ES2623875T3 - Recessed ceiling air conditioner - Google Patents

Abstract

An air conditioning apparatus, of the type embedded in the ceiling, comprising: (a) a body (1) of the air conditioning apparatus, of the type embedded in the ceiling, which includes an upper panel (1b) of the chassis; (b) a motor (4) disposed in the body (1) of the air conditioning apparatus, of the type embedded in the ceiling, in such a way that a rotating shaft (4a) is orthogonal to the upper panel (1b) of the chassis, and (c) a turbo fan (3) that includes a hub (3c) protruding downward, which covers the engine (4) and to which the rotary axis (4a) of the engine is fixed, a main plate (3b) that it extends from the periphery of an upper opening of the hub (3c), opposite the upper panel (1b) and has a plurality of blades (3a) fixed to a surface of the main plate (3b) opposite the other surface opposite the panel upper (1b) of the chassis, and a cover (3g), opposite the main plate (3b) and constituting a guided flow channel of the blades (3a), and expelling air introduced from the side of the cover through of the air passage (3e) of the inside of the fan formed on the opposite side of the motor side of the hub (3c), characterized in that a cross section is provided ctifier (1g) in an area (1f) corresponding to the main plate of the fan, opposite to the main plate (3b) of a lateral thermal insulating material (1e) of the upper panel provided within the upper panel (1b) of the chassis, of so that a hole with the main plate (3b) is a predetermined distance, and the ratio E1 / D1 of a minimum hole E1 between the grinding section (1g) and the main plate (3b) of a hole D1 between the material (1e ) Thermal insulation of the side of the upper panel and the main plate (3b), in the height direction, is 0.3 to 0.7.

Description

DESCRIPTION

Recessed ceiling air conditioner Technical field

The present invention relates to an air conditioner, of the type embedded in the ceiling, and, more specifically, it refers to an apparatus structure for an improved engine cooling capacity and noise reduction.

Background of the technique

An air conditioner, of the type recessed in the ceiling, known, includes a turbo fan which has a body of the air conditioner, of the type recessed in the ceiling, which has an upper chassis panel, an engine arranged in the inside the body of the air conditioner, of the type embedded in the ceiling, in a way in which the rotary axis is arranged at right angles to the upper panel of the chassis, a bucket that protrudes downwards, which covers the engine and that fixes the rotary axis of the motor, a main plate that extends from the periphery of an open surface at the top of the hub opposite the upper panel and that has a plurality of blades fixed to a surface of the main plate opposite to the other surface opposite the upper panel 15, and a cover opposite the main plate and forming a guide channel for the blades, an air passage on the side of the motor defined by the hub, the main plate and the covered and provided on the motor side of the hub, an air passage from the inside of the fan, provided opposite the air passage from the motor side, and a turbo fan to expel the air introduced from the side of the cover through the passage of air inside the fan (Related technique 1). In this air conditioner, of the type embedded in the ceiling, part of the air expelled from the turbo fan is guided, through a gap between the upper panel of the chassis and the main plate, into the air passage from the side of the engine on the inner side of the hub, to cool the engine. Next, the air used to cool the engine is emitted from the openings provided in the hub, in the vicinity of the surface of the side of the engine, into the air passage from the inside of the fan on the outer side of the hub.

Like another structure of an air conditioner, of the type embedded in the ceiling, in addition to the structure 25 described above, the openings in the hub are positioned on the bottom side of the hub (in the vicinity of a fixed portion of the rotary axis of the motor and the hub) instead of being positioned in the vicinity of the side surface of the engine and an auxiliary fan, which has a plurality of blades, is provided on the outer side of the hub, in a manner in which the lower side openings are covered (Related technique 2) (referred to patent document l). According to this air conditioner, of the type embedded in the ceiling, by providing the auxiliary fan, the engine cooling rate is improved by increasing the volume of air flowing around the engine and the engine operating noise, which escapes from The lower side openings are reduced by covering the lower side openings with the auxiliary fan.

Like another structure of an air conditioning apparatus, of the type embedded in the ceiling, in addition to the related Technique 2 described above, the openings provided in the hub are lateral surface openings provided 35 in the vicinity of the lateral surface of the hub, in instead of the lower lateral openings, and an auxiliary hub protruding downwards, substantially in line with the hub, and which is provided on the outer side of the hub, so that it covers the openings of the lateral surface, is provided instead of the auxiliary fan (Related technique 3) (referred to patent document 2).

[Patent document 1] Japanese Patent No. 3270567

40 [Patent document 2] Japanese Patent No. 3275474

Document US2004 / 0244403 A1 describes an air conditioner, of the type embedded in the ceiling, on which the pre-characterizing part of claim 1 is based.

