Air conditioner and vehicle

Abstract

The present invention relates to the technical field of vehicles, and particularly to an air conditioning device and an automobile. The air conditioning device includes: a housing, a blower, a refrigeration heat exchanger, and a heating heat exchanger disposed within the housing; the blower includes a motor and a centrifugal impeller drivingly connected to the motor, and the motor drives the centrifugal impeller to rotate so that gas enters the centrifugal impeller axially and is discharged from the centrifugal impeller radially. The air conditioning device provided by the present invention can achieve a small volume when the impeller diameter is the same, which is beneficial to achieving flattening; under the same volume, the impeller diameter of the blower can be larger than that of a traditional volute fan, achieving a greater air blowing capacity. Therefore, the air conditioning device provided by the present invention can achieve a high air outlet efficiency under the same volume.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicles, and particularly to an air conditioning device and an automobile. Background Art

[0002] An automotive air conditioning device generally includes a housing and a volute blower, a heat exchanger, etc. disposed within the housing. An air inlet and an air outlet are provided on the housing. The volute blower is disposed relative to the heat exchanger at a position of the housing close to the air inlet. The volute blower mainly includes an impeller, a flange, an end cover, a motor, and a volute, etc. The working principle of the volute blower in the air conditioner is to use the high-speed rotation of the impeller to force the gas to rotate, do work on the gas to increase its energy. Under the action of the centrifugal force, the gas is radially thrown out of the impeller and enters the volute. The cross-sectional area of the volute gradually increases to slow down the air flow. This deceleration effect converts the kinetic energy into pressure energy. The gas is sucked into the interior of the housing of the air conditioning device under the action of the pressure difference, and then after heat exchange to reach the set temperature, it is discharged from the air outlet. The air conditioning device with this structure is large in volume and occupies a large space. Summary of the Invention

[0003] The purpose of the present invention is to provide an air conditioning device and an automobile, so as to solve to a certain extent the technical problem that the existing air conditioning device is large in volume and occupies a large space.

[0004] The present invention provides an air conditioning device, including: a housing and a blower, a refrigeration heat exchanger, and a heating heat exchanger disposed within the housing; the blower includes a motor and a centrifugal impeller drivingly connected to the motor, and the motor drives the centrifugal impeller to rotate so that the gas enters the centrifugal impeller axially from the centrifugal impeller and is discharged radially from the centrifugal impeller.

[0005] Further, the housing includes an air inlet housing, an intermediate housing, and a air distribution housing that are sequentially communicated; the refrigeration heat exchanger is disposed within the air inlet housing, and both the blower and the heating heat exchanger are connected to the intermediate housing; a total air inlet is provided on the air inlet housing, and the total air inlet is located on a side of the refrigeration heat exchanger away from the blower; a total air outlet is provided on the air distribution housing.

[0006] Further, the air inlet of the blower is located axially of the blower and faces the refrigeration heat exchanger, and the air outlet of the blower is located radially of the blower; a flow guiding structure is provided on the intermediate housing, and the flow guiding structure is located at the air outlet of the blower, and the flow guiding structure is used to guide the gas flowing out of the air outlet of the blower in a direction away from the refrigeration heat exchanger of the blower.

[0007] Further, the guiding structure is a guiding rib; one end of the guiding rib close to the air inlet of the blower is arranged close to the blower, and the other end of the guiding rib far from the air inlet of the blower is arranged far from the blower.

[0008] Further, the guiding rib and the middle housing are integrally formed.

[0009] As an alternative, in the height direction of the heating heat exchanger, one side of the heating heat exchanger is in contact with the inner wall of the middle housing, and the other side of the heating heat exchanger is in contact with the inner wall of the housing.

[0010] As an alternative, in the height direction of the heating heat exchanger, there is a gap between one side of the heating heat exchanger and the inner wall of the middle housing, and the other side of the heating heat exchanger is in contact with the inner wall of the housing.

[0011] As an alternative, in the height direction of the heating heat exchanger, there is a gap between one side of the heating heat exchanger and the inner wall of the middle housing, and there is a gap between the other side of the heating heat exchanger and the inner wall of the housing.

[0012] Further, the air-conditioning device further includes a guiding air damper, which is rotatably connected to the heating heat exchanger; a cold air passage is formed between the guiding air damper, the inner wall of the middle housing and the heating heat exchanger, and the cold air passage communicates with the air distribution housing; a hot air passage is formed between the guiding air damper and the back surface of the blower, and the hot air passage communicates with the heating heat exchanger.

[0013] As an alternative, the housing includes an air inlet housing, a middle housing and an air distribution housing that are sequentially connected, a total air inlet is provided on the air inlet housing, and a total air outlet is provided on the air distribution housing; the blower is arranged in the air inlet housing, and the heating heat exchanger and the refrigerating heat exchanger are arranged in the middle housing; the blower is an axial-radial blower, and the axial-radial blower further includes a blower housing, and the blower housing includes a blower front housing and a blower rear housing that are connected to each other; an air inlet parallel or coincident with the axis of the centrifugal impeller is provided on the blower front housing, and an air outlet parallel or coincident with the axis of the centrifugal impeller is provided on the blower rear housing; the blower front housing and the blower rear housing are oppositely arranged, and an installation cavity is formed between the blower front housing and the blower rear housing, and the motor and the centrifugal impeller are installed in the installation cavity.

[0014] Further, the side wall of the refrigerating heat exchanger is in contact with the inner wall of the middle housing, and the side wall of the heating heat exchanger is in contact with the inner wall of the middle housing.

[0015] Further, the air conditioner further includes an air filter, and the air filter is disposed on a side of the axial-radial blower away from the total air inlet; a side wall of the air filter contacts an inner wall of the intermediate housing.

[0016] Further, the air inlet housing, the intermediate housing, and the air distribution housing are independently provided, one side of the intermediate housing is sealingly connected to the air inlet housing, and the other side of the intermediate housing is sealingly connected to the air distribution housing;

[0017] Alternatively, the air inlet housing, the intermediate housing, and the air distribution housing are integrally provided.

