WO2022218009A1

WO2022218009A1 - Air-conditioning device and automobile

Info

Publication number: WO2022218009A1
Application number: PCT/CN2022/074406
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: 2022-01-27
Publication date: 2022-10-20
Also published as: CN112918218A

Abstract

An air-conditioning device and an automobile. The air-conditioning device comprises a machine housing (10), and a blower (20), a refrigeration heat exchanger (30) and a heating heat exchanger (40), which are arranged in the machine housing (10), wherein the blower (20) comprises an electric motor (23) and a centrifugal impeller (22) in transmission connection with the electric motor (23); and the electric motor (23) drives the centrifugal impeller (22) to rotate such that gas enters the centrifugal impeller (22) in an axial direction of the centrifugal impeller (22) and is discharged from the centrifugal impeller (22) in a radial direction of the centrifugal impeller (22). The air-conditioning device can achieve a small volume when the diameter of the impeller is the same, thereby facilitating flattening; and at the same volume, the diameter of the impeller of the blower is larger than that of a traditional volute-type fan, and a greater air blowing capacity is achieved, thereby achieving a high air output efficiency at the same volume.

Description

Air conditioners and automobiles

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the priority of the Chinese Patent Application No. 202110397459X and entitled "Air Conditioning Device and Automobile" filed with the China Patent Office on April 13, 2021, the entire contents of which are incorporated herein by reference.

technical field

The present application relates to the technical field of vehicles, and in particular, to an air conditioner and an automobile.

Background technique

An automobile air conditioner usually includes a casing and a volute-type blower and a heat exchanger arranged in the casing. The casing is provided with an air inlet and an air outlet, and the volute-type blower is arranged close to the inlet of the casing relative to the heat exchanger. The location of the vent. The volute type blower mainly includes impeller, flange, end cover, motor and volute, etc. The working principle of the volute type blower in the air conditioner is to use the high-speed rotation of the impeller to force the gas to rotate, and work on the gas to increase its energy. Make the airflow decelerate. This deceleration effect converts kinetic energy into pressure energy. The gas is sucked into the casing of the air conditioner under the action of the pressure difference, and after heat exchange reaches the set temperature, it is discharged from the air outlet. The air conditioner with this structure is bulky and occupies a large space.

SUMMARY OF THE INVENTION

The present application provides an air conditioner and an automobile, so as to solve the technical problems of large volume and large space occupation of the air conditioner in the prior art to a certain extent.

The air conditioner provided by the present application may include: a casing and a blower, a cooling heat exchanger and a heating heat exchanger arranged in the casing; the blower includes a motor and a centrifugal impeller drivingly connected to the motor , the motor drives the centrifugal impeller to rotate, so that the gas enters the centrifugal impeller from the axial direction of the centrifugal impeller and discharges the centrifugal impeller from the radial direction of the centrifugal impeller.

Optionally, the casing may include an air inlet casing, an intermediate casing and an air distribution casing that are communicated in sequence; the refrigeration heat exchanger may be arranged in the air inlet casing, the blower and the system The heat exchangers can all be connected to the intermediate casing; the air inlet casing can be provided with a general air inlet, and the general air inlet can be located on the side of the refrigeration heat exchanger away from the blower; The air distribution housing may be provided with a general air outlet.

Optionally, the air inlet of the blower may be located in the axial direction of the blower and face the refrigeration heat exchanger, and the air outlet of the blower may be located in the radial direction of the blower; A flow guide structure may be provided, the flow guide structure may be located at the air outlet of the blower, and the flow guide structure may be used to guide the gas flowing out of the air outlet of the blower to be away from the cooling exchange of the blower. direction of the heater.

Optionally, the diversion structure may be a diversion rib; one end of the diversion rib close to the air inlet of the blower is arranged close to the blower, and the air diversion rib is far from the air inlet of the blower. One end is disposed away from the blower.

Optionally, the flow guide ribs may be configured in a straight plate arrangement or an arc arrangement.

Optionally, the rib can be connected and fixed to the intermediate casing by welding, snap connection or screw connection.

Optionally, the rib may be integrally formed with the intermediate casing.

Optionally, the air guide structure may be an air guide pipe, one end of the air guide pipe is provided with an inlet, and the other end of the air guide pipe extends toward the direction close to the heating heat exchanger.

As an optional solution, in the height direction of the heating heat exchanger, one side of the heating heat exchanger may be arranged in abutment with the inner wall of the intermediate casing, and the heating heat exchanger The other side of the shell can be arranged in abutment with the inner wall of the casing.

As an optional solution, in the height direction of the heating heat exchanger, a space may be provided between one side of the heating heat exchanger and the inner wall of the intermediate shell, and the heating heat exchanger The other side of the heater may be provided in abutment with the inner wall of the casing.

As an optional solution, in the height direction of the heating heat exchanger, a space may be provided between one side of the heating heat exchanger and the inner wall of the intermediate shell, and the heating heat exchanger The other side of the heater may be spaced from the inner wall of the housing.

Optionally, the air conditioning device may further include a guide air door, the air guide air door is rotatably connected to the heating heat exchanger; the air guide air door, the inner wall of the intermediate housing and the heating heat exchange A cold air channel is formed between the blowers, and the cold air channel is communicated with the air distribution housing; a hot air channel is formed between the diversion air door and the back of the blower, and the hot air channel is communicated with the heating heat exchanger .

As an optional solution, the casing may include an air inlet casing, an intermediate casing and an air distribution casing connected in sequence, the air inlet casing may be provided with a general air inlet, and the air distribution casing A total air outlet can be provided on the upper part; the blower can be arranged in the air inlet casing, the heating heat exchanger and the cooling heat exchanger can be arranged in the intermediate casing; the blower can be a shaft Radial flow blower, the axial radial flow blower can also include a fan casing, and the fan casing can include a fan front casing and a fan rear casing that are connected to each other; the fan front casing can be provided with an axis with the centrifugal impeller Parallel or overlapping air inlets, the fan rear casing may be provided with an air outlet parallel or overlapping with the axis of the centrifugal impeller; the fan front casing and the fan rear casing may be arranged oppositely, the fan An installation cavity may be formed between the fan front casing and the fan rear casing, and the motor and the centrifugal impeller may be installed in the installation cavity.

