Air conditioner indoor unit and air conditioner

Abstract

This utility model relates to an indoor unit of an air conditioner and an air conditioner. The indoor unit includes a housing and a fan and a heat exchanger sequentially disposed within the housing along a first direction. The heat exchanger includes a first heat exchange element and a second heat exchange element. A first end of the first heat exchange element extends towards the top of the housing, and a first end of the second heat exchange element extends towards the bottom of the housing. The second ends of the first and second heat exchange elements are adjacent to each other, and a first angle is formed between the first and second heat exchange elements. The fan includes an air outlet. An upper guide plate of the air outlet extends towards the first end of the first heat exchange element, and a lower guide plate of the air outlet extends towards the first end of the second heat exchange element. After the fan draws airflow into the housing, the airflow is guided by the upper and lower guide plates, so that the airflow is delivered to the first and second heat exchange elements respectively. This allows the airflow to completely cover the entire heat exchanger, thereby improving the uniformity of heat exchange and increasing the heat exchange efficiency of the indoor unit.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning technology, and in particular to an indoor air conditioning unit and an air conditioner. Background Technology

[0002] In some related technologies, the indoor unit of an air conditioner suffers from low heat exchange efficiency. Utility Model Content

[0003] Some embodiments of this utility model propose an indoor air conditioning unit and an air conditioner to alleviate the problem of low heat exchange efficiency of the indoor air conditioning unit.

[0004] In one aspect of this utility model, an indoor air conditioning unit is provided, comprising a housing and a fan and a heat exchanger sequentially disposed within the housing along a first direction;

[0005] The heat exchanger includes a first heat exchange element and a second heat exchange element. A first end of the first heat exchange element extends toward the top of the housing, and a first end of the second heat exchange element extends toward the bottom of the housing. The second ends of the first heat exchange element and the second heat exchange element are adjacent to each other, and a first angle is formed between the first heat exchange element and the second heat exchange element.

[0006] The fan includes an air outlet, with an upper guide plate of the air outlet extending toward a first end of the first heat exchanger and a lower guide plate of the air outlet extending toward a first end of the second heat exchanger.

[0007] In some embodiments, the housing is provided with a partition that divides the housing into a first chamber for accommodating the fan and a second chamber for accommodating the heat exchanger. The upper part of the partition is provided with a connecting portion, the air outlet is provided in the connecting portion, and the downstream end of the upper guide plate passes through the connecting portion and is located in the second chamber. The downstream end of the lower guide plate is connected to the top of the partition.

[0008] In some embodiments, a second included angle λ is formed between the upper guide plate and the lower guide plate, and the angle range of the second included angle λ is 25°~40°, preferably 30°~35°.

[0009] In some embodiments, in the first direction, the downstream end of the upper guide plate is closer to the heat exchanger than the downstream end of the lower guide plate.

[0010] In some embodiments, in the first direction, there is a first distance between the downstream end of the upper guide plate and the downstream end of the lower guide plate, the first distance being in the range of 40mm to 60mm, preferably 45mm to 55mm.

[0011] In some embodiments, in the first direction, the first end of the second heat exchanger is located between the downstream end of the upper guide plate and the downstream end of the lower guide plate.

[0012] In some embodiments, in the first direction, there is a second distance between the first end of the second heat exchanger and the downstream end of the lower guide plate, the second distance being in the range of 30mm to 50mm, preferably 32mm to 45mm.

[0013] In some embodiments, in the first direction, there is a first distance between the downstream end of the upper guide plate and the downstream end of the lower guide plate, and a second distance between the first end of the second heat exchanger and the downstream end of the lower guide plate, wherein the ratio of the second distance to the first distance is in the range of 0.6 to 0.9, preferably 0.7 to 0.8.

[0014] In some embodiments, in a second direction, there is a third distance between the upstream end of the upper guide plate and the upstream end of the lower guide plate, the third distance being in the range of 70 mm to 100 mm, preferably 80 mm to 90 mm, the second direction being parallel to the direction from the top to the bottom of the housing, and the second direction intersecting the first direction.

[0015] In some embodiments, in the first direction, there is a fourth distance between the center of the fan and the first end of the second heat exchanger, the fourth distance being in the range of 130mm to 170mm, preferably 140mm to 160mm.

[0016] In some embodiments, in the first direction, there is a fifth distance between the center of the fan and the downstream end of the lower guide plate, the fifth distance being in the range of 95mm to 125mm, preferably 100mm to 115mm.

[0017] In some embodiments, in the first direction, there is a fourth distance between the center of the fan and the first end of the second heat exchanger, and a fifth distance between the center of the fan and the downstream end of the lower guide plate, wherein the ratio of the fourth distance to the fifth distance is in the range of 1.1 to 1.7, preferably 1.3 to 1.5.

[0018] In some embodiments, the impeller radius of the fan ranges from 60mm to 80mm, preferably from 65mm to 75mm.

[0019] In some embodiments, in the first direction, there is a fourth distance between the center of the fan and the first end of the second heat exchanger, the ratio of the fourth distance to the impeller radius of the fan being in the range of 1.8 to 2.5, preferably 2 to 2.3.

[0020] In some embodiments, in the first direction, there is a fifth distance between the center of the fan and the downstream end of the lower guide plate, and the ratio of the fifth distance to the impeller radius of the fan is in the range of 1.2 to 1.8, preferably 1.4 to 1.7.

[0021] In some embodiments, the first heat exchanger forms a third angle α with the first line, the second heat exchanger forms a fourth angle β with the first line, the third angle α is greater than the fourth angle β, and the first line is parallel to the first direction.

[0022] In some embodiments, the first heat exchanger forms a third angle α with the first line, the angle of the third angle α being in the range of 40°~55°, preferably 43°~50°; the first line is parallel to the first direction.

[0023] In some embodiments, the second heat exchanger forms a fourth included angle β with the first line, the angle range of the fourth included angle β being 25°~45°, preferably 32°~38°; the first line is parallel to the first direction.

[0024] In some embodiments, the angle range of the first included angle is 70°~90°, preferably 80°~85°.

[0025] In some embodiments, the housing is provided with a partition that divides the housing into a first cavity for accommodating the fan and a second cavity for accommodating the heat exchanger. The sum of the dimensions of the first cavity and the second cavity extending along the first direction is a first width, and the dimension of the second cavity extending along the first direction is a second width. The second width accounts for 40% to 45% of the first width.

[0026] In some embodiments, the first width ranges from 380mm to 410mm, and the second width ranges from 155mm to 185mm.

[0027] In some embodiments, the housing has a first air vent on the side wall in the first direction and a second air vent at the bottom of the housing. The first opening size of the first air vent extending along the second direction ranges from 100mm to 130mm, preferably from 105mm to 120mm, and the second opening size of the second air vent extending along the first direction ranges from 45mm to 75mm, preferably from 50mm to 65mm. The second direction is parallel to the direction from the top to the bottom of the housing and intersects with the first direction.

[0028] In some embodiments, the housing is provided with a partition that divides the housing into a first cavity for accommodating the fan and a second cavity for accommodating the heat exchanger; the second cavity has a first air vent on its side wall in the first direction and a second air vent at its bottom; the first cavity extends along the first direction with a third width, the second cavity extends along the first direction with a second width, and the second width is equal to the third width.

[0029] In one aspect of this utility model, an air conditioner is provided, including the above-described indoor air conditioner unit.

[0030] Based on the above technical solution, this utility model has at least the following beneficial effects:

[0031] In some embodiments, the opening of the angle formed by the first heat exchanger and the second heat exchanger faces the fan; the upper guide plate and the lower guide plate provided at the air outlet of the fan extend toward the first end of the first heat exchanger and the first end of the second heat exchanger, respectively. This allows the fan to draw the airflow into the housing and guide the airflow through the upper guide plate and the lower guide plate at the air outlet, so that the airflow is delivered to the first heat exchanger and the second heat exchanger respectively. This allows the airflow to completely cover the entire heat exchanger, thereby improving the uniformity of heat exchange and increasing the heat exchange efficiency of the indoor unit of the air conditioner. Attached Figure Description

[0032] The accompanying drawings, which are included to provide a further understanding of the present invention and constitute a part of this invention, illustrate exemplary embodiments of the present invention and, together with the description thereof, serve to explain the present invention and do not constitute an undue limitation thereof. In the drawings:

[0033] Figure 1 This is a schematic diagram of an indoor air conditioner unit according to some embodiments of the present utility model;

[0034] Figure 2 This is a schematic diagram of an indoor air conditioner unit according to some embodiments of the present utility model;

[0035] Figure 3 This is a schematic diagram of an indoor air conditioning unit according to other embodiments of the present invention.

