Ducted fan

Abstract

This application relates to the field of air conditioning technology, and in particular to a ducted air conditioning unit. The ducted air conditioning unit proposed in this application includes multiple fans and a drive unit. The drive unit is disposed between adjacent fans and includes a motor and a connecting shaft. The motor drives the fans of the multiple fans to rotate through the connecting shaft. By constructing a coordinated matching relationship between the total length of the volute, the fan spacing, and the motor size, and limiting the ratio of the total volute length W to the total spacing S, the volute opening W / S is limited to the optimal range of 0.55~0.675. This allows the fan blades to form a reasonable tip clearance with the inner wall of the casing, effectively suppressing high-frequency aerodynamic noise generated by tip vortices, while ensuring smooth airflow within the casing. This reduces airflow turbulence and increased vortex noise caused by excessive clearance, and prevents airflow interference, increased structural vibration, and structural interference risks caused by insufficient clearance. This achieves a comprehensive performance improvement of low noise, large air volume, and high stability from the structural layout source.

Description

Technical Field

[0001] This application relates to the field of air conditioning technology, and in particular to a ducted air conditioner. Background Technology

[0002] The structural layout design of the fan in a ducted air conditioner affects its noise level and air volume performance. However, the fan structural layout often focuses on optimizing a single parameter or spatial partitioning design, resulting in unreasonable parameter matching. This leads to poor noise control in the ducted air conditioner and makes it difficult to achieve a balance between noise and air volume. Summary of the Invention

[0003] In view of this, this application provides a ducted air conditioner that can optimize the operating noise of the ducted air conditioner while ensuring air volume.

[0004] This application embodiment provides a duct air handling unit, the duct air handling unit comprising:

[0005] case;

[0006] A fan, numbered n, where 2≤n≤6, is spaced apart in the housing along the length of the housing. Each fan includes a volute and a fan disposed in the volute.

[0007] A drive unit is disposed between two adjacent fans. The drive unit includes a motor and a connecting shaft connected to the output end of the motor. The connecting shaft extends along the length direction, and the motor drives the fan to rotate through the connecting shaft.

[0008] Along the length direction, the length of the volute is W. i mm, the sum of the lengths of the plurality of volutes W= ;

[0009] Along the length direction, the distance between the opposite faces of two adjacent volutes is S. i mm, the sum of the spacing between the plurality of volutes is The span of the motor is M L mm, the distance between the motor and the opposite surface of the adjacent volute is S. m mm, satisfying: S=M L +S m + ;

[0010] Wherein, 0.55≤W / S≤0.675.

[0011] Optionally, in the ducted air conditioner, the diameter of the fan is φ mm and the height of the housing is h mm, satisfying: 0.6≤φ / h≤0.8.

[0012] Optionally, the duct air conditioner has a φ / h value of 0.7 ≤ φ / h ≤ 0.75.

[0013] Optionally, in the duct air conditioner, the height of the volute along the height direction of the housing is h. w mm, satisfying: 1.2≤h w / φ≤1.35.

[0014] Optionally, in the ducted air conditioner, the length of the fan is L. i mm, W i =L i +(10mm~30mm).

[0015] Optionally, the duct air conditioner has a diameter of 1.2φ≤h≤1.65φ.

[0016] Optionally, in the ducted air conditioner, 0.6φ≤L i ≤1.2φ.

[0017] Optionally, in the duct unit, the housing includes a first wall and a second wall disposed opposite to each other along the length direction;

[0018] The duct air conditioner also includes an electrical control box, which is disposed in the housing and adjacent to the first wall. The electrical control box and n fans are arranged at intervals along the length direction, and the diameter of the fan is φ mm.

[0019] Along the length direction, the distance between the electrical control box and the adjacent volute face is S1 mm, satisfying: 0.25φ≤S1.

[0020] Optionally, in the ductwork unit, along the length direction, the distance between the volute adjacent to the second wall and the opposite face of the second wall is S. n+1 mm, satisfying: S n+1 ≤0.35φ.