Description of the invention

Problems to be solved by the invention

According to Related Technique 1 described above, the air used to cool the engine flows outward from the side surface openings of the hub, into the air passage inside the fan. At this time, the air is emitted from the openings of the lateral surface to the passage of air from inside the fan, as a jet flow. Therefore, there is a problem in which the blades pass through a turbulence of the jet flow and suffer a pressure fluctuation, making the noise worse. The jet flow emitted from the openings of the lateral surface interferes with the inlet flow of the turbo fan. As a result, there are problems in the sense that the actual flow rate of the air expelled from the turbo fan is reduced, worsening the efficiency of the air supply and the noise value corresponding to the volume of air. Because the openings are provided on the lateral surface of the hub, the air does not flow sufficiently to the surface of the lower edge of the engine. In this way, there is a possibility that the engine does not cool sufficiently and is damaged by the heat generated.

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According to the related technique 2 and the related technique 3, the openings provided in the hub are covered with the auxiliary fan or the auxiliary hub. However, the auxiliary fan or auxiliary hub does not cover the entire hub, but only covers part of the hub. Therefore, similar to the related technique 1 described above, there is a possibility that the flow from the openings interferes with the inlet flow of the turbo fan, to worsen the noise.

In addition, there is a problem in which the reliability can be reduced, since, when transported, by truck or other similar means, the body of the air conditioner, the vibration generated during transport causes the turbo fan to pivot so that The outer circumferential edge of the turbo fan collides with the upper panel of the chassis of the body of the air conditioner, by point contact and the turbo fan is broken, in the worst case, due to the impact of the stress concentration.

The present invention is carried out to solve the problems identified above. A first object of the present invention is to provide an air conditioner, of the type embedded in the ceiling, of low noise, highly reliable, capable of preventing damage to the engine, improving the efficiency of engine cooling.

A second object of the present invention is to provide an air conditioner, of the type embedded in the ceiling, which is capable of preventing the fan from being damaged during transport and having high product reliability.

Means to solve the problems

According to the present invention there is provided an air conditioner, of the type embedded in the ceiling, according to the appended claims.

Advantages

According to the present invention, because an air guiding cover is provided on the inner side of a cube and this air guiding cover is formed such that the height position of the openings of the lower edge of a surface portion Circumferential is lower than that of the surface of the lower edge of the engine, the air flowing into the air passage from the side of the engine can reliably guide the air to the surface of the bottom edge of the engine. As a result, the cooling efficiency of the engine is improved and damage to the engine due to the heat generated can be prevented, allowing to obtain an air conditioner, of the type embedded in the ceiling, highly reliable.

Also, because the openings for emitting air into the air passage inside the fan are provided in the circumferential surface portion of the hub, in the vicinity of a main plate, it can be prevented that the air flowing out from the openings inside the air passage inside the fan interfere with a flow of air from the fan inlet. Therefore, a shear distortion of the fan inlet flow is suppressed, and the noise caused by the passage of the blades through the turbulent air can be reduced. In addition, an increase in noise that accompanies deterioration in air supply efficiency can be prevented, caused by interference with the air flowing out from the openings and the fan inlet flow.

In addition, because the entire hub is substantially a double structure and the openings are provided in the circumferential surface portion of the hub, in the vicinity of a main plate, as described above, the distance from the air passage of the The motor's side of the hub to the air passage inside the fan is extended, and the noise is muffled. As a result, outside leakage of engine operating noise, such as abnormal electromagnetic noise and bearing rotation noise generated in the engine, can be prevented. In addition, an air conditioning device, of the type recessed in the ceiling, of low noise, which provides a comfortable environment for residents can be obtained.

In addition, similar to noise damping, because the flow rate of the air flowing out from the openings into the air passage inside the fan is also damped, a reduction in reliability can be prevented the flow rate of the flow dissipated from the fan, and an increase in noise that accompanies the deterioration in the efficiency of the air supply can be prevented. Furthermore, due to the effect of preventing the reduction in the volume of flow of the air flow dissipated from the fan, a sufficient volume of air can be obtained to cool the engine, and the engine can be effectively cooled.

In the present invention, there are reinforcing ribs provided in an upper panel of the chassis and radially arranged air guide passages to guide part of the flow of air dissipated from the turbo fan to the engine by means of a thermal insulating material lateral to the upper panel and the reinforcement ribs provided on the inner side of the upper chassis panel are formed. Next, first, the resistance of the upper panel of the chassis can be increased by the reinforcing ribs, to allow a reduction in the thickness and weight of the upper panel 1b of the chassis and the air flow from the air-guided steps, arranged radially, the engine can be increased to improve cooling efficiency. As a result, damage to the engine can be prevented.

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Brief description of the drawings

[Fig. 1] Fig. 1 illustrates an external perspective view of the air conditioner, of the type embedded in the ceiling, according to a first embodiment of the present invention.