[0036] The labels in the attached diagram are explained as follows:

[0037] 1-Shell; 11-First cavity; 12-Second cavity; 13-First air vent; 14-Second air vent;

[0038] 2-Fan; 21-Upper guide plate; 211-Downstream end of upper guide plate; 22-Lower guide plate; 221-Downstream end of lower guide plate; 23-Air outlet;

[0039] 3-Heat exchanger; 31-First heat exchanger element; 32-Second heat exchanger element; 321-First end of the second heat exchanger element;

[0040] 4-Partition.

[0041] It should be understood that the dimensions of the various parts shown in the accompanying drawings are not drawn to actual scale. Furthermore, the same or similar reference numerals denote the same or similar components. Detailed Implementation

[0042] Various exemplary embodiments of the present invention will now be described in detail with reference to the accompanying drawings. The descriptions of the exemplary embodiments are merely illustrative and are in no way intended to limit the present invention or its application or use. The present invention can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are provided to make the present invention thorough and complete, and to fully express the scope of the present invention to those skilled in the art. It should be noted that, unless otherwise specifically stated, the relative arrangement of components and steps, the composition of materials, numerical expressions, and values ​​set forth in these embodiments should be interpreted as merely exemplary and not as limiting.

[0043] The terms "first," "second," and similar words used in this invention do not indicate any order, quantity, or importance, but are merely used to distinguish different parts. Words such as "including" or "comprising" mean that the element preceding the word encompasses the element listed after it, and do not exclude the possibility of encompassing other elements as well. Terms such as "upper," "lower," "left," and "right" are only used to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0044] In this invention, when a specific device is described as being located between a first device and a second device, an intermediary device may or may not exist between the specific device and the first or second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to the other devices without an intermediary device, or it may not be directly connected to the other devices but may have an intermediary device.

[0045] All terms used in this invention (including technical or scientific terms) have the same meaning as understood by one of ordinary skill in the art to which this invention pertains, unless otherwise specifically defined. It should also be understood that terms defined in general dictionaries should be interpreted as having meanings consistent with their meanings in the context of the relevant art, and not as idealized or highly formalized, unless expressly defined herein.

[0046] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and equipment should be considered part of the specification.

[0047] refer to Figures 1 to 3 In some embodiments, the indoor unit of the air conditioner includes a housing 1, and a fan 2 and a heat exchanger 3 arranged sequentially in the housing 1 along a first direction X.

[0048] The heat exchanger 3 includes a first heat exchange element 31 and a second heat exchange element 32. The first end of the first heat exchange element 31 extends toward the top of the shell 1, and the first end of the second heat exchange element 32 extends toward the bottom of the shell 1. The second end of the first heat exchange element 31 is adjacent to the second end of the second heat exchange element 32, and a first angle is formed between the first heat exchange element 31 and the second heat exchange element 32.

[0049] The fan 2 includes an air outlet 23, with an upper guide plate 21 extending toward the first end of the first heat exchanger 31 and a lower guide plate 22 extending toward the first end of the second heat exchanger 32.

[0050] In the above embodiment, the heat exchanger 3 is composed of a first heat exchange element 31 and a second heat exchange element 32, which are arranged at an angle. The first end of the first heat exchange element 31 and the first end of the second heat exchange element 32 extend toward the top and bottom of the housing 1, respectively. The opening of the angle formed by the first heat exchange element 31 and the second heat exchange element 32 faces the fan 2.

[0051] The air outlet 23 of the fan 2 is provided with an upper guide plate 21 and a lower guide plate 22. The upper guide plate 21 and the lower guide plate 22 extend toward the first end of the first heat exchanger 31 and the first end of the second heat exchanger 32, respectively. This allows the fan 2 to draw airflow into the housing 1 and guide the airflow through the upper guide plate 21 and the lower guide plate 22 of the air outlet 23, so that the airflow is delivered to the first heat exchanger 31 and the second heat exchanger 32, respectively. This allows the airflow to completely cover the entire heat exchanger 3, thereby improving the heat exchange uniformity of the heat exchanger 3 and improving the heat exchange efficiency of the indoor unit of the air conditioner.

[0052] In some embodiments, the dimensions of the first end to the second end of the first heat exchanger 31 are greater than the dimensions of the first end to the second end of the second heat exchanger 32.

[0053] The first heat exchanger 31 and the second heat exchanger 32 are asymmetrically arranged to correspond to the first air outlet 13 and the second air outlet 14 mentioned below. The airflow after heat exchange through the first heat exchanger 31 mainly flows to the first air outlet 13, and the airflow after heat exchange through the second heat exchanger 32 mainly flows to the second air outlet 14. The opening size of the first air outlet 13 is larger than the opening size of the second air outlet 14. Therefore, the dimension from the first end to the second end of the first heat exchanger 31 is larger than the dimension from the first end to the second end of the second heat exchanger 32.

[0054] In some embodiments, the first included angle formed between the first heat exchanger 31 and the second heat exchanger 32 may also be 180 degrees.

[0055] The second end of the first heat exchanger 31 is connected to the second end of the second heat exchanger 32, making the entire heat exchanger 3 a straight plate. Alternatively, the second end of the first heat exchanger 31 is connected to the second end of the second heat exchanger 32, making the entire heat exchanger 3 a V-shape.

[0056] In some embodiments, the fan 2 includes a centrifugal fan.

[0057] In some embodiments, the upper guide plate 21 of the air outlet 23 of the fan 2 is the upper volute of the centrifugal fan, and the lower guide plate 22 of the air outlet 23 of the fan 2 is the lower volute of the centrifugal fan.

[0058] In the above embodiment, the first direction X is parallel to the direction from the fan 2 to the heat exchanger 3, and the second direction Y is parallel to the direction from the top to the bottom of the housing 1. The first direction X intersects with the third direction.

[0059] In some embodiments, the first direction X is the width direction of the housing 1, the second direction Y is also the height direction of the housing 1, and the third direction is the length direction of the housing 1. The first direction X is perpendicular to the second direction Y, the second direction Y is perpendicular to the third direction, and the first direction X is perpendicular to the third direction.

[0060] In some embodiments, the housing 1 is provided with a partition 4, which divides the housing 1 into a first cavity 11 for accommodating the fan 2 and a second cavity 12 for accommodating the heat exchanger 3. The upper part of the partition 4 is provided with a connecting part, the air outlet 23 is provided in the connecting part, and the downstream end of the upper guide plate 21 passes through the connecting part and is located in the second cavity 12. The downstream end of the lower guide plate 22 is connected to the top of the partition 4.

[0061] In the above embodiment, the partition 4 divides the shell 1 into two functional chambers. The first chamber 11 is used to install the fan 2, and the second chamber 12 is used to install the heat exchanger 3. The connecting part is located at the upper part of the partition 4, and the air outlet 23 is located at the connecting part, so that the airflow generated by the fan 2 can directly enter the second chamber 12 through the top of the partition 4, reducing flow resistance and energy loss. The downstream end of the upper guide plate 21 extends into the interior of the second chamber 12, which can more effectively guide the airflow to the first heat exchanger 31, while the lower guide plate 22 is connected to the top of the partition 4, which is more conducive to guiding the airflow to the second heat exchanger 32. This helps to achieve uniform coverage of the entire height range of the heat exchanger 3, avoid local airflow short-circuiting or dead zones, and thus improve heat exchange efficiency.