Optionally, the side wall of the refrigeration heat exchanger is in contact with the inner wall of the intermediate casing, and the side wall of the heating heat exchanger is in contact with the inner wall of the intermediate casing.

Optionally, the air conditioner may further include an air filter, and the air filter may be arranged on the side of the axial radial blower away from the total air inlet; the side wall of the air filter may be connected with the air filter. The inner walls of the intermediate casing are in contact.

Optionally, the air inlet housing, the intermediate housing and the air distribution housing are provided independently of each other, one side of the intermediate housing is sealed with the air inlet housing, and the intermediate housing is sealed. The other side of the air distribution housing is sealedly connected with the air distribution housing;

Alternatively, the air inlet housing, the intermediate housing and the air distribution housing may be integrally provided.

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

The present application provides an automobile, which may include a vehicle body and the above-mentioned air conditioner, wherein the air conditioner is provided in the vehicle body.

The present application provides an air conditioner, which may include: a casing, and a blower, a cooling heat exchanger, and a heating heat exchanger disposed in the casing; the blower may include a motor and a connection with the motor. The centrifugal impeller connected by transmission, the motor drives the centrifugal impeller to rotate, so that the gas enters the centrifugal impeller from the axial direction of the centrifugal impeller and discharges the centrifugal impeller from the radial direction of the centrifugal impeller.

In the air conditioner provided by the present application, the motor in the blower drives the centrifugal impeller to rotate, and the impeller rotates at a high speed to suck the gas into the blower. The impeller is quickly thrown out radially, so that the gas enters the casing, and there is no need to set a casing with a specific structure in the volute type blower. When the impeller diameter is the same, the volume of the blower is small and takes up less space, which is different from the traditional volute type blower. Compared with the air-conditioning device, the air-conditioning device provided by the present application can achieve a small volume with the same impeller diameter, which is conducive to realizing flattening; under the same volume, the diameter of the impeller of the blower can be larger than that of the traditional volute type fan, so as to achieve greater blowing capacity , so that the air conditioner provided by the present application can achieve high air outlet efficiency under the same volume.

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.

FIG. 1 is a schematic structural diagram of an air conditioner according to a first embodiment of the application;

Fig. 2 is another structural schematic diagram of the air conditioner shown in Fig. 1;

3 is a schematic structural diagram of an air conditioner according to a second embodiment of the present application;

Fig. 4 is another structural schematic diagram of the air conditioner shown in Fig. 3;

5 is a schematic structural diagram of a third embodiment of the application;

6 is a schematic structural diagram of a fourth embodiment of the application;

Fig. 7 is a structural representation of the blower in the air-conditioning device shown in Fig. 6;

Fig. 8 is another structural schematic diagram of the blower shown in Fig. 7;

Fig. 9 is the structural representation of the blower housing in the blower shown in Fig. 7;

FIG. 10 is a schematic structural diagram of a fan front casing in the fan casing shown in FIG. 9;

FIG. 11 is a schematic structural diagram of the rear casing of the fan in the fan casing shown in FIG. 9 from a first perspective;

FIG. 12 is a schematic structural diagram of the rear casing of the fan in the fan casing shown in FIG. 9 from a second perspective;

Figure 13 is a schematic structural diagram of the middle cover plate in the fan casing shown in Figure 10;

Fig. 14 is the gas flow schematic diagram of the blower shown in Fig. 7;

Fig. 15 is a perspective structural diagram of the centrifugal impeller in the blower shown in Fig. 7;

Figure 16 is a sectional view of the centrifugal impeller shown in Figure 15;

Fig. 17 is another perspective structural schematic diagram of the centrifugal impeller shown in Fig. 15;

Fig. 18 is a perspective structural diagram of the blade in the centrifugal impeller shown in Fig. 15;

FIG. 19 is a schematic structural diagram of another perspective view of the blades in the centrifugal impeller shown in FIG. 15 .

Icon: 10-chassis; 20-blower; 30-refrigeration heat exchanger; 40-heating heat exchanger; 50-total air inlet; 60-total air outlet; 70- diversion rib; 80- diversion damper; 90-cold air passage; 100-hot air passage; 110-cold air position; 120-hot air position; 130-mode damper; 140-rib groove sealing structure; 150-air filter; 11-air inlet housing; 12-intermediate housing ;13-air distribution shell;21-fan shell;22-centrifugal impeller;23-motor;24-air flow channel;211-fan front shell;212-fan rear shell;213-air inlet;214-air outlet ; 215-race blade; 216-intermediate cover plate; 241-arc guide part; 2111-front containment groove; 2121-cover body; 2122-motor installation cavity; 2161-rear containment groove; 222-rear connecting plate; 223-cover plate; 224-blade; 225-hub; 226-shaft hole; 2241-sweep; 2242-blade tip; 2243-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 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.

As shown in FIGS. 1 to 4 , the present application provides an air conditioner, which may include: a casing 10 and a blower 20 , a cooling heat exchanger 30 and a heating heat exchanger 40 arranged in the casing 10 ; the blower may include The motor and the centrifugal impeller connected with the motor drive, the motor drives the centrifugal impeller to rotate, so that the gas enters the centrifugal impeller from the axial direction of the centrifugal impeller and is discharged from the centrifugal impeller radially.