[Fig. 2] Fig. 2 illustrates a longitudinal cross-sectional view of the interior of the air conditioner shown in Fig. 1.

[Fig. 3] Fig. 3 illustrates a horizontal cross-sectional view, taken along line XX in Fig. 2, viewed from the side of the upper panel and illustrates the inside of an air conditioner shown in Fig. one.

[Fig. 4] Fig. 4 illustrates an enlarged cross-sectional view of a turbo fan 3 and the neighborhood shown in Fig. 2.

[Fig. 5] Fig. 5 illustrates a perspective view of the turbo fan 3 (part 1).

[Fig. 6] Fig. 6 illustrates a perspective view of the turbo fan 3 (part 2).

[Fig. 7] Fig. 7 illustrates a perspective view of an air guiding cover 18.

[Fig. 8] Fig. 8 illustrates the relationship between a gap mmmm k between a guiding cover 18 of

air and a 4 engine and engine cooling efficiency.

[Fig. 9] Fig. 9 illustrates the relationship between G4 / G1 (ratio G4 of the total opening area in the area G1 of circular opening) and the engine cooling efficiency.

[Fig. 10] Fig. 10 illustrates the relationship between G4 / G5 (proportion of the total opening area G4 in the outlet area G5 of the turbo fan) and the noise value.

[Fig. 11] Fig. 11 illustrates the frequency characteristics of the air conditioner according to the present invention, in operation.

[Fig. 12] Fig. 12 illustrates the relationship between the volume of air supply and the noise during operation of the air conditioner according to the present invention.

[Fig. 13] Fig. 13 illustrates an enlarged cross-sectional view of an air guiding cover 18, according to another example, in the vicinity of the turbo fan 3.

[Fig. 14] Fig. 14 illustrates a longitudinal cross-sectional view of the interior of the air conditioner according to the second embodiment of the present invention.

[Fig. 15] Fig. 15 illustrates a horizontal cross-sectional view of the inside of a body 1 of an air conditioner shown in Fig. 14, viewed from the top panel.

[Fig. 16] Fig. 16 illustrates an enlarged view of a turbo fan 3 and its vicinity, shown in Fig. 14.

[Fig. 17] Fig. 17 illustrates a schematic view of a turbo fan 3 that contacts a lateral thermal insulating material 1e of the upper panel, pivoting on a support point in the fixed portion 3h of the hub 3c, and the rotating shaft 4a, operating As during transportation.

[Fig. 18] Fig. 18 illustrates a perspective view from the portion corresponding to the fan side of the thermal insulating material 1c.

[Fig. 19] Fig. 19 illustrates the change in the noise value corresponding to E1 / D1 (proportion of the hole E1 mm between the grinding section 1g and the main plate 3b in the hole D1 between the thermal insulating material 1e of the upper panel and main plate 3b in the direction of height) under the condition that the air supply volumes are equal.

[Fig. 20] Fig. 20. Illustrates a perspective view of another example of the rectifier section 1g having a different shape.

[Fig. 21] Fig. 21 illustrates a longitudinal cross-sectional view of another example of the rectifier section 1g, which has a different shape.

[Fig. 22] Fig. 22 illustrates a longitudinal cross-sectional view of the interior of the air conditioner, of the type embedded in the ceiling, according to the third embodiment of the present invention.

[Fig. 23] Fig. 23 illustrates a perspective view of a grinding plate 19 that includes a lateral surface 1h shaped as an inclined surface of a polygon.

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[Fig. 24] Fig. 24 illustrates a perspective view of a grinding plate 19 that includes a lateral surface 1h shaped as an inclined surface of a truncated cone.

[Fig. 25] Fig. 25 illustrates a longitudinal cross-sectional view of the interior of the air conditioner, of the type embedded in the ceiling, according to the fourth embodiment of the present invention.

[Fig. 26] Fig. 26 illustrates a horizontal cross-sectional view, taken along line z-z in Fig. 25.

[Fig. 27] Fig. 27 illustrates the outside of an upper panel, seen from an arrow S in Fig. 25.

[Fig. 28] Fig. 28 illustrates a partially enlarged view of the turbo fan 3 and its vicinity, illustrated in Fig. 25.

[Fig. 29] Fig. 29 illustrates a perspective view of a cross section taken along line V-V in Fig. 26.

[Fig. 30] Fig. 30 illustrates a side view of a partial cross section of a motor 4.

[Fig. 31] Fig. 31 illustrates a schematic view of an actuator substrate incorporated in the motor 4.

[Fig. 32] Fig. 32 illustrates the results of the measurement experiment of the surface temperature of the engine and the noise value corresponding to the positional relationship between the air guided steps 1k, positioned radially, and a turbo fan 3, shown in the Fig. 25.