[0018] Further, a plurality of anti-rotation vanes are provided at the air outlet, and a middle portion of the anti-rotation vanes protrudes outward; the plurality of anti-rotation vanes are spaced along a circumferential direction of the air outlet, and a setting direction of the plurality of anti-rotation vanes is the same as a rotation direction of the centrifugal impeller.

[0019] Further, an inlet angle of the anti-rotation vanes is 55°-67°, and an outlet angle of the anti-rotation vanes is 90°-93°.

[0020] The present invention provides an automobile, including a vehicle body and the above air conditioner, and the air conditioner is disposed in the vehicle body.

[0021] The present invention provides an air conditioner, including: a housing and a blower, a refrigeration heat exchanger, and a heating heat exchanger disposed in the housing; the blower includes a motor and a centrifugal impeller drivingly connected to the motor, and the motor drives the centrifugal impeller to rotate so that gas enters the centrifugal impeller axially from the centrifugal impeller and is discharged from the centrifugal impeller radially.

[0022] In the air conditioner provided by the present invention, the motor in the blower drives the centrifugal impeller to rotate. By using the high-speed rotation of the impeller, gas is sucked into the blower. The blower does work on the gas to generate a strong centrifugal force. The backward-inclined impeller blades of the centrifugal impeller quickly throw the gas along the radial direction of the centrifugal impeller, so that the gas enters the housing. There is no need to provide a housing with a specific structure in a volute blower. When the impeller diameters are the same, the volume of this blower is small and the occupied space is small. Compared with an air conditioner using a traditional volute blower, the air conditioner provided by the present invention can achieve a small volume when the impeller diameters are the same, which is beneficial to achieving flattening; under the same volume, the impeller diameter of the blower can be larger than that of a traditional volute blower, achieving a greater blowing capacity. Therefore, the air conditioner provided by the present invention can achieve a high air outlet efficiency under the same volume.

[0023] It should be understood that both the foregoing general description and the following detailed description are for purposes of illustration and example only and do not necessarily limit the present disclosure. The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate the subject matter of the present disclosure. At the same time, the specification and the drawings are used to explain the principles of the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following will briefly introduce the drawings required for use in the description of the specific embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings.

[0025] Figure 1 A schematic structural diagram of an air conditioner device according to a first embodiment of the present invention;

[0026] Figure 2 is Figure 1 Another schematic structural diagram of the air conditioner device shown;

[0027] Figure 3 A schematic structural diagram of an air conditioner device according to a second embodiment of the present invention;

[0028] Figure 4 is Figure 3 Another schematic structural diagram of the air conditioner device shown;

[0029] Figure 5 A schematic structural diagram of a third embodiment of the present invention;

[0030] Figure 6 A schematic structural diagram of a fourth embodiment of the present invention;

[0031] Figure 7 is Figure 6 A schematic structural diagram of a blower in the air conditioner device shown;

[0032] Figure 8 is Figure 7 Another schematic structural diagram of the blower shown;

[0033] Figure 9 is Figure 7 A schematic structural diagram of a blower housing in the blower shown;

[0034] Figure 10 is Figure 9 A schematic structural diagram of a front blower housing in the blower housing shown;

[0035] Figure 11 is Figure 9 A schematic structural diagram of a first perspective of a rear blower housing in the blower housing shown;

[0036] Figure 12 For Figure 9 The structural schematic diagram of the second perspective of the blower rear housing in the blower housing shown;

[0037] Figure 13 For Figure 10 The structural schematic diagram of the middle cover plate in the blower housing shown;

[0038] Figure 14 For Figure 7 The schematic diagram of gas flow of the blower shown;

[0039] Figure 15 For Figure 7 The structural schematic diagram of one perspective of the centrifugal impeller in the blower shown;

[0040] Figure 16 For Figure 15 The sectional view of the centrifugal impeller shown;

[0041] Figure 17 For Figure 15 The structural schematic diagram of another perspective of the centrifugal impeller shown;

[0042] Figure 18 For Figure 15 The structural schematic diagram of one perspective of the blades in the centrifugal impeller shown;

[0043] Figure 19 For Figure 15 The structural schematic diagram of another perspective of the blades in the centrifugal impeller shown.

[0044] Icon: 10 - housing; 20 - blower; 30 - refrigeration heat exchanger; 40 - heating heat exchanger; 50 - total air inlet; 60 - total air outlet; 70 - guide rib; 80 - guide air damper; 90 - cold air channel; 100 - hot air channel; 110 - cold air position; 120 - hot air position; 130 - mode air damper; 140 - rib groove sealing structure; 150 - air filter; 11 - air inlet housing; 12 - middle housing; 13 - air distribution housing; 21 - blower housing; 22 - centrifugal impeller; 23 - motor; 24 - air flow channel; 211 - blower front housing; 212 - blower rear housing; 213 - air inlet; 214 - air outlet; 215 - anti-rotation blade; 216 - middle cover plate; 241 - arc-shaped guide part; 2111 - front containment groove; 2121 - outer cover body; 2122 - motor installation cavity; 2161 - rear containment groove; 221 - front connection plate; 222 - rear connection plate; 223 - cover plate; 224 - blade; 225 - hub; 226 - shaft hole; 2241 - forward sweep part; 2242 - blade tip; 2243 - blade root. Specific embodiments

[0045] The technical solution of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are some but not all of the embodiments of the present invention.

[0046] Generally, the components of the embodiments of the present invention described and shown in the drawings here can be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of the present invention provided in the drawings is not intended to limit the scope of the claimed invention, but merely represents selected embodiments of the present invention.

[0047] All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the scope of protection of the present invention.

[0048] In the description of the present invention, it should be noted that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus cannot be construed as a limitation of the present invention.

[0049] As Figures 1 to 4 shown, the present invention provides an air conditioning device, including: a housing 10, and a blower 20, a refrigeration heat exchanger 30, and a heating heat exchanger 40 disposed in the housing 10; the blower includes a motor and a centrifugal impeller drivingly connected to the motor, and the motor drives the centrifugal impeller to rotate so that gas enters the centrifugal impeller axially and is discharged radially from the centrifugal impeller.