[0062] In the above embodiment, the lower guide plate 22 is fixedly connected to the top of the partition 4, which can provide stable support for the lower guide plate 22 through the partition 4, which helps to enhance the overall rigidity of the fan 2 and reduce vibration and noise.

[0063] In some embodiments, the downstream end of the lower guide plate 22 is connected to the top of the partition plate 4 and extends a very small section toward the bottom of the housing 1 and toward the heat exchanger 3 to overlap with the partition plate 4, thereby better guiding the airflow to the second heat exchanger 32.

[0064] In some embodiments, the indoor unit of the air conditioner also includes a water collection tray, which is located below the heat exchanger 3 and is used to collect the condensate generated by the heat exchanger 3.

[0065] In some embodiments, a second included angle λ is formed between the upper guide plate 21 and the lower guide plate 22, and the angle range of the second included angle λ is 25°~40°, preferably 30°~35°.

[0066] In the above embodiment, the angle λ formed between the upper guide plate 21 and the lower guide plate 22 is in the range of 25°~40°, which enables the airflow to form a moderately divergent fan-shaped airflow field after passing through the connecting part of the partition 4. This airflow field guides the airflow to the first heat exchanger 31 and the second heat exchanger 32 more evenly, thereby achieving uniform air supply to the two heat exchangers, reducing local heat exchange insufficiency caused by concentrated or deflected airflow, and improving the heat exchange uniformity of the first heat exchanger 31 and the second heat exchanger 32.

[0067] In the above embodiment, the second included angle λ formed between the upper guide plate 21 and the lower guide plate 22 is the diffusion angle of the fan 2. The selectable angle range of the second included angle λ is 25°~40°, preferably 30°~35°, for example: the second included angle λ is 33°.

[0068] In the above embodiments, when the second included angle λ is too small, less than 25°, the upper guide plate 21 and the lower guide plate 22 are too close to be parallel, and the airflow direction tends to be consistent, which can easily cause insufficient air supply in some heat exchange areas; when the second included angle λ is too large, greater than 40°, the airflow diffusion angle formed by the upper guide plate 21 and the lower guide plate 22 is too large, which may lead to airflow short circuit, increased disturbance, and even affect the static pressure efficiency of the fan; therefore, limiting the second included angle λ formed between the upper guide plate 21 and the lower guide plate 22 to the range of 25°~40°, especially 30°~35°, can achieve a better airflow distribution ratio, so that both the first heat exchange element 31 and the second heat exchange element 32 can obtain sufficient airflow coverage, and significantly improve the overall heat exchange efficiency of the heat exchanger 3.

[0069] In some embodiments, in the first direction X, the downstream end of the upper guide plate 21 is closer to the heat exchanger 3 than the downstream end of the lower guide plate 22.

[0070] In the above embodiments, the downstream end refers to the downstream direction along the airflow direction from the fan 2 to the heat exchanger 3.

[0071] In the above embodiment, in the first direction X, the upper guide plate 21 extends closer to the heat exchanger 3, shortening the distance of the airflow from the air outlet 23 of the fan 2 to the corresponding area of ​​the first heat exchanger 31, reducing the flow resistance of the airflow, and making the airflow have a higher wind speed. After the airflow enters the second cavity 12, it can reach the first heat exchanger 31 faster, and can guide more airflow to the area of ​​the first heat exchanger 31. The first heat exchanger 31 corresponds to the front air outlet (first outlet 13) on the housing 1. The airflow after heat exchange by the first heat exchanger 31 can be sent out from the front air outlet (first outlet 13), which improves the airflow speed and airflow volume of the front air outlet and improves the response speed.

[0072] In some embodiments, in the first direction X, there is a first distance B between the downstream end of the upper guide plate 21 and the downstream end of the lower guide plate 22, the size of the first distance B being 40mm to 60mm, preferably 45mm to 55mm.

[0073] In the above embodiment, if the first distance B is less than 40mm, the upper and lower airflow paths may be too close, which may easily generate eddies, backflow and other phenomena, reducing the stability of air supply; if the first distance B is greater than 60mm, the ability to centrally control the airflow may be weakened; therefore, the size range of the first distance B is 40mm~60mm, preferably 45mm~55mm. The upper guide plate 21 and the lower guide plate 22 can effectively maintain the directionality and continuity of the airflow, so that the airflow flows more evenly to the first heat exchanger 31 and the second heat exchanger 32, and improve the uniformity and guidance of the airflow organization.

[0074] In the above embodiment, in the first direction X, the size of the upper guide plate 21 is larger than the size of the lower guide plate 22.

[0075] In some embodiments, the upper guide plate 21 is the upper volute of the centrifugal fan, and the lower guide plate 22 is the lower volute of the centrifugal fan. The length of the upper volute is greater than the length of the lower volute, which can better guide the airflow to the first heat exchanger 31 and the second heat exchanger 32, adjust the airflow to the first heat exchanger 31 and the second heat exchanger 32, and improve the uniformity of heat exchange.

[0076] In some embodiments, the housing 1 has a dimension (first width E) of 450 mm in the first direction X and a first distance B of 51.5 mm.

[0077] refer to Figure 2 In some embodiments, in the first direction X, the first end 321 of the second heat exchanger 32 is located between the downstream end 211 of the upper guide plate 21 and the downstream end 221 of the lower guide plate 22.

[0078] In the above embodiment, the first end 321 of the second heat exchanger 32 is located between the downstream end 211 of the upper guide plate 21 and the downstream end 221 of the lower guide plate 22. This can shorten the distance between the fan 2 and the heat exchanger 3, allowing the first end 321 of the second heat exchanger 32 to come into contact with the airflow from the fan 2 earlier, reducing flow loss, improving airflow utilization, and shortening the distance the airflow reaches the area of ​​the second heat exchanger 32, reducing flow resistance, reducing the diffusion and eddy phenomenon of airflow inside the shell 1, better guiding the airflow to the second heat exchanger 32, and improving the heat exchange efficiency of the second heat exchanger 32.

[0079] refer to Figure 1 and Figure 2 In some embodiments, in the first direction X, there is a second distance A between the first end 321 of the second heat exchanger 32 and the downstream end 221 of the lower guide plate 22, the second distance A being 30mm to 50mm, preferably 32mm to 45mm.

[0080] In the above embodiment, if the second distance A is less than 30mm, the airflow is easily blocked by the first end 321 of the second heat exchanger 32, resulting in local eddies or backflow; if the second distance A is greater than 50mm, it will lead to excessive airflow diffusion, reducing wind speed and heat exchange efficiency; therefore, the second distance A is in the range of 30mm to 50mm, especially in the range of 32mm to 45mm, which can achieve a smooth transition of airflow, improve the wind speed uniformity on the air inlet side of the second heat exchanger 32, shorten the ineffective flow path, and increase the airflow through the heat exchange surface of the second heat exchanger 32 per unit time, thereby effectively improving the heat exchange efficiency of the second heat exchanger 32.

[0081] In some embodiments, the second distance A is 38 mm.

[0082] In some embodiments, in the first direction X, there is a first distance B between the downstream end 211 of the upper guide plate 21 and the downstream end 221 of the lower guide plate 22, and a second distance A between the first end 321 of the second heat exchanger 32 and the downstream end 221 of the lower guide plate 22. The ratio of the second distance A to the first distance B is in the range of 0.6 to 0.9, preferably 0.7 to 0.8.

