Duct type air conditioner and working method thereof

Abstract

The invention relates to the technical field of air conditioning equipment, in particular to a duct type air conditioner and a working method thereof. The duct type air conditioner comprises a shell, a fan, a V-shaped heat exchanger and an air guide mechanism, the V-shaped heat exchanger comprises a first heat exchanger and a second heat exchanger which are arranged up and down, an opening of the V-shaped heat exchanger faces the air inlet, and the first heat exchanger and the second heat exchanger can independently work in a heating state or a refrigerating state; and the air guide mechanism is arranged between the fan and the V-shaped heat exchanger and is configured to distribute the air quantity blown to the first heat exchanger and the second heat exchanger and adjust the air supply angle to the first heat exchanger and the second heat exchanger. The air guide mechanism adjusts the direction of airflow blowing to the first heat exchanger and the second heat exchanger so as to increase the vector airflow speed in the direction perpendicular to the heat exchangers.

Description

Technical Field

[0001] The present application relates to the technical field of air conditioning equipment, and in particular to an air duct unit and a working method thereof. Background Art

[0002] When ordinary duct units are used for cooling and dehumidification, it is easy to cause the indoor temperature to drop too much, which is uncomfortable. As a result, constant temperature dehumidification duct units are produced. When dehumidifying, constant temperature dehumidification duct units connect two or more heat exchangers in series, and use throttling devices to make the heat exchangers have both cooling and dehumidification and heating functions. The cold and hot air flows reach a constant temperature after mixing. Two or more heat exchangers for constant temperature dehumidification are placed vertically side by side, and the outlet air first passes through the cooling and dehumidification heat exchanger, and then passes through the heating heat exchanger. With this placement, the air volume at each position on the heat exchanger is similar, and the heat exchange is uniform, but the airflow needs to pass through the two heat exchangers in sequence, which has large wind resistance and poor capacity. Summary of the invention

[0003] In order to solve the above technical problems, the present application provides a duct machine and a working method thereof.

[0004] In order to achieve the above-mentioned purpose, according to a first aspect of an embodiment of the application, a duct air conditioner is provided.

[0005] The duct machine provided according to the embodiment of the present application includes:

[0006] A casing, wherein an air duct is formed therein, and an air inlet and an air outlet are formed at two ends of the air duct;

[0007] a fan, disposed in a region of the air duct close to the air inlet, and configured to introduce airflow from the air inlet into the air duct;

[0008] A V-shaped heat exchanger, comprising a first heat exchanger and a second heat exchanger arranged up and down, the opening of the V-shaped heat exchanger faces the air inlet, and the first heat exchanger and the second heat exchanger can independently work in a heating state or a cooling state;

[0009] The air guide mechanism is disposed between the fan and the V-shaped heat exchanger, and is configured to distribute the air volume blown to the first heat exchanger and the second heat exchanger and to adjust the air supply angle to the first heat exchanger and the second heat exchanger.

[0010] Furthermore, the air guide mechanism includes a middle partition plate arranged between the fan and the V-shaped heat exchanger, and a plurality of guide vanes rotatably arranged on the middle partition plate.

[0011] Furthermore, the air guiding mechanism includes a flexible air duct.

[0012] Furthermore, the angle between the guide vane and the horizontal plane is α, and the angle between the first heat exchanger and the horizontal plane is β, which satisfies: 0°≤α<90°, 0°<β≤90° and (α+β)≤90°.

[0013] Furthermore, the angle between the guide vane and the horizontal plane is α, and the angle between the first heat exchanger and the horizontal plane is β, which satisfies: 0°≤α≤30°, 30°≤β≤45°.

[0014] 6. The duct air conditioner according to any one of claims 1 to 5, characterized in that the duct air conditioner has a cooling mode, in which:

[0015] The first heat exchanger and the second heat exchanger both operate in a cooling state;

[0016] The air guide mechanism evenly distributes air volume to the first heat exchanger and the second heat exchanger at symmetrical air supply angles.

[0017] Furthermore, the air duct unit has a heating mode, in which:

[0018] The first heat exchanger and the second heat exchanger both operate in a heating state;

[0019] The air guide mechanism evenly distributes air volume to the first heat exchanger and the second heat exchanger at symmetrical air supply angles.

[0020] Furthermore, the duct air conditioner has a dehumidification mode. In the dehumidification mode:

[0021] One of the first heat exchanger and the second heat exchanger operates in a cooling state, and the other operates in a heating state;

[0022] The air volume distributed by the air guide mechanism to the heat exchanger working in the cooling state is greater than the air volume distributed to the heat exchanger working in the heating state.

[0023] In order to achieve the above-mentioned purpose, according to the second aspect of the embodiment of the application, a working method of a ducted air conditioner is provided, which is applied to the ducted air conditioner provided in the first aspect of the application. The working method comprises:

[0024] Determine whether the photovoltaic modules meet the power generation conditions;

[0025] If the photovoltaic module meets the power generation condition, the photovoltaic module generates electricity to supply the air conditioning system, and when the photovoltaic module generates insufficient electricity, the external power grid provides additional power to the air conditioning system;

[0026] If the photovoltaic assembly does not meet the power generation conditions, it is evaluated whether the energy storage device has sufficient power. If the energy storage device has sufficient power, the energy storage device will supply power to the air-conditioning system. If the energy storage device has insufficient power, the external power grid will supply power to the air-conditioning system.

