Air Conditioner

Abstract

The present disclosure relates to an air conditioner. An air conditioner according to an embodiment of the present disclosure comprises: a case having an intake port and a discharge port formed in a front panel; and a fan disposed inside the case and flowing air from the intake port to the discharge port. The case comprises: a lower panel forming a bottom surface; and the fan comprises: a front plate having a front intake port formed in communication with the intake port; a rear plate spaced rearward from the front plate and having a rear intake port formed therein; and a side plate connecting the front plate and the rear plate. At least one of the rear plate and the side plate includes a curved portion at the portion connected to each other, and the lower end of the fan is spaced upward from the lower panel to form a lower air passage communicating with the intake port and the rear intake port.

Description

Technology Field

[0001] The present disclosure relates to an air conditioner, and more specifically, to an air conditioner including a blower fan. Background Technology

[0002] An air conditioner is a device that performs functions such as cooling, heating, dehumidification, humidification, and ventilation indoors, and generally includes a fan that draws in and discharges air.

[0003] There are various types of blower fans used in air conditioners, such as cross-flow fans, centrifugal fans, and axial fans, depending on the purpose of use and the installation location, and in the case of certain air conditioners, a Sirocco fan, which is a type of centrifugal fan, must be adopted.

[0004] A double-suction Sirocco fan generally comprises an impeller that draws in and discharges air through rotation, and a fan housing that encloses the impeller. In this case, intake ports are formed on each side of the impeller, and since air can be drawn in and blown through two intake ports, there is an advantage in increasing the airflow volume.

[0005] However, during the process of air intake, air flows smoothly through the front intake without significant resistance, whereas air entering through the rear intake experiences flow resistance due to the structural characteristics of the case housing the Sirocco fan.

[0006] Due to this flow resistance, vortices are generated at the rear intake port, and as a result, a problem arises in which the smooth intake of air is hindered.

[0007] Due to the above problems, the amount of air circulating inside the indoor unit is reduced, which lowers the overall performance of the air conditioner, and there is a problem where noise increases due to the vortex generated around the Sirocco fan, causing discomfort to the user. The problem to be solved

[0008] The technical problem of the present disclosure is to provide an air conditioner capable of solving the various problems of the aforementioned prior art.

[0009] Another objective of the present disclosure is to provide an air conditioner that reduces flow resistance at the lower side of the fan.

[0010] Another objective of the present disclosure is to provide an air conditioner that reduces flow resistance to the front intake of the fan.

[0011] Another objective of the present disclosure is to provide an air conditioner that reduces flow resistance to the rear intake of the fan.

[0012] Another objective of the present disclosure is to provide an air conditioner that reduces flow resistance at the fan outlet.

[0013] Another objective of the present disclosure is to provide an air conditioner with reduced power consumption.

[0014] Another objective of the present disclosure is to provide an air conditioner that reduces noise generated during operation.

[0015] The problems of the present disclosure are not limited to those mentioned above, and other problems not mentioned will be clearly understood by those skilled in the art from the description below. means of solving the problem

[0016] To achieve the above objective, an air conditioner according to one embodiment of the present disclosure comprises: a case having an intake port and a discharge port formed in a front panel; and a fan disposed inside the case and flowing air from the intake port to the discharge port.

[0017] The above case includes: a lower panel forming a bottom surface, and the fan includes: a front plate having a front intake port formed therein communicating with the intake port; a rear plate spaced rearward from the front plate and having a rear intake port formed therein; and a side plate connecting the front plate and the rear plate.

[0018] At least one of the rear plate and the side plate includes a curved portion at the portion connected to each other, and the lower end of the fan is spaced upward from the lower panel to form a lower flow path connecting the intake port and the rear intake port.

[0019] The above front panel has a plurality of intake ports formed vertically, and the lowest intake port among the plurality of intake ports can be positioned below the fan.

[0020] The bottom of the above fan can be positioned above the top of the bottom intake port.

[0021] The above front panel includes a suction cover having a plurality of suction ports formed vertically, and the suction cover may include a plurality of suction vanes that guide air flowing into the plurality of suction ports.

[0022] The lower panel may further include a front guide that is positioned adjacent to the lowest intake vane among the plurality of intake vanes and guides air into the lower flow path.

[0023] The lower panel further includes a front bend portion that extends downward from the rear end of the front guide and is arranged parallel to the front plate, and the front bend portion may be positioned in front of the front plate.

[0024] The lower panel further includes a rear bend portion that extends upward from a floor wall spaced apart from the fan and is positioned parallel to the rear plate, and the rear bend portion may be positioned below the curved portion.

[0025] The above rear bend portion may be positioned in front of the above rear plate.

[0026] The above front panel includes a suction cover having a plurality of suction ports formed vertically, and the suction cover includes a plurality of suction vanes that guide air flowing into the plurality of suction ports, and the plurality of suction vanes can be arranged at the same angle.

[0027] The above case includes a rear panel spaced rearward from the front panel, the front panel is spaced rearward by a predetermined distance from the front panel, and the rear panel can be spaced forward by a predetermined distance from the rear panel.

[0028] The distance between the front plate and the front panel may be greater than the distance between the rear plate and the rear panel.

[0029] The above fan may further include an orifice disposed in the front intake port, the inner diameter of which decreases toward the rear.

[0030] The fan further includes an impeller disposed between the front plate and the rear plate and comprising a plurality of blades, and the orifice may have an inner end extending toward the center of the front intake port to cover a portion of the plurality of blades in the front-rear direction.

[0031] The inner end of the orifice may be extended to cover 40% to 60% of the blade in the front-rear direction.

[0032] The fan comprises an impeller that is positioned between the front plate and the rear plate and moves air according to rotation, and the side plate comprises a cutoff portion into which the air flowing inside the fan is branched, and the cutoff portion may be positioned parallel to the rotation axis of the impeller.

[0033] When the angle between a virtual line extending horizontally from the center of rotation of the impeller and a virtual straight line connecting the center of rotation of the impeller and the cut-off portion is called the starting angle, the starting angle may be 80° to 100°.

[0034] The above side plate includes a cutoff portion into which air flowing inside the fan is branched, and the fan may further include a reinforcing rib that is positioned on one side of the cutoff portion and extends vertically from the side plate.

[0035] Specific details of other embodiments are included in the detailed description and drawings. Effects of the invention

[0036] According to the air conditioner of the present disclosure, one or more of the following effects are provided.

