is oppositely provided to the rear housing body (12), and a mounting cavity is formed between the front housing body (11) and the rear housing body (12); and the motor (30) and the centrifugal impellers (20) are mounted within the mounting cavity, and the motor (30) is transmissionally connected to the centrifugal impellers (20). The axial radial flow blower has a small volume, axial air inlet and axial air outlet, and the aerodynamic efficiency may be improved.

Description

Axial radial blower and air conditioner

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the priority of the Chinese Patent Application No. 2021103977668 and entitled "Axial Radial Fan and Air Conditioning Device" filed with the China Patent Office 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 automobiles, and in particular, to an axial radial blower and an air conditioner.

Background technique

A volute type fan is generally used as a blowing component in an air conditioner of an automobile, and the volute type fan includes a casing and an impeller, a flange, an end cover and a motor arranged in the volute casing. The working principle of the volute fan in the air conditioner is to use the high-speed rotation of the impeller to force the gas to rotate, and to do work on the gas to increase its energy. Under the action of centrifugal force, the gas is thrown radially to the impeller into the volute casing. The cross-sectional area of the casing gradually increases from the direction close to the air inlet side to the direction away from the air inlet side to decelerate the airflow. This deceleration effect converts the kinetic energy into pressure energy, and the gas is inhaled under the action of the pressure difference and then discharged from each air outlet. Since the cross-sectional area of the volute casing gradually increases from the direction close to the air inlet side to the direction away from the air inlet side, the volume of the volute casing is large, resulting in a large volume of the volute fan, that is, the drum in the air conditioner of the automobile. The wind component is bulky.

SUMMARY OF THE INVENTION

The present application provides an axial radial flow blower and an air conditioner, so as to solve the technical problem of the large volume of the blower components in the air conditioner of the automobile to a certain extent.

The axial radial blower provided by the present application may include: a motor, a centrifugal impeller and a casing; the casing may include a front casing and a rear casing that are connected to each other; an air inlet may be provided on the front casing, so that the The rear casing may be provided with an air outlet, and the gas circulation cross-section of the air inlet and the gas circulation cross-section of the air outlet may be set to intersect with the axial direction of the centrifugal impeller; the front casing and the The rear casings can be arranged opposite to each other, an installation cavity can be formed between the front casing and the rear casing, the motor and the centrifugal impeller can be installed in the installation cavity, and the motor and the centrifugal impeller can be installed in the installation cavity. The impeller can be drive-connected.

Optionally, the opening direction of the air inlet may be configured to be parallel or coincident with the axis of the centrifugal impeller, and the opening direction of the air outlet may be configured to be parallel or coincident with the axis of the centrifugal impeller.

Optionally, the air outlet may be provided with a plurality of race-rotating vanes, and the middle of the race-rotating vanes is convexly arranged; the plurality of race-rotating vanes are arranged at intervals along the circumferential direction of the air outlet, and the The setting direction of the raceway blades is the same as the rotation direction of the centrifugal impeller.

Optionally, the raceway vanes may be configured in an arcuate arrangement.

Optionally, the inlet angle of the raceway blade may be 55°-67°, and the outlet angle of the racer blade may be 90°-93°.

Optionally, the air outlet may be arranged in an annular shape, and the air outlet may be arranged at the edge of the rear casing.

Optionally, one end of the race-rotating blade may be fixed at a position of the rear casing near the center of the rear casing, and the other end of the race-rotating blade may be fixed on the rear casing.

Optionally, the installation cavity may include an impeller installation cavity and a motor installation cavity; the rear housing may include an outer cover and an installation groove provided on the inner side of the outer cover, and the air outlet may be provided in the outer cover On the body, the installation groove can form the motor installation cavity; the outer cover can be connected with the front casing, and an impeller installation cavity can be formed between the inner wall of the outer casing and the inner wall of the front casing; The inner wall of the impeller installation cavity can be used to form an air flow channel with the impeller.

Optionally, the air flow channel may include an arc guide portion, the arc guide portion is convex in a direction away from the centrifugal impeller, and one side of the arc guide portion is close to the air inlet and faces the air inlet. The air outlet side of the centrifugal impeller is arranged, and the other side of the arc guide portion is arranged close to the air outlet.

Optionally, the arc radius of the arc guide portion may be 10mm-40mm.