In the air conditioner provided in this embodiment, the motor in the blower 20 drives the centrifugal impeller to rotate, and the impeller rotates at a high speed to suck the gas into the blower 20. The blower 20 performs work on the gas to generate a strong centrifugal force, and the backward-inclined impeller blades of the centrifugal impeller push the gas into the air. It is quickly thrown out along the radial direction of the centrifugal impeller, so that the gas enters the intermediate casing 12, and there is no need to set up a casing with a specific structure in the volute type blower. When the impeller diameter is the same, the blower has a small volume and takes up less space, which is different from the traditional Compared with the air conditioner of the volute type blower, the air conditioner provided in this embodiment can achieve a small volume with the same impeller diameter, which is conducive to realizing flattening; under the same volume, the diameter of the impeller of the blower can be larger than that of the traditional volute type fan, A larger blowing capacity is achieved, so that the air conditioner provided in this embodiment can achieve high air outlet efficiency under the same volume.

In addition, the diameter of the centrifugal impeller of the blower 20 can be larger than that of the traditional volute type centrifugal fan, and the maximum diameter of the centrifugal impeller of the blower 20 can be the same height or width as the cooling heat exchanger; the larger the diameter of the centrifugal impeller, the air volume of the blower 20 The larger the diameter of the impeller, the smaller the rotation speed of the same air volume, so the air conditioner can achieve a larger air volume and better NVH (that is, Noise, Vibration, Harshness) than traditional air conditioners. standard) level.

As shown in FIGS. 1 to 4 , the casing 10 may include an air inlet casing 11 , an intermediate casing 12 and an air distribution casing 13 connected in sequence, and the air inlet casing 11 may be provided with a general air inlet 50 for air distribution. A total air outlet 60 may be provided on the housing 13 . The heating heat exchanger 40 may be arranged in the air inlet housing 11 , and the blower 20 and the heating heat exchanger 40 may be arranged in the intermediate housing 12 .

On the basis of the above embodiment, the axial direction of the blower may be arranged to intersect with the thickness direction of the refrigerating heat exchanger, or the axial direction of the blower may be arranged to intersect the thickness direction of the heating heat exchanger.

Optionally, at least one of the thickness direction of the cooling heat exchanger 30 and the thickness direction of the heating heat exchanger is in the same direction as the axial direction of the blower 20 . In this embodiment, the axial direction of the blower 20 is arranged in the same direction as at least one of the thickness direction of the cooling heat exchanger 30 and the thickness direction of the heating heat exchanger 40, so that the flat structure of the air conditioner can be arranged, The structure of the air-conditioning device is more compact, and the space is less occupied.

It should be noted that the thickness direction of the cooling heat exchanger 30 is the air intake direction of the cooling heat exchanger 30, the thickness direction of the heating heat exchanger 40 is the air intake direction of the heating heat exchanger 40, and the air intake direction of the blower The wind direction is in the same direction as the axial direction of the blower 20 . At least one of the thickness direction of the cooling heat exchanger 30 and the thickness direction of the heating heat exchanger is in the same direction as the axial direction of the blower 20 : the axial direction of the blower 20 may be the same as the thickness direction of the cooling heat exchanger 30 In the same direction, that is, the air inlet direction of the blower 20 and the air inlet direction of the cooling heat exchanger 30 are in the same direction; it can also be that the axial direction of the blower 20 and the thickness direction of the heating heat exchanger 40 are in the same direction, that is, the air blower The air inlet direction of the 20 is in the same direction as the air inlet direction of the heating heat exchanger 40; optionally, the axial direction of the blower 20 is not only in the same direction as the thickness direction of the cooling heat exchanger 30, but also in the same direction as the heating heat exchanger. The thickness directions of the heat exchanger 40 are in the same direction, that is, the air intake direction of the cooling heat exchanger 30, the air intake direction of the blower 20, and the air intake direction of the heating heat exchanger 40 are in the same direction.

The number of heating heat exchangers 40 may be one, or two, three, or four, and so on.

As an optional solution, the cooling heat exchanger 30 can be arranged in the air inlet housing 11, the blower 20 and the heating heat exchanger 40 can be connected to the intermediate housing 12; the total air inlet 50 can be located in the cooling heat exchanger The side of the 30 away from the blower 20.

In this embodiment, the blower 20 and the heating heat exchanger 40 can be integrated in the intermediate casing 12, and the heat generated by the motor of the blower 20 during the working process can exchange heat with the gas in the intermediate casing 12, which can be combined with the heating system. The heat exchangers 40 work together to heat the gas, so as to utilize the waste heat of the motor of the blower 20 and reduce energy consumption. Different air intake structures and air distribution structures can also be configured to improve the practicability of the air conditioner.

The general air inlet 50 of the cabinet 10 can be communicated with the air inside or outside the vehicle by adjusting the inside and outside air switching damper (not shown). When the refrigerating heat exchanger is working, the air coming out from the air outlet surface of the refrigerating heat exchanger is cold air, so that the blower 20 sucks in cold air; when the refrigerating heat exchanger stops heat exchange, the The air coming out of the air outlet surface is the ambient air inside or outside the vehicle, so the air blower 20 inhales is ambient air.

As shown in FIGS. 1 to 4 , on the basis of the above embodiments, optionally, the air inlet of the blower 20 may be located in the axial direction of the blower 20 and face the refrigeration heat exchanger 30 , and the air outlet of the blower 20 may be located at In the radial direction of the blower 20; the intermediate housing 12 may be provided with a diversion structure, the diversion structure may be located at the air outlet of the blower 20, and the diversion structure may be used to guide the gas flowing out of the air outlet of the blower 20 away from the blower 20. Orientation of the refrigeration heat exchanger 30 .

In this embodiment, the gas is thrown out by the impeller blades of the blower 20 to the inner wall of the intermediate casing 12, and a diversion structure is provided at the position of the intermediate casing 12 and the air outlet of the blower 20, and the diversion structure can divert the gas from the blower The air outlet 20 is directed to the direction of the blower 20 away from the refrigerating heat exchanger 30 , and the diversion structure makes the gas flow to the rear of the blower 20 , thereby facilitating the flow of the gas to the air distribution housing 13 .