[0050] In the air conditioning device provided in this embodiment, the motor in the blower 20 drives the centrifugal impeller to rotate. By using the high-speed rotation of the impeller, gas is sucked into the blower 20. The blower 20 does work on the gas to generate a strong centrifugal force. The backward-inclined impeller blades of the centrifugal impeller quickly eject the gas along the radial direction of the centrifugal impeller, so that the gas enters the intermediate housing 12. There is no need to provide a housing with a specific structure in a volute blower. When the impeller diameters are the same, the volume of this blower is small and it occupies less space. Compared with an air conditioning device using a traditional volute blower, the air conditioning device provided in this embodiment can achieve a small volume when the impeller diameters are the same, which is beneficial to achieving flattening; under the same volume, the impeller diameter of the blower can be larger than that of a traditional volute blower, realizing a greater air blowing capacity. Therefore, the air conditioning device provided in this embodiment can achieve a high air outlet efficiency under the same volume.

[0051] In addition, the diameter of the centrifugal impeller of the blower 20 can be made larger than that of the impeller of a traditional volute centrifugal fan. The maximum diameter of the centrifugal impeller of the blower 20 can be the same height or width as that of the heat exchanger for refrigeration. The larger the diameter of the centrifugal impeller, the greater the air volume of the blower 20. The larger the impeller diameter, the lower the rotational speed for the same air volume. Therefore, this air-conditioning device can achieve a larger air volume and a better NVH (i.e., the three standards of Noise, Vibration, and Harshness) level than a traditional air conditioner.

[0052] As Figures 1 to 4 shown, the housing 10 includes an air inlet housing 11, an intermediate housing 12, and an air distribution housing 13 that are connected in sequence. A total air inlet 50 is provided on the air inlet housing 11, and a total air outlet 60 is provided on the air distribution housing 13. The heating heat exchanger 40 can be disposed in the air inlet housing 11, and the blower 20 and the heating heat exchanger 40 are disposed in the intermediate housing 12.

[0053] Based on the above embodiments, the axial direction of the blower can be intersectingly arranged with the thickness direction of the refrigeration heat exchanger, or the axial direction of the blower can be intersectingly arranged with the thickness direction of the heating heat exchanger.

[0054] Optionally, at least one of the thickness direction of the refrigeration 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 refrigeration heat exchanger 30 and the thickness direction of the heating heat exchanger 40, so as to achieve a flat structure setting of the air-conditioning device, making the structure of the air-conditioning device more compact and occupying less space.

[0055] It should be noted that the thickness direction of the refrigeration heat exchanger 30 is the air inlet direction of the refrigeration heat exchanger 30, the thickness direction of the heating heat exchanger 40 is the air inlet direction of the heating heat exchanger 40, and the air inlet direction of the blower is in the same direction as the axial direction of the blower 20. At least one of the thickness direction of the refrigeration 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: It can be that the axial direction of the blower 20 is in the same direction as the thickness direction of the refrigeration heat exchanger 30, that is, the air inlet direction of the blower 20 is in the same direction as the air inlet direction of the refrigeration heat exchanger 30; it can also be that the axial direction of the blower 20 is in the same direction as the thickness direction of the heating heat exchanger 40, that is, the air inlet direction of the blower 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 both in the same direction as the thickness direction of the refrigeration heat exchanger 30 and in the same direction as the thickness direction of the heating heat exchanger 40, that is, the air inlet direction of the refrigeration heat exchanger 30, the air inlet direction of the blower 20, and the air inlet direction of the heating heat exchanger 40 are in the same direction.

[0056] The number of the heating heat exchanger 40 may be one, or two, three, four, etc.

[0057] As an alternative, the refrigerating heat exchanger 30 is disposed in the air inlet housing 11, and both the blower 20 and the heating heat exchanger 40 are connected to the intermediate housing 12; the total air inlet 50 is located on the side of the refrigerating heat exchanger 30 away from the blower 20.

[0058] In this embodiment, the blower 20 and the heating heat exchanger 40 are integrated in the intermediate housing 12. The heat generated by the motor of the blower 20 during operation can exchange heat with the gas in the intermediate housing 12, and can cooperate with the heating heat exchanger 40 to heat the gas, thereby realizing the utilization of the waste heat of the motor of the blower 20 and reducing energy consumption. Different air inlet structures and air distribution structures can also be configured to improve the practicability of the air-conditioning device.

[0059] By adjusting the internal and external air switching damper (not shown), the total air inlet 50 of the housing 10 can be communicated with the air inside or outside the vehicle. 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 the air sucked by the blower 20 is cold air; when the refrigerating heat exchanger stops heat exchange operation, the air coming out from the air outlet surface of the refrigerating heat exchanger is the ambient air inside or outside the vehicle, so the air sucked by the blower 20 is ambient air.

[0060] As Figures 1 to 4 As shown, on the basis of the above embodiment, further, the air inlet of the blower 20 is located on the axial direction of the blower 20 and faces the refrigerating heat exchanger 30, and the air outlet of the blower 20 is located on the radial direction of the blower 20; a flow guiding structure is provided on the intermediate housing 12, and the flow guiding structure is located at the air outlet of the blower 20, and the flow guiding structure is used to guide the gas flowing out from the air outlet of the blower 20 to the direction away from the refrigerating heat exchanger 30 of the blower 20.

[0061] In this embodiment, the gas is thrown out by the impeller blades of the blower 20 to the inner wall of the intermediate housing 12, and a flow guiding structure is provided at the position of the intermediate housing 12 corresponding to the air outlet of the blower 20. The flow guiding structure can guide the gas from the air outlet of the blower 20 to the direction away from the refrigerating heat exchanger 30 of the blower 20, and the flow guiding structure enables the gas to flow backward of the blower 20, thereby facilitating the gas to flow to the air distribution housing 13.

[0062] Among them, the structural form of the flow guiding structure can be various. For example: the flow guiding structure is a duct, one end of the duct is provided with an inlet, and the other end of the duct extends in the direction close to the heating heat exchanger 40.