[0021] Optionally, the duct air conditioner has 3 to 6 fans, including a first fan and a second fan located at both ends of the length direction, and at least one third fan located between the first fan and the second fan. The first fan is adjacent to the electrical control box, and the second fan is adjacent to the second wall, satisfying at least one of the following conditions:

[0022] a) Along the length direction, the distance between the opposite faces of the volute of the first fan and the volute of the adjacent third fan is S2 mm, satisfying: 0.5φ≤S2≤0.7φ;

[0023] b) Along the length direction, the distance between the opposite faces of the volute of the second fan and the volute of the adjacent third fan is S3 mm, satisfying: 0.5φ≤S3≤0.7φ;

[0024] c) Along the length direction, the distance between the opposite faces of the volutes of two adjacent third fans is S4mm, satisfying: 0.5φ≤S4≤0.7φ.

[0025] The duct air handling unit provided in this application embodiment has at least the following beneficial effects:

[0026] The ducted air handling unit proposed in this application includes multiple fans and a drive unit. The drive unit is positioned between adjacent fans and includes a motor and a connecting shaft. The motor drives the fans of multiple fans to rotate through the connecting shaft. By constructing a coordinated matching relationship between the total length of the volute, the fan spacing, and the motor size, and limiting the ratio of the total length W of the volute to the total spacing S, the volute opening W / S is limited to the optimal range of 0.55~0.675. This allows the fan blades to form a reasonable tip clearance with the inner wall of the casing, effectively suppressing the high-frequency aerodynamic noise generated by tip vortices, while ensuring smooth airflow within the casing. Furthermore, it achieves optimal coordination between the fan arrangement density within the casing, the effective flow area of ​​the duct, and the airflow operating space. This reduces airflow turbulence and increased vortex noise caused by excessively large gaps, while preventing airflow interference, increased structural vibration, and structural interference risks caused by excessively small gaps. This achieves a comprehensive performance improvement of low noise, large air volume, and high stability from the source of structural layout. Attached Figure Description

[0027] Figure 1 This is an overall schematic diagram of a ductwork unit provided in an embodiment of this application;

[0028] Figure 2 This is a top view of a ductwork unit provided in an embodiment of this application;

[0029] Figure 3 for Figure 2 Schematic diagram of the cross-section at point AA;

[0030] Figure 4 This is a front view of a ductwork unit provided in an embodiment of this application;

[0031] Figure 5 for Figure 4 Schematic diagram of the cross-section at point BB;

[0032] Figure 6 This is a schematic diagram illustrating the relationship between the air supply noise and W / S of a ducted air conditioner provided in an embodiment of this application;

[0033] Figure 7 This is a schematic diagram showing the relationship between the air supply noise and φ / h of a ducted air conditioner provided in an embodiment of this application.

[0034] Explanation of reference numerals in the attached figures

[0035] 100 - Ductless air conditioner; 10 - Housing; 20 - Fan; 21 - Volute; 22 - Fan; 30 - Drive unit; 31 - Motor; 32 - Connecting shaft; 40 - Electrical control box; 11 - First wall; 12 - Second wall; 201 - First fan; 202 - Second fan; 203 - Third fan; X - Length direction; Y - Width direction; Z - Height direction. Detailed Implementation

[0036] To make the technical solution and beneficial effects of this application more apparent and understandable, a detailed description is provided below by listing specific embodiments. The accompanying drawings are not necessarily drawn to scale, and local features may be enlarged or reduced to more clearly show the details of the local features; unless otherwise defined, the technical and scientific terms used herein have the same meanings as those in the technical field to which this application pertains.

[0037] In the following embodiments, the parameters related to the duct air conditioning unit are defined as follows:

[0038] Shell length L k This refers to the effective length of the outer casing of the duct unit along the motor axis;

[0039] Fan diameter φ: refers to the diameter of the circle formed by the rotation trajectory of the fan blades;

[0040] Shell height h: refers to the effective overall height of the duct unit's casing along the vertical direction (Z);

[0041] Fan length L i : Refers to the effective length of the i-th fan along the axial direction;

[0042] Volute length: refers to the length of the volute along the motor axis;

[0043] Circular space: refers to the gap between two adjacent circular shells;

[0044] Motor span M L : Refers to the width of the motor;

[0045] Motor gap S m : Refers to the gap between the motor and the volute.