[0037] Among the multiple intake ports, the lowest intake port is positioned below the fan, thereby reducing flow resistance at the bottom of the fan and increasing the airflow.

[0038] An orifice with an inner diameter that decreases toward the rear is placed at the front intake port, which can reduce flow resistance to the front intake port.

[0039] At least one of the rear plate and the side plate of the fan includes a curved portion, so that the flow resistance to the rear intake can be reduced.

[0040] The cutoff section is positioned parallel to the impeller's rotation axis, so that flow resistance at the fan discharge port can be reduced.

[0041] In addition, due to the structure that reduces Euro resistance, the power consumed to generate the same airflow can be reduced.

[0042] Multiple intake vanes are arranged at the same angle, thereby resolving the imbalance in airflow between the front intake and the rear intake, and reducing noise generated during the operation of the air conditioner.

[0043] The effects of the present disclosure are not limited to those mentioned above, and other unmentioned effects will be clearly understood by those skilled in the art from the description in the claims. Brief explanation of the drawing

[0044] FIG. 1 is a perspective view of an air conditioner according to one embodiment of the present disclosure. FIG. 2 is a cross-sectional view of an air conditioner according to one embodiment of the present disclosure. FIG. 3 is an exploded perspective view of an air conditioner and a fan according to one embodiment of the present disclosure. FIG. 4 is a front view of a suction cover according to one embodiment of the present disclosure. Figure 5 is an enlarged view of the case and fan shown in Figure 2. FIG. 6 illustrates the air flow pattern in the lower flow path according to the first comparative example and one embodiment of the present disclosure. FIG. 7 shows the pressure distribution of a rear intake port according to a first comparative example and an embodiment of the present disclosure from the front. FIG. 8 shows the performance of an air conditioner with a lower flow path formed according to a first comparative example and an embodiment of the present disclosure in numerical terms. FIG. 9 is a rear view of a curved surface according to one embodiment of the present disclosure. FIG. 10 illustrates a second comparative example and a curved surface according to one embodiment of the present disclosure. FIG. 11 shows the performance of an air conditioner including a curved surface according to a second comparative example and an embodiment of the present disclosure in numerical terms. FIG. 12 is a front view of an orifice according to one embodiment of the present disclosure. Figure 13 is a frontal view of an orifice with an opening ratio of 0%. Figure 14 is a frontal view of an orifice with an opening ratio of 77%. Figure 15 shows the performance of the air conditioner according to the opening ratio of the orifice in numerical terms. Figure 16 is a diagram for explaining the starting angle of the cutoff section. FIG. 17 is for illustrating a cutoff portion according to one embodiment of the present disclosure, and shows the fan viewed from above. FIG. 18 is intended to illustrate the cutoff section according to the third comparative example, and shows the fan viewed from above. FIG. 19 is intended to illustrate the cutoff section according to the fourth comparative example, and shows the fan viewed from above. Figure 20 shows the performance of an air conditioner according to the shape of the cutoff section in numerical terms. Specific details for implementing the invention

[0045] Hereinafter, embodiments disclosed in this specification will be described in detail with reference to the attached drawings. Identical or similar components regardless of drawing symbols are given the same reference number, and redundant descriptions thereof will be omitted.

[0046] The suffixes "module" and "part" used for components in the following description are assigned or used interchangeably solely for the ease of drafting the specification, and do not inherently possess distinct meanings or roles.

[0047] In addition, when describing the embodiments disclosed in this specification, if it is determined that a detailed description of related prior art may obscure the essence of the embodiments disclosed in this specification, such detailed description is omitted. Furthermore, the attached drawings are intended only to facilitate understanding of the embodiments disclosed in this specification, and the technical concept disclosed in this specification is not limited by the attached drawings; it should be understood that they include all modifications, equivalents, and substitutions that fall within the concept and technical scope of this disclosure.

[0048] Terms including ordinal numbers, such as first, second, etc., may be used to describe various components, but said components are not limited by said terms. These terms are used solely for the purpose of distinguishing one component from another.

[0049] When it is stated that one component is "connected" or "connected" to another component, it should be understood that while it may be directly connected or connected to that other component, there may also be other components in between. On the other hand, when it is stated that one component is "directly connected" or "directly connected" to another component, it should be understood that there are no other components in between.

[0050] A singular expression includes a plural expression unless the context clearly indicates otherwise.

[0051] In this application, terms such as “comprising” or “having” are intended to specify the existence of the features, numbers, steps, actions, components, parts, or combinations thereof described in the specification, and should be understood as not precluding the existence or addition of one or more other features, numbers, steps, actions, components, parts, or combinations thereof.

[0052] The directional indications of Up (U), Down (D), Forward (F), and Back (R) shown in the drawings are for convenience of explanation only and do not limit the technical concepts disclosed in this specification.

[0054] Referring to FIG. 1, the external structure of an air conditioner (1) according to one embodiment of the present disclosure can be seen.

[0055] The air conditioner (1) may include a front panel (11) including an intake cover (20).

[0056] The front panel (11) can be positioned at the front of the air conditioner (1). The front panel (11) can cover the internal components of the air conditioner (1) so that they are not exposed.

[0057] The intake cover (20) can be positioned in front of the air conditioner (1). The intake cover (20) can be positioned on the lower side of the front panel (11).

[0058] The intake port (3) and the discharge port (4, see FIG. 2) are formed on the front panel (11). The intake port (3) may be formed on the intake cover (20). Multiple intake ports (3) may be formed on the intake cover (20). The discharge port (4) may be formed on the upper part of the front panel (11). The discharge port (4) may be formed on top of the intake port (3).

[0059] The discharge vane (15) can be placed in the discharge port (4). The discharge vane (15) can be formed to be long in the left-right direction. The discharge vane (15) can be a plurality of vanes arranged in the up-down direction.

[0060] As shown in the drawing, when the discharge vane (15) is positioned parallel to the front panel (11), the discharge vane (15) can shield the discharge port (4) in the front and rear directions. When the power of the air conditioner (1) is turned off, the discharge vane (15) can shield the discharge port (4).

[0062] Referring to FIG. 2, the internal structure of an air conditioner (1) according to one embodiment of the present disclosure can be seen.

[0063] The air conditioner (1) includes a fan (30) that flows air from the intake port (3) to the discharge port (4). The fan (30) is placed inside the case (10).