Optionally, the edge of the air inlet may be provided with a front side containing groove, the centrifugal impeller may be provided with a front side connecting plate, and the front side connecting plate may be inserted into the front side containing groove.

Optionally, the axial radial flow blower may further include a middle cover plate; the inner side of the outer cover may be provided with a groove, and the middle cover plate may cover the groove with the outer cover, and the middle cover may The cover plate may be provided with a connection hole for passing through the motor, the edge of the connection hole may be provided with a rear side accommodating groove, the centrifugal impeller may be provided with a rear side connection plate, and the rear side connection plate may be is inserted into the rear side containing groove.

Optionally, the cross-sectional shape of the front side containing groove may be V-shaped, or W-shaped, or U-shaped, and the cross-sectional shape of the rear side containing groove may be V-shaped, W-shaped, or U-shaped.

Optionally, the distance between the top end of the front side connecting plate and the bottom of the front side containing groove can be 4mm-6mm, and the side part of the front side connecting plate and the side part of the front side containing groove The shortest distance between can be 4mm-6mm;

And/or, the distance between the top end of the rear side connecting plate and the bottom of the rear side accommodating groove can be 4mm-6mm, and the side part of the rear side connecting plate and the side part of the rear side accommodating groove The shortest distance between can be 4mm-6mm.

The present application provides an air conditioner, which may include: a casing and the above-mentioned axial-radial blower, and the axial-radial blower may be arranged in the casing.

The axial radial blower provided by the invention includes: a motor, a centrifugal impeller and a casing; the casing includes a front casing and a rear casing that are connected to each other; the front casing is provided with an air inlet, and the rear casing is provided with an air inlet. An air outlet is provided, and the gas circulation cross-section of the air inlet and the gas circulation cross-section of the air outlet are arranged to intersect with the axial direction of the centrifugal impeller; the front casing and the rear casing are arranged opposite to each other, An installation cavity is formed between the front casing and the rear casing, the motor and the centrifugal impeller are installed in the installation cavity, and the electric motor is in driving connection with the centrifugal impeller.

During the working process of the axial radial flow blower provided by the present application, the motor rotates, which drives the centrifugal impeller to rotate, a low pressure area is formed in the middle of the centrifugal impeller, and the outside of the axial radial flow blower is in a high pressure area. Drive the gas to move on the blade surface of the centrifugal impeller, the gas moves with the centrifugal impeller and obtains a large amount of kinetic energy, and finally is thrown into the casing along the radial direction of the centrifugal impeller along the blade. Exhaust, so as to achieve axial inlet and outlet air, and the gas flows through the axial and radial directions. The axial radial flow blower provided by the present application makes the gas obtain kinetic energy through the centrifugal impeller, realizes air suction and exhaust, and the casing can change the flow direction of the gas, so the casing does not need to be arranged so that the cross-sectional area is from the side close to the air inlet side to the farther away from the air inlet side. The structure with the gradually increasing direction can realize the small volume of the casing, and then can realize the small volume of the axial radial flow blower and take up less space. If the axial radial flow blower provided by the present application is used as a blowing component of an automobile air conditioner, then this The air blowing component is small in size and occupies a small space; in addition, the axial radial flow blower provided by the present application can realize axial air inlet and axial air outlet. Can improve aerodynamic efficiency.

It is to be understood that both the foregoing general description and the following detailed description have been presented for purposes of illustration and description and are not necessarily intended to limit the present disclosure. The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate the subject matter of the present disclosure. At the same time, the specification and drawings serve to explain the principles of the present disclosure.

Description of drawings

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

1 is a schematic structural diagram of an axial radial blower provided by an embodiment of the application;

Fig. 2 is another structural representation of the axial radial blower shown in Fig. 1;

Fig. 3 is the structural representation of the casing in the axial radial blower shown in Fig. 1;

FIG. 4 is a schematic structural diagram of a front casing in the casing shown in FIG. 3;

FIG. 5 is a schematic structural diagram of the rear casing in the casing shown in FIG. 3 from a first perspective;

FIG. 6 is a schematic structural diagram of the rear casing in the casing shown in FIG. 3 from a second viewing angle;

Fig. 7 is the structural schematic diagram of the middle cover plate in the casing shown in Fig. 3;

Fig. 8 is the gas flow schematic diagram of the axial-radial blower shown in Fig. 1;

Fig. 9 is a perspective structural representation of the centrifugal impeller in the axial-radial blower shown in Fig. 1;

Figure 10 is a sectional view of the centrifugal impeller shown in Figure 9;

Fig. 11 is another perspective structural schematic diagram of the centrifugal impeller shown in Fig. 9;

Fig. 12 is a perspective structural schematic diagram of a blade in the centrifugal impeller shown in Fig. 9;

FIG. 13 is a schematic structural diagram from another perspective of the blades in the centrifugal impeller shown in FIG. 9 .