Wherein, the structure of the air guide structure can be various, for example, the air guide structure can be an air guide pipe, one end of the air guide pipe is provided with an inlet, and the other end of the air guide pipe extends toward the direction close to the heating heat exchanger 40 .

As an optional solution, the diversion structure can be a diversion rib 70; the end of the diversion rib 70 close to the air inlet of the blower 20 is set closer to the blower 20 than the end of the diversion rib 70 far away from the air inlet of the blower 20 . That is, the end of the air guide rib 70 close to the air inlet of the blower 20 is arranged close to the blower 20, and the end of the air guide rib away from the air inlet of the blower is installed away from the blower. In the radial direction, the end of the guide rib 70 close to the refrigeration heat exchanger 30 is set lower than the end of the guide member close to the heating heat exchanger 40 , and the guide rib 70 blocks the direction of gas flow to the refrigeration heat exchanger 30 , so as to guide the gas to the direction of the heating heat exchanger 40 . The diversion structure of this structure is simple and easy to process.

Wherein, the guide ribs 70 may be arranged in a straight plate, and optionally, the guide ribs 70 may be arranged in an arc shape.

The flow guide rib 70 can be connected and fixed with the intermediate casing 12 by welding, snap connection or screw connection.

Optionally, the guide ribs 70 may be integrally formed with the intermediate casing 12, that is, the intermediate casing 12 is provided with openings at both ends, wherein the first opening communicates with the air inlet casing 11, and the second opening communicates with the air distribution casing. The body 13 communicates with each other, and the guide ribs 70 are formed on the intermediate casing 12 near the first opening. The first opening of the intermediate casing 12 is optionally arranged in an annular shape, so as to be matched with the air inlet of the blower 20 .

As shown in FIG. 5 , on the basis of the above-mentioned embodiment, optionally, in the height direction of the heating heat exchanger, one side of the heating heat exchanger can be arranged in abutment with the inner wall of the intermediate casing, and the heating The other side of the heat exchanger may be arranged in abutment with the inner wall of the casing. In this embodiment, all the air from the blower passes through the heating heat exchanger, and then enters the air distribution housing.

As shown in FIG. 1 to FIG. 5 , the air conditioning device may further include a diversion damper 80 , which is rotatably connected to the heating heat exchanger 40 ; the diversion damper 80 , the inner wall of the intermediate housing 12 and the heating heat exchange A cold air channel 90 can be formed between the blowers 40, and the cold air channel 90 communicates with the air distribution housing 13;

In this embodiment, when the operation of the cooling heat exchanger 30 does not require the operation of the heating heat exchanger 40, the diversion damper 80 can be rotated to contact the back of the blower 20 (that is, the flange of the blower 20). The position of the deflector damper 80 at this time is defined as the cold air position 110. At this time, the cold air passage 90 is fully opened, the hot air passage 100 is closed, and the gas from the blower 20 can directly enter the rear air distribution housing 13 from the cold air passage 90. , and then discharged from the general air outlet 60; when the cooling heat exchanger 30 is not working and the heating heat exchanger 40 is working, the air guide damper 80 can be rotated to abut against the inner wall of the intermediate housing 12, and the guide air at this time can be defined. The position of the air flow door 80 is the hot air position 120. At this time, the hot air passage 100 is fully opened, the cold air passage 90 is closed, and the gas from the blower 20 can enter the heating heat exchanger 40 through the hot air passage 100, thereby completing the gas heating; When the air flow door 80 is located between the cold air and warm air positions, the cold air passage 90 and the hot air passage 100 are both open, and part of the cold air from the blower 20 enters the air distribution housing 13 through the cold air passage 90, and the other part enters through the hot air passage 100. In the heating heat exchanger 40, the hot air from the heating heat exchanger 40 also enters the air distribution box, and the cold air and the hot air are mixed in the distribution housing, and then discharged from the general air outlet 60.

As shown in FIG. 1 and FIG. 2 , in the height direction of the heating heat exchanger 40 , a space may be provided between one side of the heating heat exchanger 40 and the inner wall of the intermediate casing 12 , and the heating heat exchanger 40 The other side of the housing can be arranged in abutment with the inner wall of the housing. In this embodiment, the air guide ribs 70 and the air guide damper 80 may be provided only on the upper part of the intermediate casing 12 .

As shown in FIGS. 3 and 4 , in the height direction of the heating heat exchanger 40 , a space may be provided between one side of the heating heat exchanger 40 and the inner wall of the intermediate casing 12 , and the heating heat exchanger 40 The other side of the housing may be spaced from the inner wall of the housing. In this embodiment, the air guide ribs 70 and the air guide dampers 80 are provided on both the upper and lower parts of the intermediate casing 12 .

As an optional solution, as shown in FIG. 6 to FIG. 19 , the casing may include an air inlet casing 11 , an intermediate casing 12 and an air distribution casing 13 connected in sequence, and the air inlet casing 11 may be provided with a general The air inlet 50 and the air distribution casing can be provided with a total air outlet 60; the blower can be arranged in the air inlet casing, and the heating heat exchanger and the cooling heat exchanger can be arranged in the middle casing; the blower can be an axial radial blower, The axial radial flow blower may also include a fan casing 21, which may include a fan front casing 211 and a fan rear casing 212 that are connected to each other; the fan front casing 211 may be provided with an air inlet parallel or coincident with the axis of the centrifugal impeller 213, the fan rear casing 212 can be provided with an air outlet 214 that is parallel or coincident with the axis of the centrifugal impeller; the fan front casing 211 and the fan rear casing 212 can be opposite An installation cavity is formed, and the motor and centrifugal impeller can be installed in the installation cavity.

