Duct-type air conditioner

Abstract

A duct-type air conditioner (100), comprising an air duct member (110), a driven fan wheel (120), and a heat exchanger (130), wherein the air duct member (110) is provided with an air outlet (111); a first side wall (1) of the air outlet (111) comprises at least a curved expansion surface recessed in a direction away from a second side wall (2); the first side wall (1) and the second side wall (2) are disposed opposite each other in a first direction; the heat exchanger (130) comprises a first portion (131) and a second portion (132); in the first direction, the second portion (132) and the first side wall (1) are located on the same side; and in a vertical plane passing through the air outlet (111), the first portion (131), and the second portion (132), the number of heat exchange tubes (136) in the first portion (131) is less than the number of heat exchange tubes (136) in the second portion (132).

Description

Ductless air conditioner

[0001] Cross-reference to related applications

[0002] This application claims priority to Chinese Patent Application No. 202411854751.X, filed on December 16, 2024, entitled "Ductless Air Conditioner". Technical Field

[0003] This application relates to the field of duct air conditioning technology, and more particularly to a duct air conditioning system. Background Technology

[0004] In related technologies, the design of the connection port inside the duct air conditioner for connecting the ventilation wheel chamber and the heat exchange chamber is unreasonable, resulting in loud noise when the airflow passes through the connection port, which in turn causes loud noise when the duct air conditioner is working, affecting the user's experience.

[0005] Application content

[0006] This application aims to at least partially address one of the technical problems in the related art.

[0007] Therefore, this application proposes a duct air conditioner that helps reduce noise when airflow passes through the air outlet and ensures that the heat exchanger's heat exchange effect is matched with the airflow velocity, thereby improving the heat exchanger's heat exchange effect.

[0008] According to an embodiment of this application, a ducted air conditioner includes: an air duct component having an air outlet, the first sidewall of the air outlet having at least one curved expansion surface recessed in a direction away from a second sidewall, the first sidewall and the second sidewall being disposed opposite each other in a first direction; a drive impeller disposed within the air duct component; and a heat exchanger disposed on the air outlet side of the air duct component, the heat exchanger including: a first part and a second part, wherein in the first direction, the second part and the first sidewall are located on the same side, and in a vertical plane passing through the air outlet, the first part and the second part, the number of heat exchange tubes in the first part is N1, the number of heat exchange tubes in the second part is N2, and the heat exchanger satisfies the following relationship: N1 < N2.

[0009] According to the embodiments of the present application, the duct air conditioner reduces the air resistance of the air outlet to the airflow by forming at least a portion of the first sidewall of the air outlet into an expansion surface with a curved shape that is concave in the direction away from the second sidewall. This helps to reduce the noise generated when the airflow passes through the air outlet. By making the number of heat exchange tubes in the second part of the heat exchanger located on the same side as the first sidewall greater than the number of heat exchange tubes in the first part, it can be effectively ensured that the heat exchange capacity of the second part is matched with the flow velocity of the airflow passing through the first sidewall, thereby improving the heat exchange effect of the second part on the airflow and thus improving the heat exchange effect of the heat exchanger on the airflow.

[0010] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0011] Figure 1 is a structural schematic diagram of the duct machine described in an embodiment of this application;

[0012] Figure 2 is a schematic diagram of the assembly of the drive impeller and the ductwork according to an embodiment of this application;

[0013] Figure 3 is a structural schematic diagram of the air duct component described in an embodiment of this application;

[0014] Figure 4 is a schematic diagram of the heat exchanger described in an embodiment of this application;

[0015] Figure 5 is a schematic diagram showing the effect of the ratio between the number of heat exchange tubes N1 in the first part and the number of heat exchange tubes N2 in the second part on the heat exchanger's heat exchange capacity, as described in the embodiments of this application.

[0016] Figure 6 is a schematic diagram showing the effect of the ratio between the number of heat exchange tubes and β in the second part of the embodiment of this application on the heat exchanger's heat exchange capacity.

[0017] Figure 7 is a schematic diagram showing the effect of the ratio between the width P1 of the second part and the width P2 of the first part on the heat exchanger's heat transfer capacity, as described in the embodiments of this application.

[0018] Figure 8 is a schematic diagram showing the effect of the ratio between L1 and L2 on the heat exchanger's heat transfer capacity according to an embodiment of this application;

[0019] Figure 9 is a schematic diagram of the structure of the first turbulence group according to an embodiment of this application;

[0020] Figure 10 is a schematic diagram of the structure of the second turbulence group described in the embodiment of this application. Detailed Implementation

[0021] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this application, and should not be construed as limiting this application.

[0022] In the description of this application, it should be understood that the terms "length," "width," "thickness," "upper," "lower," "vertical," "horizontal," "top," and "bottom," etc., indicating orientation or positional relationships based on the orientation or positional relationships shown in the accompanying drawings, are used only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application. Furthermore, features defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0023] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0024] The duct air conditioner 100 according to an embodiment of this application is described below with reference to Figures 1-10.

[0025] Referring to Figures 1 to 3, the duct air conditioner 100 according to an embodiment of this application includes: an air duct component 110, a drive impeller 120, and a heat exchanger 130. The air duct component 110 is provided with an air outlet 111. The first sidewall 1 of the air outlet 111 includes at least an expansion surface with a curved shape that is recessed in a direction away from the second sidewall 2. The first sidewall 1 and the second sidewall 2 are arranged opposite to each other in a first direction. The drive impeller 120 is disposed inside the air duct component 110, and the heat exchanger 130 is disposed on the air outlet side of the air duct component 110.

[0026] The drive impeller 120 can drive the airflow toward the air outlet 111. The airflow can flow through the air outlet 111 to the air outlet side of the duct component 110. That is, the airflow driven by the drive impeller 120 can flow through the air outlet 111 to the heat exchanger 130. The heat exchanger 130 can exchange heat with the airflow. In this way, by making at least a portion of the first sidewall 1 of the air outlet 111 form an expansion surface with a curved shape that is concave away from the second sidewall 2, the air resistance of the air outlet 111 to the airflow is reduced, the smoothness of the airflow when passing through the air outlet 111 is improved, and the noise generated when the airflow passes through the air outlet 111 is reduced, thereby helping to reduce the noise of the duct machine 100 during operation.