Reference numerals: 10-chassis; 20-centrifugal impeller; 30-motor; 40-air flow channel; 11-front housing; 12-rear housing; 13-air inlet; 14-air outlet; 15-race-rotating vane ;16-intermediate cover plate;41-arc guide part;111-front containing groove;121-outer cover;122-motor installation cavity;161-rear containing groove;21-front connecting plate;22-rear Side connecting plate; 23-cover plate; 24-blade; 25-hub; 26-shaft hole; 241-sweep part; 242-blade tip; 243-blade root.

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.

The components of the embodiments of the present application generally described and shown in the drawings herein may be arranged and designed in a variety of different configurations. Thus, the following detailed description of the embodiments of the application provided in the accompanying drawings is not intended to limit the scope of the application as claimed, but is merely representative of selected embodiments of the application.

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, 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 this application can be understood in specific situations.

It should be noted that, in the embodiment of the present application, “front” refers to the upstream from the air inlet 13 to the air outlet 14 in the overall direction, and “rear” refers to the downstream from the air inlet 13 to the air outlet 14 in the overall direction.

As shown in FIGS. 1 to 7 , the present application provides an axial-radial blower, which may include: a motor 30 , a centrifugal impeller 20 and a casing 10 ; the casing 10 may include a front casing 11 and a rear casing that are connected to each other. body 12; the front housing 11 may be provided with an air inlet 13, the rear housing 12 may be provided with an air outlet 14, the air flow cross section of the air inlet and the gas flow cross section of the air outlet can be arranged to intersect with the axial direction of the centrifugal impeller; the front casing 11 and the rear casing 12 can be arranged opposite to each other, and an installation cavity can be formed between the front casing 11 and the rear casing 12, The motor 30 and the centrifugal impeller 20 can be installed in the installation cavity, and the motor 30 and the centrifugal impeller 20 can be drive-connected.

During the working process of the axial-radial blower provided in this embodiment, the motor 30 rotates, which drives the centrifugal impeller 20 to rotate, a low-pressure area is formed in the middle of the centrifugal impeller 20, and the outside of the axial-radial blower is in a high-pressure area, and the pressure difference causes the outside air to enter the centrifugal impeller through the air inlet. , so that the centrifugal impeller drives the gas to move on the blade surface of the centrifugal impeller, the gas moves with the centrifugal impeller and obtains a large amount of kinetic energy, and is finally thrown into the casing 10 along the radial direction of the centrifugal impeller along the blades, and the gas is in the inner wall of the casing 10. Under the blocking, the air is discharged from the air outlet 14, so as to realize the axial air inlet and the axial air outlet, and the gas flows through the axial and radial directions. The axial radial flow blower provided in this embodiment enables the gas to obtain kinetic energy through the centrifugal impeller 20 to realize air suction and exhaust, and the casing 10 can change the flow direction of the gas. Therefore, the casing 10 does not need to be arranged such that the cross-sectional area is closer to the air inlet side. The structure gradually increases in the direction away from the air inlet side, so that the volume of the casing 10 can be small, and then the axial radial flow blower can be small in size and occupy less space. The axial radial flow blower provided in this embodiment is used as an air conditioner for an automobile The blower component of the device type is small in size and occupies a small space; in addition, the axial-radial flow blower provided in this embodiment can realize the axial air inlet and the axial air outlet. Compared with the axial air inlet, the radial To discharge air, the axial radial flow blower provided in this embodiment can improve the aerodynamic efficiency.