[Fig. 33] Fig. 33 illustrates the upper chassis panel 1b of an air conditioner, of the type embedded in the ceiling, according to a fifth embodiment, seen from the side of a lateral thermal insulating material 1eb of the upper panel.

[Fig. 34] Fig. 34 illustrates a plan view of the exterior of the upper panel 1b of the chassis of an air conditioner, of the type embedded in the ceiling, according to a fifth embodiment.

[Fig. 35] Fig. 35 illustrates a perspective view of a cross section taken along line V-V in Fig. 33.

Best way to carry out the invention

First realization

Next, it will be described, with reference to Figs. 1 to 7, an air conditioner, of the type embedded in the ceiling, according to a first embodiment of the present invention.

Fig. 1 illustrates an exterior perspective view of the air conditioner according to the present invention. Fig. 2 illustrates a longitudinal cross-sectional view of the interior of the air conditioner shown in Fig. 1. Fig. 3 illustrates a horizontal cross-sectional view taken along line XX in Fig. 2, seen from the side of the upper panel and illustrates the interior of the body 1 of the air conditioner shown in Fig. 1. Fig. 4 illustrates an enlarged cross-sectional view of a turbo fan 3 and its vicinity, shown in Fig. 2. Fig. 5 illustrates a perspective view of the turbo fan 3 mounted on the body 1 of the air conditioner, of the type embedded in the ceiling, according to the present invention. Fig. 6 illustrates a perspective view of the turbo fan 3 shown in Fig. 5, shown rotated from top to bottom. Fig. 7 illustrates a perspective view of an air guiding cover 18 arranged in the turbo fan 3.

In Fig. 1, the body 1 of the air conditioner is embedded in the ceiling of a room 15, in a manner in which a decorative panel 2, substantially square, provided in the lower portion of the body 1 of the air apparatus conditioning, can be seen. The air conditioner, of the type embedded in the ceiling, includes suction grilles 2a, substantially square, which communicate with an air inlet 11a (reference to Fig. 2) to absorb air into the body 1 of the apparatus of air conditioning, and panel outlets 2b, which communicate with an outlet 16a of the body (reference to Fig. 2), aligned with the sides of the decorative panel 2, both provided in the central area of the decorative panel 2, and also includes blades 2c for air flow direction, provided at the outputs 2b of the panel.

As shown in Figs. 2 and 3, the chassis of the body 1 of the air conditioning apparatus is constituted by the side panels 1a of the chassis, and an upper panel 1b of the chassis, fixed to the area surrounded by the side panels 1a of the chassis. The side panels 1a of the chassis and the top panel 1b of the chassis are composed of rolled metal members. A thermal insulating material 1c is fixed to at least part of the surfaces of the side panels 1a of the chassis and of the upper panel 1b of the chassis, on the inner side of the body 1 of the air conditioner, to form the side walls of the passage of air. Inside the body 1 of the air conditioner, a motor 4 is provided, arranged so that its rotary axis 4a is arranged at right angles to the upper panel 1b of the chassis, a centrifugal air blower, which includes the turbo fan 3

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rotationally driven by the engine 4, and a heat exchanger 6, substantially C-shaped, arranged vertically, so that it surrounds the turbo fan 3.

Under the heat exchanger 6, a drain pan 12, composed of foamed material, and a box 13 of electrical components, housing electronic components, such as a control substrate, are arranged. Two final portions 6a of the heat exchanger 6, substantially C-shaped, are connected with a heat exchanger connection plate 7, such that the heat exchanger 6 and the heat exchanger connection plate 7, as a all, they form a substantially square shape. On the outer side (side panel side 1a of the chassis) of the heat exchanger connection plate 7, as shown in Fig. 3, a gap is provided between the heat exchanger connection plate 7 and a 1d side thermal insulation material of the side panel. A space 10, which houses tubenas, is formed by covering the upper end and the lower end of the recess with the upper panel 1b of the chassis and the drain pan 12, respectively. Inside the space 10, which houses the tubenas, a head 8 is arranged connected to a tube 6b of the heat exchanger, which extends from one of the final portions 6a and a distributor 9.