[0064] The case (10) may include a rear panel (12) spaced rearward from the front panel (11). A fan (30) may be positioned between the intake cover (20) and the rear panel (12). The fan (30) may be positioned spaced apart from the intake cover (20) and the rear panel (12). As a result, a space may be formed between the intake cover (20) and the fan (30) and between the rear panel (12) and the fan (30).

[0065] The intake cover (20) may include a front plate (21) and an intake vane (22). The front plate (21) may be positioned parallel to the front panel (11). The front plate (21) may be positioned in an up-and-down direction. The front plate (21) may protect a component inside the air conditioner (1) positioned at the rear of the intake cover (20).

[0066] The intake vane (22) can guide air entering the intake port (3). The intake vane (22) can be connected to the front plate (21). The intake vane (22) can be positioned at an angle to the front plate (21). As a result, when viewing the air conditioner (1) from the front, internal components including the fan (30) may not be visible.

[0067] The intake port (3) may be an opening through which air from outside the air conditioner (1) flows into the air conditioner (1). The intake port (3) may be formed between a plurality of vertically arranged front plates (21).

[0068] The intake port (3) may be located inside the air conditioner (1). For example, the space between a plurality of intake vanes (22) arranged vertically may be referred to as the intake port (3).

[0069] The air conditioner (1) may include a heat exchanger (2). Air can exchange heat with a refrigerant passing through the inside of the heat exchanger (2). As a result, the air conditioner (1) can perform heating and cooling.

[0070] The heat exchanger (2) can be placed inside the case (10). The heat exchanger (2) can be placed above the fan (30). Air discharged from the fan (30) can pass through the heat exchanger (2) and be discharged through the discharge port (4).

[0071] The discharge vane (15) can be placed in the discharge port (4). The discharge vane (15) may include horizontal vanes and vertical vanes. The discharge vane (15) can control the direction of air discharged from the discharge port (4). Meanwhile, unlike FIG. 1, this drawing shows the discharge vane (15) in a rotated state.

[0073] Referring to FIG. 3, the configuration of an air conditioner (1) and a fan (30) according to one embodiment of the present disclosure can be seen.

[0074] The case (10) may include a first side panel (16), a second side panel (17), an upper panel (13), and a lower panel (14) connecting the front panel (11) and the rear panel (12).

[0075] The first side panel (16) and the second side panel (17) may be spaced apart from each other in the left-right direction. The first side panel (16) and the second side panel (17) may be arranged side by side.

[0076] For example, the first side panel (16) may form the left side of the case (10), and the second side panel (17) may form the right side of the case (10).

[0077] The upper panel (13) and the lower panel (14) may be spaced apart from each other in the vertical direction. The upper panel (13) and the lower panel (14) may be arranged side by side.

[0078] A case (10) having a rectangular shape may have a structure in which five sides excluding the front panel (11) are manufactured as a single unit and the front panel (11) is attached to the remaining five sides. Alternatively, it may have a structure in which all six sides are manufactured individually and joined together.

[0079] The case (10) can form a space enclosed by a front panel (11), a rear panel (12), an upper panel (13), a lower panel (14), a first side panel (16), and a second side panel (17). Accordingly, the case (10) can accommodate various components including a fan (30) and a heat exchanger (2) inside.

[0080] The fan (30) may include a fan housing (31), an impeller (35), an orifice (36), an air filter (37), and a motor (38). The fan housing (31) may include a front plate (32), a rear plate (33), and a side plate (34).

[0081] The front plate (32) can form the front surface of the fan (30). The front plate (32) can be placed parallel to the front panel (11).

[0082] The front plate (32) forms a front intake port (321) that communicates with the intake port (3). Air introduced into the intake port (3) can be introduced into the fan (30) through the front intake port (321).

[0083] The rear plate (33) can form the rear surface of the fan (30). The rear plate (33) can be spaced rearward from the front plate (32). The rear plate (33) can be positioned parallel to the front plate (32).

[0084] The rear plate (33) forms a rear intake port (331). Air introduced through the intake port (3) can be introduced into the fan (30) through the rear intake port (331).

[0085] The side plate (34) connects the front plate (32) and the rear plate (33). The side plate (34) can surround at least a portion of the front plate (32) and the rear plate (33).

[0086] Meanwhile, in this drawing, the front plate (32) and the side plate (34) are connected and the rear plate (33) is spaced apart from the side plate (34), but this is merely to explain the structure of the fan housing (31), and the front plate (32), the rear plate (33), and the side plate (34) may be manufactured as a single unit or manufactured individually and connected.

[0087] The fan housing (31) can form a space in which an impeller (35) is accommodated. The impeller (35) can be placed inside the fan housing (31). The impeller (35) can form an air flow as it rotates.

[0088] The orifice (36) can be placed in the front intake port (321). The orifice (36) has a smaller inner diameter as it extends toward the rear, so that it can guide the air flowing into the front intake port (321).

[0089] As a result, the air resistance entering the front intake port (321) can be reduced, and the noise generated during the operation of the air conditioner (1) can be reduced.

[0090] The orifice (36) can form an orifice hole (361). The orifice hole (361) can communicate with the front suction port (321).

[0091] The air filter (37) can be positioned in front of the orifice (36). The air filter (37) can be positioned in front of the front intake port (321). The air filter (37) can prevent foreign substances, such as dust, from entering the inside of the fan (30).

[0092] The motor (38) can be positioned at the rear of the fan (30). The motor (38) can be connected to the rear panel (12). The motor (38) can be connected to the impeller (35).

[0093] As the motor (38) rotates, the impeller (35) rotates, and negative pressure can be formed inside the fan housing (31). Accordingly, air can be introduced into the fan housing (31) through the front intake port (321) and the rear intake port (331) and discharged toward the heat exchanger (2) on the upper side.

[0095] Referring to FIG. 4, a suction cover (20) according to one embodiment of the present disclosure can be seen.

[0096] In this drawing, the suction vane (22) is not shown for convenience, but the suction vane (22) can be connected to the front plate (21), and the suction vane (22) can be seen when looking at the suction cover (20) from the front.

[0097] The suction port (3) can be formed in the left-right direction. Multiple suction ports (3) can be formed vertically.

[0098] Multiple intake ports (3) may be formed with the same size. Multiple intake ports (3) may have the same width in the left-right direction. Multiple intake ports (3) may have the same height. The vertical length (l1) of the intake port (3) or the vertical width (l1) of the intake port (3) may be smaller than the vertical length of the front plate (21).