[0046] In some embodiments of this application, a duct air conditioner 100 is provided, such as... Figure 1-5As shown, the duct air conditioner 100 includes: a housing 10, fans 20, and a drive unit 30. There are n fans 20, where 2 ≤ n ≤ 6, spaced apart along the length X of the housing 10. Each fan 20 includes a volute 21 and a fan 22 disposed within the volute 21. The drive unit 30 is positioned between adjacent fans 20 and includes a motor 31 and a connecting shaft 32 connected to the output end of the motor 31. The connecting shaft 32 extends along the length X, and the motor 31 drives the fan 22 to rotate via the connecting shaft 32. The length of the volute 21 along the length X is W. i mm, the sum of the lengths of the multiple volutes 21 W = Along the length direction X, the distance between the opposite faces of two adjacent volutes 21 is S. i mm, the sum of the spacing between the multiple volutes 21 is The span of motor 31 is M L mm, the distance between the opposite surfaces of the motor 31 and the adjacent volute 21 is S m mm, satisfying: S=M L +S m + Where 0.55≤W / S≤0.675.

[0047] In existing technologies, the fan layout of ducted air conditioners is only optimized for a single size or simply divided into spaces. The system does not systematically match parameters such as volute length, fan clearance, and motor arrangement. This can easily lead to problems such as unreasonable arrangement density and unbalanced airflow area, resulting in large airflow disturbance, high air supply noise, and unstable air volume output.

[0048] The ducted fan 100 proposed in this application includes multiple fans 20 and a drive unit 30. The drive unit 30 is disposed between adjacent fans 20 and includes a motor 31 and a connecting shaft 32. The motor 31 drives the fans 22 of the multiple fans 20 to rotate through the connecting shaft 32. By constructing a coordinated matching relationship between the total length of the volute 21, the spacing between the fans 20, and the size of the motor 31, the ratio of the total length of the volute 21 to the total spacing is limited. Specifically, by limiting the ratio of the total length W of the volute 21 to the total spacing S in the optimal range of 0.55 to 0.675, a reasonable blade tip clearance can be formed between the fan blades 22 and the inner wall of the casing, effectively suppressing the high-frequency aerodynamic noise generated by the blade tip vortex. At the same time, the arrangement density of the fan 20 in the casing, the effective flow area of ​​the air duct and the airflow operation space are optimized in coordination. This reduces airflow turbulence and increased eddy noise caused by excessive gaps, and prevents airflow interference, increased structural vibration and even structural interference risks caused by excessively small gaps. This achieves a comprehensive performance improvement of low noise, large air volume and high stability from the source of structural layout.

[0049] In some embodiments, such as Figure 6As shown, with the increase of W / S, the air supply noise first decreases and then increases. When W / S is in the range of 0.55 to 0.675, the air supply noise is below 36 dB(A). This parameter range can effectively balance the duct structure layout and the requirement for low-noise air supply, providing an optimal basis for duct size design.

[0050] In some embodiments, the drive motor 31 and the fan 22 are arranged in separate areas and connected to the connecting shaft 32 via a coupling. The motor 31 is fixed to the sealing plate inside the housing 10. The sealing plate has a reinforcing rib structure to reduce the transmission of vibration of the motor 31 to the housing 10 and reduce the coupling amplification of vibration noise and aerodynamic noise.

[0051] In some embodiments of the ducted air conditioner 100, the diameter of the fan 22 is φ mm, and the height of the housing 10 is h mm, satisfying: 0.6≤φ / h≤0.8. Controlling the ratio of the fan diameter φ to the housing height h within the range of 0.6~0.8 ensures that the rotating flow field of the fan 22 is reasonably adapted to the internal space of the housing 10, effectively reducing the aerodynamic noise caused by unreasonable blade tip clearance, while ensuring smooth air intake and exhaust, and balancing air volume output and noise suppression.

[0052] In some embodiments of the ducted air conditioner 100, 0.7 ≤ φ / h ≤ 0.75. Further limiting φ / h to the optimal range of 0.7~0.75, through the design of the φ / h ratio, the air inlet resistance of a single fan is rationally distributed. Under static pressure, the fan arrangement density within the housing is optimized, reducing mutual interference between airflows from adjacent fans and lowering the disturbance noise generated by airflow superposition. Simultaneously, sufficient buffer space is reserved for airflow inlet and outlet, ensuring stable airflow Q output and achieving the lowest possible noise. Compared to traditional layouts, the noise level can be reduced by 3-8 dB(A), and the noise frequency is concentrated in the low-frequency range, significantly improving comfort; the airflow loss rate is ≤5%, achieving low noise while ensuring the rated airflow Q.