Specifically, the gas circulation cross-section of the air inlet and the gas circulation cross-section of the air outlet are both set to intersect with the axial direction of the centrifugal impeller, which may be: the opening direction of the air inlet may be parallel or coincide with the axis of the centrifugal impeller 20, and the air outlet 14 The opening direction of the fan can be parallel or coincident with the axis of the centrifugal impeller 20, so that the axial radial flow blower can better axially enter the air and axially discharge the air.

As shown in FIG. 5 , the air outlet 14 may be provided with a plurality of race-rotating blades 15 , and the middle of the race-rotating vanes 15 is convex (that is, the middle of the race-rotating vanes is convex compared to the ends of the race-rotating vanes). A plurality of the race-rotating blades 15 are arranged at intervals along the circumferential direction of the air outlet 14, and the setting direction of the plurality of the race-rotating vanes 15 is the same as the rotation direction of the centrifugal impeller 20, which can be understood as, When the rotational direction of the centrifugal impeller 20 is clockwise, the plurality of race-rotating blades 15 are spaced clockwise (the middle parts of the plurality of race-rotating vanes 15 are all convex in the counter-clockwise direction), when the rotational direction of the centrifugal impeller 20 is reverse When clockwise, the plurality of race-rotating vanes 15 are arranged at intervals in the counterclockwise direction (the middle portions of the plurality of race-rotating vanes 15 are all convex in the clockwise direction).

In this embodiment, a plurality of derotational blades 15 can be arranged at the air outlet 14, and the arrangement direction of the plurality of derotational blades 15 can be arranged in the same direction as the rotation direction of the centrifugal impeller 20. On the one hand, the wind is guided to reduce the rotation speed and energy. On the other hand, it can make the wind flow more uniformly, which can improve the aerodynamic efficiency and increase the uniformity of the air outlet. As shown in FIG. 8 , which is a schematic diagram of the effect of simulating the axial-radial blower provided in this embodiment, it can be seen that the gas thrown to the edge by the centrifugal impeller can flow to the middle of the axial-radial blower under the action of the race-rotating blades, The anti-rotation blade can guide the wind direction of the edge to the middle, so as to avoid the gas scattered at the edge of the air outlet, thereby improving the aerodynamic efficiency and the uniformity of the air outlet.

Wherein, the racemic blade 15 may include successively connected blade segments, a corner is formed between two adjacent blade segments, and a plurality of blade segments are sequentially connected to form an arched racemic blade 15 .

As an optional solution, as shown in FIG. 5 , the race-rotating blades 15 can be arranged in an arc shape, that is, the surfaces of the race-rotating vanes 15 are smooth without corners and are streamlined. It is beneficial to guide the wind to reduce the rotation speed, reduce the loss of energy, and make the wind flow more evenly.

Wherein, the number of race-rotating vanes 15 can be set according to specific needs, for example, the number of race-rotating vanes 15 is 9-27 (for example: 9, 10, 13, 16, 18, 20, 22, 25 or 27, etc.) .

As shown in FIG. 5 , on the basis of the above embodiment, optionally, the inlet angle β of the raceway blade 15 may be 55°˜67° (for example: 55°, 57°, 60°, 61°, 63°, 65° or 67°, etc.), the outlet angle of the racemic blade 15 can be 90°-93° (for example: 90°, 90.5°, 91°, 91.5°, 92°, 92.5° or 93° etc.), the inlet angle β of the raceway blade 15 can be set to 55°-67°, and at the same time, the outlet angle can be set to 90°-93°, which is more conducive to improving the start-up efficiency and the uniformity of the gas outlet.

As shown in FIG. 6 , on the basis of the above embodiment, optionally, the air outlet 14 may be arranged in a ring shape, and the air outlet 14 may be arranged at the edge of the rear casing 12 . In this embodiment, the air outlet 14 is arranged at the edge of the rear casing 12, so that it can be arranged closer to the peripheral side of the centrifugal impeller 20, thereby improving the air outlet efficiency.

One end of the de-rotating blade 15 may be fixed on one side of the air outlet 14 , and the other end of the de-rotating blade 15 may be fixed on the other side of the air outlet 14 .

As an optional solution, as shown in FIG. 5 , on the basis of the above embodiment, optionally, one end of the raceway blade 15 can be fixed on the rear casing 12 near the rear casing 12 . At the center position, the other end of the de-rotating blade 15 can go over the air outlet 14 to be fixed on the rear casing 12 . The fixing method of the derotational vanes 15 in this embodiment facilitates the integral molding of the rear casing 12, thereby improving the production efficiency.