[0027] The first sidewall 1 can be integrally formed as an expansion surface with a curved shape that is concave in the direction away from the second sidewall 2, or the middle part of the first sidewall 1 can be constructed as an expansion surface with a curved shape that is concave in the direction away from the second sidewall 2. The specific structure of the first sidewall 1 can be determined according to actual production requirements, and no specific limitation is made here.

[0028] The “first direction” can be the height direction of the ducted air conditioner 100. When the first direction is defined as the height direction of the ducted air conditioner 100, one of the first side wall 1 and the second side wall 2 can be the top wall of the air outlet 111 and the other can be the bottom wall of the air outlet 111. The “first direction” can also be the length direction of the ducted air conditioner 100. When the first direction is defined as the length direction of the ducted air conditioner 100, the first side wall 1 and the second side wall 2 can be the two side walls of the air outlet 111 in the length direction of the ducted air conditioner 100.

[0029] Referring to Figures 1 and 4, the heat exchanger 130 includes a first part 131 and a second part 132. In a first direction, the second part 132 and the first sidewall 1 are located on the same side. On the vertical plane passing through the air outlet 111, the first part 131 and the second part 132 (i.e., the vertical plane shown in Figure 1), the number of heat exchange tubes 136 in the first part 131 is N1, and the number of heat exchange tubes 136 in the second part 132 is N2. The heat exchanger 130 satisfies the following relationship: N1 < N2.

[0030] Considering that the first sidewall 1 includes at least an expansion surface with a curved shape that is concave in the direction away from the second sidewall 2, the airflow velocity will increase when the airflow flows through the expansion surface with the curved shape. By making the number of heat exchange tubes 136 of the second part 132 located on the same side as the first sidewall 1 greater than the number of heat exchange tubes 136 of the first part 131, the heat exchange efficiency of the second part 132 can be effectively improved. This is beneficial to ensuring that the heat exchange tubes 136 of the second part 132 can fully exchange heat with the airflow flowing through it, and to ensuring that the heat exchange capacity of the second part 132 can meet the heat exchange requirements of the airflow flowing through the first sidewall 1, and to improving the heat exchange effect of the heat exchanger 130 on the airflow.

[0031] In related technologies, the sidewalls of the air outlet are usually formed as straight surfaces, which results in a lot of noise when the airflow passes through the air outlet, which in turn leads to a lot of noise when the duct air conditioner is working, affecting the user's hearing.

[0032] This application reduces the air resistance of the air outlet 111 to the airflow by forming at least a portion of the first sidewall 1 of the air outlet 111 into an expansion surface with a concave curved shape in the direction away from the second sidewall 2. This helps to reduce the noise generated when the airflow passes through the air outlet 111. By making the number of heat exchange tubes 136 in the second part 132 of the heat exchanger 130 located on the same side as the first sidewall 1 greater than the number of heat exchange tubes 136 in the first part 131, it can be effectively ensured that the heat exchange capacity of the second part 132 is matched with the flow velocity of the airflow passing through the first sidewall 1, thereby improving the heat exchange effect of the second part 132 on the airflow and thus improving the heat exchange effect of the heat exchanger 130 on the airflow.

[0033] Referring to Figure 5, in some embodiments of this application, the heat exchanger 130 satisfies 1.6≤N2 / N1≤1.8.

[0034] On the same vertical plane, the number N1 of heat exchange tubes 136 in the first part 131 and the number N2 of heat exchange tubes 136 in the second part 132 satisfy the relationship: 1.6≤N2 / N1≤1.8. Through simulation test, it is found that when the heat exchanger 130 satisfies 1.6≤N2 / N1≤1.8, the heat exchange capacity of the heat exchanger 130 is within the optimal range, that is, the heat exchange performance of the heat exchanger 130 is in the optimal range. This ensures the heat exchange effect of the second part 132 on the airflow while effectively increasing the overall heat exchange capacity of the heat exchanger 130, so that the heat exchanger 130 can achieve efficient heat exchange.

[0035] When N2 / N1 < 1.6, the overall heat exchange capacity of heat exchanger 130 is small, resulting in poor heat exchange effect. Furthermore, the heat exchange capacity of the first part 131 and the second part 132 is relatively similar, which may lead to a mismatch between the heat exchange capacity of the first part 131 and the heat exchange capacity of the second part 132 and the flow velocity of the airflow passing through them. This may result in the second part 132 being unable to fully exchange heat with the airflow passing through it, or the heat exchange capacity of the first part 131 being too large, increasing the energy consumption of heat exchanger 130.

[0036] When N2 / N1 > 1.8, the overall heat exchange capacity of heat exchanger 130 decreases, resulting in poor heat exchange performance. Furthermore, the number of heat exchange tubes 136 in the first part 131 differs significantly from the number of heat exchange tubes 136 in the second part 132. This mismatch between the heat exchange capacity of the first part 131 and the heat exchange capacity of the second part 132 and the flow velocity of the airflow passing through them can easily lead to an excessive heat exchange capacity in the second part 132, increasing the energy consumption of heat exchanger 130. Additionally, the excessive air resistance in the second part 132 affects its heat exchange performance. Finally, the first part 131 cannot fully exchange heat with the airflow passing through it, thus affecting the heat exchange performance of heat exchanger 130.

[0037] In some embodiments of this application, the first part 131 includes multiple rows of heat exchange tubes 136, and the second part 132 includes multiple rows of heat exchange tubes 136. The number of rows of heat exchange tubes 136 in the first part 131 is less than the number of rows of heat exchange tubes 136 in the second part 132.

[0038] By making the number of rows of heat exchange tubes 136 in the second part 132 greater than the number of rows of heat exchange tubes 136 in the first part 131, the heat exchange efficiency of the second part 132 is effectively improved. This helps to ensure that the heat exchange capacity of the second part 132 can meet the heat exchange requirements of the airflow flowing through the first sidewall 1, and helps to improve the heat exchange effect of the heat exchanger 130 on the airflow.