[0099] Among the multiple intake ports (3), the intake port (3) located at the bottom can be called the lowest intake port (301). The distance (h1) at which the bottom of the lowest intake port (301) is separated from the ground can be greater than the vertical length (l1) of the intake port (3).

[0100] In this case, air can flow smoothly into the air conditioner (1) through the lowest intake port (301), while preventing dust, foreign matter, etc. from the floor from entering the air conditioner (1).

[0102] Referring to FIG. 5, a cross-section of the suction cover (20) and the fan (30) according to one embodiment of the present disclosure can be seen.

[0103] The direction in which air is drawn can be controlled by the intake vane (22). For example, the intake vane (22) can be formed to be inclined upward toward the rear. In this case, the air can be directed upward by the intake vane (22) and drawn into the front intake port (321).

[0104] Depending on the angle (θ1) between the horizontal direction and the suction vane (22), the flow rate of air flowing into the suction port (3) and the flow resistance may vary. The angle (θ1) between the horizontal direction and the suction vane (22) may preferably be 25° to 28°. At the above angle, the flow rate of air can be sufficiently secured and the flow resistance can be reduced.

[0105] When the air flow rate increases, the amount of air discharged from the discharge port (4) increases, and the cooling and heating performance can be improved.

[0106] A plurality of suction vanes (22) may be arranged parallel to each other. A plurality of suction vanes (22) may form an angle equal to the horizontal direction. The angle may be θ1.

[0107] As a result, air is evenly introduced into the air conditioner (1) from multiple intake ports (3), and interference between the air introduced from one intake port (3) and the air introduced from another intake port (3) can be prevented. Therefore, flow resistance can be reduced and intake flow rate can be increased.

[0108] Multiple intake ports (3) can be arranged at equal intervals in the vertical direction. When intake ports (3) are arranged at equal intervals, air can be evenly introduced from the intake cover (20). Accordingly, the flow resistance can be reduced and the intake flow rate can be increased.

[0109] The bottom of the fan (30) is spaced upward from the lower panel (14) to form a lower air passage (6). The lower air passage (6) is connected to the intake port (3) and the rear intake port (331). Accordingly, air introduced into the case (10) through the intake port (3) can be introduced into the fan (30) through the lower air passage (6) and the rear intake port (331).

[0110] As will be described later, as the difference in air flow rate between the front intake port (321) and the rear intake port (331) decreases, the pressure difference applied to the fan (30) decreases, so that noise generated by the fan (30) is reduced and power consumption can be saved.

[0111] Therefore, it may be desirable to allow as much air as possible to flow into the rear intake port (331) without increasing the resistance of the Euro.

[0112] The lowest intake port (301) may be positioned below the fan (30). In this case, air introduced from the lowest intake port (301) may flow into the lower airway (6).

[0113] In addition, the lowest intake port (301) is positioned below the fan (30) so that the lower flow path (6) can be formed more widely, and the flow path resistance is reduced, which can result in effects such as increased flow rate and reduced power consumption.

[0114] The bottom of the fan (30) may be positioned above the top of the bottom intake (301). The distance (h2) at which the top of the bottom intake (301) is separated from the ground may be smaller than the distance (h3) at which the bottom of the fan (30) is separated from the ground.

[0115] In this case, the amount of air flowing into the rear intake port (331) through the lower channel (6) can be maximized. Therefore, various advantages as described above can occur.

[0116] Meanwhile, the front plate (32) may be spaced a predetermined distance rearward from the front panel (11). The rear plate (33) may be spaced a predetermined distance forward from the rear panel (12). As a result, air can be smoothly introduced into the front intake port (321) and the rear intake port (331).

[0117] The distance between the front plate (32) and the front panel (11) may be greater than the distance between the rear plate (33) and the rear panel (12). As a result, more air can be drawn into the front intake port (321), which has low resistance, and the total flow rate of air flowing through the fan (30) may be increased.

[0118] Meanwhile, the lower panel (14) may include a front guide (141). The front guide (141) may be positioned adjacent to the suction vane (22) positioned at the bottom among the plurality of suction vanes (22).

[0119] Generally, when a wall or similar surface that the fluid contacts exists along the flow path, the fluid flows along that wall or similar surface due to the Coanda effect.

[0120] Accordingly, air introduced through the lowest intake port (301) can be guided to the lower flow path (6) along the intake vane (22) positioned at the bottom and the adjacent front guide (141).

[0121] The lower panel (14) may include a front bend (142) extending downward from the rear end of the front guide (141). The front bend (142) may be positioned parallel to the front plate (32). The front bend (142) may be positioned further forward than the front plate (32). As a result, the lower flow path (6) may be formed more widely, thereby reducing flow resistance.

[0122] Additionally, the front bend (142) is extended downward, so that air flowing along the front guide (141) does not flow to the bottom wall (143) but is separated at the boundary between the front guide (141) and the front bend (142) and flows along the bottom of the fan (30). Accordingly, the path of air flowing to the rear intake port (331) is shortened, which has the effect of increasing the flow rate.

[0123] The lower panel (14) may include a bottom wall (143). The bottom wall (143) may be positioned parallel to the ground. The bottom wall (143) may be spaced downward from the bottom of the fan (30). Thus, the intake passage may be formed wide.

[0124] The lower panel (14) may include a rear bend (144). The rear bend (144) may extend upward from the bottom wall (143). The rear bend (144) may be positioned parallel to the rear plate (33).

[0125] Accordingly, the rear bend (144) can change the direction so that air flowing along the bottom of the fan (30) or air flowing through the lower passage (6) flows toward the upper side where the rear intake port (331) is located.

[0126] The rear bend portion (144) may be positioned below the curved portion (332). The curved portion (332) may be formed at the part where the side plate (34, see FIG. 9) and the rear plate (33, see FIG. 9) of the fan housing (31) are connected. This will be explained in detail in FIG. 9, but the resistance to the flow path to the rear intake port (331) may be reduced by the curved portion (332).

[0127] When the rear bend portion (144) is positioned below the curved portion (332), air guided upward along the rear bend portion (144) can be easily drawn into the rear intake port (331) along the curved portion (332). Accordingly, flow resistance is reduced, and the air flow rate through the fan (30) can be increased when consuming the same amount of power.

[0128] The rear bend portion (144) can be positioned further forward than the rear plate (33). As a result, when air guided upward along the rear bend portion (144) flows into the rear intake port (331), the path of the air can be shortened and the air flow rate through the fan (30) can be increased.