In this embodiment, the blower can be an axial radial blower. The rotation of the motor 23 drives the centrifugal impeller 20 to rotate. The gas enters the centrifugal impeller 22 from the air inlet 213, and the blades of the centrifugal impeller 20 throw the gas from the radial direction of the centrifugal impeller 20 to the blower. In the casing 21, the gas is discharged from the air outlet 214 under the blocking of the inner wall of the fan casing 210, so as to realize the axial air inlet and the axial air outlet, and the gas flows axially and radially.

The axial-radial flow blower in this embodiment can realize axial air inlet and axial air outlet. Compared with axial air inlet and radial air outlet, the blower provided in this embodiment can improve aerodynamic efficiency, so that the output of the air conditioner can be improved. The wind efficiency is high; and the axial radial flow blower provided in this embodiment can discharge air axially, so that it is possible to avoid setting a flow guide structure in the casing, so that the structure of the air conditioner can be simple, the parts and components are small, and the occupied space is small. Makes the overall structure compact. Although the axial radial flow blower includes a fan casing arranged outside the centrifugal impeller, the fan casing can only play the role of changing the gas flow direction and guiding the gas, and it is not necessary to set the same structure as the casing of the volute type blower. The volume is still much smaller than that of a volute blower.

Optionally, both the windward surface of the cooling heat exchanger and the windward surface of the heating heat exchanger intersect with the axial direction of the axial-radial blower, for example: vertical.

As shown in FIG. 6 , on the basis of the above embodiment, optionally, the side wall of the refrigeration heat exchanger is in contact with the inner wall of the intermediate casing, and the side wall of the heating heat exchanger is in contact with the inner wall of the intermediate casing.

In this embodiment, the axial radial flow blower can achieve axial air outlet, and both the side wall of the cooling heat exchanger and the side wall of the heating heat exchanger can be arranged in contact with the inner wall of the intermediate shell, that is, it can be understood as zero Interval setting (zero interval is not absolute, installation error cannot be excluded), which can make the structure of the air conditioner more compact and the volume smaller.

As shown in FIG. 6 , on the basis of the above-mentioned embodiment, optionally, the air conditioner may further include an air filter 150, and the air filter 150 may be arranged on the side of the axial radial blower away from the main air inlet; the air filter 150 The side wall of the can be in contact with the inner wall of the intermediate housing. In this embodiment, the air filter is arranged after the axial radial blower and before the heating heat exchanger and the cooling heat exchanger. The air filter can filter the gas entering the air conditioner to prevent impurities from affecting the subsequent cooling and heat exchange. Heaters and heating heat exchangers are affected.

As shown in FIG. 11 , on the basis of the above-mentioned embodiment, optionally, a plurality of race-rotating vanes 215 may be provided at the air outlet 214 , and the middle of the race-rotating vane 215 is convex (that is, the middle of the race-rotating vane is relatively A plurality of race-rotating vanes 215 are arranged at intervals along the circumferential direction of the air outlet 214, and the setting direction of the plurality of race-rotating vanes 215 is the same as the rotation direction of the centrifugal impeller 20, it can be understood Therefore, when the rotation direction of the centrifugal impeller 20 is clockwise, the plurality of race-rotating blades 215 are arranged at intervals in the clockwise direction (the middle parts of the plurality of race-rotating blades 215 are all convex in the counter-clockwise direction), and when the rotation direction of the centrifugal impeller 20 is clockwise When it is counterclockwise, the plurality of race-rotating vanes 215 are arranged at intervals in the counter-clockwise direction (the middle portions of the plurality of race-rotating vanes 215 are all convex in the clockwise direction).

In this embodiment, a plurality of derotational blades 215 are arranged at the air outlet 214, and the arrangement direction of the plurality of derotational blades 215 is set 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 loss. On the other hand, the wind can flow more uniformly, thereby improving the aerodynamic efficiency and increasing the uniformity of the air outlet. As shown in FIG. 8 , which is a schematic diagram of the effect of simulating the 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 blower under the action of the race-rotating blades, and the race-rotating blades can flow to the middle of the blower. Guide the wind at the edge to the middle to prevent the gas from being scattered at the edge of the air outlet, thereby improving the aerodynamic efficiency and the uniformity of the air outlet.

Wherein, the racemic blade 215 may include sequentially 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 215 .

As an optional solution, as shown in FIG. 11 , the race-rotating blades 215 are arranged in an arc shape, that is, the surfaces of the race-rotating vanes 215 are smooth without corners and are streamlined. The fluid resistance of the race-rotating vanes 215 is small, which is more conducive to Guiding the wind reduces rotational speed, reduces energy loss, and makes the wind flow more evenly.

Wherein, the number of race-rotating blades 215 can be set according to specific needs, for example, the number of race-rotating vanes 215 is 9-27 (for example: 9, 10, 13, 16, 18, 20, 22, 25 or 27, etc.) .

As shown in FIG. 11 , on the basis of the above embodiment, optionally, the inlet angle β of the raceway blade 215 may be 55°˜67° (for example: 55°, 57°, 60°, 61°, 63° , 65° or 67°, etc.), the outlet angle θ of the racemic blade 215 can be 90°-93° (for example: 90°, 90.5°, 91°, 91.5°, 92°, 92.5° or 93°, etc.), The inlet angle β of the race-rotating blade 215 is set at 55°-67°, and the outlet angle θ thereof is set at 90°-93°, which is more conducive to improving the start-up efficiency and the uniformity of the gas outlet.

As shown in FIG. 11 , on the basis of the above embodiment, optionally, the air outlet 214 may be arranged in a ring shape, and the air outlet 214 may be arranged at the edge of the rear casing 212 of the fan. In this embodiment, the air outlet 214 can be disposed at the edge of the rear casing 212 of the fan, so that it can be disposed closer to the peripheral side of the centrifugal impeller 20, thereby improving the air outlet efficiency.