[0027] Furthermore, the working method also includes:

[0028] While the photovoltaic module generates electricity to supply the air conditioning system, evaluating whether the energy storage device needs to be charged;

[0029] If the energy storage device needs to be charged, the excess electricity supplied by the photovoltaic module other than the air conditioning system is used to charge the energy storage device;

[0030] If the energy storage device does not need to be charged, the excess electricity supplied by the photovoltaic components other than the air-conditioning system is fed to the external power grid.

[0031] In order to achieve the above-mentioned purpose, according to the third aspect of the embodiment of the application, a working method of a photovoltaic storage air conditioner is provided, which is applied to the photovoltaic storage air conditioner provided in the first aspect of the application, and the photovoltaic storage air conditioner is not connected to an external power grid in a normal working state. The working method includes:

[0032] Obtaining the working mode of the duct air conditioner;

[0033] According to the working mode, the working states of the first heat exchanger and the second heat exchanger are controlled, and the air volume blown to the first heat exchanger and the second heat exchanger is distributed through the air guide mechanism, and the air supply angle to the first heat exchanger and the second heat exchanger is adjusted.

[0034] Furthermore, when the working mode of the air duct unit is a dehumidification mode, one of the first heat exchanger and the second heat exchanger is controlled to work in a cooling state, and the other one is controlled to work in a heating state;

[0035] Get target humidity D 目标 、Ambient humidity D 环 , calculate the humidity difference △D=D 环 -D 目标 ;

[0036] If △D≥B, the ratio of the air volume allocated to the heat exchanger working in the cooling state to the air volume allocated to the heat exchanger working in the heating state shall be implemented according to M1; if A≤△D<B, the ratio of the air volume allocated to the heat exchanger working in the cooling state to the air volume allocated to the heat exchanger working in the heating state shall be implemented according to M2; if 0≤△D<A, the ratio of the air volume allocated to the heat exchanger working in the cooling state to the air volume allocated to the heat exchanger working in the heating state shall be implemented according to M3; wherein B>A, M1>M2>M3.

[0037] The duct machine and its working method provided in the embodiment of the present application have the following beneficial effects: the air guide mechanism adjusts the direction of the airflow blowing toward the first heat exchanger and the second heat exchanger to increase the vector airflow velocity in the direction perpendicular to the heat exchanger. Set the angle between the air outlet direction of the air guide mechanism and the horizontal plane to α, the angle between the first heat exchanger and the horizontal plane to β, and the initial airflow velocity to V, then the vector airflow velocity in the direction perpendicular to the heat exchanger is sin(α+β)·V, the minimum value of the angle between the air outlet direction of the air guide mechanism and the horizontal plane is 0°, that is, the air outlet direction of the air guide mechanism 300 is horizontal, and the maximum value of the angle between the air outlet direction of the air guide mechanism and the horizontal plane is 90°-β, that is, the air outlet direction of the air guide mechanism is directly perpendicular to the heat exchanger, so 0°≤(α+β)≤90° is satisfied. Compared with the horizontal air outlet mode, the increase ratio of the vector airflow velocity in the direction perpendicular to the heat exchanger in this embodiment can reach [sin(α+β)-sinβ]*100%. BRIEF DESCRIPTION OF THE DRAWINGS

[0038] The drawings constituting a part of this application are used to provide a further understanding of this application, so that other features, purposes and advantages of this application become more obvious. The schematic embodiment drawings and their descriptions of this application are used to explain this application and do not constitute an improper limitation on this application. In the drawings:

[0039] Figure 1 A structural diagram of a duct machine provided in the related art is schematically given;

[0040] Figure 2 for Figure 1 The air flow simulation diagram of the duct machine in working state is shown;

[0041] Figure 3 A structural diagram of another duct machine provided in the related art is schematically given;

[0042] Figure 4 for Figure 3 The air flow simulation diagram of the duct machine in working state is shown;

[0043] Figure 5 The structure diagram of the duct unit provided in the embodiment of the present application in cooling or heating mode is schematically shown;

[0044] Figure 6 for Figure 5 The air flow simulation diagram of the duct machine in working state is shown;

[0045] Figure 7 is a graphical illustration of the angle α between the guide vane and the horizontal plane;

[0046] Figure 8is a graphic illustration of the angle β between the heat exchanger and the horizontal plane;

[0047] Fig. 9 The structural diagram of the duct air conditioner in the dehumidification mode provided in the embodiment of the present application is schematically given;

[0048] Fig.10 for Fig. 9 The air flow simulation diagram of the duct machine in working state is shown;

[0049] Fig.11 A flowchart of the dehumidification working method of the duct air conditioner provided in the present application is schematically given.

[0050] In the figure:

[0051] 100, housing;

[0052] 110. Air duct;

[0053] 120. Air inlet;

[0054] 130. Air outlet;

[0055] 200, fan;

[0056] 300, air guide mechanism;

[0057] 310, middle partition;

[0058] 320, guide vane;

[0059] 400, a first heat exchanger;

[0060] 500. Second heat exchanger. DETAILED DESCRIPTION

[0061] In order to enable those skilled in the art to better understand the solution of the present application, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work should fall within the scope of protection of the present application.

[0062] It should be noted that the terms "including" and "having" and any variations thereof in the specification and claims of the present application and the above-mentioned drawings are intended to cover non-exclusive inclusions. For example, a system, product or device comprising a series of units is not necessarily limited to those units explicitly listed, but may include units that are not explicitly listed or inherent to these products or devices.