[0129] The lower panel (14) may include a rear connection part (145). The rear connection part (145) may be a portion connected to the rear panel (12). The rear connection part (145) may be located below the bottom of the fan (30). Thus, the lower flow path (6) may be formed widely.

[0130] Meanwhile, air introduced from the intake port (3) can be introduced into the rear intake port (331) through the upper air passage (5). The upper air passage (5) may be formed such that a part of the side plate (34, see FIG. 3) is spaced apart from the first side panel (16) or the second side panel (17).

[0131] The direction of flow must be changed so that air flows into the rear intake port (331), and the intake vane (22) can be positioned so that it is inclined upward toward the rear, so the flow resistance of the lower flow path (6) can be smaller than the flow resistance of the upper flow path (5).

[0132] Therefore, it may be desirable for more air to flow through the lower channel (6) than through the upper channel (5).

[0134] Referring to FIGS. 6 to 8, the performance of cases where air introduced into the lowest intake port (301) flows into the lower flow path (6) and cases where it does not flow into the lower flow path (6) will be explained.

[0135] Referring to FIG. 6, the air flow inside the air conditioner (1) according to the first comparative example and one embodiment of the present disclosure can be observed.

[0136] FIG. 6(a) shows the air flow of a first comparative example in which air introduced through the lowest intake port (301a) does not flow into the lower passage (6). FIG. 6(b) shows the air flow inside an air conditioner (1) according to one embodiment of the present disclosure in which air introduced through the lowest intake port (301) flows into the lower passage (6).

[0137] In the first comparison of FIG. 6(a), it can be seen that the distance (h2a) from the ground to the top of the lowest intake port (301a) is greater than the distance (h3a) from the ground to the bottom of the fan (30).

[0138] As a result, it can be seen that the air entering through the lowest intake port (301a) does not flow into the lower airway (6) and enters the inside of the fan (30) through the front intake port (321).

[0139] In one embodiment of FIG. 6(b), it can be seen that the distance (h2) from the ground to the top of the lowest intake port (301) is smaller than the distance (h3) from the ground to the bottom of the fan (30).

[0140] As a result, it can be confirmed that the air introduced into the lowest intake port (301) flows through the lower channel (6) and enters the rear intake port (331).

[0142] Referring to FIG. 7, the air pressure distribution at the rear intake port (331) of the air conditioner (1) according to the first comparative example and one embodiment of the present disclosure can be observed. The darker the color, the greater the negative pressure.

[0143] Meanwhile, for convenience, this drawing is based on the view of the fan (30) from the front.

[0144] In one embodiment according to the present disclosure of FIG. 7(b), unlike the first comparative example of FIG. 7(a), it can be seen that the pressure is evenly distributed at the rear intake port (331).

[0145] This may be a difference depending on whether the air introduced from the lowest intake port (301) as described above flows into the lower flow path (6) at the bottom of the fan (30).

[0146] In addition, if the pressure is evenly distributed at the rear intake port (331), the pressure difference applied to the fan (30) is reduced, the load applied to the fan (30) is reduced, and noise can be reduced.

[0148] Referring to FIG. 8, figures related to the performance of the air conditioner (1) according to the first comparative example and one embodiment of the present disclosure can be seen.

[0149] Referring to FIG. 8(a), when the first comparative example and the present disclosure form the same airflow of 37 CMM (Cubic Meter per Minute), the rotational speed of the impeller (35), power consumption, and generated noise can be checked.

[0150] It can be confirmed that the first comparative example generates a rotational speed of 456 RPM, a power consumption of 125.4 W, and a noise of 49.4 dB when forming an airflow of 37 CMM, whereas the embodiment of the present disclosure generates a rotational speed of 449 RPM, a power consumption of 121.2 W, and a noise of 49.1 dB.

[0151] That is, as the air introduced into the lowest intake port (301) flows into the lower passage (6), the rotational speed, power consumption, and noise of the impeller (35) required to form the same airflow volume can be numerically confirmed.

[0152] Referring to FIG. 8(b), when the same power is supplied to the air conditioner (1) according to the first comparative example and the embodiment of the present disclosure, the air volume formed by the fan (30) and the ratio of the air volume flowing into the front intake port (321) and the air volume flowing into the rear intake port (331) relative to the total air volume can be confirmed.

[0153] When the same power is supplied to the air conditioner (1) according to the first comparative example and the embodiment of the present disclosure, it can be seen that a larger air volume is formed in the embodiment of the present disclosure. This may be the result of air flowing into the lowest intake port (301) into the lower air passage (6).

[0154] In the first comparative example, when the fan (30) forms an airflow of 37.9 CMM, 85.5% of the air is drawn in from the front intake port (321) and 14.5% of the air is drawn in from the rear intake port (331), whereas in the case of the embodiment of the present disclosure, when the fan (30) forms an airflow of 38.2 CMM, 79.3% of the air is drawn in from the front intake port (321) and 20.7% of the air is drawn in from the rear intake port (331).

[0155] As such, as the difference in air flow rate entering through the front intake port (321) and the rear intake port (331) decreases, the pressure difference applied to the fan (30) decreases, and the torque applied to the impeller (35) decreases, thereby improving power consumption and reducing noise generated by the fan (30), which can be confirmed numerically.

[0157] Referring to FIG. 9, the structure of a fan housing (31) according to one embodiment of the present disclosure can be seen. This drawing shows the fan housing (31) viewed from the rear.

[0158] As described above, the fan housing (31) may be composed of a front plate (32), a rear plate (33), and a side plate (34). As a result, the fan housing (31) can form an internal space and discharge air introduced through the front intake port (321) and the rear intake port (331) to the upper fan discharge port (39).

[0159] The fan outlet (39) may have a rectangular cross-section. This may have the same shape as the cross-section of the case (10). The fan outlet (39) may be surrounded by a front panel (11), a rear panel (12), a first side panel (16), and a second side panel (17).

[0160] As a result, air can be widely diffused into the internal space of the case (10) above the fan (30) through the fan outlet (39) and smoothly discharged to the outside of the air conditioner (1) through the outlet (4). In addition, it is possible to prevent the air discharged through the fan outlet (39) from being re-sucked into the front intake port (321) or the rear intake port (331).

[0161] At least one of the rear plate (33) and the side plate (34) includes a curved portion (332) at the portion where they are connected to each other. The curved portion (332) may be formed along the connection portion between the rear plate (33) and the side plate (34). The curved portion (332) can reduce the resistance of air flowing into the rear intake port (331).