One end of the de-rotating blade 215 may be fixed on one side of the air outlet 214 , and the other end of the de-rotating blade 215 may be fixed on the other side of the air outlet 214 .

As an optional solution, as shown in FIG. 11 , on the basis of the above-mentioned embodiment, optionally, one end of the raceway blade 215 may be fixed at a position of the fan rear casing 212 close to the center of the fan rear casing 212 . , the other end of the de-rotating blade 215 can go over the air outlet 214 to be fixed on the rear casing 212 of the fan. The fixing method of the derotational vanes 215 in this embodiment facilitates the integral molding of the rear casing 212 of the fan, thereby improving the production efficiency.

As shown in FIG. 7 and FIG. 8 , specifically, the installation cavity may include an impeller installation cavity and a motor installation cavity 2122 ; the fan rear housing 212 may include an outer cover body 2121 and an installation groove provided on the inner side of the outer cover body 2121 , and the air outlet 214 It can be arranged on the outer cover body 2121, and the installation groove forms a motor installation cavity 2122; the outer cover body 2121 can be connected with the fan front casing 211, and an impeller installation cavity can be formed between the inner wall of the outer casing body 2121 and the inner wall of the fan front casing 211; the impeller The inner wall of the installation cavity can be used to form an air flow channel 24 with the impeller.

The air flow channel 40 may include an arc guide portion 241 . The arc guide portion 241 is convex in a direction away from the centrifugal impeller 20 , and one side of the arc guide portion 241 is close to the air inlet 213 and faces the air outlet of the centrifugal impeller 20 . The other side of the arc guide portion 241 is arranged close to the air outlet 214 .

In this embodiment, the arc guide portion 241 can be surrounded by the side of the centrifugal impeller 20, the middle portion of the arc guide portion 241 is far away from the centrifugal impeller 20, and the two sides of the arc guide portion 241 are close to the centrifugal impeller 20, then The air flow channel 40 is set at the side of the centrifugal impeller 20 by turning, so that a labyrinth structure can be formed. The air outlet side of the impeller 20 is arranged oppositely), the side part of the arc guide part 241 guides the gas to the other side of the arc guide part 241, and then guides the gas to the air outlet 214; the arc guide The labyrinth structure formed by the part 241 can avoid the reverse flow of the gas, 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 fan casing 210 , the front casing 211 of the fan can be set at least close to the rear casing 212 of the fan. The inner wall part of the fan is arc-shaped, and the inner wall part of the fan front casing 211 forms half of the arc guide part 241. Similarly, the inner wall of the fan rear casing 212 at least close to the fan front casing 211 is arc-shaped. The inner wall part of the rear casing forms half of the arc guide part 241. After connecting the fan front casing 211 and the fan rear casing 212, the inner wall of the fan front casing 211 is close to the fan rear casing 212. Part of the inner wall of the fan rear casing 212 close to the fan front casing 211 is spliced together to form a circular arc guide portion 241 .

The radius of the arc guide portion 241 may be set according to specific conditions. Optionally, the arc radius of the arc guide portion 241 is 10mm-40mm, for example: 10mm, 15mm, 20mm, 25mm, 30mm, 35mm, or 40mm.

As shown in FIG. 8 , on the basis of the above embodiment, optionally, the edge of the air inlet 213 can be provided with a front containing groove 2111 , the centrifugal impeller 20 can be provided with a front connecting plate 221 , and the front connecting plate 221 can be inserted In the front containing groove 2111. In this embodiment, the air inlet side of the centrifugal impeller 20 extends out of the air inlet 213 of the front housing 211 of the fan, and the front connecting plate is inserted into the front housing groove 2111, which improves the efficiency of the centrifugal impeller 20 and the front housing 211 of the fan. The tightness between them can reduce gas leakage, thereby improving the air outlet efficiency of the gas.

The cross-sectional shape of the front containing groove 2111 may be V-shaped or W-shaped, and the optional cross-sectional shape of the front containing groove 2111 is U-shaped, which is simple in structure and easy to manufacture.

Optionally, the distance h1 between the top of the front connecting plate 221 and the bottom of the front containing groove 2111 is 4mm-6mm (for example: 4mm, 4.5mm, 5mm, 5.5mm or 6mm, etc.), and the side of the front connecting plate 221 The shortest distance h2 from the side of the front containing groove 2111 is 4mm-6mm (for example: 4mm, 4.3mm, 4.6mm, 5mm, 5.4mm, 5.8mm or 6mm), this setting can play a better role on the one hand. The sealing effect, on the other hand, can prevent the volume of the front containing groove 2111 from being too large.

As shown in FIG. 8 , on the basis of the above-mentioned embodiment, optionally, the blower may further include a middle cover plate 216; the inner side of the outer cover body 2121 may be provided with a groove (which can reduce weight and facilitate the rear casing of the blower). body 212 is formed), the middle cover plate 216 is connected with the outer cover body 2121 (for example, by welding, glue connection, interference connection or welding, etc.) to cover the groove (to avoid gas stagnation in the groove and affect the air outlet), the middle The cover plate 216 is provided with a connecting hole for passing through the motor 30 , the edge of the connecting hole is provided with a rear containing groove 2161 , the centrifugal impeller 20 is provided with a rear connecting plate 222 , and the rear connecting plate 222 is inserted into the rear containing groove 2161 .

In this embodiment, the rear side connecting plate can be inserted in the rear containing groove 2161, which improves the sealing between the centrifugal impeller 20 and the middle cover plate 216, reduces gas leakage, and further improves the air outlet efficiency.

The cross-sectional shape of the rear containing groove 2161 may be V-shaped or W-shaped, and the optional cross-sectional shape of the rear containing groove 2161 is U-shaped, which is simple in structure and easy to manufacture.