[0063] In this application, the directions or positional relationships indicated by the terms "upper", "lower", "inner", "middle", "outer", etc. are based on the directions or positional relationships shown in the drawings. These terms are mainly used to better describe the present application and its embodiments, and are not used to limit the indicated devices, elements or components to have a specific direction, or to be constructed and operated in a specific direction.

[0064] In addition, some of the above terms may be used to express other meanings in addition to indicating orientation or positional relationship. For example, the term "on" may also be used to express a certain dependency or connection relationship in some cases. For those of ordinary skill in the art, the specific meanings of these terms in this application can be understood according to specific circumstances.

[0065] In addition, the terms "disposed", "connected", and "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0066] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application may be combined with each other.

[0067] like Figure 1 As shown, in the related art, the duct air conditioner includes a casing 100, a fan 200, a middle partition 310, a first heat exchanger 400 and a second heat exchanger 500. A horizontally arranged air duct 110 is formed in the casing 100, and an air inlet 120 and an air outlet 130 are formed at both ends of the air duct 110; the middle partition 310 divides the air duct 110 in the duct air conditioner into two areas, the centrifugal fan 200 is on one side of the middle partition 310, and the first heat exchanger 400 and the second heat exchanger 500 are on the other side of the middle partition 310; the fan 200 is arranged in the area of ​​the air duct 110 close to the air inlet 120, and is configured to introduce the airflow from the air inlet 120 into the air duct 110; the first heat exchanger 400 and the second heat exchanger 500 are placed vertically side by side in the air duct 110 and perpendicular to the extension direction of the air duct 110. During operation, the first heat exchanger 400 is in a cooling state, and the second heat exchanger 500 is in a heating state. The fan 200 drives the airflow to first pass through the first heat exchanger 400 to complete cooling and dehumidification, and then pass through the second heat exchanger 500 to complete heating, thereby achieving a constant temperature dehumidification function. The air outlet direction of the fan 200 through the middle partition 310 is horizontal, and the angles with the two heat exchangers are both 90°. The airflow velocity at the middle partition 310 is set to V, and the vector airflow velocity in the direction perpendicular to the heat exchanger is V·sin90°=V. By Figure 2 As can be seen from the airflow simulation effect diagram, the wind enters from the left boundary, and the wind pressure at each point on the right boundary is uniform, and the wind pressure on the upper and lower walls is large. The first heat exchanger 400 and the second heat exchanger 500 are placed vertically side by side. Although the vector wind speed is large, the wind pressure on the heat exchanger surface parallel to the right boundary is uniform, and the overall heat exchange is uniform, this placement method causes a large wind pressure on the upper and lower walls, and the airflow needs to pass through the two heat exchangers in sequence, resulting in large wind resistance and poor capacity.

[0068] like Figure 3 As shown, in the related art, the duct air conditioner includes a casing 100, a fan 200, a middle partition 310, a first heat exchanger 400 and a second heat exchanger 500. A horizontally arranged air duct 110 is formed in the casing 100, and an air inlet 120 and an air outlet 130 are formed at both ends of the air duct 110; the middle partition 310 divides the air duct 110 in the duct air conditioner into two areas, the centrifugal fan 200 is on one side of the middle partition 310, and the first heat exchanger 400 and the second heat exchanger 500 are on the other side of the middle partition 310; the fan 200 is arranged in the area of ​​the air duct 110 close to the air inlet 120, and is configured to introduce the airflow from the air inlet 120 into the air duct 110; the first heat exchanger 400 and the second heat exchanger 500 are symmetrically arranged up and down in the air duct 110 to form a V-shaped heat exchanger, and the opening of the V-shaped heat exchanger faces the air inlet 120. During operation, the first heat exchanger 400 is in a cooling state, and the second heat exchanger 500 is in a heating state. After the fan 200 drives the airflow into the air duct 110, a part of the airflow passes through the first heat exchanger 400 to complete cooling and dehumidification, and the other part passes through the second heat exchanger 500 to complete heating. The two parts of the airflow are mixed after passing through the heat exchanger, thereby achieving a constant temperature dehumidification function. The air outlet direction of the fan 200 through the middle partition 310 is horizontal, and the angles between the two heat exchangers and the horizontal direction are both 40°, that is, the angle between the air outlet direction and the heat exchanger is 40°. The airflow velocity at the middle partition 310 is set to V, and the vector airflow velocity in the direction perpendicular to the heat exchanger is V·sin40°≈0.64V. By Figure 4 The airflow simulation effect diagram shows that the wind enters from the left boundary, and the wind pressure at each point on the right boundary is uniform, and the wind pressure is large on the upper and lower walls. However, when the V-shaped heat exchanger is placed up and down, the vector wind speed drops by 36%, and the heat exchanger is at a large angle of 50° with the right boundary. The wind pressure of the heat exchanger is uneven, and the wind pressure on the upper and lower walls is large, resulting in uneven overall heat exchange.

[0069] Based on this, Figure 5As shown, the embodiment of the present application provides a duct air conditioner, which mainly includes a housing 100, a fan 200, a V-shaped heat exchanger and an air guide mechanism 300, wherein an air duct 110 is formed in the housing 100, and an air inlet 120 and an air outlet 130 are formed at both ends of the air duct 110; the fan 200 is arranged in the air duct 110 in an area close to the air inlet 120, and is configured to introduce airflow from the air inlet 120 into the air duct 110; the V-shaped heat exchanger includes a first heat exchanger arranged up and down The first heat exchanger 400 and the second heat exchanger 500 are respectively provided with a V-shaped heat exchanger 400 and a second heat exchanger 500, the opening of the V-shaped heat exchanger faces the air inlet 120, and the first heat exchanger 400 and the second heat exchanger 500 can independently operate in a heating state or a cooling state; the air guide mechanism 300 is arranged between the fan 200 and the V-shaped heat exchanger, and is configured to distribute the air volume blown to the first heat exchanger 400 and the second heat exchanger 500 and to adjust the air supply angle to the first heat exchanger 400 and the second heat exchanger 500.