As shown in FIG. 1 and FIG. 2 , specifically, the installation cavity may include an impeller installation cavity and a motor installation cavity 122 ; the rear housing 12 may include an outer cover 121 and a mounting cavity disposed inside the outer cover 121 . The air outlet 14 can be arranged on the outer cover body 121, and the installation groove can form the motor installation cavity 122; the outer cover body 121 can be connected with the front case 11, and the outer cover body 121 An impeller installation cavity can be formed between the inner wall of the front casing 11 and the inner wall of the front housing 11; the inner wall of the impeller installation cavity can be used to form an air flow channel 40 between the impeller and the impeller.

Wherein, the air flow channel 40 may include an arc guide portion 41, the arc guide portion 41 is convex in a direction away from the centrifugal impeller 20, and one side of the arc guide portion 41 is close to the inlet. The air outlet 13 is disposed facing the air outlet side of the centrifugal impeller 20 , and the other side of the arc guide portion 41 is disposed close to the air outlet 14 .

In this embodiment, the arc guide portion 41 can be surrounded by the side of the centrifugal impeller 20 , the middle portion of the arc guide portion 41 can be far away from the centrifugal impeller 20 , and the two sides of the arc guide portion 41 can be close to the centrifugal impeller 20 . , then the wind flow channel 40 is turned and arranged at the side of the centrifugal impeller 20, so that a labyrinth structure can be formed. The side part of the arc guide part 41 guides the gas to the other side of the arc guide part 41, and then guides the gas to the air outlet 14; the arc The labyrinth structure formed by the flow guide portion 41 can prevent the gas from flowing backward, thereby improving the air outlet efficiency.

Since the two sides of the arc flow passage are closer to the centrifugal impeller 20 than the middle, in order to enable the motor 30 and the centrifugal blades to be assembled into the installation cavity of the casing 10 , the front casing 11 can be arranged at least close to the inner wall of the rear casing 12 The part is arc-shaped, and the inner wall part of the front casing 11 forms half of the arc guide part 41. Similarly, the rear casing 12 is arranged at least in the inner part close to the front casing 11 is arc-shaped. The inner wall part of the front casing 11 forms half of the arc guide part 41. After connecting the front casing 11 and the rear casing 12, the inner wall part of the front casing 11 close to the rear casing 12 and the rear casing 12 close to the front casing 12. Parts of the inner wall of the housing 11 are spliced together to form a circular arc guide portion 41 .

The radius of the arc guide portion 41 may be set according to specific conditions. Optionally, the arc radius of the arc guide portion 41 may be 10mm-40mm, for example: 10mm, 15mm, 20mm, 25mm, 30mm, 35mm, or 40mm.

As shown in FIG. 2, on the basis of the above embodiment, optionally, the edge of the air inlet 13 may be provided with a front side containing groove 111, and the centrifugal impeller 20 may be provided with a front side connecting plate 21, so The front side connecting plate 21 can be inserted into the front side accommodating groove 111 . In the present embodiment, the air inlet side of the centrifugal impeller 20 extends out of the air inlet 13 of the front casing 11 , and the front side connecting plate is inserted into the front side accommodating groove 111 , which improves the gap between the centrifugal impeller 20 and the front casing 11 . The airtightness can reduce the gas leakage, thereby improving the air outlet efficiency of the gas.

The cross-sectional shape of the front side containing groove 111 can be V-shaped or W-shaped, and the optional front-side containing groove 111 has a U-shaped cross-sectional shape, which is simple in structure and easy to manufacture.

Optionally, the distance h1 between the top of the front side connecting plate 21 and the bottom of the front side containing groove 111 may be 4mm-6mm (for example: 4mm, 4.5mm, 5mm, 5.5mm or 6mm, etc.), The shortest distance h2 between the side part of the front side connecting plate 21 and the side part of the front side containing groove 111 may be 4mm-6mm (for example: 4mm, 4.3mm, 4.6mm, 5mm, 5.4mm, 5.8mm) Or 6mm), on the one hand, this setting can achieve a better sealing effect, and on the other hand, it can prevent the volume of the front side containing groove 111 from being too large.