[0053] In some embodiments, such as Figure 7 As shown, with the increase of φ / h, the air supply noise also shows a trend of first decreasing and then increasing. When φ / h < 0.7, due to the excessively large housing height relative to the fan diameter, the increased blade tip clearance leads to the formation of a large area of ​​low-speed recirculation zone on the inner wall of the housing, causing broadband vortex noise. When φ / h > 0.75, due to the relatively insufficient housing height, the airflow in and out of the duct is obstructed, and the blade tip blockage effect is obvious, resulting in a sharp increase in high-frequency noise. Only when φ / h is in the preferred range of 0.7~0.75 can the air supply noise be stably controlled below 36dB(A), achieving the optimal balance between air intake resistance and blade tip clearance, which can significantly suppress the noise generated by airflow disturbance and improve the quietness of the entire unit.

[0054] In some embodiments of the duct unit 100, such as Figure 3As shown, along the height direction Z of the housing 10, the height of the volute 21 is h w mm, satisfying: 1.2 ≤ h w / φ ≤ 1.35. Controlling the ratio of the height h of the volute 21 w to the diameter φ of the fan 22 within 1.2 to 1.35 can enable the volute 21 to completely wrap the rotation area of the fan 22, effectively guide the smooth flow of the air flow, reduce the noise generated by the impact and backflow of the air flow inside the volute 21, and at the same time reduce the space waste and the increase of wind resistance caused by the excessive height of the volute 21. In addition, the height h of the volute 21 w is less than the height h of the housing 10 (i.e., h w < h), so that an air flow buffer channel is formed between the top of the volute 21 and the inner wall of the housing 10, and a reasonable return air space is reserved at the top of the housing 10, avoiding the generation of high-frequency noise due to the top wall of the volute 21 being too close to the inner wall of the housing 10.

[0055] In some embodiments of the air duct machine 100, the length of the fan 22 is L i mm, W i = L i +(10 mm to 30 mm). Setting the length of the volute 21 to be the length of the fan plus a margin of 10 to 30 mm can not only ensure that the fan 22 is completely accommodated and operates without interference inside the volute 21, but also reserve a reasonable air flow buffer space at the end of the fan 22, reduce the end vortex and friction noise, and improve the running stability of the fan 20.

[0056] In some embodiments of the air duct machine 100, 1.2φ ≤ h ≤ 1.65φ. Limiting the height h of the housing to 1.2 to 1.65 times the diameter φ of the fan can enable the internal height of the housing 10 and the size of the fan 22 to form an optimal structural match, not only ensure that the fan 22 rotates without interference, but also form a reasonable upper and lower air flow channels, reduce the noise generated by the air flow hitting the housing 10, and improve the air supply uniformity.

[0057] In some embodiments of the air duct machine 100, 0.6φ ≤ L i ≤ 1.2φ. Limiting the length L of the fan i within 0.6 to 1.2 times the diameter φ of the fan can balance the air supply area of the fan 22 and the strength of the volute 21. While ensuring sufficient air supply volume, it reduces the problems of increased vibration and noise caused by the fan 22 being too long, and realizes the coordinated optimization of air volume and noise.

[0058] In some embodiments of the air duct machine 100, such as Figure 5As shown, the housing 10 includes a first wall 11 and a second wall 12 arranged opposite each other along the length direction X. The duct unit 100 also includes an electrical control box 40, which is disposed in the housing 10 and adjacent to the first wall 11. The electrical control box 40 and n fans 20 are arranged at intervals along the length direction X, and the diameter of the fan 22 is φ mm. Along the length direction X, the distance between the opposite surfaces of the electrical control box 40 and the adjacent volute 21 is S1 mm, satisfying: 0.25φ≤S1. By setting the distance S1 between the electrical control box 40 and the adjacent volute 21 to not less than 0.25φ, sufficient installation space and heat dissipation gap can be reserved for the electrical control box 40, while reducing the obstruction and disturbance of the airflow caused by the electrical control box 40, and preventing the airflow from impacting the electrical control box 40 and generating additional noise.