[0070] In the above embodiment, the air guide mechanism 300 adjusts the direction of the airflow blowing toward the first heat exchanger 400 and the second heat exchanger 500 to increase the vector airflow velocity in the direction perpendicular to the heat exchanger. Set the angle between the air outlet direction of the air guide mechanism 300 and the horizontal plane to α, the angle between the first heat exchanger 400 and the horizontal plane to β, and the initial airflow velocity to V, then the vector airflow velocity in the direction perpendicular to the heat exchanger is sin(α+β)·V, the minimum value of the angle between the air outlet direction of the air guide mechanism 300 and the horizontal plane is 0°, that is, the air outlet direction of the air guide mechanism 300 is horizontal, and the maximum value of the angle between the air outlet direction of the air guide mechanism 300 and the horizontal plane is 90°-β, that is, the air outlet direction of the air guide mechanism 300 is directly perpendicular to the heat exchanger, so 0°≤(α+β)≤90° is satisfied, relative to Figure 3 For the horizontal air outlet mode shown, in this embodiment, the increase ratio of the vector air flow velocity in the direction perpendicular to the heat exchanger can reach [sin(α+β)-sinβ]*100%.

[0071] Still taking the example that the angle between the first heat exchanger 400 and the second heat exchanger 500 and the horizontal plane is 40°, assuming that the inclination angle α of the air outlet direction of the air guide mechanism 300 and the horizontal plane is 10°, at this time, the angle between the air outlet direction and the two heat exchangers is 50°, and the vector velocity of the air flow in the direction perpendicular to the heat exchanger is V·sin50°≈0.77V. Compared with Figure 3 For the horizontal air outlet mode shown in FIG. 1 , the vector airflow velocity in the direction perpendicular to the heat exchanger can be increased by 13%. The air outlet is further symmetrically distributed to the first heat exchanger 400 and the second heat exchanger 500 through the air guide mechanism 300, and the airflow simulation effect diagram is as shown in FIG. Figure 6As shown in the figure, the simulation results show that when the wind enters from the left boundary, the wind pressure in the upper, middle and lower areas on the right boundary is large, and the wind pressure on the upper and lower walls is small. After adding the wind guide mechanism 300, the vector wind speed is increased by 13% compared with the case without adding the wind guide structure, the wind pressure on the upper and lower walls is reduced, the wind pressure uniformity of the heat exchanger is improved, and the overall heat exchange uniformity is improved.

[0072] In some embodiments, the air guide mechanism 300 includes a middle partition 310 disposed between the fan 200 and the V-shaped heat exchanger, and a plurality of guide vanes 320 rotatably disposed on the middle partition 310. The middle partition 310 is disposed between the fan 200 and the V-shaped heat exchanger, and is used to separate the airflow channel and provide installation and rotation support for the guide vanes 320. The plurality of guide vanes 320 are rotatably mounted on the middle partition 310, and the angle can be adjusted according to different operating conditions. The rotation of the guide vanes 320 adjusts the direction of the airflow, optimizes the airflow distribution, and increases the vector airflow velocity in the direction perpendicular to the heat exchanger. In addition, the airflow guided by the fan 200 can be proportionally distributed to the first heat exchanger 400 and the second heat exchanger 500, thereby improving the accuracy of airflow control.

[0073] When the airflow generated by the fan 200 passes through the middle partition 310, it will be guided by the guide vane 320 on the middle partition 310. The angle adjustment of the guide vane 320 determines the direction and distribution ratio of the airflow when it enters the V-shaped heat exchanger. Specifically, by adjusting the ratio of the upward rotation and downward rotation of the guide vane 320, the air volume ratio of the airflow blowing to the first heat exchanger 400 and the second heat exchanger 500 can be changed; the rotation angle of the guide vane 320 changes the incident angle of the airflow entering the heat exchanger, thereby optimizing the vector airflow velocity perpendicular to the direction of the heat exchanger. The guide vane 320 in the air guide mechanism 300 can flexibly adjust the angle according to different operating modes (such as cooling, heating, constant temperature dehumidification) to change the airflow distribution ratio. For example, when the first heat exchanger 400 and the second heat exchanger 500 are in different heat exchange states (such as one cooling and one heating), the guide vane 320 can reasonably distribute the airflow to maximize the heat exchange efficiency; for example, when the two heat exchangers are in heating or cooling state at the same time, the guide vane 320 can optimize the airflow distribution and improve the overall uniformity.

[0074] The guide vane 320 changes the airflow direction and forms a superposition effect with the angle between the first heat exchanger 400 and the second heat exchanger 500, so that the vector airflow velocity in the direction perpendicular to the heat exchanger is significantly increased. The increased airflow velocity can enhance the heat exchange effect between the airflow and the heat exchanger surface, thereby improving the overall performance.