As shown in FIG. 2, on the basis of the above-mentioned embodiment, optionally, the axial-radial blower may further include an intermediate cover plate 16; the inner side of the outer cover body 121 may be provided with grooves (which can reduce weight). , it is also convenient for the rear shell 12 to be formed), the middle cover 16 can be connected with the outer cover 121 (for example, by welding, glue connection, interference connection or welding, etc.) to cover the groove (to avoid gas The middle cover 16 may be provided with a connection hole for passing through the motor 30, and the edge of the connection hole may be provided with a rear side containing groove 161, the centrifugal The impeller 20 may be provided with a rear connecting plate 22 , and the rear connecting plate 22 may be inserted into the rear containing groove 161 .

In this embodiment, the rear side connecting plate can be inserted into the rear side accommodating groove 161, which improves the sealing between the centrifugal impeller 20 and the middle cover plate 16, reduces gas leakage, and optionally improves the air outlet of the gas. efficiency.

Wherein, the cross-sectional shape of the rear side containing groove 161 can be V-shaped or W-shaped, and the optional cross-sectional shape of the rear side containing groove 161 is U-shaped, which is simple in structure and easy to manufacture.

Optionally, the distance h1 between the top end of the rear side connecting plate 22 and the bottom of the rear side containing groove 161 may be 4mm-6mm (for example: 4mm, 4.5mm, 5mm, 5.5mm or 6mm, etc.), The shortest distance h2 between the side part of the rear side connecting plate 22 and the side part of the rear side containing groove 161 may be 4mm-6mm (for example: 4mm, 4.3mm, 4.6mm, 5mm, 5.4mm, 5.8mm) or 6 mm), on the one hand, this setting can achieve a better sealing effect, and on the other hand, it can prevent the volume of the rear side containing groove 161 from being too large.

As shown in FIGS. 9 to 13 , the centrifugal impeller may include a cover plate 23 , blades 24 and a hub 25 that are fixedly connected in sequence, so that the blades 24 are located between the cover plate 23 and the cover plate 23 in the axial direction of the hub 25 . Between the hubs 25, the cover plate can be provided with an opening for air circulation, the front connecting plate can be arranged on the edge of the opening, and the rear connecting plate can be arranged on the side of the hub away from the cover plate; the blades 24 can be It is a backward curved blade, and the blade 24 may have a forward sweep. A shaft hole 26 for connecting the drive shaft may be formed on the hub.

In this embodiment, the centrifugal impeller can use space-distorted backward-curved blades. After the accelerated air enters the impeller, the degree of fit with the blades 24 is high, and the energy added to the airflow in the centrifugal impeller is mainly converted into pressure energy, which ensures high efficiency. The swept portion 241 of the blade 24 at the inlet is beneficial to reduce the aerodynamic noise generated after the airflow hits the centrifugal impeller.

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

Optionally, the swept angle of the swept portion 241 may be γ, and 81°≤γ≤86°.

Optionally, the forward sweep angle of the forward sweep portion 241 may be γ, and γ is 83°.

Optionally, the blade outlet angle of the blade 24 may be α, and 60°≤β≤70°.

Optionally, the blade outlet angle of the blade 24 may be α, and α is 65°.

The blade may have a blade tip 242 and a blade root 243. Optionally, the radius of the blade root 243 of the blade 24 at the inlet may be R _h , and the radius of the blade tip 242 at the inlet may be R _s , and 0.35≤R _h / R _s ≤ 0.4. The inlet mentioned in this embodiment refers to the inlet of the centrifugal impeller.

Optionally, the radius of the blade root 243 of the blade 24 at the inlet may be _Rh , the radius of the blade tip 242 at the inlet may be R _s , and _Rh /R _s =0.37.

Optionally, the angle between the tangential direction of the blade tip profile of the blade 24 at the inlet and the rotational direction of the centrifugal impeller at the blade tip may be α ₁ , and 56°≤α ₁ ≤64°.

Optionally, the angle between the tangential direction of the blade tip profile of the blade 24 at the inlet and the rotation direction of the centrifugal impeller at the blade tip may be α ₁ , and α ₁ =62°.

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

Wherein, R ₂ is the centrifugal impeller outlet radius of the centrifugal impeller; u ₂ is the peripheral speed,

is the flow coefficient at the outlet of the centrifugal impeller.