The centrifugal air blower includes the turbo fan 3 and a flaring 5 which constitutes a passage 23a of air entering the turbo fan 3. The turbo fan 3 includes a hub 3c that protrudes downward, which covers the engine 4 and which fixes the rotary shaft 4a of the motor 4 in place, a substantially ring-shaped main plate 3b, extending from the periphery of the upper opening of the hub 3c to oppose the upper panel 1b of the chassis and including a plurality of blades 3a fixed to the surface opposite the surface that opposes the upper panel 1b of the chassis, a cover 3g that opposes the main plate 3b and constitutes a guide channel for the blades 3a. The upper edge of the hub 3c is formed as a single unit with the main plate 3b, and the lower edge of the hub 3c is fixed to the rotary axis 4a of the motor 4. Aqrn, the hub 3c is constituted as a single unit that integrates a portion 3ca of circumferential surface, with a hollow cone shape, whose diameter decreases from the circumferential surface portion of the main plate 3b to the lower portion of the circumferential surface portion 3ca, a flat surface portion 3cb extending from the opening of the lower edge of the portion 3ca of circumferential surface to the rotary axis 4a, and a cylindrical portion 3cc extends from the inner circumference of the flat surface portion 3cb to the axis 4a of the motor. In the circumferential surface portion 3ca, a plurality of openings 3d are formed along a concentric circle in the vicinity of the main plate 3b. The hub 3c, which has the structure described above, is fixed to the axis 4a of the motor with the cylindrical portion 3cc. The dimensions of the hub 3c are designed such that, in this fixed position, a gap E1, formed between the main plate 3b, formed as a single unit with the hub 3c, and a thermal insulating material 1e of the upper panel side, has a default interval.

On the inner side (side of the engine 4) of the hub 3c of the turbo fan 3, an air guiding cover 18 is provided. An air passage 3f is formed from the side to the engine between the air guide cover 18 and the engine 4. The air guide cover 18 grinds the air, flowing from the gap E1, formed between the upper panel 1b of the chassis and the main plate 3b, inside the air passage f of the side of the engine, to the engine 4. As shown in Fig. 7, the air guiding cover 18 includes a ring-shaped portion 18a, in the form of a ring, and a portion 18c of circumferential surface, in the shape of a hollow cone, whose diameter decreases so that the cross-sectional area of the air passage 3f of the motor side decreases from the portion of the inner circumferential surface of the portion 18a flange to the edge bottom of the opening 18b. The circumferential surface portion 18c is provided at an angle substantially equal to that of the circumferential surface portion 3ca of the cube 3c, and so that the gap E2 between the circumferential surface portion 18c and the circumferential surface portion 3ca has a predetermined range . The air guiding cover 18 is formed so that the height of the opening 18b of the lower edge of the circumferential surface portion 18c is lower than a surface 4b of the lower edge of the motor 4. The air guiding cover 18 is large the air flowing into the air passage 3f from the side of the engine to the entire engine 4. The air guiding cover 18, having the structure described above, is composed of metal members, such as aluminum and steel plates plating, which have a high thermal conductivity. The air guiding cover 18 is fixed, by fusion, to the main plate 3b by the flange portion 18a, in a suspended position, and rotates together with the turbo fan 3, by means of the rotation of the engine 4.

Next, the operation of the air conditioner, of the type embedded in the ceiling, having the structure described above will be described.

During operation of the air conditioner, the engine 4 is driven and the turbo fan 3 rotates in the direction indicated by an arrow A (reference to Figs. 3, 5 and 6). Next, the air in room 15 is introduced from the inlet grilles 2a, as indicated by an arrow B. After removing the dust in a filter 14, the air is introduced to the turbo fan 3 through the flaring 5 Subsequently, the air C1 dissipated from an outlet 3i of the turbo fan 3 is heated or cooled, as it passes through the heat exchanger 6. Next, the air conditioning is carried out by expelling the air C1 from the outlet 2b of the panel into the room 15, while controlling the direction of air flow, with the blade 2c for addressing the air flow rotated by a motor of shovels, not shown in the drawings. In the cooling operation, the condensed water generated by the condensation of the air in room 15 in the heat exchanger 6, is drained outside the body 1 of the air conditioner, by means of a drain pump 17.

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As shown in Fig. 4, which illustrates the enlarged view of the turbo fan 3 and its vicinity, the flow B introduced into the fan turbo 3 is divided into an air flow C1, which flows from the turbo fan 3 to the heat exchanger 6, and a flow C2, which flows through the gap E1 between the main plate 3b and the thermal insulating material 1e side of the upper panel, which flows into the air passage 3f from the motor side, around the motor 4, which flows through the opening 18b of the lower edge of the air guidance cover 18, which flows through the gap E2 between the hub 3c and the air guidance cover 18, emitted from the openings 3d to step 3e of air inside the fan, and joining the flow B of air entering the fan.

In this flow C2, first, the air flowing into the air passage 3f from the motor side (motor side 4) of the inner side of the air guiding cover 18, through the gap E1, generates a flow of air directed to the opening 18b of the lower edge. Here, because the air guiding cover 18 is formed such that the height of the opening 18b of the lower edge of the circumferential surface portion 18c is lower than the surface of the lower edge of the motor 4, the flowing air inside the air passage 3f of the side of the motor can be reliably guided to the surface 4b of the lower edge of the motor 4. In this way, the entire surface of the motor 4 can be cooled, and the heat of the coils and of the elements inside the engine 4 can be radiated.