[0075] By integrating the guide vane 320 on the middle partition 310, the structure of the air guide mechanism 300 is more compact, which is convenient for installation in the limited space of the air duct machine. The middle partition 310 is used as both an airflow separation component and a guide vane 320 support component. The integrated design reduces the number of components and reduces the manufacturing cost.

[0076] In the embodiment of the present application, by introducing the air guide mechanism 300 of the middle partition plate 310 and a plurality of rotatable guide vanes 320, the air duct unit has been significantly improved in terms of air flow distribution and direction control. This design not only increases the air flow vector velocity perpendicular to the direction of the heat exchanger, but also improves the uniformity of air flow distribution, further improves the overall performance of the heat exchanger, and provides an effective solution for efficient constant temperature dehumidification of the air duct unit.

[0077] In some embodiments, Figure 7 and 8 As shown, the angle between the guide vane 320 and the horizontal plane is α, the angle between the first heat exchanger 400 and the horizontal plane is β, and since the first heat exchanger 400 and the second heat exchanger 500 are symmetrically arranged up and down, the angle between the second heat exchanger 500 and the horizontal plane is also β, which satisfies: 0°≤α<90°, 0°<β≤90° and (α+β)≤90°. It should be noted that the guide vane 320 in the present application can be as follows Figure 7 As shown in the upper part, it is inclined upward relative to the horizontal plane, and can also be as shown in the upper part. Figure 7 As shown in the lower part, it is inclined downward relative to the horizontal plane. For example, an upward inclination of 10° and a downward inclination of 10° relative to the horizontal plane can both be recorded as α=10°. Similarly, Figure 8 As shown, when the first heat exchanger 400 and the second heat exchanger 500 are symmetrically arranged, although the inclination directions of the heat exchangers forming the angle are opposite, the first heat exchanger 400 is inclined at 40° relative to the horizontal plane, and the second heat exchanger 500 is also inclined at 40° relative to the horizontal plane, and the angles between the two and the horizontal plane can be recorded as β=40°.

[0078] 0°≤α<90° enables the inclination angle of the guide vane 320 to be gradually adjusted from horizontal air outlet to vertical direction, but not completely vertical. 0°<β≤90° enables the inclination angle of the first heat exchanger 400 or the second heat exchanger 500 to be placed from nearly horizontal to nearly vertical, but not completely horizontal. (α+β)≤90° is a joint constraint condition, that is, the sum of the air outlet direction adjusted by the guide vane 320 and the installation angle of the first heat exchanger 400 does not exceed 90°, ensuring the reasonable matching of the air guide angle and the heat exchanger direction to avoid the airflow deviating from the heat exchanger surface.

[0079] Under the above constraints, the angle α of the guide vane 320 and the inclination angle β of the heat exchanger jointly determine the contact angle between the airflow and the surface of the heat exchanger, which can enable the airflow to blow better toward the surface of the heat exchanger and obtain a relatively large component in the direction perpendicular to the heat exchanger, thereby improving the heat exchange efficiency.

[0080] Further preferably, the angle between the guide vane 320 and the horizontal plane is α, and the angle between the first heat exchanger 400 and the horizontal plane is β, which satisfies: 0°≤α≤30°, 30°≤β≤45°.

[0081] The factors to be considered for the inclination angle β of the heat exchanger are mainly the structure of the heat exchanger itself. The heat exchanger usually consists of three or two rows of heat exchange tubes. The diameters of the heat exchange tubes are φ5mm and φ7mm, which are more commonly used. The thickness of the duct machine casing 100 is generally 200mm. Considering the above structural settings, the advantageous value range of β is 30° to 45°, and further preferably 36° to 42°.

[0082] The factors to be considered for the angle α of the guide vane 320 are: the horizontal distance between the guide vane 320 and the heat exchanger is generally about 100 mm, the thickness of the duct casing 100 is generally 200 mm, the distribution of the air guide blades and the distance from the top and bottom of the casing 100; assuming that the guide vane 320 is designed to be 4 pieces, the distance from the top of the casing 100 can be set to 38 mm, 74 mm, 110 mm, and 146 mm respectively. At this time, the advantageous value range of α is 0° to 30°.

[0083] The air duct unit may have a variety of operating modes, including cooling mode, heating mode and dehumidification mode.

[0084] like Figure 5 and 6 As shown, when the air duct unit operates in cooling mode: the first heat exchanger 400 and the second heat exchanger 500 both operate in cooling state; the air guide mechanism 300 evenly distributes the air volume to the first heat exchanger 400 and the second heat exchanger 500 at symmetrical air supply angles.

[0085] The first heat exchanger 400 and the second heat exchanger 500 both work in a cooling state, and are used to reduce the air flow temperature and realize the overall cooling function. The air guide mechanism 300 adjusts the angle of the guide vane 320 to supply air to the first heat exchanger 400 and the second heat exchanger 500 at a symmetrical air supply angle, that is, the air flow rate allocated to the first heat exchanger 400 and the second heat exchanger 500 is basically equal, thereby ensuring the consistency of the heat exchange efficiency of the two and improving the overall cooling effect. Through the symmetrical working mode and uniform air supply design of the dual heat exchangers, the ambient temperature can be quickly reduced, and the duct machine can be ensured to operate stably and efficiently in the cooling mode. When the ambient temperature is high, the symmetrical cooling mode of the duct machine can significantly improve the heat exchange efficiency and indoor temperature control effect.

[0086] like Figure 5 and 6As shown, when the air duct unit operates in the heating mode: the first heat exchanger 400 and the second heat exchanger 500 both operate in the heating state; the air guide mechanism 300 evenly distributes the air volume to the first heat exchanger 400 and the second heat exchanger 500 at a symmetrical air supply angle.