[0162] As mentioned above, when a wall surface in contact with the fluid exists along the fluid flow path, the fluid flows along the wall surface due to the Coanda effect. Furthermore, the more curved the surface, the more easily the fluid flows along the wall without separation.

[0163] Therefore, the fluid flowing along the side plate (34) can flow along the curved portion (332) to the rear plate (33) without being separated from the side plate (34) and enter the rear intake port (331).

[0164] As a result, the path of air flowing into the rear intake port (331) is shortened, and the flow resistance is reduced, so the flow rate formed by the fan (30) is increased and power consumption can be reduced.

[0165] Meanwhile, the curvature of the curved portion (332) can be varied. For example, the curvature can be varied to minimize flow resistance depending on the flow rate formed by the fan (30), the size of the front intake port (321) and the rear intake port (331), the length of the side plate (34) in the front-rear direction, etc.

[0166] The side plate (34) may include a cutoff portion (341). The cutoff portion (341) may be a boundary surface where air is discharged and re-inhaled. The cutoff portion (341) may be a point where the air flowing inside the fan (30) branches off.

[0167] For example, when the impeller (35) placed inside the fan housing (31) rotates, air can flow inside the fan housing (31) in response to the rotation of the impeller (35). The air flowing inside the fan housing (31) can be branched out at the cutoff section (341) and discharged to the fan discharge port (39), or can continue to flow along the side plate (34).

[0168] Depending on the shape and position of the cutoff section (341), the flow rate and flow resistance of the air discharged to the fan outlet (39) may vary. This is explained in detail in FIGS. 16 to 20.

[0169] Meanwhile, the fan (30) may include a reinforcing rib (344). The reinforcing rib (344) may be positioned on one side of the cut-off portion (341) and may extend vertically from the side plate (34). Multiple reinforcing ribs (344) may be positioned.

[0170] The reinforcing rib (344) can improve the rigidity of the fan (30). For example, if a heat exchanger (2) is placed above the fan (30), a large stress may be applied to the cut-off portion (341). In this case, the reinforcing rib (344) can be extended vertically to distribute the stress and improve rigidity.

[0171] The reinforcing rib (344) can be formed in a direction intersecting the front plate (32) and the rear plate (33). The reinforcing rib (344) can be spaced apart from the cut-off portion (341) in the left and right directions.

[0172] As a result, a space may be formed between a part of the side plate (34) and the reinforcing rib (344). Meanwhile, if multiple reinforcing ribs (344) are formed, a space may also be formed between the reinforcing ribs (344). In this case, the rigidity of the fan (30) can be improved without increasing the flow resistance of the upper flow path (5, see FIG. 5) mentioned above.

[0174] Referring to FIGS. 10 and FIGS. 11, the performance of the rear portion of the fan (30) including a curved portion (332) and the case where it does not include a curved portion (332) is described.

[0175] Referring to FIG. 10, the rear portion of the fan (30) according to the second comparative example and one embodiment of the present disclosure can be seen.

[0176] FIG. 10(a) shows the rear portion of a fan (30b) according to a second comparative example that does not include a curved portion (332). FIG. 10(b) shows the rear portion of a fan (30) according to an embodiment of the present disclosure that includes a curved portion (332).

[0177] In the second comparative example of FIG. 10(a), it can be seen that the side plate (34b) and the rear plate (33b) are connected at an angle. In this case, the air flowing along the side plate (34b) may be separated at the connection with the rear plate (33b) and may not be able to flow along the rear plate (33b).

[0178] Therefore, as air flows into the rear intake port (331), the flow resistance increases and the air path lengthens, which can reduce the flow rate.

[0179] In one embodiment of FIG. 10(b), it can be seen that at least one of the side plate (34) and the rear plate (33) includes a curved portion (332). In this case, air flowing along the side plate (34) is not separated at the curved portion (332) connected to the rear plate (33) and can be introduced into the rear intake port (331) along the rear plate (33).

[0180] Therefore, as air flows into the rear intake port (331), the resistance to the flow path is reduced, and the air path is shortened, so the flow rate can be increased.

[0182] Referring to FIG. 11, the second comparative example and the performance of the air conditioner (1) of the present disclosure can be seen with respect to the presence or absence of the curved portion (332).

[0183] It can be confirmed that when the second comparative example and the present disclosure form the same airflow of 37 CMM, the second comparative example generates a rotational speed of 426 RPM, a power consumption of 109.1 W, and a noise of 48.3 dB, whereas the embodiment of the present disclosure generates a rotational speed of 425 RPM, a power consumption of 106.4 W, and a noise of 48.1 dB.

[0184] That is, as the rear portion of the fan (30) includes a curved portion (332), it can be numerically confirmed that the rotational speed, power consumption, and noise of the impeller (35) required to form the same airflow are reduced.

[0185] In addition, this may mean that when the same power is supplied to the air conditioner (1) according to the second comparative example and the embodiment of the present disclosure, the air conditioner (1) of the present disclosure forms a larger air volume and exhibits superior performance.

[0187] Referring to FIGS. 12 to 15, the performance of the air conditioner (1) according to the opening ratio of the orifice (36) will be explained.

[0188] Referring to FIG. 12, an orifice (36) according to one embodiment of the present disclosure can be seen. This drawing shows a fan (30) viewed from the front, with an impeller (35) placed inside the fan housing (31) and an orifice (36) placed in the front intake port (321).

[0189] The impeller (35) may include blades (351). The blades (351) may be arranged along the inner circumference of the impeller (35) in a direction intersecting the front plate (32) or the rear plate (33). Multiple blades (351) may be arranged. The blades (351) may be arranged at an angle with respect to the rotational direction of the impeller (35).

[0190] As a result, when the impeller (35) rotates, the air is moved by the blade (351) and can flow in the same direction as the rotation direction of the impeller (35).

[0191] The impeller (35) may include a motor hole (352). The motor hole (352) may be a part where the rotation axis of the motor (38, see FIG. 5) is connected. The motor (38) is connected to the impeller (35) through the motor hole (352), and the impeller (35) can rotate in response to the rotation of the motor (38) to form an air flow.

[0192] The opening ratio of the orifice (36) may refer to the ratio in which the blade (351) of the impeller (35) is obscured by the orifice (36) when the fan (30) is viewed from the front. This may vary depending on the length in which the inner end of the orifice (36) extends toward the center of the front intake (321).