[0039] In some embodiments of this application, each row of heat exchange tubes 136 in the first part 131 is defined as a first heat exchange tube, and each row of heat exchange tubes 136 in the second part 132 is defined as a second heat exchange tube. The number of first heat exchange tubes in each row is less than the number of second heat exchange tubes in each row. This is beneficial because the heat exchange capacity of the second heat exchange tubes in each row is greater than the heat exchange capacity of the first heat exchange tubes in each row. This is beneficial because the heat exchange capacity of the second part 132 is greater than the heat exchange capacity of the first part 131. This is beneficial because the heat exchange capacity of the second part 132 can meet the heat exchange requirements of the airflow flowing through the first sidewall 1, and it is beneficial to improve the heat exchange effect of the heat exchanger 130 on the airflow.

[0040] Referring to Figures 2 and 3, in some embodiments of this application, the first sidewall 1 is the bottom wall of the air outlet 111.

[0041] Considering the insufficient space on the upper side of the air outlet 111 (i.e. above the top wall of the air outlet 111), the bottom wall of the air outlet 111 can be set as an expansion surface with a curved shape that is recessed in the direction away from the second side wall 2. This facilitates the processing of the air outlet 111, helps reduce the noise generated when the airflow flows through the air outlet 111, and avoids the airflow from flowing out of the air outlet 111 along the second direction due to the expansion surface with a curved shape being set on the connecting wall 3 of the air outlet 111. This avoids the airflow from not being able to flow sufficiently through the heat exchanger 130 due to the airflow flowing along the second direction after it flows out of the air outlet 111, thus improving the heat exchange effect between the airflow and the heat exchanger 130.

[0042] "First direction" refers to the height direction of the duct unit 100, and "second direction" refers to the length direction of the duct unit 100. For specific direction diagrams, please refer to Figures 2 and 3.

[0043] Referring to Figures 2 and 3, in some embodiments of this application, the expansion surface is formed as an arc surface.

[0044] The bottom wall of the air outlet 111 is formed as a concave arc surface in the direction away from its top wall. The arc surface has less resistance to airflow compared to other curved surfaces (such as conical surfaces), which helps to further reduce the noise generated when the airflow passes through the air outlet 111, and thus helps to further reduce the noise generated when the air duct machine 100 is working. At the same time, the arc surface is easy to process, which helps to improve the processing convenience of the air outlet 111.

[0045] Referring to Figure 3, in some embodiments of this application, the length of the air outlet 111 in the second direction is L, the arc length of the expansion surface is R, and L and R satisfy the relationship: 1.015≤R / L≤1.34, and the first direction and the second direction are set perpendicularly.

[0046] By designing the length of the air outlet 111 and the arc length of the expansion surface, it is beneficial to ensure that the air velocity distribution after the air flows through the air outlet 111 is within a suitable range, which is beneficial to improving the comfort of the air outlet of the duct unit 100 and improving the heat exchange effect of the heat exchanger 130 on the airflow, thereby improving the comfort of the air outlet temperature of the duct unit 100 and thus improving the user experience.

[0047] Referring to Figures 2 and 3, in some embodiments of this application, the air outlet 111 includes a connecting wall 3 disposed opposite to each other, and the first side wall 1 and the second side wall 2 are connected by the connecting wall 3; in the first direction, the height of the connecting wall 3 is H1, the maximum height of the air outlet 111 is H2, β is defined as H2 / H1, and β satisfies the relationship: 1.18≤β≤1.83.

[0048] Two connecting walls 3 are arranged opposite each other in the second direction and are used to connect the first side wall 1 and the second side wall 2. The height dimension of the connecting wall 3 in the first direction is defined as H1. The distance between the top wall of the air outlet 111 and the farthest position of the expansion surface is defined as the maximum height H2 of the air outlet 111. By designing the height dimension of the connecting wall 3 and the maximum height of the air outlet 111, it is beneficial to ensure that the air velocity distribution after the air flows through the air outlet 111 is within a suitable range, which is beneficial to improving the comfort of the air outlet of the duct unit 100 and improving the heat exchange effect of the heat exchanger 130 on the airflow, thereby improving the comfort of the air outlet temperature of the duct unit 100 and thus improving the user experience.

[0049] Referring to Figures 2 to 4 and Figure 6, in some embodiments of this application, N2 and β satisfy the relationship: 15.5≤N2 / β≤24.

[0050] By designing the correlation between the number N2 of heat exchange tubes 136 in the second part 132, the height H1 of the connecting wall 3 of the air outlet 111, and the maximum height H2 of the air outlet 111, and through simulation analysis, it is found that when the ratio of the number N2 of heat exchange tubes 136 in the second part 132 to the maximum height H2 of the air outlet 111 and the height H1 of the connecting wall 3 satisfies the relationship: 15.5≤N2 / β≤24, where β=H2 / H1, the heat exchange capacity of the heat exchanger 130 is within the optimal range, that is, the heat exchange performance of the heat exchanger 130 is within the optimal range, so as to improve the heat exchange efficiency of the heat exchanger 130 to the airflow and achieve high-efficiency heat exchange of the heat exchanger 130.

[0051] In some embodiments of this application, the height of the first part 131 in the first direction is H3, where H3 ≤ H1.

[0052] In the first direction, the height of the first part 131 is less than the height of the connecting wall 3, which is beneficial to the second part 132 being opposite to the first side wall 1, thereby facilitating the second part 132 to exchange heat with the airflow flowing through the first side wall 1, which is beneficial to improving the heat exchange efficiency of the heat exchanger 130 to the airflow and to achieving high-efficiency heat exchange of the heat exchanger 130.

[0053] Referring to Figures 1 and 4, in some embodiments of this application, the heat exchanger 130 includes a windward side 133 and a leeward side 134. The windward side 133 is opposite to the air outlet 111. After the airflow flows out of the air outlet 111, it flows to the windward side 133 of the heat exchanger 130. The airflow can also flow into the heat exchanger 130 to exchange heat with the heat exchange tube 136. After heat exchange, the airflow flows out of the heat exchanger 130 from the leeward side 134.