[0087] The first heat exchanger 400 and the second heat exchanger 500 both work in a heating state, and are used to increase the air flow temperature to achieve the heating function of the indoor space. The air guide mechanism 300 adjusts the angle of the guide vane 320 to supply air to the first heat exchanger 400 and the second heat exchanger 500 at symmetrical air supply angles, that is, the air flow rate allocated to the first heat exchanger 400 and the second heat exchanger 500 is basically equal, thereby ensuring the consistency of the heat exchange efficiency of the two and improving the overall heating effect. Through the symmetrical working mode and uniform air supply design of the dual heat exchangers, the indoor temperature can be quickly increased in a short time, and the heating effect can be ensured to cover the entire space. It is suitable for environments that require rapid heating in winter, such as indoor spaces such as homes, offices, and shops.

[0088] like Fig. 9 As shown, when the air duct unit operates in the dehumidification mode: one of the first heat exchanger 400 and the second heat exchanger 500 operates in a cooling state, and the other operates in a heating state; the air guide mechanism 300 distributes more air volume to the heat exchanger operating in the cooling state than to the heat exchanger operating in the heating state.

[0089] One of the first heat exchanger 400 and the second heat exchanger 500 works in the cooling state and is responsible for reducing the airflow temperature so as to effectively dehumidify; the other heat exchanger works in the heating state and is responsible for heating the airflow to ensure that the air is not too cold and to prevent the indoor temperature from being too low. The air guide mechanism 300 distributes more air volume to the heat exchanger working in the cooling state than to the heat exchanger working in the heating state, the purpose of which is to increase the air volume passing through the cooling heat exchanger to improve the dehumidification effect, and at the same time, distribute less air volume to the heating heat exchanger to prevent the indoor temperature from being too high.

[0090] The cooling heat exchanger distributes more airflow, enhances the dehumidification capacity, and ensures effective removal of moisture from the air, while maintaining a comfortable indoor temperature through the heating heat exchanger. While dehumidifying, it ensures that the indoor environment will not be uncomfortable due to too low a temperature. The air volume distribution of the air guide mechanism 300 can be intelligently adjusted to automatically adjust the air volume according to different humidity requirements, ensuring the dehumidification effect while optimizing energy efficiency.

[0091] like Fig. 9As shown, the duct air conditioner is working in the dehumidification mode. The first heat exchanger 400 is working in the cooling state, and the second heat exchanger 500 is working in the heating state. In the figure, there are 4 groups of guide vanes 320 designed in the vertical direction. The upper three groups of guide vanes 320 blow air obliquely upward to blow toward the first heat exchanger 400, and the lower group of guide vanes 320 blow air obliquely downward to blow toward the second heat exchanger 500. The angle between each guide vane 320 and the horizontal plane is 10°, and the air is asymmetrically distributed to the first heat exchanger 400 and the second heat exchanger 500. The angle between the heat exchanger and the horizontal plane is still set to 40°. At this time, the angle between the air outlet direction and the heat exchanger is 50°, and the vector velocity of the air flow velocity in the direction perpendicular to the heat exchanger is V·sin50°≈0.77V. According to Fig.10 The simulation effect diagram shows that the wind enters from the left boundary, the wind pressure is high in the upper 2 / 3 area and the lower 1 / 3 area on the right boundary, and the wind pressure on the upper and lower walls is low. The vector wind speed is increased by 13% compared to when the wind guide blades are not added, the wind pressure on the upper and lower walls is reduced, and the area covered by the high wind pressure of the first heat exchanger 400 is larger than that of the second heat exchanger 500, and the air volume obtained by the first heat exchanger 400 is greater than that of the second heat exchanger 500.

[0092] In some embodiments, the air guide mechanism 300 may be a flexible air duct 110, and the functions of airflow distribution and direction adjustment are realized by the adjustable flexible air duct 110. This design has higher flexibility and adaptability, and can meet the requirements of airflow direction and distribution under different operating conditions. The flexible air duct 110 is preferably made of a material with high toughness and deformability (such as silicone, polyurethane, etc.), and can change shape and direction as needed. The flexible structure ensures the adjustability and adaptability of the air duct 110, and avoids the limitations of the traditional rigid air duct 110 in a complex structure. The shape and direction of the flexible air duct 110 can be controlled by an external force (such as a motor) to change the airflow path and direction, and can be dynamically adjusted during operation to adapt to different working states of the heat exchanger (such as cooling, heating, and constant temperature dehumidification).

[0093] The flexible air duct 110 is disposed between the fan 200 and the V-shaped heat exchanger. By changing the shape of the air duct 110, the air flow distribution ratio can be adjusted so that the air flow is blown toward the first heat exchanger 400 and the second heat exchanger 500. The angle and direction of the flexible air duct 110 can be adjusted to change the incident angle of the air flow with the first heat exchanger 400 and the second heat exchanger 500, thereby optimizing the contact effect between the air flow and the heat exchanger.

[0094] By introducing the flexible air duct 110, the flexibility of the air guide mechanism 300 in airflow direction and distribution is greatly improved. This design can adapt to a variety of operating conditions and effectively solves the limitations of the traditional rigid air guide mechanism 300 in airflow distribution and direction adjustment. At the same time, the flexible air duct 110 design reduces wind resistance and noise, improves the overall performance of the duct unit, and provides a better solution for efficient operation such as constant temperature dehumidification.