Next, the air used to cool the surface of the engine 4 flows outwardly from the opening 18b of the lower edge of the air guide cover 18 and contacts the flat surface portion 3cb of the hub 3c. Subsequently, the air is guided upwards through the gap E2 and is emitted from the openings 3d to the air passage 3e inside the fan. Here, because the openings 3d are formed in the portion 3ca of the circumferential surface of the hub 3c on the side of the main plate 3b (in the vicinity of the main plate 3b), it can be prevented that the air flowing out from the 3d openings towards the air passage 3e inside the fan interfere with the flow B of the fan inlet air. Therefore, a shear distortion of the fan inlet flow B can be suppressed, and the noise caused by the blades 3a when passing through a turbulent air can be reduced. In addition, an increase in noise caused by a deterioration of the air supply efficiency, caused by the air that interferes with the air with the flow B of air entering the fan can be prevented.

Because the entire hub 3c is substantially in a double structure and the openings 3d are provided on the side of the main board 3b of the circumferential surface portion 3ca of the hub 3c, the length of the air passage from the air passage 3f from the side of the motor of the hub 3c to the air passage 3e of the inside of the fan is greater than that in the case that the hub was of a single structure and the openings for emitting air from the inner side of the hub to the outside were provided in the vicinity of the lateral surface of the engine or if part of the hub was in a double structure and the position of the openings were low. Therefore, the noise is muffled and the operating noise, such as abnormal electromagnetic noise or bearing rotation noise generated in the motor 4, is reduced.

Similar to noise damping, the flow rate of the air flowing out from the openings 3d to the air passage 3e inside the fan is also damped. Accordingly, a reduction in the flow rate of the flow C1 of air dissipated from the fan, caused by the air flowing out from the openings 3d into the air passage 3e inside the fan and interfering with the flow B of Fan inlet air can be reliably prevented, and an increase in noise that accompanies the degradation of air supply efficiency can be prevented. Furthermore, due to the effect of preventing a reduction in the flow C1 of air dissipated from the fan, a sufficient volume of air can be obtained to cool the engine and the engine 4 can be efficiently cooled.

Next, with reference to Figs. 8 to 12, the dimensional design of each component of the turbo fan 3 will be described to sufficiently obtain a cooling effect of an engine 4 and a noise reduction effect. Relevant dimensions include the gap mm mm k between the air guide cover 18 and the lower edge of the motor 4 (the distance between the lower edge of the motor 4 and the surface of the circumferential surface portion 18c along a perpendicular line extending from the lower edge of the engine 4 to the surface of the circumferential surface portion 18c of the air guide cover 18), an area G5 of the outlet 3i of the turbo fan 3, a circular opening area G1 in the recess E2 between the air guiding cover 18 and the hub 3c (ie, the opening area obtained by taking a circular cross-section of the air guiding cover 18 and the hub 3c along an orthogonal plane a the 3ca portion of circumferential surface), and an area G4 of total opening of the openings 3d (total area of all openings 3d).

Fig. 8 illustrates the relationship between the minimum egg space k between the air guide cover 18 and the lower edge of the engine 4 and the engine cooling efficiency. The engine cooling efficiency is represented by the proportion of (h1-h2) in h1, where h1 represents the engine temperature when the 3d openings are provided and h2 represents the engine temperature when the 3d openings are not provided.

As shown in Fig. 8, it is preferable to fix the gap gap mm or 8 mm or more, so that the air guiding cover 18 does not collide with the motor 4 when it is pivoted horizontally on a support point in the rotary axis 4a during transport, and 25 mm or less, so that a staggered deterioration of the engine cooling efficiency does not occur. By using these dimensions, sufficient air flows into the surface of the engine so that stable engine cooling efficiency can be achieved and can

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prevent damage caused by heat generated in the engine.

Fig. 9 illustrates the relationship between G4 / G1 (the ratio of the total opening area G4 in the circular opening area G1) and the engine cooling efficiency.

As shown in Fig. 9, if G4 / G1 is 40% or more, the flow resistance in the passage from the gap E2 between the air guide cover 18 and the hub 3c to the openings 3d of the hub 3c is not too large, and a minimum of air flows, so that a high and stable engine cooling efficiency is achieved, and damage caused by the heat generated in the engine 4 can be prevented.

Fig. 10 (a) illustrates the relationship between G4 / G5 (the ratio of the total opening area G4 in the outlet area G5 of the turbo fan) and the noise values. Fig. 10 (b) illustrates the relationship between G4 / G5 (the ratio of the total opening area G4 in the outlet area G5 of the turbo fan) and the engine cooling efficiency.