[0054] The first part 131 extends obliquely toward the leeward side 134 in a downward direction. The second part 132 includes an oblique part 1321 and a transition part 1322. The transition part 1322 is formed in an arc shape. The upper end of the transition part 1322 is connected to the first part 131, and the lower end of the transition part 1322 is connected to the oblique part 1321. The oblique part 1321 extends obliquely toward the windward side 133 in a downward direction.

[0055] In the top-to-bottom direction, the inclined portion 1321 extends from the leeward side 134 towards the windward side 133, and the first portion 131 extends from the windward side 133 towards the leeward side 134. The upper end of the transition portion 1322 is connected to the first portion 131, and the lower end of the transition portion 1322 is connected to the inclined portion 1321. In the direction extending from the leeward side 134 towards the windward side 133, the distance between the inclined portion 1321 and the first portion 131 gradually increases in the first direction. The increased airflow, when it flows towards the heat exchanger 130 and impacts the windward end of the heat exchanger 130, the inclined portion 1321 and the first portion 131 located on the windward side 133 can guide the airflow, preventing the airflow from scattering outward after impacting the radiator. This reduces the airflow escaping from the windward end of the heat exchanger 130, improves the effect of the airflow flowing towards the heat exchanger 130, and allows the airflow to fully flow through the heat exchanger 130, improving the heat exchange effect of the airflow and thus improving the working efficiency of the heat exchanger 130.

[0056] In addition, constructing the transition section 1322 as an arc shape can effectively reduce the resistance of the heat exchanger 130 to the airflow and help reduce turbulence.

[0057] Referring to Figure 1, in some embodiments of this application, the angle A between the leeward side 134 of the inclined portion 1321 and the horizontal plane satisfies the relationship: 48°≤A≤58°.

[0058] By designing the angle A between the leeward side 134 of the inclined portion 1321 and the horizontal plane, the condensate on the heat exchanger 130 is allowed to flow down, preventing the condensate from accumulating on the heat exchanger 130 and affecting its heat exchange effect. At the same time, it helps to prevent the airflow from the air outlet 111 from being affected because the heat exchanger 130 is too close to the air outlet 111.

[0059] When A < 48°, the condensate has poor flow on the heat exchanger 130, causing it to accumulate and affecting its heat exchange efficiency. When A > 58°, the heat exchanger 130 tends to move closer to the air outlet 111, which reduces the distance between the heat exchanger 130 and the air outlet 111. This obstructs the airflow and reduces the smoothness of the airflow, resulting in poor heat exchange efficiency.

[0060] Table 1 shows the effect of the different angles between the leeward side 134 of the second part 132 and the horizontal plane on the heat exchanger capacity of prototype No. 1 (the ducted air conditioner of the related technology) and prototype No. 2 (the ducted air conditioner 100 of this application) when the number of heat exchange tubes 136 of the heat exchanger 130, the diameter of the heat exchange tubes 136, and the overall expansion height of the heat exchanger 130 are the same. As can be seen from Table 1, the heat exchange capacity of prototype No. 2 (i.e., the ducted air conditioner 100 of this application) is significantly better than that of prototype No. 1 (i.e., the ducted air conditioner of the related technology).

[0061] In prototype 1, the heat exchange capacity of the first part of the heat exchanger is greater than that of the second part, and in prototype 2, the heat exchange capacity of the second part 132 of the heat exchanger 130 is greater than that of the first part 131.

[0062] Table 1

[0063] Referring to Figures 1 and 4, in some embodiments of this application, in the direction from the windward side 133 to the leeward side 134, the width of the inclined portion 1321 is P1, and the width of the first portion 131 is P2, wherein P1 > P2.

[0064] The dimension of the inclined portion 1321 extending from the windward side 133 to the leeward side 134 is defined as the width dimension P1 of the inclined portion 1321. The dimension of the first portion 131 extending from the windward side 133 to the leeward side 134 is defined as the width dimension P2 of the first portion 131. By making the width dimension of the inclined portion 1321 greater than the width dimension of the first portion 131, it is beneficial to make the flow path of the airflow when passing through the inclined portion 1321 greater than the flow path of the airflow when passing through the first portion 131. This allows the airflow to fully exchange heat with the inclined portion 1321, which is beneficial to improving the heat exchange effect between the airflow and the inclined portion 1321.

[0065] Referring to Figure 7, in some embodiments of this application, the heat exchanger 130 satisfies: 1.2≤P1 / P2≤1.45.

[0066] The width dimension P1 of the inclined portion 1321 and the width dimension P2 of the first portion 131 satisfy the relationship: 1.2≤P1 / P2≤1.45. Through simulation test, it is found that when the heat exchanger 130 satisfies 1.2≤P1 / P2≤1.45, the heat exchange capacity of the heat exchanger 130 is within the optimal range, that is, the heat exchange performance of the heat exchanger 130 is within the optimal range, which effectively improves the heat exchange capacity of the heat exchanger 130 and enables the heat exchanger 130 to achieve efficient heat exchange.

[0067] When P1 / P2 < 1.2 or P1 / P2 > 1.45, the heat exchanger 130 has a small heat exchange capacity and poor heat exchange ability, which will lead to poor working performance of the duct machine 100.

[0068] Referring to Figures 1 and 4, in some embodiments of this application, the heat exchanger 130 further includes heat exchange fins 135, and heat exchange tubes 136 pass through the heat exchange fins 135; adjacent heat exchange fins 135 are provided with airflow spaces.

[0069] Multiple heat exchange fins 135 are provided. In the direction extending from the leeward side 134 to the windward side 133, the distance between the heat exchange fins 135 of the inclined portion 1321 and the heat exchange fins 135 of the first portion 131 gradually increases in the first direction. The heat exchange fins 135 located in the transition portion 1322 are connected between the heat exchange fins 135 of the inclined portion 1321 and the heat exchange fins 135 of the first portion 131.