[0063] As an alternative, the flow guiding structure is a flow guiding rib 70; one end of the flow guiding rib 70 close to the air inlet of the blower 20 is arranged closer to the blower 20 than the other end of the flow guiding rib 70 far from the air inlet of the blower 20. That is, one end of the flow guiding rib 70 close to the air inlet of the blower 20 is arranged close to the blower 20, and the other end of the flow guiding rib far from the air inlet of the blower is arranged far from the blower. It can also be understood that the flow guiding rib 70 is arranged obliquely. In the radial direction of the blower 20, one end of the flow guiding rib 70 close to the refrigeration heat exchanger 30 is arranged lower than one end of the flow guiding member close to the heating heat exchanger 40. The flow guiding rib 70 blocks the direction in which the gas flows towards the refrigeration heat exchanger 30, thereby guiding the gas towards the heating heat exchanger 40. The flow guiding structure of this kind of structure is simple and easy to process.

[0064] Among them, the flow guiding rib 70 can be arranged in a straight plate shape. Optionally, the flow guiding rib 70 is arranged in an arc shape.

[0065] The flow guiding rib 70 can be connected and fixed to the middle housing 12 by welding, clamping or screw connection.

[0066] Optionally, the flow guiding rib 70 and the middle housing 12 are integrally formed. That is, both ends of the middle housing 12 are open. Among them, the first opening is communicated with the air inlet housing 11, and the second opening is communicated with the air distribution housing 13. The flow guiding rib 70 is formed at a position of the middle housing 12 close to the first opening. Optionally, the first opening of the middle housing 12 is arranged in a circular ring shape to be adapted to the air inlet of the blower 20.

[0067] As Figure 5 shown, on the basis of the above-mentioned embodiment, further, in the height direction of the heating heat exchanger, one side of the heating heat exchanger is abutted against the inner wall of the middle housing, and the other side of the heating heat exchanger is abutted against the inner wall of the housing. In this embodiment, all the air coming out of the blower passes through the heating heat exchanger and then enters the air distribution housing.

[0068] As Figures 1 to 5 shown, the air conditioning device further includes a flow guiding air door 80. The flow guiding air door 80 is rotatably connected to the heating heat exchanger 40; a cold air channel 90 is formed among the flow guiding air door 80, the inner wall of the middle housing 12 and the heating heat exchanger 40. The cold air channel 90 is communicated with the air distribution housing 13; a hot air channel 100 is formed between the flow guiding air door 80 and the back surface of the blower. The hot air channel 100 is communicated with the heating heat exchanger 40.

[0069] In this embodiment, when the refrigeration heat exchanger 30 works and the heating heat exchanger 40 does not need to work, the diversion air door 80 can be rotated to abut against the back surface of the blower 20 (i.e., the flange of the blower 20). The position of the diversion air door 80 at this time can be defined as the cold air position 110. At this time, the cold air passage 90 is completely opened and the hot air passage 100 is closed. The gas coming out of the blower 20 can directly enter the rear air distribution housing 13 through the cold air passage 90 and then be discharged from the main air outlet 60. When the refrigeration heat exchanger 30 does not work and the heating heat exchanger 40 works, the diversion air door 80 can be rotated to abut against the inner wall of the middle housing 12. The position of the diversion air door 80 at this time can be defined as the hot air position 120. At this time, the hot air passage 100 is completely opened and the cold air passage 90 is closed. The gas coming out of the blower 20 can enter the heating heat exchanger 40 through the hot air passage 100, thereby completing the gas heating. When the diversion air door 80 is located between the cold air position and the warm air position, both the cold air passage 90 and the hot air passage 100 are opened. A part of the cold air coming out of the blower 20 enters the air distribution housing 13 through the cold air passage 90, and the other part enters the heating heat exchanger 40 through the hot air passage 100. The hot air coming out of the heating heat exchanger 40 also enters the air distribution box. The cold air and the hot air are mixed in the air distribution housing and then discharged from the main air outlet 60.

[0070] As Figure 1 and Figure 2 shown, in the height direction of the heating heat exchanger 40, there is a gap between one side of the heating heat exchanger 40 and the inner wall of the middle housing 12, and the other side of the heating heat exchanger 40 is in contact with the inner wall of the housing. In this embodiment, the diversion ribs 70 and the diversion air door 80 can be provided only on the upper part of the middle housing 12.

[0071] As Figure 3 and Figure 4 shown, in the height direction of the heating heat exchanger 40, there is a gap between one side of the heating heat exchanger 40 and the inner wall of the middle housing 12, and there is a gap between the other side of the heating heat exchanger 40 and the inner wall of the housing. In this embodiment, the diversion ribs 70 and the diversion air door 80 are provided on both the upper part and the lower part of the middle housing 12.

[0072] As an alternative, as Figures 6 to 19As shown in the figure, the housing includes an air inlet housing 11, an intermediate housing 12, and an air distribution housing 13 that are connected in sequence. A total air inlet 50 is provided on the air inlet housing 11, and a total air outlet 60 is provided on the air distribution housing. 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 blower, and the axial-radial blower further includes a blower housing 21, and the blower housing 21 includes a blower front housing 211 and a blower rear housing 212 that are connected to each other. An air inlet 213 parallel or coincident with the axis of the centrifugal impeller is provided on the blower front housing 211, and an air outlet 214 parallel or coincident with the axis of the centrifugal impeller is provided on the blower rear housing 212. The blower front housing 211 and the blower rear housing 212 are arranged opposite to each other, and an installation cavity is formed between the blower front housing and the blower rear housing. The motor and the centrifugal impeller are installed in the installation cavity.

[0073] In this embodiment, the blower is an axial-radial blower. The motor 23 rotates to drive the centrifugal impeller 20 to rotate. Gas enters the centrifugal impeller 22 from the air inlet 213. The blades of the centrifugal impeller 20 throw the gas radially out of the centrifugal impeller 20 into the blower housing 21. Blocked by the inner wall of the blower housing 210, the gas is discharged from the air outlet 214, thereby realizing axial air inlet and axial air outlet, and the gas flows axially and radially.