[0193] When the orifice (36) covers a portion of the blade (351) in the front and rear directions, the flow resistance to the front intake port (321) is reduced, and at the same time, the amount of air whose flow direction is abruptly changed by the blade (351) is reduced, thereby reducing the stress applied to the blade (351). Thus, the performance of the air conditioner can be improved.

[0194] Meanwhile, in the case of the present drawing, the blade (351) is covered by 50% by the orifice (36), so the opening rate of the orifice (36) can be said to be 50%.

[0196] Referring to Fig. 13, an orifice (36b) with an opening rate of 0% can be seen.

[0197] Since the opening rate of the orifice (36b) is 0%, the blade (351) can be completely covered by the orifice (36b) when viewing the fan (30) from the front.

[0198] In this case, the air introduced through the front intake port (321) may not flow directly into the space between the blades (351). The air introduced through the front intake port (321) flows into the fan (30) along the orifice (36), and then, due to centrifugal force, is pushed outward by the impeller (35) and comes into contact with the blades (351), thereby changing the direction of flow.

[0200] Referring to FIG. 14, an orifice (36c) with an opening ratio of 77% can be seen. In this drawing, the obscured blade (351) is not indicated by a dotted line for comparison with FIG. 12 and FIG. 13, but part of the blade (351) is obscured by the orifice (36).

[0201] In this case, the air introduced into the front intake port (321) can flow directly into the space between the blades (351). Therefore, the direction of flow can be changed by coming into contact with the blades (351) as the impeller (35) rotates.

[0203] Referring to FIG. 15, when forming the same airflow, the values ​​related to the performance of the air conditioner (1) according to the opening ratio of the orifice (36) can be checked.

[0204] It can be confirmed that when the opening rate of the orifice (36) is 0%, the air conditioner (1) generates a rotational speed of 462 RPM, a power consumption of 127.4 W, and a noise of 50.3 dB.

[0205] It can be confirmed that when the opening ratio is 50%, it generates a rotational speed of 460 RPM, power consumption of 125.7 W, and noise of 50.3 dB, and when the opening ratio is 77%, it generates a rotational speed of 466 RPM, power consumption of 128.6 W, and noise of 50.4 dB.

[0206] This means that when the same amount of power is supplied, the largest amount of air is formed when the opening rate of the orifice (36) is 50%.

[0207] In this way, the performance of the air conditioner (1) can be improved within a specific range, rather than when the opening ratio of the orifice (36) is excessively small or large.

[0208] This may be because if the opening ratio is too small, the size of the front intake port (321) decreases, reducing the flow rate, and conversely, if the opening ratio is too large, the stress applied to the blade (351) increases.

[0209] Therefore, when the opening rate of the orifice (36) is 40% to 60%, unlike other opening rates, the effect of reducing power consumption and noise can be maximized.

[0211] Referring to FIGS. 16 to 20, the performance of the air conditioner (1) according to the shape and arrangement of the cutoff section (341) is explained.

[0212] Referring to FIG. 16, the fan housing (31) can be seen from the front. This is to explain the starting angle of the cut-off section (341), and may differ from the fan housing (31) of the air conditioner (1) according to the embodiment of the present disclosure.

[0213] The X-axis represents the horizontal axis, the Y-axis represents the vertical axis, and the Z-axis represents the axis parallel to the rotation axis of the impeller (35). The Z-axis is defined as counterclockwise as the positive direction. The sign θ represents the reference angle, represents the cutoff start angle at which the cutoff position begins.

[0214] The reference angle (θ) refers to the angle rotated counterclockwise (Z-axis direction) with respect to the X-axis.

[0215] Cutoff start angle ( ) may be the angle between the X-axis and a virtual straight line connecting the rotation center (C) of the impeller (35) and the cutoff part (341).

[0216] Cutoff start angle ( Depending on the shape and position of the cutoff section (341), the flow rate and flow resistance of the air discharged from the fan (30) may vary.

[0218] Referring to FIG. 17, a view of the fan (30) according to an embodiment of the present disclosure can be seen from above.

[0219] The cutoff portion (341) may include a front portion (342) and a rear portion (343). The front portion (342) may refer to the area where the cutoff portion (341) contacts the front plate (32). The rear portion (343) may refer to the area where the cutoff portion (341) contacts the rear plate (33).

[0220] Cutoff start angle ( ) may be the smaller of the reference angle of the front part (342) and the reference angle of the rear part (343).

[0221] In the case of an embodiment of the present disclosure, the reference angle of the front part (342) and the reference angle of the rear part (343) may be the same, and the cutoff start angle ( ) can be 90°.

[0222] When the reference angle of the front part (342) and the reference angle of the rear part (343) are the same, the cutoff part (341) can be positioned parallel to the rotation axis or Z-axis of the impeller (35).

[0223] As a result, when the impeller (35) rotates, the air inside the fan (30) can be simultaneously branched from the front (342) and rear (343) of the cutoff section (341) and discharged to the fan outlet (39).

[0225] Referring to FIG. 18, a view of the fan (30c) according to the third comparative example can be seen from the top.

[0226] In the case of the third comparative example, the reference angles of the front part (342c) and the rear part (343c) of the cutoff part (341c) may be different. For example, the reference angle of the front part (342c) may be 105° and the reference angle of the rear part (343c) may be 90°. At this time, the cutoff start angle ( ) can be 90°, which is the smaller value between 105° and 90°.

[0227] The air inside the fan (30c) is cut off at the starting angle ( It can first branch off at the angle corresponding to ).

[0228] In the case of the third comparative example, the reference angle of the rear portion (343c) is the cutoff start angle ( Since it is, air can first be branched from the rear section (343c) and discharged through the fan outlet (39), and then air can be branched from the front section (342c) and discharged.

[0229] Meanwhile, the air inside the fan (30c) can flow more to the side with lower resistance between the front and rear sections.

[0231] Referring to FIG. 19, the upper view of the fan (30d) according to the fourth comparative example can be seen.

[0232] In the case of the fourth comparative example, the reference angles of the front part (342d) and the rear part (343d) of the cutoff part (341d) may be different. For example, the reference angle of the front part (342d) may be 90°, and the reference angle of the rear part (343d) may be 105°. At this time, the cutoff start angle ( ) can be 90°, which is the smaller value between 105° and 90°.

[0233] In addition, the cutoff portion (341d) of the fourth comparative example can be formed three-dimensionally, unlike the shape that connects the front portion (342d) and the rear portion (343d) by the shortest distance.