[0070] The heat exchange fins 135 of the first part 131 and the heat exchange fins 135 of the second part 132 can be integrally formed, and then the heat exchange fins 135 can be bent into the above shape through subsequent processing to facilitate the processing and assembly of the heat exchanger 130; the heat exchange fins 135 of the inclined part 1321, the heat exchange fins 135 of the transition part 1322 and the heat exchange fins 135 of the first part 131 can also be set separately, and then processed and assembled by splicing, which is beneficial to the disassembly and maintenance of the heat exchanger 130; of course, it is understood that the processing method of the heat exchanger 130 can be determined according to the actual production requirements, and no specific limitation is made here.

[0071] Meanwhile, multiple heat exchange fins 135 are spaced apart along the thickness direction (or the second direction) of the heat exchange fins 135, and an airflow space is provided between adjacent heat exchange fins 135. Heat exchange tubes 136 are inserted through the multiple heat exchange fins 135 along the thickness direction of the heat exchange fins 135. The heat exchange tubes 136 can dissipate heat through the heat exchange fins 135. Airflow can flow into the airflow space from the windward end of the heat exchanger 130 and come into contact with the heat exchange fins 135 and the heat exchange tubes 136, so that the airflow can exchange heat with the heat exchange fins 135 and the heat exchange tubes 136. The airflow after heat exchange can flow out of the heat exchanger 130 from the leeward side 134. The multiple heat exchange fins 135 can increase the heat exchange area of ​​the heat exchange tubes 136 to further improve the heat exchange effect between the airflow and the heat exchanger 130.

[0072] Referring to Figures 1 and 4, at least a portion of the heat exchange fins 135 are provided with air channels 1351 extending through them in the thickness direction, and the air channels 1351 are connected to the air flow space.

[0073] The airflow channel 1351 on the heat exchange fin 135 is connected to the airflow space on both sides of the heat exchange fin 135 in the thickness direction. The airflow can flow from the airflow space on one side of the heat exchange fin to the airflow space on the other side of the heat exchange fin 135 through the airflow channel 1351. Compared with the airflow directly flowing through the airflow space on one side of the heat exchange fin 135, the airflow path can be extended by setting the airflow channel 1351, so as to improve the heat exchange effect between the airflow and the heat exchange fin 135.

[0074] Air channels 1351 can be provided on a portion of the heat exchange fins 135 to facilitate the manufacturing of the heat exchanger 130; alternatively, air channels 1351 can be provided on all heat exchange fins 135 to improve the heat exchange capacity of the heat exchanger 130. It is understood that the number of heat exchange fins 135 with air channels 1351 can be determined according to the heat exchange requirements of the heat exchanger 130, and no specific limitation is made here.

[0075] Combining Figures 1 and 4, the number of air channels 1351 corresponding to the first part 131 is less than the number of air channels 1351 corresponding to the second part 132.

[0076] Considering that the bottom wall of the air outlet 111 is formed as an arc surface, resulting in a higher airflow velocity through the bottom wall of the air outlet 111, the number of airflow channels 1351 corresponding to the second part 132 is greater than the number of airflow channels 1351 corresponding to the first part 131. This can improve the heat exchange capacity of the second part 132, making the heat exchange capacity of the first part 131 and the second part 132 match the airflow velocity through them, which is beneficial to improving the heat exchange effect of the heat exchanger 130.

[0077] Referring to Figures 1 and 4, in some embodiments of this application, the heat exchange tube 136 closest to the windward side 133 is defined as the first row of heat exchange tubes 1361, and the heat exchange tube 136 closest to the leeward side 134 is defined as the last row of heat exchange tubes 1362. The number of air channels 1351 corresponding to the first row of heat exchange tubes 1361 is greater than the number of air channels 1351 corresponding to the last row of heat exchange tubes 1362.

[0078] In the direction from the windward side 133 to the leeward side 134, the heat exchanger 130 is provided with multiple rows of heat exchange tubes 136. Each row of heat exchange tubes 136 is provided with an airflow channel 1351. When the airflow enters the heat exchanger 130, the airflow preferentially exchanges heat with the first row of heat exchange tubes 1361. At this time, the airflow temperature is the lowest and the temperature difference between the airflow and the first row of heat exchange tubes 1361 is the largest. After the airflow exchanges heat with multiple rows of heat exchange tubes 136 in sequence, it flows to the last row of heat exchange tubes 1362. The temperature difference of 62 is minimized. By making the number of air channels 1351 corresponding to the first row of heat exchange tubes 1361 greater than the number of air channels 1351 corresponding to the last row of heat exchange tubes 1362, the effect of the air channels 1351 set for the first row of heat exchange tubes 1361 on airflow turbulence is improved, the heat exchange time between the airflow and the first row of heat exchange tubes 1361 is increased, and the heat exchange effect of the first row of heat exchange tubes 1361 on the airflow is improved, which is conducive to improving the heat exchange effect of the heat exchanger 130 on the airflow.

[0079] Referring to Figures 1 and 4, in some embodiments of this application, in the first part 131 or the second part 132, the distance between the center of the heat exchange tube 136 on the windward side 133 and the edge of the heat exchange fin 135 is L1; the distance between the center of the heat exchange tube 136 on the leeward side 134 and the edge of the heat exchange fin 135 is L2, where L1 is greater than L2.

[0080] In either Part 131 or Part 132, the distance between the center of the heat exchange tube 136 closest to the windward side 133 and the edge of the heat exchange fin 135 on the windward side 133 is L1, and the distance between the center of the heat exchange tube 136 closest to the leeward side 134 and the edge of the heat exchange fin 135 on the leeward side 134 is L2. By making L1 greater than L2, the area of ​​the heat exchange fin 135 closest to the windward side 133 (i.e., the area between the center of the heat exchange tube 136 closest to the windward side 133 and the edge of the heat exchange fin 135 on the windward side 133) is greater than the area of ​​the heat exchange fin 135 on the leeward side 134 (i.e., the area between the center of the heat exchange tube 136 closest to the windward side 133 and the edge of the heat exchange fin 135 on the windward side 133). The area between the center of heat exchange fin 135 and the edge of heat exchange fin 135 on the leeward side 134 is considered. When the airflow flows in from the windward side 133, the temperature difference between the airflow and the heat exchanger 130 is large. As the airflow gradually flows towards the leeward side 134, the temperature difference between the airflow and the heat exchanger 130 gradually decreases. Therefore, it is necessary to make the heat exchange effect of the heat exchanger 130 near the windward side 133 higher than that near the leeward side 134 in order to meet the heat exchange requirements of the airflow. This is achieved by making the heat exchange area of ​​the heat exchange fin 135 near the windward side 133 larger than that of the heat exchange fin 135 near the leeward side 134 to ensure the heat exchange effect of the heat exchanger 130 and meet the different heat exchange requirements of the airflow.