[0074] The axial-radial 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 the pneumatic efficiency, thereby making the air outlet efficiency of the air conditioning device high. Moreover, the axial-radial blower provided in this embodiment can blow air axially, so that a flow guiding structure can be avoided being arranged inside the housing, thereby making the structure of the air conditioning device simple, with fewer components, less occupied space, and a compact overall structure. Although the axial-radial blower includes a blower housing arranged outside the centrifugal impeller, the blower housing only needs to play the role of changing the gas flow direction and guiding the gas, and there is no need to set a structure like the housing of a volute blower. The volume of the axial-radial blower is still much smaller than that of the volute blower.

[0075] Optionally, the windward surface of the cooling heat exchanger and the windward surface of the heating heat exchanger both intersect with the axis of the axial-radial blower, for example: perpendicular.

[0076] As Figure 6 As shown in the figure, on the basis of the above embodiment, further, the side wall of the cooling heat exchanger is in contact with the inner wall of the intermediate housing, and the side wall of the heating heat exchanger is in contact with the inner wall of the intermediate housing.

[0077] In this embodiment, the axial-radial flow blower can achieve axial air outlet. Therefore, it can be set that the side walls of the refrigerating heat exchanger and the heating heat exchanger are both in contact with the inner wall of the intermediate housing, that is, it can be understood as a zero-gap setting (the zero-gap is not absolute, and installation errors cannot be excluded). In this way, the structure of the air-conditioning device can be made more compact and the volume can be smaller.

[0078] As Figure 6 shown, on the basis of the above embodiment, further, the air-conditioning device further includes an air filter 150, and the air filter 150 is arranged on the side of the axial-radial flow blower away from the total air inlet; the side wall of the air filter 150 is in contact with the inner wall of the intermediate housing. In this embodiment, the air filter is arranged behind the axial-radial flow blower and in front of the heating heat exchanger and the refrigerating heat exchanger. The air filter can filter the gas entering the air-conditioning device to avoid impurities from affecting the subsequent refrigerating heat exchanger and heating heat exchanger.

[0079] As Figure 11 shown, on the basis of the above embodiment, further, a plurality of anti-rotation vanes 215 are arranged at the air outlet 214, and the middle part of the anti-rotation vanes 215 protrudes outward (that is, the middle part of the anti-rotation vanes protrudes compared with the end part of the anti-rotation vanes); the plurality of anti-rotation vanes 215 are arranged at intervals along the circumferential direction of the air outlet 214, and the arrangement direction of the plurality of anti-rotation vanes 215 is the same as the rotation direction of the centrifugal impeller 20. It can be understood that when the rotation direction of the centrifugal impeller 20 is clockwise, the plurality of anti-rotation vanes 215 are arranged at intervals clockwise (the middle parts of the plurality of anti-rotation vanes 215 protrude in the counterclockwise direction), and when the rotation direction of the centrifugal impeller 20 is counterclockwise, the plurality of anti-rotation vanes 215 are arranged at intervals counterclockwise (the middle parts of the plurality of anti-rotation vanes 215 protrude in the clockwise direction).

[0080] In this embodiment, a plurality of anti-rotation vanes 215 are arranged at the air outlet 214, and the arrangement direction of the plurality of anti-rotation vanes 215 is the same as the rotation direction of the centrifugal impeller 20. On the one hand, it guides the air to reduce the rotation speed and reduce the energy loss. On the other hand, it can make the air flow more evenly, so as to improve the aerodynamic efficiency and increase the air outlet uniformity of the gas. As Figure 8 shown, it is a schematic diagram of the simulation effect of the blower provided in this embodiment. It can be seen that the gas thrown to the edge by the centrifugal impeller can flow towards the middle of the blower under the action of the anti-rotation vanes. The anti-rotation vanes can guide the air at the edge towards the middle, avoiding the gas from scattering at the edge of the air outlet, thereby improving the aerodynamic efficiency and the air outlet uniformity.

[0081] Among them, the anti-rotation vanes 215 can include blade segments connected in sequence, and there are corners formed between adjacent two blade segments. The plurality of blade segments are connected in sequence to form an arched anti-rotation vane 215.

[0082] As an alternative, as Figure 11 shown, the swirl blade 215 is arranged in an arc shape, that is, the surface of the swirl blade 215 is smooth without corners and is streamlined. This kind of swirl blade 215 has small fluid resistance, which is more conducive to guiding the wind to reduce the rotation speed, reduce energy loss, and make the wind flow more evenly.

[0083] Among them, the number of the swirl blades 215 can be set according to specific needs. For example, the number of the swirl blades 215 is 9 - 27 (such as: 9, 10, 13, 16, 18, 20, 22, 25 or 27, etc.) pieces.

[0084] As Figure 11 shown, on the basis of the above - mentioned embodiment, further, the inlet angle β of the swirl blade 215 is 55° - 67° (such as: 55°, 57°, 60°, 61°, 63°, 65° or 67°, etc.), and the outlet angle θ of the swirl blade 215 is 90° - 93° (such as: 90°, 90.5°, 91°, 91.5°, 92°, 92.5° or 93°, etc.). The inlet angle β of the swirl blade 215 is set to 55° - 67°, and at the same time, its outlet angle θ is set to 90° - 93°, which is more conducive to improving the starting efficiency and the air - outlet uniformity of the gas.

[0085] As Figure 11 shown, on the basis of the above - mentioned embodiment, further, the air outlet 214 is arranged in a ring shape, and the air outlet 214 is arranged at the edge of the fan rear housing 212. In this embodiment, the air outlet 214 is arranged at the edge of the fan rear housing 212, and it can be closer to the circumferential side of the centrifugal impeller 20, so as to improve the air - outlet efficiency.

[0086] Among them, one end of the swirl blade 215 can be fixed on one side of the air outlet 214, and the other end of the swirl blade 215 is fixed on the other side of the air outlet 214.