As shown in Fig. 10 (a), if G4 / G5 is 10% or less, the flow of air emitted from the openings 3d does not interfere with the flow B of fan inlet air and, thus , the noise value is small. As shown in Fig. 10 (b), if G4 / G5 is 0.5% or more, a stable engine cooling efficiency is obtained. In this way, by setting G4 / G5 between 0.5% and 10%, stable engine cooling efficiency can be achieved with low noise.

As described above, when setting the dimensions so that the relationships between each of the components (air guide and motor cover 18, air guide cover 18 and hub 3c, and openings 3d and the output 3i) is maintained, damage caused by the heat generated in the engine 4 with low noise can be prevented and an air conditioning body, of the type recessed in the ceiling, of high quality, with low noise can be obtained.

Fig. 11 illustrates the frequency characteristics of the air conditioner according to the present invention, in operation, and illustrates the comparative results with respect to a known air conditioner. The horizontal axis represents the frequency, and the longitudinal axis represents the noise SPL value. The experimental result shows a comparison of the structure according to the present invention and a known structure (a cube of unique structure having openings formed in the vicinity of the surface of the side of the motor of the hub, to emit the air from inside the cube to the outside of the cube). As shown in Fig. 11, it can be confirmed that abnormal electromagnetic noise or bearing rotation noise generated in motor 4 can be reduced.

Fig. 12 illustrates the relationship between the volume of air supply and the noise during operation of the air conditioner according to the present invention and illustrates the comparative result with that of a known air conditioner. The horizontal axis represents the volume of air supply, and the longitudinal axis represents the noise value.

As shown in Fig. 12, it can be confirmed that, when the air supply volumes are equal, the noise is reduced more for the structure according to the present invention compared to the known structure (a single structure cube having openings formed in the vicinity of the lateral surface of the hub motor, to emit air from inside the hub to the outside of the hub).

Thus, according to the first embodiment of the present invention, because the air guiding cover 18 is provided on the inner side (motor side 4) of the hub 3c and this air guiding cover 18 is formed so that the height of the opening 18b of the lower edge of the circumferential surface portion 18c is lower than the surface 4b of the lower edge of the engine 4, the air that has passed into the air passage 3f of the side of the engine can be guided , reliably, to the surface 4b of the lower edge of the motor 4. In this way, the entire surface of the motor 4 can be cooled, and the heat of the coils and the elements inside the motor 4 can be radiated. As a result, the cooling efficiency of the engine is improved and engine damage caused by heat generation can be prevented, and a highly reliable air conditioner of the type embedded in the ceiling can be obtained.

Because the openings 3d for emitting air to the air passage 3e of the interior of the fan are provided on the main plate 3b of the portion 3ca of circumferential surface of the hub 3c, it can be prevented that the air emitted from the openings 3d to the air passage inside the fan interferes with the flow B of air entering the fan. Therefore, a shear distortion of the fan inlet air flow B can be suppressed, and the noise caused by the blades 3a when passing through the turbulent air can be reduced. In addition, an increase in noise that accompanies the deterioration in air supply efficiency caused by interference from the air emitted with the air flowing out from the openings and the flow B of fan inlet air can be prevented.

Because the hub 3c is substantially a double structure, as a whole, and the openings 3d are provided on the side of the main plate 3b of the circumferential surface portion 3ca of the hub 3c, as described above, the distance from the air passage 3f of the motor side of the hub 3c to the air passage 3e of the inside of the fan is extended, and the noise is muffled. As a result, in comparison with that of a hub having a single structure or a partially double structure, the leakage of engine operating noise, such as abnormal electromagnetic noise or bearing rotation noise, generated in the bearing can be reduced

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4 engine, outside. As a result, a low noise recessed air conditioner can be provided that provides a comfortable environment for residents.

Similar to noise damping, the air flow rate that flows outward from the openings 3d into the air passage 3e inside the fan is also damped. Consequently, a reduction in the flow rate of flow C1 of air dissipated from the fan can be reliably prevented, which is caused by interference between the air flowing out from the openings 3d into the air passage 3e from the inside of the fan and the flow B of air entering the fan, and an increase in noise that accompanies a degradation in the efficiency of the air supply can be prevented. Furthermore, due to the prevention effect of the reduction in the flow volume of the air flow C1 of dissipated air from the fan, a sufficient volume of air can be ensured to cool the engine, and the engine 4 can be efficiently cooled.

The circumferential surface portion 18c of the air guiding cover 18 is in the shape of a hollow cone and its diameter decreases so that the cross-sectional area of the air passage 3f on the side of the engine gradually decreases towards the bottom edge of an opening 18b, the air flow inside the air passage 3f of the motor side rises towards the opening 18b of the lower edge. As a result, cooling can be performed efficiently on the entire engine 4 from the top of the engine 4 to the surface 4b of the bottom edge of the engine 4, which is not sufficiently cooled in a known apparatus.