[0095] The present application also discloses a working method of a duct machine, which is applied to the duct machine provided by the above-mentioned embodiment of the present application. The working method includes the following steps:

[0096] S100, obtaining the working mode of the ducted air conditioner. The current working mode of the ducted air conditioner can be obtained according to the external environment, user settings or the judgment of the control system. The working mode may include cooling mode, heating mode, dehumidification mode, etc., to determine the operating state of the ducted air conditioner.

[0097] S200. According to the working mode, the working states of the first heat exchanger 400 and the second heat exchanger 500 are controlled, and the air volume blown to the first heat exchanger 400 and the second heat exchanger 500 are distributed through the air guide mechanism 300, and the air supply angle to the first heat exchanger 400 and the second heat exchanger 500 is adjusted.

[0098] According to the selected working mode, the working state of the first heat exchanger 400 and the second heat exchanger 500 is controlled to ensure that they are in an appropriate cooling or heating state to meet different operating requirements. For example, in the cooling mode, both heat exchangers work in the cooling state; in the heating mode, both heat exchangers work in the heating state; in the dehumidification mode, one works in the cooling state and the other works in the heating state. According to the working state of the heat exchanger, the working state of the air guide mechanism 300 is adjusted to reasonably distribute the air volume blown to the first and second heat exchangers 500. By adjusting the air supply angle, it is ensured that the airflow is reasonably distributed on the surface of the heat exchanger, thereby improving the heat exchange efficiency and overall comfort. For example, in the dehumidification mode, the air guide mechanism 300 may allocate more air volume to the heat exchanger working in the cooling state and allocate less air volume to the heat exchanger working in the heating state.

[0099] The status of the heat exchanger and the air guide mechanism 300 is automatically adjusted according to different working modes to ensure that the duct air conditioner can achieve the best temperature control and humidity control effect in each mode. By properly controlling the air volume and angle, the heat exchange efficiency can be improved and energy consumption can be reduced. According to environmental requirements (such as cooling, heating or dehumidification), appropriate air flow and temperature and humidity control are provided to improve user comfort.

[0100] In some embodiments, Fig.11As shown, when the operating mode of the air duct machine is the dehumidification mode, the working method of the air duct further includes:

[0101] S210. Control one of the first heat exchanger 400 and the second heat exchanger 500 to operate in the refrigeration state, and the other to operate in the heating state;

[0102] S220. Obtain the target humidity D 目标 , the ambient humidity D 环 , and calculate the humidity difference △D = D 环 - D 目标 ; the target humidity D 目标 is the humidity value that the user expects to reach, and the ambient humidity D 环 is the actual humidity value in the current environment. Since the absolute humidity is related to the temperature, the humidity here refers to the relative humidity. The human body has a high degree of comfort at a humidity of 45 - 65%, and it will be stuffy and uncomfortable when it is higher than 80%. Here, D 目标 = 45% can be given, and the dehumidification mode will be turned on only when the relative humidity is relatively high.

[0103] S230. If △D ≥ B, the ratio of the air volume allocated to the heat exchanger operating in the refrigeration state to the air volume allocated to the heat exchanger operating in the heating state is executed according to M1; if A ≤ △D < B, the ratio of the air volume allocated to the heat exchanger operating in the refrigeration state to the air volume allocated to the heat exchanger operating in the heating state is executed according to M2; if 0 ≤ △D < A, the ratio of the air volume allocated to the heat exchanger operating in the refrigeration state to the air volume allocated to the heat exchanger operating in the heating state is executed according to M3; where B > A and M1 > M2 > M3.

[0104] The humidity difference △D in this step is used to determine how to allocate the air volume and adjust the ratio of the air volume allocated to the heat exchangers operating in the refrigeration state and the heating state. The specific allocation rules are as follows:

[0105] If △D ≥ B, the ratio of the air volume allocated to the heat exchanger operating in the refrigeration state to the air volume allocated to the heat exchanger operating in the heating state is executed according to M1. M1 is a preset ratio, indicating that the refrigeration dehumidification demand is the highest at this time, and more air volume is allocated to the refrigeration heat exchanger.

[0106] If A ≤ △D < B, the ratio of the air volume allocated to the heat exchanger operating in the refrigeration state to the air volume allocated to the heat exchanger operating in the heating state is executed according to M2. M2 is less than M1, indicating that the refrigeration dehumidification demand is relatively high at this time, and more air volume is allocated to the refrigeration heat exchanger.

[0107] If 0 ≤ △D < A, the ratio of the air volume allocated to the heat exchanger operating in the refrigeration state to the air volume allocated to the heat exchanger operating in the heating state is executed according to M3. M3 is the minimum ratio, indicating that the refrigeration demand is low at this time, and indicating that the refrigeration and dehumidification and heating demands are relatively balanced at this time.

[0108] Among them, A, B, M1, M2, and M3 are all pre-set parameters, which respectively determine different ranges of the humidity difference △D and the corresponding air volume allocation ratios. These parameters can be adjusted according to actual needs to achieve the best humidity control effect. For example, A = 20%, B = 35%; M1 can be set to 2.5. At this time, the angles of the four groups of guide vanes 320 in the figure can be set according to the array C1 = [tilted obliquely upward by 25°, tilted obliquely upward by 17°, tilted obliquely upward by 10°, tilted obliquely upward by 3°] from top to bottom; M2 can be set to 1.7. At this time, the angles of the four groups of guide vanes 320 in the figure can be set according to the array C2 = [tilted obliquely upward by 25°, tilted obliquely upward by 15°, tilted obliquely upward by 5°, tilted obliquely downward by 25°] from top to bottom; M3 can be set to 1. At this time, the angles of the four groups of guide vanes 320 in the figure can be set according to the array C3 = [tilted obliquely upward by 25°, tilted obliquely upward by 10°, tilted obliquely downward by 10°, tilted obliquely downward by 25°] from top to bottom.