[0087] As an alternative, as Figure 11 shown, on the basis of the above - mentioned embodiment, further, one end of the swirl blade 215 is fixed at a position close to the center of the fan rear housing 212, and the other end of the swirl blade 215 passes over the air outlet 214 to be fixed on the fan rear housing 212. The fixing method of the swirl blade 215 in this embodiment is convenient for the integral molding of the fan rear housing 212, thereby improving the production efficiency.

[0088] As Figure 7 and Figure 8As shown in the figure, specifically, the installation cavity includes an impeller installation cavity and a motor installation cavity 2122; the rear housing 212 of the blower includes an outer housing 2121 and an installation groove provided on the inner side of the outer housing 2121. The air outlet 214 is provided on the outer housing 2121, and the installation groove forms the motor installation cavity 2122; the outer housing 2121 is connected to the front housing 211 of the blower, and an impeller installation cavity is formed between the inner wall of the outer housing 2121 and the inner wall of the front housing 211 of the blower; the inner wall of the impeller installation cavity is used to form an air flow passage 24 with the impeller.

[0089] Among them, the air flow passage 40 includes an arc-shaped diversion part 241. The arc-shaped diversion part 241 protrudes in a direction away from the centrifugal impeller 20. One side of the arc-shaped diversion part 241 is close to the air inlet 213 and is arranged facing the air outlet side of the centrifugal impeller 20, and the other side of the arc-shaped diversion part 241 is close to the air outlet 214.

[0090] In this embodiment, the arc-shaped diversion part 241 surrounds the side of the centrifugal impeller 20. The middle part of the arc-shaped diversion part 241 is far from the centrifugal impeller 20, and both sides of the arc-shaped diversion part 241 are close to the centrifugal impeller 20. Then the air flow passage 40 is bent at the position on the side of the centrifugal impeller 20, so as to form a labyrinth structure. When the gas is radially ejected from the centrifugal impeller 20, the gas reaches one side of the arc-shaped diversion part 241 (this side is arranged opposite to the air outlet side of the centrifugal impeller 20). This side part of the arc-shaped diversion part 241 diverts the gas to the other side of the arc-shaped diversion part 241, and then guides the gas to the air outlet 214; the labyrinth structure formed by the arc-shaped diversion part 241 can prevent gas backflow, thereby improving the air outlet efficiency.

[0091] Since both sides of the arc-shaped flow passage part are closer to the centrifugal impeller 20 than the middle part, in order to be able to assemble the motor 30 and the centrifugal impeller into the installation cavity of the blower housing 210, at least the inner wall part of the front housing 211 of the blower close to the rear housing 212 of the blower can be set to be arc-shaped. This inner wall part of the front housing 211 of the blower forms half of the arc-shaped diversion part 241. Similarly, at least the inner part of the rear housing 212 of the blower close to the front housing 211 of the blower is set to be arc-shaped. This inner wall part of the rear housing forms half of the arc-shaped diversion part 241. After connecting the front housing 211 of the blower and the rear housing 212 of the blower, the inner wall part of the front housing 211 of the blower close to the rear housing 212 of the blower and the inner wall part of the rear housing 212 of the blower close to the front housing 211 of the blower are spliced to form the arc-shaped diversion part 241.

[0092] Among them, the radius of the arc-shaped diversion part 241 can be set according to specific conditions. Optionally, the arc radius of the arc-shaped diversion part 241 is 10 mm - 40 mm, for example: 10 mm, 15 mm, 20 mm, 25 mm, 30 mm, 35 mm or 40 mm, etc.

[0093] Such as Figure 8As shown, on the basis of the above embodiments, further, a front containment groove 2111 is provided at the edge of the air inlet 213, and a front connection plate 221 is provided on the centrifugal impeller 20. The front connection plate 221 is inserted into the front containment 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 blower, and the front-side connection plug is inserted into the front containment groove 2111, improving the sealing performance between the centrifugal impeller 20 and the front housing 211 of the blower, reducing gas leakage, and thus improving the air outlet efficiency of the gas.

[0094] Among them, the cross-sectional shape of the front containment groove 2111 can be V-shaped or W-shaped, etc. Optionally, the cross-sectional shape of the front containment groove 2111 is U-shaped, with a simple structure and easy to process and manufacture.

[0095] Optionally, the distance h1 between the top end of the front connection plate 221 and the bottom of the front containment groove 2111 is 4 mm - 6 mm (for example: 4 mm, 4.5 mm, 5 mm, 5.5 mm or 6 mm, etc.), and the shortest distance h2 between the side of the front connection plate 221 and the side of the front containment groove 2111 is 4 mm - 6 mm (for example: 4 mm, 4.3 mm, 4.6 mm, 5 mm, 5.4 mm, 5.8 mm or 6 mm). Such a setting can, on the one hand, play a good sealing role, and on the other hand, avoid the front containment groove 2111 being too large in volume.

[0096] As Figure 8 As shown, on the basis of the above embodiments, further, the blower further includes an intermediate cover plate 216; a groove is provided on the inner side of the outer cover 2121 (which can play a role in weight reduction and also facilitate the molding of the rear housing 212 of the blower). The intermediate cover plate 216 is connected to the outer cover 2121 (such as by welding, adhesive connection, interference connection or welding, etc.) to cover the groove (to prevent gas from staying in the groove and affecting the air outlet). A connection hole for passing through the motor 30 is provided on the intermediate cover plate 216, and a rear containment groove 2161 is provided at the edge of the connection hole. A rear connection plate 222 is provided on the centrifugal impeller 20, and the rear connection plate 222 is inserted into the rear containment groove 2161.

[0097] In this embodiment, the rear-side connection plug is inserted into the rear containment groove 2161, improving the sealing performance between the centrifugal impeller 20 and the intermediate cover plate 216, reducing gas leakage, and thus further improving the air outlet efficiency of the gas.

[0098] Among them, the cross-sectional shape of the rear containment groove 2161 can be V-shaped or W-shaped, etc. Optionally, the cross-sectional shape of the rear containment groove 2161 is U-shaped, with a simple structure and easy to process and manufacture.