[0083] In the above embodiments, if the ratio of the second distance A to the first distance B is less than 0.6, the first end 321 of the second heat exchanger 321 is too close to the downstream end 221 of the lower guide plate 22, which easily forms an airflow obstruction zone; if the ratio of the second distance A to the first distance B is greater than 0.9, the first end 321 of the second heat exchanger 321 is too far from the downstream end 221 of the lower guide plate 22, and the airflow easily diffuses, reducing the wind speed utilization rate. Therefore, the ratio of the second distance A to the first distance B is controlled within the range of 0.6 to 0.9, preferably 0.7 to 0.8, so that the airflow entering the second heat exchanger 32 remains within the effective guidance range after leaving the lower guide plate 22, reducing the disordered diffusion of airflow inside the shell 1, improving the uniformity of airflow flowing to the first heat exchanger 31 and the second heat exchanger 32, and enabling the airflow to transition more smoothly from between the upper guide plate 21 and the lower guide plate 22 to the heat exchange area, reducing eddies, backflows, and other phenomena, and significantly reducing the pressure loss and energy loss of the airflow in the second cavity 12. Especially within the preferred range of 0.7 to 0.8, the airflow can more fully cover the second heat exchanger 32 without causing excessively high local wind speeds or disturbances due to excessively short distances. At the same time, it reduces excessive airflow diffusion caused by an excessively large ratio of the second distance A to the first distance B, allowing the airflow to flow more evenly to the first heat exchanger 31 and the second heat exchanger 32, thereby improving the overall heat exchange efficiency of the heat exchanger 3.

[0084] In some embodiments, the ratio of the second distance A to the first distance B is 0.74.

[0085] In some embodiments, in the second direction Y, there is a third distance H between the upstream end of the upper guide plate 21 and the upstream end of the lower guide plate 22, the third distance H being in the range of 70mm~100mm, preferably 80mm~90mm, the second direction Y being parallel to the direction from the top to the bottom of the housing 1, and the second direction Y intersecting the first direction X.

[0086] In the above embodiment, when the third distance H is in the range of 70mm~100mm, an effective guiding space can be formed that is adapted to the cross-section of the air outlet 23 of the fan 2. If the third distance H is less than 70mm, it may cause the airflow channel to be narrow, increase the flow resistance, and reduce the air supply efficiency. If the third distance H is greater than 100mm, it will weaken the guiding effect, resulting in serious airflow diffusion and reduced control accuracy. Therefore, the range of the third distance H is 70mm~100mm, preferably 80mm~90mm, which can ensure sufficient flow area and maintain good guiding performance, making the transition of airflow from the outlet of the fan 2 to the guide plate smoother, reducing energy loss, and also helping to maintain the pressure stability at the air outlet 23 of the fan 2 and improve the overall operating efficiency.

[0087] In the above embodiment, the third distance H corresponds to the outlet height of the centrifugal fan casing.

[0088] In some embodiments, the third distance H is 84 mm.

[0089] In some embodiments, the upstream end of the upper guide plate 21 is located within the first cavity 11 and connected to the volute of the fan 2, and the upstream end of the lower guide plate 22 is located within the first cavity 11 and connected to the volute of the fan 2. The upper guide plate 21 and the lower guide plate 22 are the volute tongues of the fan 2, used to guide the airflow.

[0090] The downstream end of the upper guide plate 21 extends into the second cavity 12, and the downstream end of the lower guide plate 22 is connected to the top of the partition 4 and extends to one side of the partition 4 located in the second cavity 12. The downstream end of the upper guide plate 21 is larger in size than the downstream end of the lower guide plate 22 extending into the second cavity 12.

[0091] In some embodiments, the direction from the upstream end to the downstream end of the upper guide plate 21 is approximately parallel to the first direction X, and the direction from the upstream end to the downstream end of the lower guide plate 22 has an angle greater than zero with the first direction X. The downstream end of the lower guide plate 22 is located obliquely below the upstream end of the lower guide plate 22. The inclined arrangement of the lower guide plate 22 can better guide the airflow to the second heat exchanger 32, thereby improving the heat exchange efficiency of the second heat exchanger 32.

[0092] In some embodiments, in the first direction X, there is a fourth distance G between the center of the fan 2 and the first end of the second heat exchanger 32, the size of the fourth distance G being 130mm to 170mm, preferably 140mm to 160mm.

[0093] In the above embodiment, the airflow delivered by the fan 2 needs a certain space for diffusion and rectification before entering the heat exchange area; the fourth distance G defines the flow path length of the airflow from the center of the fan 2 to the first end of the second heat exchanger 32; if the fourth distance G is less than 130mm, the airflow may not have fully expanded before entering the heat exchange area, which may easily cause excessive local wind speed and increased pressure loss; if the fourth distance G is greater than 170mm, it may cause disordered diffusion of the airflow inside the casing 1, reducing the wind speed utilization rate; therefore, the size range of the fourth distance G is 130mm~170mm, preferably 140mm~160mm, which can enable the airflow to obtain a better rectification effect, which is conducive to forming a uniform and stable heat exchange airflow field and improving heat exchange efficiency and heat exchange effect; in addition, limiting the fourth distance G to the range of 130mm~170mm helps to shorten the size between the fan 2 and the heat exchanger 3 in the first direction X, reduce the overall width of the air conditioning indoor unit, and make the whole structure more compact.

[0094] In some embodiments, the fourth distance G is 150 mm.

[0095] In some embodiments, in the first direction X, there is a fifth distance F between the center of the fan 2 and the downstream end of the lower guide plate 22, the fifth distance F being in the range of 95mm to 125mm, preferably 100mm to 115mm.

[0096] In the above embodiment, the lower guide plate 22 is mainly used to guide the airflow to the second heat exchanger 32. A reasonable fifth distance F can enable the airflow to have good velocity distribution and directionality when entering the working area of ​​the lower guide plate 22. If the fifth distance F is less than 95mm, the airflow will not be fully expanded before entering the guiding area, which may easily cause excessive local wind speed and increased pressure loss. If the fifth distance F is greater than 125mm, it may cause excessive airflow diffusion and reduce the guiding effect. Therefore, the size range of the fifth distance F is 95mm~125mm, preferably 100mm~115mm, which can improve the control capability of the lower guide plate 22 on the airflow, reduce eddies and backflow phenomena, improve the airflow delivery efficiency to the second heat exchanger 32, and thus improve the overall heat exchange performance.

[0097] In some embodiments, the fifth distance F is 108 mm.

[0098] In some embodiments, in the first direction X, there is a fourth distance G between the center of the fan 2 and the first end of the second heat exchanger 32, and a fifth distance F between the center of the fan 2 and the downstream end of the lower guide plate 22. The ratio of the fourth distance G to the fifth distance F is in the range of 1.1 to 1.7, preferably 1.3 to 1.5.

[0099] In the above embodiment, the fourth distance G represents the distance from the center of the fan 2 to the first end of the second heat exchanger 32, that is, the path length of the airflow flowing towards the heat exchange area; the fifth distance F represents the distance from the center of the fan 2 to the end of the lower guide plate 22, that is, the free diffusion section before the airflow enters the guiding area. After the airflow is sent out from the outlet 23 of the fan 2, it first passes through the free diffusion area of ​​the fifth distance F, and then is directionally guided by the lower guide plate 22, and finally enters the second heat exchanger 32 for heat exchange.

[0100] The ratio of the fourth distance G to the fifth distance F reflects the path distribution characteristics of the airflow from the outlet 23 of the fan 2 to the heat exchanger after being guided and controlled. If the ratio of the fourth distance G to the fifth distance F is less than 1.1, the first end of the second heat exchanger 32 is too close to the downstream end of the lower guide plate 22, which may cause the airflow to enter the heat exchange area before it has fully expanded, resulting in excessively high local wind speed and increased pressure loss. If the ratio of the fourth distance G to the fifth distance F is greater than 1.7, the first end of the second heat exchanger 32 is too far from the downstream end of the lower guide plate 22, and the airflow diffuses severely inside the shell 1, reducing the wind speed utilization rate. Therefore, the ratio of the fourth distance G to the fifth distance F is in the range of 1.1 to 1.7, preferably 1.3 to 1.5, which can both provide sufficient diffusion space for the airflow and guide it to the heat exchange area in a timely manner, achieving a balance between efficient heat exchange and stable airflow organization.

[0101] The ratio of the fourth distance G to the fifth distance F is preferably in the range of 1.3 to 1.5, which can make the airflow supply of the second heat exchanger 32 more sufficient, and will not cause airflow attenuation due to excessive path length, thereby achieving dynamic balance and coordinated air supply between the corresponding areas of the first heat exchanger 31 and the second heat exchanger 32.