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

u ₂ =2πR ₂ n (2);

where n is the rotational speed of the centrifugal impeller.

Optionally, _{90mm≤R2≤110mm} , and

Optionally, the thickness of the blades 24 at the inlet of the centrifugal impeller may be δ ₁ , where 0.8mm≦δ ₁ ≦1.5mm.

Optionally, the thickness of the blades 24 at the inlet of the centrifugal impeller may be δ ₁ , and δ ₁ =1.1 mm.

Optionally, the thickness of the blades 24 at the outlet of the centrifugal impeller may be δ ₂ , and 1.3 mm≤δ ₂ ≤2.5 mm.

Optionally, the thickness of the blades 24 at the outlet of the centrifugal impeller may be δ ₂ , and δ ₂ =1.9 mm.

Optionally, the number of the blades 24 may be 19 or 23; the root radius of the blades 24 at the inlet may be 28.8 mm; the tip radius of the blades 24 at the inlet may be 72 mm; The blade angle at the tip of the blade 24 may be 62°, and the blade angle at the root of the blade 24 at the inlet may be 37°; the outlet width of the centrifugal impeller may be 25mm, the blade angle at the outlet of the centrifugal impeller may be 65°, and the centrifugal impeller The outlet radius may be 92.1 mm; the axial length of the centrifugal impeller may be 40.2 mm.

The embodiment of the present application can achieve the required target air volume through the smaller axial size of the centrifugal impeller, and at the same time, under operating conditions, the flow field in the centrifugal impeller is guaranteed to be more stable, the overall efficiency of the automobile air-conditioning blower is improved, and the automobile Air conditioning assembly noise.

Specific principle:

Before the incoming air enters the centrifugal impeller, the forward-swept blade structure ensures that the airflow enters the centrifugal impeller more uniformly and stably; because the blades are space-distorted backward-curved blades, the airflow in the centrifugal impeller channel is urged to fit with the blades; When flowing to the outlet of the centrifugal impeller, the stability of the flow field at the outlet of the centrifugal impeller is improved due to the backward curved structure of the blade. In addition, the turning loss of the airflow in the backward curved centrifugal impeller is relatively small, and the efficiency of the entire centrifugal impeller is also improved.

It should be noted that, in order to realize the normal operation of the axial radial flow blower, the axial radial flow blower may also include a PCB board.

The embodiment of the present application also provides an air conditioner, which may include a casing 10 and an axial radial blower, and the axial radial blower may be arranged in the casing 10 . The air conditioner provided in this embodiment is compact in structure and small in volume; it can achieve larger air volume and better NVH level than traditional air conditioners.

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. In the description provided herein, numerous specific details are set forth. It will be understood, however, that the embodiments of the present application may be practiced without these specific details. In some instances, well-known methods, structures and techniques have not been shown in detail in order not to obscure an understanding of this description. Furthermore, those skilled in the art will appreciate that although some of the embodiments herein include certain features, but not others, included in other embodiments, that combinations of features of the different embodiments are intended to be within the scope of the present application And form different embodiments.

Industrial Applicability

The present application provides an axial radial blower and an air conditioner. The axial radial blower includes: a motor, a centrifugal impeller and a casing; the casing includes a front casing and a rear casing that are connected to each other; the front casing is provided with an air inlet, and the rear casing is provided with an air inlet. There is an air outlet, and the gas circulation cross-section of the air inlet and the gas circulation cross-section of the air outlet are arranged to intersect with the axial direction of the centrifugal impeller; the front casing and the rear casing are oppositely arranged, so An installation cavity is formed between the front casing and the rear casing, the motor and the centrifugal impeller are installed in the installation cavity, and the electric motor is in driving connection with the centrifugal impeller. The axial radial flow blower provided by the present application has a small volume, and the axial air inlet and the axial air outlet can improve the aerodynamic efficiency.

Furthermore, it will be appreciated that the axial radial blower and air conditioner of the present application is reproducible and can be used in a variety of industrial applications. For example, the axial radial blower and air conditioner of the present application can be used in the field of automobile technology.