[0099] Optionally, the distance h1 between the top end of the rear connecting plate 222 and the bottom of the rear receiving groove 2161 is 4 mm - 6 mm (for example: 4 mm, 4.5 mm, 5 mm, 5.5 mm or 6 mm, etc.), and the shortest distance h2 between the side of the rear connecting plate 222 and the side of the rear receiving groove 2161 is 4 mm - 6 mm (for example: 4 mm, 4.3 mm, 4.6 mm, 5 mm, 5.4 mm, 5.8 mm or 6 mm). Such a setting can, on the one hand, achieve a better sealing effect, and on the other hand, avoid the rear receiving groove 2161 from being too large in volume.

[0100] As Figures 15 to 19 shown, on the basis of the above embodiment, further, the centrifugal impeller includes a cover plate 223, blades 224 and a hub 225 that are fixedly connected in sequence, so that the blades 224 are located between the cover plate 223 and the hub 225 in the axial direction of the hub 225. The cover plate is provided with an opening for air flow, the front connecting plate is arranged at 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 backward curved blades, and the blades 224 have a swept-forward part. An axial hole 226 for connecting the drive shaft is formed on the hub.

[0101] In this embodiment, the centrifugal impeller adopts backward curved blades with spatial twist. After the accelerated air enters the impeller, it fits well with the blades 224. The energy added to the air flow in the centrifugal impeller is mainly converted into pressure energy, ensuring the requirement of high efficiency; the swept-forward part 2241 of the blades 224 at the inlet is beneficial to reducing the aerodynamic noise generated after the air flow impacts the centrifugal impeller.

[0102] Optionally, the centrifugal impeller is an axial-radial flow closed centrifugal impeller that guides the air flow to enter axially and flow out radially.

[0103] Optionally, the swept-forward inclination angle of the swept-forward part 2241 is γ, and 81° ≤ γ ≤ 86°.

[0104] Optionally, the swept-forward inclination angle of the swept-forward part 2241 is γ, and γ is 83°.

[0105] Optionally, the blade outlet angle of the blades 224 is α, and 60° ≤ β ≤ 70°.

[0106] Optionally, the blade outlet angle of the blades 224 is α, and α is 65°.

[0107] The blade has a blade tip 2242 and a blade root 2243. Optionally, the radius of the blade root 2243 of the blade 224 at the inlet is R h , and the radius of the blade tip 2242 at the inlet is R s , and 0.35 ≤ R h / R s ≤ 0.4. In this embodiment, the inlet refers to the inlet of the centrifugal impeller.

[0108] Optionally, the root radius of the blade 224 at the inlet is R h , and the tip radius of the blade 224 at the inlet is R s , and R h / R s = 0.37.

[0109] Optionally, the angle between the tangential direction of the blade profile at the tip of the blade 224 at the inlet and the rotation direction of the centrifugal impeller at the tip is α1, and 56° ≤ α1 ≤ 64°.

[0110] Optionally, the angle between the tangential direction of the blade profile at the tip of the blade 224 at the inlet and the rotation direction of the centrifugal impeller at the tip is α1, and α1 = 62°.

[0111] Optionally, the outlet width of the centrifugal impeller is b2, and b2 is calculated by formula (1), and formula (1) is:

[0112] b2 = Q / (2π × R2 × φ × u2) (1);

[0113] wherein, R2 is the outlet radius of the centrifugal impeller of the centrifugal impeller; u2 is the circumferential velocity, and φ is the flow coefficient at the outlet of the centrifugal impeller.

[0114] Optionally, u2 is calculated by formula (2), and formula (2) is:

[0115] u2 = 2πR2n (2);

[0116] wherein, n is the rotational speed of the centrifugal impeller.

[0117] Optionally, 90mm ≤ R2 ≤ 110mm, and 0.2 ≤ φ ≤ 0.3.

[0118] Optionally, the thickness of the blade 224 at the inlet of the centrifugal impeller is δ1, and 0.8mm ≤ δ1 ≤ 1.5mm.

[0119] Optionally, the thickness of the blade 224 at the inlet of the centrifugal impeller is δ1, and δ1 = 1.1mm.

[0120] Optionally, the thickness of the blade 224 at the outlet of the centrifugal impeller is δ2, and 1.3mm ≤ δ2 ≤ 2.5mm.

[0121] Optionally, the thickness of the blade 224 at the outlet of the centrifugal impeller is δ2, and δ2 = 1.9mm.

[0122] Optionally, the number of blades 224 is 19 or 23; the root radius of the blades 224 at the inlet is 28.8 mm; the tip radius of the blades 224 at the inlet is 72 mm; the blade angle at the tip of the blades 224 at the inlet is 62°, and the blade angle at the root of the blades 224 at the inlet is 37°; the outlet width of the centrifugal impeller is 25 mm, the outlet blade angle of the centrifugal impeller is 65°, and the outlet radius of the centrifugal impeller is 92.1 mm; the axial length of the centrifugal impeller is 40.2 mm.

[0123] The embodiment of the present invention can achieve the required target air volume through a smaller axial dimension of the centrifugal impeller. At the same time, under the operating conditions, the flow field inside the centrifugal impeller is ensured to be more stable, the overall efficiency of the automotive air-conditioning blower is improved, and the noise of the automotive air-conditioning assembly is reduced.

[0124] Specific principle:

[0125] Before the oncoming air enters the centrifugal impeller, the pre-swept blade structure ensures that the air flow enters the centrifugal impeller more evenly and stably; since the blades are spatially twisted backward-curved blades, it promotes the fitting of the air flow in the centrifugal impeller passage with the blades; when the air flow reaches the outlet of the centrifugal impeller, due to the backward-curved structure of the blades, the stability of the flow field at the outlet of the centrifugal impeller is improved. Moreover, the turning loss of the air flow in the backward-curved centrifugal impeller is relatively small, and the efficiency of the entire centrifugal impeller is also improved.

[0126] It should be noted that, in order to enable the normal operation of the blower, the blower may further include a PCB board.

[0127] Based on any of the above embodiments, further, as Figures 1 to 6 shown, the total air outlet 60 may include a plurality of mode air outlets, and mode air dampers 130 are provided in each of the plurality of mode air outlets, so as to control the air volume.