[0102] Furthermore, the ratio of the fourth distance G to the fifth distance F is in the range of 1.1 to 1.7, preferably 1.3 to 1.5, which can also shorten the overall length of the casing 1, making the structure of the air conditioner indoor unit more compact and facilitating miniaturization.

[0103] In some embodiments, the ratio of the fourth distance G to the fifth distance F is 1.4.

[0104] In some embodiments, the impeller radius R of the fan 2 ranges from 60mm to 80mm, preferably from 65mm to 75mm.

[0105] In the above embodiments, the impeller radius R is a key parameter that determines the air volume, static pressure capacity, and overall size of the fan 2.

[0106] In the above embodiments, if the impeller radius R of the fan 2 is too small, less than 60 mm, it will be difficult to meet the wind speed and air volume required by the heat exchanger 3, affecting the heat exchange efficiency; if the impeller radius R of the fan 2 is too large, greater than 80 mm, it may cause the size of the fan 2 to exceed the standard, affecting the compactness of the overall structure. Therefore, the impeller radius R of the fan 2 is between 60 mm and 80 mm, preferably between 65 mm and 75 mm, which enables the fan 2 to output a stable airflow with low power consumption, and can also maintain efficient operation within a wide operating range, reducing starting current and operating noise.

[0107] The impeller radius R of fan 2 also affects the outlet cross-section size and airflow distribution characteristics. If the impeller radius R of fan 2 is too large, the airflow diffusion angle is large, which can easily cause the guide plate to fail to effectively concentrate the airflow. If the impeller radius R of fan 2 is too small, the airflow intensity is insufficient, affecting the heat exchange efficiency. Therefore, the impeller radius R of fan 2 is between 60mm and 80mm, preferably between 65mm and 75mm, which can create a good matching relationship between the outlet airflow of fan 2 and the guide plate, which is conducive to achieving uniform air supply and efficient heat exchange.

[0108] Furthermore, the impeller radius R of the fan 2 is between 60mm and 80mm, preferably between 65mm and 75mm, which also helps to control the distance between the fan 2 and the heat exchanger 3 along the first direction X (such as the fourth distance G and the fifth distance F), improves the overall structural compactness, and facilitates the miniaturization of the air conditioning indoor unit.

[0109] In some embodiments, the impeller radius R of the fan 2 is 70 mm.

[0110] In some embodiments, in the first direction X, there is a fourth distance G between the center of the fan 2 and the first end of the second heat exchanger 32, and the ratio of the fourth distance G to the impeller radius R of the fan 2 is in the range of 1.8 to 2.5, preferably 2 to 2.3.

[0111] In the above embodiment, the fourth distance G represents the distance from the center of the fan 2 to the first end of the second heat exchanger 32, that is, the path length of the airflow to the heat exchange area; the impeller radius R determines the air volume, static pressure capacity, and airflow diffusion characteristics of the fan 2. The ratio of the fourth distance G to the impeller radius R of the fan 2 reflects the relative path distribution characteristics of the airflow from the outlet 23 of the fan 2 to the heat exchange area.

[0112] After the airflow is sent out from the outlet 23 of the fan 2, it needs a certain space for diffusion and rectification before entering the heat exchange area. If the ratio of the fourth distance G to the impeller radius R of the fan 2 is less than 1.8, it means that the heat exchanger 3 is too close to the fan 2, and the airflow enters the heat exchange area before it has fully expanded, which can easily cause excessive local wind speed and increased pressure loss. If the ratio of the fourth distance G to the impeller radius R of the fan 2 is greater than 2.5, the heat exchanger 3 is too far from the fan 2, and the airflow diffuses disorderly inside the shell 1, reducing the wind speed utilization rate. Therefore, the ratio of the fourth distance G to the impeller radius R of the fan 2 is in the range of 1.8 to 2.5, preferably 2 to 2.3, which can achieve better rectification effect of the airflow, which is conducive to forming a uniform and stable heat exchange airflow field, improving the heat exchange efficiency of the second heat exchanger 32, and also helps to reduce vibration and noise caused by airflow impact.

[0113] Furthermore, the ratio of the fourth distance G to the impeller radius R of the fan 2 is in the range of 1.8 to 2.5, preferably 2 to 2.3. This can shorten the overall length of the casing 1, while ensuring the effectiveness of the airflow channel, optimizing the space utilization efficiency of the whole structure, and improving the compactness and energy efficiency of the air conditioning indoor unit.

[0114] In some embodiments, the ratio of the fourth distance G to the impeller radius R of the fan 2 is 2.14.

[0115] In some embodiments, in the first direction X, there is a fifth distance F between the center of the fan 2 and the downstream end of the lower guide plate 22, and the ratio of the fifth distance F to the impeller radius R of the fan 2 is in the range of 1.2 to 1.8, preferably 1.4 to 1.7.

[0116] In the above embodiment, the fifth distance F represents the distance from the center of the fan 2 to the end of the lower guide plate 22; the impeller radius R determines the air volume, static pressure capacity and airflow diffusion characteristics of the fan 2; the ratio of the fifth distance F to the impeller radius R of the fan 2 reflects the relative path distribution characteristics of the airflow before it enters the heat exchange area from the air outlet of the fan 2.

[0117] In the above embodiments, if the ratio of the fifth distance F to the impeller radius R of the fan 2 is less than 1.2, it means that the downstream end of the lower guide plate 22 is too close to the fan 2, and the airflow leaves the guiding area before it has fully expanded, resulting in disordered diffusion of the airflow inside the casing 1 and reduced guiding efficiency. If the ratio of the fifth distance F to the impeller radius R of the fan 2 is greater than 1.8, the downstream end of the lower guide plate 22 is too far from the fan 2, which can easily cause excessively high local wind speeds and increased pressure loss. Therefore, the ratio of the fifth distance F to the impeller radius R of the fan 2 is in the range of 1.2 to 1.8. The preferred value of 1.4 to 1.7 can achieve better airflow rectification, which is conducive to forming a uniform and stable guiding airflow, reducing ineffective diffusion, and increasing the wind speed and air volume at the inlet of the heat exchanger. It also improves the wind speed uniformity and heat exchange efficiency on the surface of the second heat exchange element 32, and optimizes the airflow distribution ratio between the corresponding areas of the first heat exchange element 31 and the second heat exchange element 32. This ensures that the airflow flowing to the lower second heat exchange element 32 is sufficient, and that the airflow is not disturbed due to the short distance, thereby achieving dynamic balance and coordinated air supply between the upper and lower heat exchange areas.

[0118] In some embodiments, the ratio of the fifth distance F to the impeller radius R of the fan 2 is 1.54.

[0119] In some embodiments, the first heat exchanger 31 forms a third angle α with the first line L, and the second heat exchanger 32 forms a fourth angle β with the first line L. The third angle α is greater than the fourth angle β, and the first line is parallel to the first direction X.

[0120] In the above embodiment, the angle α formed by the upper first heat exchanger 31 and the first line L is relatively large, while the angle β formed by the lower second heat exchanger 32 and the first line L is relatively small. The first heat exchanger 31 and the second heat exchanger 32 have different response characteristics to the airflow path. This differentiated design can dynamically adjust the air supply ratio of the upper and lower heat exchange areas according to the actual airflow direction, avoiding excessive or insufficient air supply in some areas, thereby achieving airflow balance and coordinated operation between the upper and lower heat exchange areas.

[0121] The first heat exchanger 31 adopts a larger tilt angle (third included angle α), which can better receive the concentrated airflow from the upper guide plate 21; the second heat exchanger 32 adopts a smaller tilt angle (fourth included angle β), which can more effectively receive the diffused airflow from the lower guide plate 22; with the third included angle α being greater than the fourth included angle β, the airflow path is smoother and the pressure distribution is more uniform, which helps to reduce the load fluctuation of the fan 2, reduce the risk of low-frequency resonance, improve the quietness and operational stability during use, and also improve the overall consistency of airflow organization and heat exchange efficiency.

[0122] In the above embodiments, the inclined arrangement of the first heat exchanger 31 and the second heat exchanger 32 can increase the heat exchange area and flexibly adjust the installation position of the first heat exchanger 31 and the second heat exchanger 32 in the housing 1, which helps to shorten the dimension in the height direction and improve the integration.