[0081] Referring to Figures 1, 4 and 8, in some embodiments of this application, the heat exchanger 130 satisfies the relationship: 1.2≤L1 / L2≤1.45.

[0082] In either the first part 131 or the second part 132, the distance between the center of the heat exchange tube 136 arranged near the windward side 133 and the edge of the heat exchange fin 135 located on the windward side 133 is L1, and the distance between the center of the heat exchange tube 136 arranged near the leeward side 134 and the edge of the heat exchange fin 135 located on the leeward side 134 is L2. Through simulation tests, it is found that when the heat exchanger 130 satisfies the relationship 1.2≤L1 / L2≤1.45, the heat exchange capacity of the heat exchanger 130 is within the optimal range, that is, the heat exchange performance of the heat exchanger 130 is in the optimal range, which effectively improves the heat exchange capacity of the heat exchanger 130 and enables the heat exchanger 130 to achieve efficient heat exchange.

[0083] When L1 / L2 < 1.2 and L1 / L2 > 1.45, the heat exchanger 130 has a small heat exchange capacity and poor heat exchange ability, which can easily lead to poor working performance of the duct air conditioner 100.

[0084] Referring to Figures 1, 4, and 9, in some embodiments of this application, the airflow channel 1351 includes a first airflow channel a, and the heat exchange fins 135 include: a body portion 1352, the body portion 1352 including a plurality of through holes for passing through the heat exchange tube 136; the body portion 1352 includes at least one set of first turbulence groups 13521, each set of first turbulence groups 13521 including a plurality of louvers c, each louver c being connected to the body portion 1352, and the first airflow channel a being defined between adjacent louvers c.

[0085] The main body 1352 is provided with a plurality of through holes arranged at intervals. A plurality of heat exchange tubes 136 are provided in a one-to-one correspondence with the plurality of through holes. Each heat exchange tube 136 can be inserted through the through hole into the heat exchange fin 135, and the heat exchange tube 136 can exchange heat through the heat exchange fin 135. The heat exchange fin 135 can increase the heat exchange area of ​​the heat exchange tube 136, which is beneficial to improving the heat exchange effect of the heat exchange tube 136.

[0086] The main body 1352 is provided with a first turbulence group 13521, which includes multiple louvers c. The louvers c are used to turbulent the airflow. The louvers c are connected to the main body 1352 to ensure the stability of the louvers c. Multiple airflow channels 1351 are formed on the main body 1352. The multiple airflow channels 1351 include a first airflow channel a. The first airflow channel a is formed by the space between adjacent louvers c. Each first airflow channel a is spaced apart. When the airflow flows through the heat exchange fins 135, it can flow into the first airflow channel a on one side of the heat exchange fins 135 and flow to the other side of the heat exchange fins 135. The first airflow channel a can increase the time for the airflow to flow through the heat exchange fins 135, so that the airflow can fully exchange heat with the heat exchange fins 135, which is beneficial to improving the heat exchange effect of the heat exchange tube 136 on the airflow, thereby improving the heat exchange performance of the heat exchanger 130.

[0087] Multiple first turbulence groups 13521 can be provided, for example, there can be 2, 3 or 4 first turbulence groups 13521. Multiple first turbulence groups 13521 are arranged at intervals on the main body 1352, which is conducive to further improving the heat exchange effect between the heat exchange fins 135 and the airflow, thereby further improving the heat exchange performance of the heat exchanger 130. It is understood that the number of first turbulence groups 13521 can be determined according to the heat exchange requirements of the heat exchanger 130, and no specific limitation is made here.

[0088] In related technologies, the heat exchange time between the airflow and the fins is short, and the airflow cannot fully exchange heat, resulting in poor heat exchange effect of the fins on the airflow and low heat utilization rate of the heat exchange tubes, thus reducing the heat exchange performance of the heat exchanger.

[0089] This application increases the time for airflow to pass through the heat exchange fins 135 and the heat exchange tubes 136 by setting a first turbulence group 13521 on the heat exchange fins 135, thereby improving the heat utilization rate of the heat exchange tubes 136 and allowing the airflow to fully exchange heat, thus improving the heat exchange performance of the heat exchanger 130. In addition, the first turbulence group 13521 also has the effect of reducing noise.

[0090] Referring to Figures 1, 4 and 10, in some embodiments of this application, the airflow channel 1351 further includes a second airflow channel b, and the heat exchange fins 135 further include at least one set of second turbulence groups 1353. Each set of second turbulence groups 1353 includes a plurality of spaced bridge plates d, and each bridge plate d defines a second airflow channel b between itself and the body portion 1352.

[0091] The second airflow channel b is defined between the bridge plate d and the main body 1352. The second airflow channel b is provided to penetrate the main body 1352 in the thickness direction of the heat exchange fin 135. When the airflow passes through one side of the heat exchange fin 135, the airflow can flow through the second airflow channel b to the other side of the heat exchange fin 135, so that the second turbulence group 1353 can play a turbulence role, further increasing the time for the airflow to pass through the heat exchange fin 135, ensuring that the airflow can fully exchange heat, and further improving the heat exchange effect of the heat exchanger 130 on the airflow.

[0092] There can be one first turbulence group 13521 and multiple second turbulence groups 1353. The specific number of second turbulence groups 1353 can be determined according to the heat exchange requirements of heat exchanger 130, and no specific limit is made here. The first turbulence group 13521 and the second turbulence group 1353 are set at intervals and evenly distributed, which helps to ensure the turbulence effect of the first turbulence section and the second turbulence section, thereby ensuring the heat exchange effect of the airflow.