Claims

An axial radial blower is characterized in that it comprises: a motor, a centrifugal impeller and a casing; the casing comprises a front casing and a rear casing that are connected to each other; the front casing is provided with an air inlet, and the rear casing The casing is provided with an air outlet, and the gas circulation cross-section of the air inlet and the gas circulation cross-section of the air outlet are both set to intersect with the axial direction of the centrifugal impeller; the front casing and the rear casing Oppositely arranged, an installation cavity is formed between the front casing and the rear casing, the motor and the centrifugal impeller are installed in the installation cavity, and the electric motor and the centrifugal impeller are drive-connected.
The axial-radial flow blower according to claim 1, wherein the opening direction of the air inlet is configured to be parallel or coincident with the axis of the centrifugal impeller, and the opening direction of the air outlet is configured to be parallel to the axis of the centrifugal impeller. The axes are parallel or coincident.
The axial-radial flow blower according to claim 1 or 2, wherein a plurality of race-rotating vanes are arranged at the air outlet, and the middle of the race-rotating vanes is arranged convexly; The tuyere is arranged at intervals in the circumferential direction, and the arrangement direction of the plurality of race-rotating blades is the same as the rotation direction of the centrifugal impeller.
The axial-radial flow blower according to claim 3, wherein the raceway blades are configured to be arranged in an arc.
The axial-radial flow blower according to claim 3 or 4, characterized in that, the inlet angle of the race-rotating blade is 55°-67°, and the outlet angle of the race-rotating blade is 90°-93°.
The axial-radial blower according to any one of claims 3 to 5, wherein the air outlet is arranged in an annular shape, and the air outlet is arranged at the edge of the rear casing.
The axial-radial blower according to claim 6, wherein one end of the race-rotating vane is fixed at a position of the rear casing close to the center of the rear casing, and the other end of the race-rotating vane is fixed on the rear casing.
The axial-radial blower according to any one of claims 1-7, wherein the installation cavity comprises an impeller installation cavity and a motor installation cavity; the rear housing comprises an outer cover and a an installation groove on the inner side, the air outlet is arranged on the outer cover body, and the installation groove forms the motor installation cavity; the outer cover body is connected with the front case, and the inner wall of the outer cover body and the front An impeller installation cavity is formed between the inner walls of the casing; the inner wall of the impeller installation cavity is used to form an air flow channel with the impeller.
The axial-radial flow blower according to claim 8, wherein the air flow channel comprises a circular arc guide portion, the arc guide portion is convex in a direction away from the centrifugal impeller, and the arc guide portion is One side of the arc air guide portion is arranged close to the air inlet and faces the outlet side of the centrifugal impeller, and the other side of the arc guide portion is arranged close to the air outlet.
The axial radial flow blower according to claim 9, wherein the arc radius of the arc guide portion is 10mm-40mm.
The axial radial flow blower according to any one of claims 8 to 10, wherein the edge of the air inlet is provided with a front side containing groove, the centrifugal impeller is provided with a front side connecting plate, the front side The side connecting plate is inserted into the front side accommodating groove.
The axial-radial blower according to claim 11, wherein the axial-radial blower further comprises an intermediate cover; the inner side of the outer cover is provided with a groove, and the intermediate cover and the outer cover The groove is covered, the middle cover is provided with a connection hole for passing through the motor, the edge of the connection hole is provided with a rear side accommodating groove, the centrifugal impeller is provided with a rear side connection plate, the The rear side connecting plate is inserted into the rear side accommodating groove.
The axial radial flow blower according to claim 12, wherein the cross-sectional shape of the front side containing groove is V-shaped, or W-shaped, or U-shaped, and the cross-sectional shape of the rear side containing groove is V-shaped, Or W type, or U type.
The axial-radial blower according to claim 12 or 13, wherein the distance between the top end of the front side connecting plate and the bottom of the front side accommodating groove is 4mm-6mm, and the distance between the front side connecting plate The shortest distance between the side part and the side part of the front side containing groove is 4mm-6mm;

And/or, the distance between the top end of the rear side connecting plate and the bottom of the rear side accommodating groove is 4mm-6mm, and the distance between the side portion of the rear side connecting plate and the side portion of the rear side accommodating groove is 4mm-6mm. The shortest distance between them is 4mm-6mm.
An air conditioner is characterized in that, comprising: a casing and the axial radial blower according to any one of claims 1-14, wherein the axial radial blower is arranged in the casing.