[0109] This embodiment intelligently adjusts the air volume allocation by refining the humidity difference, ensuring more accurate and efficient humidity control in the dehumidification mode. Automatically adjusts the air volume allocation ratio according to the humidity change, effectively balancing the energy consumption of refrigeration and heating, and achieving an energy-saving effect. By adjusting the air volume ratio according to the humidity demand, it ensures that users can obtain comfortable air circulation in different humidity environments. This method is applicable to scenarios that require precise humidity control, such as dehumidification in high-humidity environments, basement air conditioning, medical places, etc., providing efficient dehumidification effects and comfortable air environments.

[0110] In some embodiments of this specification, they are described in a progressive or parallel manner. Each embodiment focuses on the differences from other embodiments. For the same or similar parts between the various embodiments, reference can be made to each other.

[0111] The above description is only the specific implementation manners of the present application, enabling those skilled in the art to understand or implement the present application. Various modifications to these embodiments will be obvious to those skilled in the art. The general principles defined herein can be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application will not be limited to these embodiments shown herein, but will conform to the widest scope consistent with the principles and novel features claimed herein.

Claims

1. A duct machine, characterized in that: include: A casing, wherein an air duct is formed therein, and an air inlet and an air outlet are formed at two ends of the air duct; a fan, disposed in a region of the air duct close to the air inlet, and configured to introduce airflow from the air inlet into the air duct; A V-shaped heat exchanger, comprising a first heat exchanger and a second heat exchanger arranged up and down, the opening of the V-shaped heat exchanger faces the air inlet, and the first heat exchanger and the second heat exchanger can independently work in a heating state or a cooling state; The air guide mechanism is disposed between the fan and the V-shaped heat exchanger, and is configured to distribute the air volume blown to the first heat exchanger and the second heat exchanger and to adjust the air supply angle to the first heat exchanger and the second heat exchanger.

2. The air duct machine according to claim 1, characterized in that: The air guide mechanism comprises a middle partition plate arranged between the fan and the V-shaped heat exchanger, and a plurality of guide vanes rotatably arranged on the middle partition plate.

3. The air duct machine according to claim 1, characterized in that: The air guiding mechanism comprises a flexible air duct.

4. The air duct machine according to claim 2, characterized in that: The angle between the guide vane and the horizontal plane is α, and the angle between the first heat exchanger and the horizontal plane is β, which satisfies: 0°≤α<90°, 0°<β≤90° and (α+β)≤90°.

5. The air duct machine according to claim 2, characterized in that: The angle between the guide vane and the horizontal plane is α, and the angle between the first heat exchanger and the horizontal plane is β, which satisfies: 0°≤α≤30°, 30°≤β≤45°.

6. The air duct machine according to any one of claims 1 to 5, characterized in that: The duct machine has a cooling mode, in which: The first heat exchanger and the second heat exchanger both operate in a cooling state; The air guide mechanism evenly distributes air volume to the first heat exchanger and the second heat exchanger at symmetrical air supply angles.

7. The air duct machine according to any one of claims 1 to 5, characterized in that: The duct machine has a heating mode, in which: The first heat exchanger and the second heat exchanger both operate in a heating state; The air guide mechanism evenly distributes air volume to the first heat exchanger and the second heat exchanger at symmetrical air supply angles.

8. The air duct machine according to any one of claims 1 to 5, characterized in that: The duct machine has a dehumidification mode, in which: One of the first heat exchanger and the second heat exchanger operates in a cooling state, and the other operates in a heating state; The air volume distributed by the air guide mechanism to the heat exchanger working in the cooling state is greater than the air volume distributed to the heat exchanger working in the heating state.

9. A working method of a duct air conditioner, applied to the duct air conditioner according to any one of claims 1 to 8, characterized in that: The working method comprises: Obtaining the working mode of the duct air conditioner; According to the working mode, the working states of the first heat exchanger and the second heat exchanger are controlled, and the air volume blown to the first heat exchanger and the second heat exchanger is distributed through the air guide mechanism, and the air supply angle to the first heat exchanger and the second heat exchanger is adjusted.

10. The working method of the air duct machine according to claim 9, characterized in that: When the working mode of the air duct unit is the dehumidification mode, controlling one of the first heat exchanger and the second heat exchanger to work in a cooling state and the other to work in a heating state; Get target humidity D 目标 、Ambient humidity D 环 , calculate the humidity difference △D=D 环 -D 目标 ; If △D≥B, the ratio of the air volume allocated to the heat exchanger working in the cooling state to the air volume allocated to the heat exchanger working in the heating state shall be implemented according to M1; if A≤△D<B, the ratio of the air volume allocated to the heat exchanger working in the cooling state to the air volume allocated to the heat exchanger working in the heating state shall be implemented according to M2; if 0≤△D<A, the ratio of the air volume allocated to the heat exchanger working in the cooling state to the air volume allocated to the heat exchanger working in the heating state shall be implemented according to M3; wherein B>A, M1>M2>M3.

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