Optionally, the distance h1 between the top of the rear connecting plate 222 and the bottom of the rear accommodating groove 2161 may be 4mm-6mm (for example: 4mm, 4.5mm, 5mm, 5.5mm or 6mm, etc.), and the side of the rear connecting plate 222 The shortest distance h2 between the outer part and the side part of the rear containing groove 2161 can be 4mm-6mm (for example: 4mm, 4.3mm, 4.6mm, 5mm, 5.4mm, 5.8mm or 6mm), this setting can on the one hand play a more Good sealing effect, on the other hand, can prevent the volume of the rear containing groove 2161 from being too large.

As shown in FIG. 15 to FIG. 19 , on the basis of the above embodiment, optionally, the centrifugal impeller may include a cover plate 223 , a blade 224 and a hub 225 that are fixedly connected in sequence, so that the blades are in the axial direction of the hub 225 . 224 is located between the cover plate 223 and the hub 225, the cover plate is provided with an opening for air circulation, the front connecting plate is arranged on the edge of the opening, and the rear connecting plate is arranged on the side of the hub away from the cover plate; the blades 224 are bent backwards. blade, and blade 224 has a swept portion. A shaft hole 226 for connecting the drive shaft is formed on the hub.

In this embodiment, the centrifugal impeller adopts space-distorted backward-curved blades. After the accelerated air enters the impeller, it has a high degree of fit with the blades 224. The energy added to the airflow in the centrifugal impeller is mainly converted into pressure energy, which ensures efficient Requirements: The swept portion 2241 of the blade 224 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 out radially.

Optionally, the swept angle of the swept portion 2241 may be γ, and 81°≤γ≤86°.

Optionally, the swept angle of the swept portion 2241 may be γ, and γ is 83°.

Optionally, the vane exit angle of vane 224 may be α, and 60°≤α≤70°.

Alternatively, the vane exit angle of vanes 224 may be α, and α is 65°.

The blade may have a tip 2242 and a root 2243. Optionally, the radius of the root 2243 of the blade 224 at the inlet may be _Rh , and the radius of the tip 2242 at the inlet may be _Rs , and _0.35≤Rh / _Rs≤0.4 . The inlet in this embodiment refers to the inlet of the centrifugal impeller.

Alternatively, the radius of the root 2243 of the blade 224 at the inlet may be _Rh , the radius of the tip 2242 at the inlet may be R _s , and _Rh /R _s =0.37.

Optionally, the included angle between the tangential direction of the blade tip profile of the blade 224 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 224 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 can be b ₂ , and b ₂ is calculated by formula (1), and formula (1) is:

b ₂ =Q/(2π×R ₂ ×φ×u ₂ ) (1);

Among them, 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 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 224 at the inlet of the centrifugal impeller may be δ ₁ , where 0.8 mm≦δ ₁ ≦1.5 mm.

Optionally, the thickness of the blades 224 at the inlet of the centrifugal impeller may be δ ₁ , and δ ₁ =1.1 mm.

Optionally, the thickness of the blades 224 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 224 at the outlet of the centrifugal impeller may be δ ₂ , and δ ₂ =1.9 mm.

Optionally, the number of blades 224 may be 19 or 23; the root radius of the blades 224 at the inlet may be 28.8 mm; the tip radius of the blades 224 at the inlet may be 72 mm; the blade angle at the tip of the blades 224 at the inlet It can be 62°, the blade angle at the blade root of the blade 224 at the inlet can be 37°; the outlet width of the centrifugal impeller can be 25mm, the blade angle of the centrifugal impeller outlet can be 65°, and the radius of the centrifugal impeller outlet can be 92.1mm; The axial length may be 40.2mm.

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 blower, the blower may also include a PCB board.

On the basis of any of the above-mentioned embodiments, optionally, as shown in FIG. 1 to FIG. 6 , the total air outlet 60 may include a plurality of mode air outlets, and the mode air doors 130 are arranged in the plurality of mode air outlets, so that the air outlet volume can be controlled .

On the basis of any of the above-mentioned embodiments, optionally, as shown in FIG. 1 to FIG. 6 , the air inlet housing 11 , the intermediate housing 12 and the air distribution housing 13 are provided independently of each other, and one side of the intermediate housing 12 is arranged independently of each other. It is sealingly connected with the air inlet housing 11 , and the other side of the intermediate housing 12 is sealingly connected with the air distribution housing 13 . In this embodiment, the air inlet housing 11 , the intermediate housing 12 and the air distribution housing 13 are arranged independently of each other, which facilitates maintenance or repair of the internal structure of the air conditioner, and can also be replaced separately for the three. The rib-groove sealing structure 140 may be used to connect the intermediate casing 12 to the air inlet casing 11 , and the rib-groove sealing structure 140 may be used to connect the intermediate casing 12 to the air distribution casing 13 .

Alternatively, the air inlet housing 11 , the intermediate housing 12 and the air distribution housing 13 are integrally formed, that is, the casing 10 is integrally formed and has high strength.

It should be noted that, in the embodiment of the present application, “front” refers to the upstream of the overall direction of the air from the air inlet 213 to the air outlet 214 , and “rear” refers to the downstream of the overall direction of the air from the air inlet 213 to the air outlet 214 .

The embodiment of the present application also provides an automobile, which may include a vehicle body and the above-mentioned air conditioning device, and the air conditioning device may be arranged in the vehicle body. All the beneficial technical effects of the invention will not be repeated here.

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 air conditioner and an automobile. The air conditioner comprises: a casing and a blower, a cooling heat exchanger and a heating heat exchanger arranged in the casing; the blower comprises a motor and a centrifugal impeller drivingly connected with the motor, and the motor drives The centrifugal impeller rotates so that the gas enters the centrifugal impeller from the axial direction of the centrifugal impeller and exits the centrifugal impeller from the radial direction of the centrifugal impeller. The air conditioner provided by the present application can achieve a small volume with the same impeller diameter, which is conducive to realizing flattening; under the same volume, the diameter of the impeller of the blower can be larger than that of the traditional volute type fan, so as to achieve greater blowing capacity, so the present application provides The air conditioner can achieve high air outlet efficiency under the same volume.