[0123] In some embodiments, the first heat exchanger 31 forms a third angle α with the first line L, the angle of the third angle α being in the range of 40°~55°, preferably 43°~50°; the first line L is parallel to the first direction X.

[0124] In the above embodiment, the first heat exchanger 31 is located at the upper part of the shell 1 and corresponds to the downstream front air outlet (first outlet 13). Setting an appropriate tilt angle (third included angle α) for the first heat exchanger 31 enables it to more effectively receive the mainstream airflow guided from the upper guide plate 21. If the third included angle α is less than 40°, the first heat exchanger 31 is too close to the horizontal direction, easily causing the airflow to slide across the surface without sufficient contact, reducing heat exchange efficiency. If the third included angle α is greater than 55°, the first heat exchanger 31 is too vertical, which may cause excessively high local wind speeds and increased pressure loss. Therefore, the angle range of the third included angle α is 40°~55°, preferably 43°~50°, which allows the surface of the first heat exchanger 31 to obtain better airflow coverage, improves the heat exchange capacity per unit area, reduces the overall system flow resistance, improves the air delivery efficiency of the fan 2, and increases the utilization rate of the heat exchange surface of the first heat exchanger 31, contributing to a highly efficient and stable heat exchange process.

[0125] The third included angle α is preferably 43°~50°, which can make the airflow more consistent in direction when entering the heat exchange area, reduce eddies and backflow phenomena, make the airflow more easily flow smoothly along the heat exchange surface, and reduce the risk of boundary layer separation.

[0126] Furthermore, the inclined arrangement of the first heat exchanger 31 can maintain good heat exchange performance while increasing its heat exchange area. It can also flexibly adjust its installation position in the housing 1 so that the first heat exchanger 31 avoids other internal components (such as the air guide plate set at the first outlet 13), which is conducive to the miniaturization of the air conditioning indoor unit.

[0127] In some embodiments, the angle of the third included angle α is 46.5°.

[0128] In some embodiments, the second heat exchanger 32 forms a fourth included angle β with the first line L, the angle range of the fourth included angle β is 25°~45°, preferably 32°~38°; the first line L is parallel to the first direction X.

[0129] In the above embodiment, the second heat exchanger 32 is located at the lower part of the shell 1, corresponding to the lower air outlet (second outlet 14). Setting an appropriate tilt angle (fourth included angle β) for the second heat exchanger 32 allows the airflow to more evenly cover its heat exchange surface, avoiding excessively high or low local wind speeds. If the fourth included angle β is less than 25°, the second heat exchanger 32 is too close to the horizontal direction, which may cause the airflow to slide across the surface without sufficient contact, reducing heat exchange efficiency. If the fourth included angle β is greater than 45°, the second heat exchanger 32 is too vertical, which may cause excessive local pressure loss and uneven airflow distribution. Therefore, the angle range of the fourth included angle β is 25°~45°, preferably 32°~38°, which allows the airflow to flow more smoothly along the heat exchange surface, reducing the risk of boundary layer separation, reducing the overall system flow resistance, improving the fan's air delivery efficiency, obtaining a uniform airflow distribution, and enhancing the overall heat exchange capacity.

[0130] Furthermore, the inclined arrangement of the second heat exchanger 32 allows for flexible adjustment of its installation position within the housing 1 while increasing its heat exchange area. The fourth included angle β ranges from 25° to 45°, preferably from 32° to 38°, which not only ensures good heat exchange performance of the second heat exchanger 32 but also helps to avoid other internal components (such as air guide plates at the first air outlet 13 and the second air outlet 14), thus contributing to the compactness and miniaturization of the air conditioning indoor unit.

[0131] In some embodiments, the angle of the fourth included angle β is 35.5°.

[0132] In some embodiments, the angle range of the first included angle formed between the first heat exchanger 31 and the second heat exchanger 32 is 70°~90°, preferably 80°~85°.

[0133] In the above embodiment, the first heat exchanger 31 and the second heat exchanger 32 constitute the main flow path of the airflow from the fan 2. Setting an appropriate first angle can create a guiding space between them that adapts to the direction of the mainstream airflow. If the first angle is too small, less than 70°, the distance between the first heat exchanger 31 and the second heat exchanger 32 will be too narrow, resulting in a restricted airflow channel, increased flow resistance, and hindering the improvement of heat exchange efficiency. If the first angle is too large, greater than 90°, the first heat exchanger 31 and the second heat exchanger 32 will be too dispersed, reducing the guiding effect, making the airflow easily diffuse, affecting the air supply efficiency, and correspondingly reducing the heat exchange efficiency. Therefore, the angle range of the first angle is 70°~90°, preferably 80°~85°. This not only helps to improve the overall ventilation efficiency and maintain the balance between the upper and lower airflows, but also prevents the airflow density in some areas from being too high or too low, making the airflow distribution between the upper and lower heat exchange areas more uniform, preventing local overcooling or overheating caused by uneven airflow, and improving the stability of equipment operation and user comfort.

[0134] In some embodiments, the upper guide plate 21 and the lower guide plate 22 are used to guide airflow to the corresponding heat exchanger. The first included angle between the first heat exchanger 31 and the second heat exchanger 32 needs to match its guiding path. The angle range of the first included angle is 70°~90°, preferably 80°~85°, which makes the space between the first heat exchanger 31 and the second heat exchanger 32 more conducive to receiving concentrated airflow from the upper guide plate 21 and the lower guide plate 22, improving the utilization rate of the heat exchange surface and helping to achieve an efficient and stable heat exchange process. In addition, the setting of the first included angle can shorten the space inside the shell 1 along the first direction X without sacrificing the heat exchange area, which helps to achieve miniaturization design. At the same time, the first included angle between the first heat exchanger 31 and the second heat exchanger 32 also makes it easier to avoid other internal components (such as the air guide plates set at the first air outlet 13 and the second air outlet 14), preventing interference with other components.

[0135] In some embodiments, the angle of the first included angle is 82.5°.

[0136] In some embodiments, the housing 1 is provided with a partition 4, which divides the housing 1 into a first cavity 11 for accommodating the fan 2 and a second cavity 12 for accommodating the heat exchanger 3. The sum of the dimensions of the first cavity 11 and the second cavity 12 extending along the first direction X is the first width E, and the dimension of the second cavity 12 extending along the first direction X is the second width D. The second width D accounts for 40% to 45% of the first width E.

[0137] In the above embodiments, controlling the length of the heat exchange zone (i.e., the second width D) to 40% to 45% of the overall width (i.e., the first width E) can reduce airflow separation, eddies and backflow caused by unreasonable space utilization, shorten the size of the housing 1 in the first direction X, improve the compactness of the internal structure of the housing 1, and facilitate the miniaturization design of the air conditioning indoor unit.

[0138] In some embodiments, the first width E ranges from 380mm to 410mm, and the second width D ranges from 155mm to 185mm.

[0139] In the above embodiments, by limiting the first width E to 380mm~410mm and the second width D to 155mm~185mm, precise control over the internal spatial layout of the casing 1 is achieved. By setting specific ranges for the first width E and the second width D, the ratio of the second width D to the first width E falls within the target range. This ensures that the distance between the outlet of the fan 2 and the heat exchanger 3 is appropriate, allowing the airflow to smoothly transition to the heat exchange area after leaving the fan 2. This reduces eddies and pressure losses caused by abrupt path changes, improves the air delivery efficiency of the fan 2 and the uniformity of the air velocity distribution on the heat exchanger surface, and achieves a balance between compact structure and high efficiency.

[0140] The first width E ranges from 380mm to 410mm, which meets the demand for thinner and lighter home appliances; at the same time, the second width D ranges from 155mm to 185mm, which ensures that the length of the heat exchanger reaches more than 160mm, meeting the basic requirements for heat exchange area.

[0141] In some embodiments, the dimension of the first cavity 11 extending along the first direction X is a third width C, which may be 225 mm.