[0093] Referring to Figures 1 and 4, in some embodiments of this application, the heat exchange tube 136 closest to the windward side 133 is defined as the first row of heat exchange tubes 1361, and the heat exchange tube 136 closest to the leeward side 134 is defined as the last row of heat exchange tubes 1362. The number of first turbulence groups 13521 in the first row of heat exchange tubes 1361 is greater than the number of first turbulence groups 13521 in the last row of heat exchange tubes 1362. Alternatively, the number of first turbulence groups 13521 in the first row of heat exchange tubes 1361 located in the second part 132 is greater than the number of first turbulence groups 13521 in the first row of heat exchange tubes 1361 located in the first part 131.

[0094] After the airflow enters the heat exchanger 130, it preferentially flows through the first row of heat exchange tubes 1361 and exchanges heat. The temperature difference between the airflow and the first row of heat exchange tubes 1361 is the largest. After exchanging heat with multiple rows of heat exchange tubes 136 in sequence, the airflow flows to the last row of heat exchange tubes 1362. The temperature difference between the airflow and the last row of heat exchange tubes 1362 is the smallest. By making the number of first turbulence groups 13521 in the first row of heat exchange tubes 1361 greater than the number of first turbulence groups 13521 in the last row of heat exchange tubes 1362, the turbulence effect of the airflow channels 1351 set for the first row of heat exchange tubes 1361 is improved, the heat exchange time between the airflow and the first row of heat exchange tubes 1361 is increased, and the heat exchange effect of the first row of heat exchange tubes 1361 on the airflow is improved. This is beneficial to improving the heat exchange effect of the heat exchanger 130 on the airflow.

[0095] Because the airflow velocity in the ducted air conditioner 100 flowing towards the second part 132 is greater than the airflow velocity flowing towards the first part 131, the number of first turbulence groups 13521 in the first row of heat exchange tubes 1361 in the second part 132 is greater than the number of first turbulence groups 13521 in the first row of heat exchange tubes 1361 in the first part 131. This results in a greater number of airflow channels 1351 in the first row of heat exchange tubes 1361 in the second part 132 than the number of corresponding airflow channels 1351 in the first row of heat exchange tubes 1361 in the first part 131. This enhances the turbulence effect of the airflow channels 1351 in the second part 132 corresponding to the first row of heat exchange tubes 1361, making the heat exchange effect between the first row of heat exchange tubes 1361 in the second part 132 and the airflow greater than that between the first row of heat exchange tubes 1361 in the first part 131. This ensures that the heat exchange capacity of different positions of the heat exchanger 130 is adapted to the airflow velocity.

[0096] In some specific embodiments, the heat exchange fins 135 can be configured with different turbulence groups in different regions according to the distribution of airflow velocity and the temperature gradient change of airflow through the heat exchange fins 135. The following describes the configuration of the turbulence groups on the heat exchange fins 135, taking the first part 131 of the heat exchanger 130 as having two rows of heat exchange tubes 136 and the second part 132 as having three rows of heat exchange tubes 136. The second part 132 includes a first row of heat exchange tubes 1361, a middle row of heat exchange tubes 1363 and a last row of heat exchange tubes 1362.

[0097] For example, only the first turbulence group 13521 can be provided on the heat exchange fin 135. In this structure, the number of louvers c of each first turbulence group 13521 corresponding to the first row of heat exchange tubes 1361 of the first part 131 can be 4-8, the number of louvers c of each first turbulence group 13521 corresponding to the last row of heat exchange tubes 1362 of the first part 131 can be 2-6, the number of louvers c of each first turbulence group 13521 corresponding to the first row of heat exchange tubes 1361 of the second part 132 can be 4-8, the number of louvers c of the first turbulence group 13521 corresponding to the middle row of heat exchange tubes 1363 of the second part 132 can be 2-6, and the number of louvers c of the first turbulence group 13521 corresponding to the last row of heat exchange tubes 1362 of the second part 132 can be 2-4.

[0098] Alternatively, only the second turbulence group 1353 can be set on the heat exchange fins 135. In this structure, the number of bridge plates d for each second turbulence group 1353 set for the first row of heat exchange tubes 1361 of the first part 131 can be 3-6, the number of bridge plates d for each second turbulence group 1353 set for the last row of heat exchange tubes 1362 of the first part 131 can be 2-5, the number of bridge plates d for each second turbulence group 1353 set for the first row of heat exchange tubes 1361 of the second part 132 can be 3-6, the number of bridge plates d for each second turbulence group 1353 set for the middle row of heat exchange tubes 1363 of the second part 132 can be 2-5, and the number of bridge plates d for each second turbulence group 1353 set for the last row of heat exchange tubes 1362 of the second part 132 can be 2-4.

[0099] Alternatively, a first turbulence group 13521 and a second turbulence group 1353 may be respectively provided on the heat exchange fins 135. Preferably, the first turbulence group 13521 is provided on the heat exchange fins 135 near the windward side 133, and the second turbulence group 1353 is provided on the leeward side 134. For example, the first row of heat exchange tubes 1361 of the second part 132 is provided with the first turbulence group 13521, and the middle row of heat exchange tubes 1363 and the last row of heat exchange tubes 1362 can be provided with the second turbulence group 1353. Alternatively, the first row of heat exchange tubes 1361 and the middle row of heat exchange tubes 1363 of the second part 132 are provided with the first turbulence group 13521, and the last row of heat exchange tubes 1362 is provided with the second turbulence group 1353. The first row of heat exchange tubes 1361 of the first part 131 is provided with the first turbulence group 13521, and the last row of heat exchange tubes 1362 is provided with the second turbulence group 1353.

[0100] Referring to FIG3, in some embodiments of this application, the duct machine 100 further includes a drive motor 140, which is disposed on the duct component 110 and is connected to the drive impeller 120 for transmission. When the drive motor 140 is running, it can make the drive impeller 120 rotate to drive the airflow in the duct machine 100.