Furthermore, it will be appreciated that the air conditioners and automobiles of the present application are reproducible and can be used in a variety of industrial applications. For example, the air conditioner and the automobile of the present application can be used in the field of vehicle technology.

Claims

An air conditioner is characterized by comprising: a casing and a blower, a cooling heat exchanger and a heating heat exchanger arranged in the casing; the blower comprises a motor and a centrifugal impeller drivingly connected with the motor , the motor drives the centrifugal impeller to rotate, so that the gas enters the centrifugal impeller from the axial direction of the centrifugal impeller and discharges the centrifugal impeller from the radial direction of the centrifugal impeller.
The air conditioner according to claim 1, wherein the casing comprises an air inlet casing, an intermediate casing and an air distribution casing which are connected in sequence; the refrigeration heat exchanger is arranged in the air inlet casing , the blower and the heating heat exchanger are both connected to the intermediate casing; the air inlet casing is provided with a general air inlet, and the general air inlet is located far from the cooling heat exchanger. One side of the blower; the air distribution housing is provided with a general air outlet.
The air conditioner according to claim 2, wherein the air inlet of the blower is located in the axial direction of the blower and faces the refrigeration heat exchanger, and the air outlet of the blower is located on the diameter of the blower. upward; the intermediate casing is provided with a flow guide structure, the flow guide structure is located at the air outlet of the blower, and the flow guide structure is used to guide the gas flowing out from the air outlet of the blower to the air outlet of the blower. The direction away from the refrigeration heat exchanger.
The air conditioner according to claim 3, wherein the air guide structure is a guide rib; One end far away from the air inlet of the blower is arranged away from the blower.
The air conditioner according to claim 4, characterized in that, the guide ribs are configured to be straight or arc-shaped.
The air conditioner according to claim 4 or 5, characterized in that, the air guide rib is connected and fixed to the intermediate casing by welding, snap connection or screw connection.
The air conditioner according to any one of claims 4 to 6, wherein the air guide rib and the intermediate casing are provided to be integrally formed.
The air-conditioning device according to claim 3, wherein the air guide structure is an air guide pipe, one end of the air guide pipe is provided with an inlet, and the other end of the air guide pipe extends to be close to the heat exchanger. direction of the heater.
The air conditioner according to any one of claims 2 to 8, characterized in that, in the height direction of the heating heat exchanger, one side of the heating heat exchanger and a distance between one side of the heating heat exchanger and the intermediate casing The inner wall is arranged in abutment, and the other side of the heating heat exchanger is arranged in abutment with the inner wall of the casing.
The air conditioner according to any one of claims 2 to 8, characterized in that, in the height direction of the heating heat exchanger, one side of the heating heat exchanger and a distance between one side of the heating heat exchanger and the intermediate casing A space is provided between the inner walls, and the other side of the heating heat exchanger is arranged in abutment with the inner wall of the housing; or, in the height direction of the heating heat exchanger, the heating and heat exchanger A space is provided between one side of the heat exchanger and the inner wall of the intermediate shell, and a space is provided between the other side of the heating heat exchanger and the inner wall of the shell.
The air conditioner according to claim 10, further comprising a guide air door, the guide air door is rotatably connected to the heating heat exchanger; the guide air door, the inner wall of the intermediate casing A cold air channel is formed between the heat exchanger and the heating heat exchanger, and the cold air channel is communicated with the air distribution shell; a hot air channel is formed between the air guide door and the back of the blower, and the hot air channel is connected to the air distribution housing. The heating heat exchanger is in communication.
The air conditioner according to claim 1, wherein the casing comprises an air inlet casing, an intermediate casing and an air distribution casing which are connected in sequence, and the air inlet casing is provided with a general air inlet, so The air distribution housing is provided with a general air outlet; the blower is arranged in the air inlet housing, and the heating heat exchanger and the cooling heat exchanger are arranged in the intermediate housing;

The blower is an axial radial flow blower, and the axial radial flow blower further includes a fan casing, and the fan casing includes a fan front casing and a fan rear casing that are connected to each other; the fan front casing is provided with the centrifugal impeller. The axis of the fan is parallel or coincident with the air inlet, and the rear casing of the fan is provided with an air outlet that is parallel or coincident with the axis of the centrifugal impeller; the front casing of the fan and the rear casing of the fan are oppositely arranged, and the fan An installation cavity is formed between the fan front casing and the fan rear casing, and the motor and the centrifugal impeller are installed in the installation cavity.
The air conditioner according to claim 12, wherein the side wall of the refrigerating heat exchanger is in contact with the inner wall of the intermediate casing, and the side wall of the heating heat exchanger is in contact with the inner wall of the intermediate casing. Inner wall contact.
The air conditioner according to claim 13, characterized in that, the air conditioner further comprises an air filter, and the air filter is arranged on a side of the axial radial blower away from the general air inlet; the air filter The side wall of the device is in contact with the inner wall of the intermediate housing.
The air conditioner according to any one of claims 12 to 14, wherein a plurality of race-rotating vanes are provided at the air outlet, and the middle of the race-rotating vanes is arranged convexly; The rotary vanes are arranged at intervals along the circumferential direction of the air outlet, and the arrangement direction of the plurality of race-rotating vanes is the same as the rotation direction of the centrifugal impeller.
The air conditioner according to claim 15, wherein the inlet angle of the race-rotating vanes is 55°-67°, and the outlet angle of the race-rotating vanes is 90°-93°.
An automobile is characterized by comprising a vehicle body and the air conditioner according to any one of claims 1-16, wherein the air conditioner is arranged in the vehicle body.