[0234] In the case of the fourth comparative example, the reference angle of the front part (342d) is the cutoff start angle ( Since it is, air can first be branched from the front section (342d) and discharged through the fan outlet (39), and then air can be branched and discharged from the rear section (343d).

[0235] In the case of the fourth comparative example, the cutoff portion (341d) is formed three-dimensionally, so the flow resistance at the fan discharge port (39) may differ from that of the present disclosure or the third comparative example.

[0237] Referring to FIG. 20, the performance of the air conditioner (1) according to the shape of the cutoff section (341) can be checked.

[0238] As disclosed in the present disclosure, when the reference angle is the same in the front part (342) and the rear part (343) so that the cut-off part (341) is arranged parallel to the rotation axis of the impeller (35), when forming an air volume of 37 CMM, it can generate a rotational speed of 468 RPM, a power consumption of 135.5 W, and a noise of 49.9 dB.

[0239] It can be confirmed that when forming the same airflow of 37 CMM, the third comparative example generates a rotational speed of 476 RPM, power consumption of 139 W, and noise of 50.0 dB, and the fourth comparative example generates a rotational speed of 473 RPM, power consumption of 138.1 W, and noise of 50.5 dB.

[0240] That is, it can be confirmed that the shape of the cutoff portion (341) according to the embodiment of the present disclosure has the lowest flow resistance, resulting in low power consumption and low noise generation.

[0241] In addition, this may mean that the largest amount of airflow is formed in the air conditioner (1) according to the embodiment of the present disclosure when the same power is supplied.

[0242] Thus, the performance of the air conditioner (1) can be improved when the cutoff section (341) is positioned parallel to the rotation axis of the impeller (35). When the starting angle of the cutoff section (341) is 80° to 100°, the cutoff section (341) can have a structure that minimizes flow resistance while smoothly controlling the flow of air.

[0243] Meanwhile, the reason why the air conditioner (1) according to one embodiment of the present disclosure has different values ​​in FIGS. 8, 11, 15, and 20, even though it forms the same airflow of 37 CMM, may be because the experiment was conducted in a state having the same structure as the comparative example, except for the characteristic parts, for accurate comparison with the comparative example.

[0244] Although preferred embodiments of the present disclosure have been illustrated and described above, the present disclosure is not limited to the specific embodiments described above. Various modifications are possible by those skilled in the art without departing from the essence of the present disclosure as claimed in the claims, and such modifications should not be understood individually from the technical spirit or perspective of the present disclosure. Explanation of the symbols

[0246] 3: Intake port 301: Bottommost intake 6 : Lower Euro 10 : Case 11 : Front panel 12 : Rear panel 14 : Bottom panel 30 : Fan 32 : Front panel 321 : Anterior intake port 33 : Back panel 331 : Rear intake 34 : Side panel 341 : Cut-off section 36 : Orifice

Claims

Claim 1 An air conditioner comprising: a case having an intake port and an exhaust port formed on a front panel; and a fan disposed inside the case and flowing air from the intake port to the exhaust port, wherein the case comprises: a lower panel forming a bottom surface, and the fan comprises: a front plate having a front intake port formed in communication with the intake port; a rear plate spaced rearward from the front plate having a rear intake port formed therein; and a side plate connecting the front plate and the rear plate, wherein at least one of the rear plate and the side plate has a curved portion at the portion connecting them, and the lower end of the fan is spaced upward from the lower panel to form a lower air passage communicating with the intake port and the rear intake port. Claim 2 In claim 1, the front panel has a plurality of intake ports formed vertically, and the lowest intake port among the plurality of intake ports is positioned below the fan. Claim 3 In Clause 2, the lower part of the fan is positioned above the upper part of the lowest intake port of the air conditioner. Claim 4 An air conditioner according to claim 1, wherein the front panel comprises a suction cover having a plurality of suction ports formed vertically, the suction cover comprises a plurality of suction vanes that guide air flowing into the plurality of suction ports, and the lower panel further comprises a front guide that is positioned adjacent to the suction vane positioned at the bottom among the plurality of suction vanes and guides air into the lower air passage. Claim 5 In claim 4, the lower panel further includes a front bend portion that extends downward from the rear end of the front guide and is arranged parallel to the front plate, and the front bend portion is an air conditioner arranged in front of the front plate. Claim 6 In claim 4, the lower panel further includes a rear bend portion extending upward from a floor wall spaced apart from the fan and arranged parallel to the rear plate, and the rear bend portion is positioned below the curved portion of the air conditioner. Claim 7 In claim 6, the rear bend portion is an air conditioner positioned in front of the rear plate. Claim 8 In claim 1, the front panel includes a suction cover having a plurality of suction ports formed vertically, and the suction cover includes a plurality of suction vanes that guide air flowing into the plurality of suction ports, and the plurality of suction vanes are arranged at the same angle. Claim 9 In claim 1, the case comprises a rear panel spaced rearward from the front panel, the front panel is spaced rearward by a predetermined distance from the front panel, and the rear panel is spaced forward by a predetermined distance from the rear panel, forming an air conditioner. Claim 10 In claim 9, an air conditioner in which the distance between the front plate and the front panel is greater than the distance between the rear plate and the rear panel. Claim 11 In claim 1, the fan further comprises an orifice disposed in the front intake port and having an inner diameter that decreases toward the rear. Claim 12 In claim 11, the fan further comprises an impeller disposed between the front plate and the rear plate and including a plurality of blades, and the orifice is an air conditioner in which an inner end extends toward the center of the front intake port to cover a portion of the plurality of blades in the front-rear direction. Claim 13 In claim 12, the inner circumferential end of the orifice extends to cover 40% to 60% of the blade in the front-rear direction. Claim 14 In claim 1, the fan comprises an impeller disposed between the front plate and the rear plate and which flows air according to rotation, and the side plate comprises a cutoff portion into which the air flowing inside the fan is branched, and the cutoff portion is disposed parallel to the rotation axis of the impeller. Claim 15 An air conditioner according to claim 14, wherein the angle between a virtual line extending horizontally from the center of rotation of the impeller and a virtual straight line connecting the center of rotation of the impeller and the cut-off portion is called the starting angle, and the starting angle is 80° to 100°. Claim 16 An air conditioner according to claim 1, wherein the side plate includes a cutoff portion into which air flowing inside the fan is branched, and the fan is disposed on one side of the cutoff portion and further includes a reinforcing rib extending vertically from the side plate.

Images