[0059] In some embodiments of the duct unit 100, such as Figure 5 As shown, along the length direction X, the distance between the volute 21 adjacent to the second wall 12 and the opposite surface of the second wall 12 is S. n+1 mm, satisfying: S n+1 ≤0.35φ. The distance S between the end volute 21 and the shell wall is... n+1 By controlling the clearance to within 0.35φ, airflow backflow caused by excessive end clearance can be reduced, ensuring effective airflow output and suppressing high-frequency noise generated by end vortices. In some embodiments, the clearance S between the motor 31 and the volute 21 is... m The thickness of ≥20mm ensures unobstructed heat dissipation airflow for the motor 31, preventing heat buildup that could lead to reduced efficiency. On the other hand, it forms an effective physical vibration isolation layer, blocking the high-frequency vibration of the motor 31 from being directly transmitted to the adjacent volute 21 through the rigid connection, further reducing the electromagnetic noise of the motor 31 and the aerodynamic noise of the fan 20.

[0060] In some embodiments of the duct unit 100, such as Figure 5 As shown, the number n of the fans 20 is 3 to 6, including a first fan 201 and a second fan 202 located at both ends of the length direction X, and at least one third fan 203 located between the first fan 201 and the second fan 202. The first fan 201 is adjacent to the electrical control box 40, and the second fan 202 is adjacent to the second wall 12.

[0061] In some embodiments of the duct unit 100, such as Figure 5As shown, along the length direction X, the distance between the opposite faces of the volute 21 of the first fan 201 and the volute 21 of the adjacent third fan 203 is S2 mm, satisfying: 0.5φ≤S2≤0.7φ. By limiting the distance S2 between the volutes of the end first fan 201 and the adjacent third fan 203 to this range, a reasonable airflow buffer interval can be formed between the end first fan 201 and the adjacent third fan 203. This reduces the phenomenon of mutual compression and disturbance superposition of the end airflow and the middle airflow caused by the excessively small distance, and also prevents the waste of space at the front end of the casing caused by the excessively large distance, ensuring uniform air intake at the end and lower noise.

[0062] In some embodiments of the duct unit 100, such as Figure 5 As shown, along the length direction X, the distance between the opposite faces of the volute 21 of the second fan 202 and the volute 21 of the adjacent third fan 203 is S3 mm, satisfying: 0.5φ≤S3≤0.7φ. By limiting the distance S3 between the volutes of the end second fan 202 and the adjacent intermediate third fan 203 to this range, the airflow at the end can be smoothly transitioned, reducing airflow backflow and vortex aggravation at the end, while ensuring that the operation of the end second fan 202 and the intermediate third fan 203 does not interfere with each other, thus reducing the aerodynamic noise at the tail of the whole machine.

[0063] In some embodiments of the duct unit 100, such as Figure 5 As shown, along the length direction X, the distance between the opposite faces of the volutes 21 of two adjacent third fans 203 is S4 mm, satisfying: 0.5φ≤S4≤0.7φ. By limiting the volute distance S4 between adjacent third fans 203 in this range, multiple intermediate fans can form a uniform and symmetrical airflow channel, ensuring stronger synchronization of air delivery by each fan and less vibration, significantly reducing the superimposed noise and airflow interference when multiple fans are running in parallel.

[0064] It is understandable that by controlling the volute distances S2, S3, and S4 between the end fans and the intermediate fans, and between the intermediate fans, within the optimal range of 0.5φ to 0.7φ, multiple fans can form a uniform and symmetrical airflow buffer space along the length direction. This reduces the aerodynamic noise caused by the mutual interference and superposition of airflow between adjacent fans due to excessively small distances, and also prevents the waste of casing space and airflow attenuation caused by excessively large distances. As a result, the coordinated operation of multiple fans is more stable, the air delivery is more uniform, and the overall operating noise is lower.

[0065] In some embodiments of the duct air conditioner 100, along the length direction X, the volute distances S2, S3, and S4 between the first fan 201, the second fan 202, and the intermediate third fan 203 all satisfy: 0.5φ≤S2≤0.7φ, 0.5φ≤S3≤0.7φ, and 0.5φ≤S4≤0.7φ. This forms a uniform buffer airflow layer between adjacent fans, reduces airflow interference, and lowers the noise of multiple fans operating.

[0066] In some embodiments of the duct air conditioner 100, multiple fans 22 are arranged coaxially along the X-axis, with equal gaps between adjacent fans 22, and the rotation center coincides with the center of the housing, further optimizing airflow distribution and reducing structural vibration noise.