[0128] Based on any of the above embodiments, further, as Figures 1 to 6 shown, the air inlet housing 11, the intermediate housing 12, and the air distribution housing 13 are independently provided. One side of the intermediate housing 12 is hermetically connected to the air inlet housing 11, and the other side of the intermediate housing 12 is hermetically connected to the air distribution housing 13. In this embodiment, the air inlet housing 11, the intermediate housing 12, and the air distribution housing 13 are independently provided, which facilitates the maintenance or repair of the internal structure of the air-conditioning device, and can also replace the three respectively. The intermediate housing 12 can be connected to the air inlet housing 11 by a rib-groove sealing structure 140, and the intermediate housing 12 can be connected to the air distribution housing 13 by a rib-groove sealing structure 140.

[0129] Alternatively, the air inlet housing 11, the intermediate housing 12, and the air distribution housing 13 are integrally provided, that is, the housing 10 is integrally formed, with high strength.

[0130] It should be noted that in the embodiments of the present invention, "front" refers to the upstream in the overall direction of the air flow from the air inlet 213 to the air outlet 214, and "rear" refers to the downstream in the overall direction of the air flow from the air inlet 213 to the air outlet 214.

[0131] An embodiment of the present invention further provides an automobile, which includes a vehicle body and the above-mentioned air conditioning device. The air conditioning device is arranged inside the vehicle body. The automobile of this embodiment includes the air conditioning device of any of the above technical solutions. Therefore, it has all the beneficial technical effects of this air conditioning device and will not be elaborated here.

[0132] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit them. Although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still modify the technical solutions described in the foregoing embodiments, or perform equivalent replacements on some or all of the technical features. These modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention. In the specification provided here, a large number of specific details are described. However, it can be understood that the embodiments of the present invention can be practiced without these specific details. In some instances, well-known methods, structures, and technologies have not been shown in detail so as not to obscure the understanding of this specification. In addition, those skilled in the art can understand that although some of the embodiments herein include certain features included in other embodiments but not other features, the combination of the features of different embodiments means that it is within the scope of the present invention and forms different embodiments.

Claims

1. An air conditioning device, characterized in that, Comprising: A casing, a blower, a refrigeration heat exchanger and a heating heat exchanger disposed within the casing; the blower includes a motor and a centrifugal impeller drivingly connected to the motor, and the motor drives the centrifugal impeller to rotate so that gas enters the centrifugal impeller axially and exits the centrifugal impeller radially. The casing includes an air inlet housing, an intermediate housing and a air distribution housing that are sequentially communicated. A total air inlet is provided on the air inlet housing, and a total air outlet is provided on the air distribution housing; the blower is disposed within the air inlet housing, and the heating heat exchanger and the refrigeration heat exchanger are disposed within the intermediate housing. The blower is an axial-radial blower, and the axial-radial blower further includes a blower housing, and the blower housing includes a blower front housing and a blower rear housing that are connected to each other; an air inlet parallel or coincident with the axis of the centrifugal impeller is provided on the blower front housing, and an air outlet parallel or coincident with the axis of the centrifugal impeller is provided on the blower rear housing; the blower front housing and the blower rear housing are oppositely disposed, and an installation cavity is formed between the blower front housing and the blower rear housing, and the motor and the centrifugal impeller are installed within the installation cavity. The installation cavity includes an impeller installation cavity and a motor installation cavity; the blower rear housing includes an outer cover body and an installation groove provided on the inner side of the outer cover body, the air outlet is provided on the outer cover body, and the installation groove forms the motor installation cavity; the outer cover body is connected to the blower front housing, and an impeller installation cavity is formed between the inner wall of the outer cover body and the inner wall of the blower front housing; the inner wall of the impeller installation cavity is used to form an air flow path with the impeller. Wherein, the air flow path includes an arc-shaped guiding portion that protrudes away from the centrifugal impeller, one side of the arc-shaped guiding portion is close to the air inlet and faces the air outlet side of the centrifugal impeller, and the other side of the arc-shaped guiding portion is close to the air outlet. The arc-shaped guiding portion surrounds the side portion of the centrifugal impeller, the middle portion of the arc-shaped guiding portion is far from the centrifugal impeller, and the two sides of the arc-shaped guiding portion are close to the centrifugal impeller, so that the air flow path turns at the side portion of the centrifugal impeller, thereby forming a labyrinth structure. A front accommodating groove is provided at the edge of the air inlet, and a front connecting plate is provided on the centrifugal impeller, and the front connecting plate is inserted into the front accommodating groove. The blower further includes an intermediate cover plate; a groove is provided on the inner side of the outer cover body, and the intermediate cover plate is connected to the outer cover body to cover the groove. A connection hole for passing through the motor is provided on the intermediate cover plate, a rear accommodating groove is provided at the edge of the connection hole, and a rear connecting plate is provided on the centrifugal impeller, and the rear connecting plate is inserted into the rear accommodating groove.

2. The air conditioner according to claim 1, characterized in that, The side wall of the refrigeration heat exchanger contacts the inner wall of the intermediate housing, and the side wall of the heating heat exchanger contacts the inner wall of the intermediate housing.

3. The air-conditioning device according to claim 2, characterized in that, The air conditioner further includes an air filter, and the air filter is disposed on the side of the axial-radial blower away from the total air inlet; the side wall of the air filter contacts the inner wall of the intermediate housing.

4. The air-conditioning device according to claim 1, characterized in that, A plurality of swirl-vanishing blades are provided at the air outlet, and the middle part of the swirl-vanishing blades protrudes outward; the plurality of swirl-vanishing blades are arranged at intervals along the circumferential direction of the air outlet, and the arrangement direction of the plurality of swirl-vanishing blades is the same as the rotation direction of the centrifugal impeller.

5. The air-conditioning device according to claim 4, characterized in that, The inlet angle of the swirl-vanishing blade is 55° to 67°, and the outlet angle of the swirl-vanishing blade is 90° - 93°.

6. A vehicle, characterized in that, It includes a vehicle body and the air-conditioning device according to any one of claims 1-5, and the air-conditioning device is arranged in the vehicle body.

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