[0142] refer to Figure 3 In some embodiments, the housing 1 has a first air vent 13 on the side wall in the first direction X, and a second air vent 14 on the bottom of the housing 1. The first opening size M of the first air vent 13 extending in the second direction Y is in the range of 100mm~130mm, preferably 105mm~120mm. The second opening size N of the second air vent 14 extending in the first direction X is in the range of 45mm~75mm, preferably 50mm~65mm. The second direction Y is parallel to the direction from the top to the bottom of the housing 1, and the second direction Y intersects with the first direction X.

[0143] In the above embodiment, the air conditioner indoor unit has a first air outlet 13 and a second air outlet 14. The first air outlet 13 is located on the front side of the air conditioner indoor unit and is used to discharge air to the front side of the air conditioner indoor unit. The second air outlet 14 is located on the bottom of the air conditioner indoor unit and is used to discharge air from the bottom of the air conditioner indoor unit.

[0144] In the above embodiment, the first air outlet 13 is the front air outlet of the indoor unit of the air conditioner, which is used to send air upward into the indoor space. It is suitable for quickly adjusting the temperature and avoiding direct cold air blowing. The second air outlet 14 is the lower air outlet of the indoor unit of the air conditioner, which is responsible for sending air downward. It is often used for comfort control in the area near the floor and improves the speed of temperature adjustment.

[0145] In the above embodiments, if the first opening size M or the second opening size N is too large, it may cause the air velocity on the outlet side of the heat exchanger 3 to decrease, affecting the heat exchange efficiency; if the second opening size N is too small, it will increase the local resistance, resulting in an increase in the load on the fan 2. Therefore, the range of the first opening size M is 100mm~130mm, preferably 105mm~120mm, and the range of the second opening size N is 45mm~75mm, preferably 50mm~65mm. This makes it easier for the airflow to maintain a laminar flow state, reduces the energy loss caused by boundary layer separation, improves the fan's air delivery efficiency, reduces the system's operating energy consumption, increases the heat exchange efficiency per unit time, and improves the overall performance of the equipment. Especially in miniaturized air conditioning indoor units, a reasonable air outlet size can reduce the overall size of the unit without sacrificing performance.

[0146] In the above embodiments, the first air vent 13 can supply air independently, the second air vent 14 can supply air independently, or the first air vent 13 and the second air vent 14 can supply air simultaneously. By reasonably setting the ratio of the first opening size M and the second opening size N, it is helpful to achieve a dynamic balance between the upper and lower air supply. If the first opening size M is too small, it will limit the upper air supply capacity. If the second opening size N is too large, it may cause the bottom airflow to be too strong and affect the overall comfort.

[0147] In some embodiments, the first opening size M is 110 mm; the second opening size N is 57 mm.

[0148] In some embodiments, the housing 1 is provided with a partition 4, which divides the housing 1 into a first cavity 11 for accommodating the fan 2 and a second cavity 12 for accommodating the heat exchanger 3; the second cavity 12 is provided with a first air vent 13 on the side wall located in the first direction X, and a second air vent 14 is provided at the bottom of the second cavity 12; the first cavity 11 extends along the first direction X with a dimension of a third width C, and the second cavity 12 extends along the first direction X with a dimension of a second width D, the second width D being equal to the third width C.

[0149] In the above embodiment, the third width C equals the second width D, indicating that the first cavity 11 accommodating the fan 2 and the second cavity 12 accommodating the heat exchanger 3 have the same size in the first direction X. Under the equal width structure, the transition distance between the fan 2 and the heat exchanger 3 is consistent, which helps to form a uniform and stable airflow field, reduce local eddies and backflow caused by asymmetrical flow, reduce pressure loss, improve ventilation efficiency, and reduce vibration and noise caused by airflow disturbance.

[0150] Furthermore, for air conditioning indoor units that require a compact layout, the equal-width design helps to compress the width space while still ensuring sufficient heat exchange area and fan installation space, achieving the best balance between space utilization and performance assurance.

[0151] In the above embodiments, the first air vent 13 and the second air vent 14 are used to guide airflow from the front and bottom of the housing 1, respectively. Users can choose to have the first air vent 13 or the second air vent 14 vent, or have the first air vent 13 and the second air vent 14 vent vent simultaneously, to meet different user needs and improve user comfort.

[0152] In some embodiments, a first air vent 13 and a second air vent 14 are simultaneously provided on the housing 1. The housing 1 extends 450 mm along the first direction X. The first cavity 11 and the second cavity 12 each occupy half of the space. The first cavity 11 and the second cavity 12 extend 225 mm along the first direction X.

[0153] In some embodiments, the first opening size M of the first air vent 13 is larger than the second opening size N of the second air vent 14. Since the first heat exchanger 31 corresponds to the first air vent 13 and the second heat exchanger 32 corresponds to the second air vent 14, the dimension from the first end to the second end of the first heat exchanger 31 is larger than the dimensions from the first end to the second end of the second heat exchanger 32. This ensures that the larger air vent has a matching airflow capacity and heat exchange area, thereby improving the heat exchange effect. Furthermore, the third angle α formed by the first heat exchanger 31 and the first line L is larger than the fourth angle β formed by the second heat exchanger 32 and the first line L. This setting not only adapts to the structural layout where the first opening size M of the first air vent 13 is larger than the second opening size N of the second air vent 14, but also helps to improve the airflow coverage and heat exchange efficiency of the upper heat exchange area. The angle and setting position of the first angle formed between the first heat exchanger 31 and the second heat exchanger 32 are also used to avoid interference with the air guide plates set at the first air vent 13 and the second air vent 14, thereby ensuring the normal operation of the air guide plates.

[0154] Some embodiments of this utility model also provide an air conditioner, which includes the indoor unit of any of the above-mentioned air conditioners.

[0155] In some embodiments, the air conditioner includes a ducted unit.

[0156] Based on the above embodiments of the present invention, in the absence of explicit denial or conflict, the technical features of one embodiment can be advantageously combined with one or more other embodiments.

[0157] Although specific embodiments of the present invention have been described in detail by way of examples, those skilled in the art should understand that the above examples are for illustrative purposes only and are not intended to limit the scope of the present invention. Those skilled in the art should understand that modifications can be made to the above embodiments or equivalent substitutions can be made to some technical features without departing from the scope and spirit of the present invention. The scope of the present invention is defined by the appended claims.

Claims

1. An indoor unit for an air conditioner, characterized in that, It includes a housing (1) and a fan (2) and a heat exchanger (3) arranged sequentially in the housing (1) along a first direction (X); The heat exchanger (3) includes a first heat exchange element (31) and a second heat exchange element (32). The first end of the first heat exchange element (31) extends toward the top of the shell (1), and the first end of the second heat exchange element (32) extends toward the bottom of the shell (1). The second end of the first heat exchange element (31) is adjacent to the second end of the second heat exchange element (32), and a first angle is formed between the first heat exchange element (31) and the second heat exchange element (32). The fan (2) includes an air outlet (23), the upper guide plate (21) of the air outlet (23) extends toward the first end of the first heat exchanger (31), and the lower guide plate (22) of the air outlet (23) extends toward the first end of the second heat exchanger (32).

2. The indoor unit of the air conditioner according to claim 1, characterized in that, The housing (1) is provided with a partition (4), which divides the housing (1) into a first chamber (11) for accommodating the fan (2) and a second chamber (12) for accommodating the heat exchanger (3). The upper part of the partition (4) is provided with a connecting part, the air outlet (23) is located in the connecting part, and the downstream end of the upper guide plate (21) passes through the connecting part and is located in the second chamber (12). The downstream end of the lower guide plate (22) is connected to the top of the partition (4).

3. The indoor unit of the air conditioner according to claim 1, characterized in that, The upper guide plate (21) and the lower guide plate (22) form a second included angle λ, the angle range of the second included angle λ is 25°~40°.

4. The indoor unit of the air conditioner according to claim 1, characterized in that, In the first direction (X), the downstream end of the upper guide plate (21) is closer to the heat exchanger (3) than the downstream end of the lower guide plate (22).