[0101] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0102] Although embodiments of this application have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the claims and their equivalents.

Claims

1. A ducted fan engine wherein, include: The air duct component is provided with an air outlet. The first sidewall of the air outlet includes at least an expansion surface with a curved shape that is recessed in a direction away from the second sidewall. The first sidewall and the second sidewall are arranged opposite to each other in a first direction. A drive fan wheel is disposed within the air duct component; A heat exchanger is disposed on the air outlet side of the air duct component. The heat exchanger includes a first part and a second part, wherein, in the first direction, the second part and the first sidewall are located on the same side. On the vertical plane passing through the air outlet, the first part, and the second part, the number of heat exchange tubes in the first part is N1, the number of heat exchange tubes in the second part is N2, and the heat exchanger satisfies the following relationship: N1 < N2.

2. The ducted fan machine of claim 1, wherein, The heat exchanger satisfies 1.6≤N2 / N1≤1.

8.

3. The ducted fan machine according to claim 1 or 2, wherein, The first part includes multiple rows of heat exchange tubes, and the second part includes multiple rows of heat exchange tubes, wherein the number of rows of heat exchange tubes in the first part is less than the number of rows of heat exchange tubes in the second part.

4. The ducted fan machine of claim 3, wherein, Each row of heat exchange tubes in the first part is defined as a first heat exchange tube, and each row of heat exchange tubes in the second part is defined as a second heat exchange tube, wherein the number of first heat exchange tubes in each row is less than the number of second heat exchange tubes in each row.

5. The ducted fan machine according to any one of claims 1-4, wherein, The first sidewall is the bottom wall of the air outlet.

6. The ducted fan machine according to any one of claims 1-5, wherein, The expansion surface is formed as a circular arc surface.

7. The ducted fan machine of claim 6 wherein, The length of the air outlet in the second direction is L, and the arc length of the expansion surface is R. L and R satisfy the relationship: 1.015≤R / L≤1.

34. The first direction and the second direction are set perpendicularly.

8. The ducted fan machine according to any one of claims 1-7, wherein, The air outlet includes a connecting wall disposed opposite to each other, and the first side wall and the second side wall are connected by the connecting wall; In the first direction, the height of the connecting wall is H1, the maximum height of the air outlet is H2, and β is defined as H2 / H1, and β satisfies the relationship: 1.18≤β≤1.

83.

9. The ducted fan machine of claim 8, wherein, N2 and β satisfy the following relationship: 15.5≤N2 / β≤24.

10. The ducted fan machine according to claim 8 or 9, wherein, The height of the first part in the first direction is H3, where H3 ≤ H1.

11. The ducted fan machine according to any one of claims 1-10, wherein, The heat exchanger includes a windward side and a leeward side, with the windward side opposite the air outlet. The first part extends obliquely toward the leeward side in a downward direction. The second part includes an oblique portion and a transition portion. The transition portion is formed in an arc shape. The upper end of the transition portion is connected to the first part, and the lower end of the transition portion is connected to the oblique portion. The oblique portion extends obliquely toward the windward side in a downward direction.

12. The ducted fan machine of claim 11, wherein, The angle A between the leeward side of the inclined section and the horizontal plane satisfies the following relationship: 48°≤A≤58°.

13. The ducted fan machine according to claim 11 or 12, wherein, In the direction from the windward side to the leeward side, the width of the inclined portion is P1, and the width of the first portion is P2, wherein P1 > P2.

14. The ducted fan machine of claim 13, wherein, The heat exchanger satisfies: 1.2≤P1 / P2≤1.

45.

15. The ducted fan machine according to any one of claims 1-14, wherein, The heat exchanger further includes heat exchange fins, and the heat exchange tubes pass through the heat exchange fins; The adjacent heat exchange fins are provided with air flow space, and at least a portion of the heat exchange fins are provided with air flow channels that penetrate through them in the thickness direction, and the air flow channels are connected to the air flow space; The number of air channels corresponding to the first part is less than the number of air channels corresponding to the second part.

16. The ducted fan machine of claim 15, wherein, The heat exchanger includes a windward side and a leeward side. The windward side is opposite to the air outlet. The heat exchange tube closest to the windward side is defined as the first row of heat exchange tubes, and the heat exchange tube closest to the leeward side is defined as the last row of heat exchange tubes. The number of air channels corresponding to the first row of heat exchange tubes is greater than the number of air channels corresponding to the last row of heat exchange tubes.

17. The ducted fan machine of claim 15 or 16, wherein, The heat exchanger includes a windward side and a leeward side. The windward side is opposite to the air outlet. In the first part or the second part, the distance between the center of the heat exchange tube on the windward side and the edge of the heat exchange fin is L1; the distance between the center of the heat exchange tube on the leeward side and the edge of the heat exchange fin is L2, where L1 is greater than L2.

18. The ducted fan engine of any one of claims 15-17, wherein, The airflow channel includes a first airflow channel, and the heat exchange fins include: The body portion includes a plurality of through holes for passing through the heat exchange tube; The main body includes at least one first airflow group, each first airflow group including a plurality of louvers, each louver being connected to the main body, and adjacent louvers defining a first airflow channel.

19. The ducted fan machine of claim 18 wherein, The airflow channel further includes a second airflow channel, and the heat exchange fins further include at least one set of second turbulence groups. Each set of second turbulence groups includes a plurality of spaced-apart bridge plates, and each bridge plate defines a second airflow channel between itself and the body portion.

20. The ducted fan engine of claim 19, wherein, The heat exchanger includes a windward side and a leeward side. The windward side is opposite to the air outlet. The heat exchange tubes closest to the windward side are defined as the first row of heat exchange tubes, and the heat exchange tubes closest to the leeward side are defined as the last row of heat exchange tubes. The number of the first turbulence groups in the first row of heat exchange tubes is greater than the number of the first turbulence groups in the last row of heat exchange tubes. Alternatively, the number of the first turbulence groups in the first row of heat exchange tubes located in the second part is greater than the number of the first turbulence groups in the first row of heat exchange tubes located in the first part.

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