[0067] The ducted air conditioner 100 proposed in this application, by controlling the ratio of the total length to the total spacing of the volute 21 (W / S) and the ratio of the fan diameter (φ) to the height (h) of the casing (φ / h), can reduce the operating noise by 3–8 dB(A) compared to the layout of traditional ducted air conditioners. The noise frequency is concentrated in the low-frequency range, significantly improving comfort. At the same time, the air volume loss rate is controlled within 5%, ensuring stable air volume output while achieving low-noise operation.

[0068] In this application, the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "height," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the purpose of simplifying the description of this application and do not indicate that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. In other words, they should not be construed as limitations on this application.

[0069] In this application, unless otherwise expressly defined, the terms "installation," "connection," "linking," "fixing," "setting," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral part; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can also refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0070] It should be understood that the above embodiments are exemplary and are not intended to encompass all possible implementations included in the claims. Various modifications and changes can be made to the above embodiments without departing from the scope of this disclosure. Similarly, the various technical features of the above embodiments can be arbitrarily combined to form other embodiments of this application that may not be explicitly described. Therefore, the above embodiments only illustrate several implementations of this application and do not limit the scope of protection of this patent application.

Claims

1. A ducted air conditioner, characterized in that, The duct unit includes: case; A fan, numbered n, where 2≤n≤6, is spaced apart in the housing along the length of the housing. Each fan includes a volute and a fan disposed in the volute. A drive unit is disposed between two adjacent fans. The drive unit includes a motor and a connecting shaft connected to the output end of the motor. The connecting shaft extends along the length direction, and the motor drives the fan to rotate through the connecting shaft. Along the length direction, the length of the volute is W. i mm, the sum of the lengths of the plurality of volutes W= ; Along the length direction, the distance between the opposite faces of two adjacent volutes is S. i mm, the sum of the spacing between the plurality of volutes is The span of the motor is M L mm, the distance between the motor and the opposite surface of the adjacent volute is S. m mm, satisfying: S=M L +S m + ; Wherein, 0.55≤W / S≤0.

675.

2. The duct air conditioner according to claim 1, characterized in that, The fan has a diameter of φ mm and the housing has a height of h mm, satisfying the condition: 0.6≤φ / h≤0.

8.

3. The duct air conditioner according to claim 2, characterized in that, 0.7≤φ / h≤0.

75.

4. The duct air conditioner according to claim 2 or 3, characterized in that, Along the height direction (Z) of the shell, the height of the volute is h. w mm, satisfying: 1.2≤h w / φ≤1.

35.

5. The duct air conditioner according to claim 1, characterized in that, The length of the fan is L. i mm, W i =L i +(10mm~30mm).

6. The duct air conditioner according to claim 2 or 3, characterized in that, 1.2φ≤h≤1.65φ.

7. The duct air conditioner according to claim 2 or 3, characterized in that, 0.6φ≤L i ≤1.2φ。 8. The duct air conditioner according to claim 1, characterized in that, The housing includes a first wall and a second wall disposed opposite to each other along the length direction; The duct air conditioner also includes an electrical control box, which is disposed in the housing and adjacent to the first wall. The electrical control box and n fans are arranged at intervals along the length direction, and the diameter of the fan is φ mm. Along the length direction, the distance between the electrical control box and the adjacent volute face is S1 mm, satisfying: 0.25φ≤S1.

9. The duct air conditioner according to claim 8, characterized in that, Along the length direction, the distance between the volute adjacent to the second wall and the opposite face of the second wall is S. n+1 mm, satisfying: S n+1 ≤0.35φ.

10. The duct air conditioner according to claim 9, characterized in that, The number of fans n is 3 to 6, including a first fan and a second fan located at both ends of the length direction, and at least one third fan located between the first fan and the second fan. The first fan is adjacent to the electrical control box, and the second fan is adjacent to the second wall, satisfying at least one of the following conditions: a) Along the length direction, the distance between the opposite faces of the volute of the first fan and the volute of the adjacent third fan is S2 mm, satisfying: 0.5φ≤S2≤0.7φ; b) Along the length direction, the distance between the opposite faces of the volute of the second fan and the volute of the adjacent third fan is S3 mm, satisfying: 0.5φ≤S3≤0.7φ; c) Along the length direction, the distance between the opposite faces of the volutes of two adjacent third fans is S4 mm, satisfying: 0.5φ≤S4≤0.7φ.

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