5. The indoor unit of the air conditioner according to claim 4, characterized in that, In the first direction (X), there is a first distance (B) between the downstream end of the upper guide plate (21) and the downstream end of the lower guide plate (22), and the size of the first distance (B) is in the range of 40mm to 60mm.

6. The indoor unit of the air conditioner according to claim 4, characterized in that, In the first direction (X), the first end of the second heat exchanger (32) is located between the downstream end of the upper guide plate (21) and the downstream end of the lower guide plate (22).

7. The indoor unit of the air conditioner according to claim 6, characterized in that, In the first direction (X), there is a second distance (A) between the first end of the second heat exchanger (32) and the downstream end of the lower guide plate (22), the second distance (A) being 30mm to 50mm in size.

8. The indoor unit of the air conditioner according to claim 6, characterized in that, In the first direction (X), there is a first distance (B) between the downstream end of the upper guide plate (21) and the downstream end of the lower guide plate (22), and a second distance (A) between the first end of the second heat exchanger (32) and the downstream end of the lower guide plate (22), and the ratio of the second distance (A) to the first distance (B) is in the range of 0.6 to 0.

9.

9. The indoor unit of the air conditioner according to claim 1, characterized in that, In the second direction (Y), there is a third distance (H) between the upstream end of the upper guide plate (21) and the upstream end of the lower guide plate (22), the third distance (H) being in the range of 70 mm to 100 mm. The second direction (Y) is parallel to the direction from the top to the bottom of the housing (1), and the second direction (Y) intersects with the first direction (X).

10. The indoor unit of the air conditioner according to claim 1, characterized in that, In the first direction (X), there is a fourth distance (G) between the center of the fan (2) and the first end of the second heat exchanger (32), the fourth distance (G) being in the range of 130mm to 170mm.

11. The indoor unit of the air conditioner according to claim 1, characterized in that, In the first direction (X), there is a fifth distance (F) between the center of the fan (2) and the downstream end of the lower guide plate (22), the fifth distance (F) being in the range of 95mm to 125mm.

12. The indoor unit of the air conditioner according to claim 1, characterized in that, In the first direction (X), there is a fourth distance (G) between the center of the fan (2) and the first end of the second heat exchanger (32), and a fifth distance (F) between the center of the fan (2) and the downstream end of the lower guide plate (22), and the ratio of the fourth distance (G) to the fifth distance (F) is in the range of 1.1 to 1.

7.

13. The indoor unit of the air conditioner according to claim 1, characterized in that, The impeller radius (R) of the fan (2) is in the range of 60mm to 80mm.

14. The indoor unit of the air conditioner according to claim 1, characterized in that, In the first direction (X), there is a fourth distance (G) between the center of the fan (2) and the first end of the second heat exchanger (32), and the ratio of the fourth distance (G) to the impeller radius (R) of the fan (2) is in the range of 1.8 to 2.

5.

15. The indoor unit of the air conditioner according to claim 1, characterized in that, In the first direction (X), there is a fifth distance (F) between the center of the fan (2) and the downstream end of the lower guide plate (22), and the ratio of the fifth distance (F) to the impeller radius (R) of the fan (2) is in the range of 1.2 to 1.

8.

16. The indoor unit of the air conditioner according to claim 1, characterized in that, The first heat exchanger (31) forms a third angle α with the first line (L), and the second heat exchanger (32) forms a fourth angle β with the first line (L). The third angle α is greater than the fourth angle β, and the first line (L) is parallel to the first direction (X).

17. The indoor unit of the air conditioner according to claim 1, characterized in that, The first heat exchanger (31) forms a third included angle α with the first line (L), and the angle range of the third included angle α is 40°~55°; the first line (L) is parallel to the first direction (X).

18. The indoor unit of the air conditioner according to claim 1, characterized in that, The second heat exchanger (32) forms a fourth included angle β with the first line (L), the angle range of the fourth included angle β is 25°~45°; the first line (L) is parallel to the first direction (X).

19. The indoor unit of the air conditioner according to claim 1, characterized in that, The angle range of the first included angle is 70°~90°.

20. The indoor unit of the air conditioner according to claim 1, characterized in that, The housing (1) is provided with a partition (4), which divides the housing (1) into a first cavity (11) for accommodating the fan (2) and a second cavity (12) for accommodating the heat exchanger (3). The sum of the dimensions of the first cavity (11) and the second cavity (12) extending along the first direction (X) is the first width (E), and the dimension of the second cavity (12) extending along the first direction (X) is the second width (D). The second width (D) accounts for 40% to 45% of the first width (E).

21. The indoor unit of the air conditioner according to claim 20, characterized in that, The first width (E) has a size range of 380mm to 410mm, and the second width (D) has a size range of 155mm to 185mm.

22. The indoor unit of the air conditioner according to claim 1, characterized in that, The housing (1) has a first air vent (13) on the side wall in the first direction (X) and a second air vent (14) at the bottom of the housing (1). The first opening size (M) of the first air vent (13) extending in the second direction (Y) is in the range of 100mm~130mm, and the second opening size (N) of the second air vent (14) extending in the first direction (X) is in the range of 45mm~75mm. The second direction (Y) is parallel to the direction from the top to the bottom of the housing (1) and intersects with the first direction (X).

23. The indoor unit of the air conditioner according to claim 1, characterized in that, The housing (1) is provided with a partition (4), which divides the housing (1) into a first cavity (11) for accommodating the fan (2) and a second cavity (12) for accommodating the heat exchanger (3). The second cavity (12) has a first air vent (13) on its side wall in the first direction (X) and a second air vent (14) at its bottom. The first cavity (11) extends along the first direction (X) with a third width (C), and the second cavity (12) extends along the first direction (X) with a second width (D), which is equal to the third width (C).

24. The indoor unit of the air conditioner according to claim 3, characterized in that, The second included angle λ ranges from 30° to 35°.

25. The indoor unit of the air conditioner according to claim 5, characterized in that, The size range of the first distance (B) is 45mm to 55mm.

26. The indoor unit of the air conditioner according to claim 7, characterized in that, The second distance (A) has a size range of 32mm to 45mm.

27. The indoor unit of the air conditioner according to claim 8, characterized in that, The ratio of the second distance (A) to the first distance (B) is in the range of 0.7 to 0.

8.

28. The indoor unit of the air conditioner according to claim 9, characterized in that, The range of the third distance (H) is 80mm to 90mm.

29. The indoor unit of the air conditioner according to claim 10, characterized in that, The size range of the fourth distance (G) is 140mm to 160mm.

30. The indoor unit of the air conditioner according to claim 11, characterized in that, The fifth distance (F) has a size range of 100mm to 115mm.

31. The indoor unit of the air conditioner according to claim 12, characterized in that, The ratio of the fourth distance (G) to the fifth distance (F) is in the range of 1.3 to 1.

5.

32. The indoor unit of the air conditioner according to claim 13, characterized in that, The impeller radius (R) of the fan (2) is in the range of 65mm to 75mm.

33. The indoor unit of the air conditioner according to claim 14, characterized in that, The ratio of the fourth distance (G) to the impeller radius (R) of the fan (2) is in the range of 2 to 2.

3.

34. The indoor unit of the air conditioner according to claim 15, characterized in that, The ratio of the fifth distance (F) to the impeller radius (R) of the fan (2) is in the range of 1.4 to 1.

7.

35. The indoor unit of the air conditioner according to claim 17, characterized in that, The angle range of the third included angle α is 43°~50°.

36. The indoor unit of the air conditioner according to claim 18, characterized in that, The angle range of the fourth included angle β is 32°~38°.

37. The indoor unit of the air conditioner according to claim 19, characterized in that, The angle range of the first included angle is 80°~85°.

38. The indoor unit of the air conditioner according to claim 22, characterized in that, The first opening size (M) of the first air vent (13) extending along the second direction (Y) ranges from 105mm to 120mm; the second opening size (N) of the second air vent (14) extending along the first direction (X) ranges from 50mm to 65mm.

39. An air conditioner, characterized in that, Including the air conditioning indoor unit according to any one of claims 1 to 38.

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