When designing each of the components so that the minimum gap k is between 8 mm or more and 25 mm or less, G4 / G1 is 40% or more, and G4 / G5 is between 0.5 % or more and 10% or less, damage caused by the heat generated in the engine 4, with low noise and can obtain a body of air conditioner, of the type embedded in the ceiling, of high quality and low noise can be prevented .

Because the air guiding cover 18 is composed of metal members, such as aluminum plates and plated steel, which have a high thermal conductivity, the heat from the heated air around the motor is transmitted to the guiding cover 18 of air. Also, because the air guiding cover 18 rotates together with the turbo fan 3, the volume of air passing in contact with the surface of the air guiding cover 18 is increased compared to that in the case in which the air guiding cover 18 is formed so that it does not rotate, and heat radiation is encouraged. In this way, a high engine cooling effect can be achieved. As a result, damage due to the heat generation of the motor 4, with little noise, can be prevented, and a highly reliable body of air conditioning apparatus, of the type embedded in the ceiling, can be obtained.

Because the openings formed in the fixing member of the motor 4, that is, the openings 3d of the hub 3c, are provided on the side of the lower edge (i.e., the side of the main plate 3b) instead of the side of the tip of the truncated cone, the area of the members (cube 3c) between the adjacent 3d openings is large compared to that in which the 3d openings, having the same opening area, are provided on the lower side surface or in the vicinity of the lower edge, such as in a known cube. For this reason, great resistance is achieved against the torque generated by the motor 4.

According to the first embodiment of the present invention, the circumferential surface portion 18c of the air guiding cover 18 and the circumferential surface portion 3ca of the hub 3c are substantially parallel to each other. On the contrary, as shown in Fig. 13, a cylindrical portion 18d can be provided by folding the circumferential surface portion 18c of the air guiding cover 18 along the outer peripheral surface on the side of the motor 4 When said structure is used, because the air flowing into the air guiding cover 18 on the side of the engine 4 can be reliably arranged along the surface of the engine 4, the efficiency engine cooling can be improved even more. Similar to that described above, an air conditioner, of the type recessed in the ceiling, can be obtained, highly reliable and with little noise, which is capable of reducing the abnormal electromagnetic noise and the rotational noise of the bearings, and which It is capable of preventing engine damage 4.

Second embodiment

Next, it will be described, with reference to Figs. 14 to 19, an air conditioner, of the type embedded in the ceiling, according to a second embodiment of the present invention.

Fig. 14 illustrates a longitudinal cross-sectional view of the interior of the air conditioner according to the second embodiment of the present invention. Fig. 15 illustrates a horizontal cross-sectional view of the interior of the body 1 of the air conditioner, shown in Fig. 14, seen from the top panel. Fig. 16 illustrates an enlarged view of a turbo fan 3 and its vicinity, shown in Fig. 14. Fig. 17 illustrates a schematic view of a turbo fan 3 that makes contact with a lateral thermal insulating material 1e of the upper panel by pivoting at a support point at a fixed point of the hub 3c and the rotating shaft 4a during transport. In these drawings, the same components as those of the first embodiment shown in Figs. 1 to 4, are represented by the same reference numbers, and their descriptions are omitted.

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The second embodiment is the same as the first embodiment shown in Fig. 2, except that in the lateral thermal insulating material 1e of the upper panel, a rectifying section 1g is provided to limit the volume of flow flowing from the hollow E1 to the lateral of the motor 4, in an area 1f corresponding to the main fan plate, ring-shaped, opposite to the main plate 3b. In this way, the volume of flow emitted from the openings 3d to the air passage 3e inside the fan is reduced to reduce noise. The grinding section 1g is provided as a single unit with the lateral thermal insulating material 1e of the upper panel.

The shape of the grinding section 1g is described in detail below, with reference to Figs. 16 to 18. Fig. 18 illustrates a perspective view of the portion corresponding to the fan side of the thermal insulating material 1c.

The grinding section 1g has substantially a ring shape, and the distance from the main plate 3b, in the direction of height, is reduced from the outer circumferential portion to the inner circumferential portion. The minimum gap E1 between the grinding section 1g and the main plate 3b and a gap D1 between the main plate 3b and the thermal insulating material 1e of the upper panel, in the height direction, are fixed to establish a predetermined relationship. In addition, a lateral surface 1h of the grinding section 1g, as shown in Fig. 17, is formed at an angle so that, when the turbo fan 3 pivots at a support point in a fixed portion 3h of the hub 3c and the rotary axis 4a, and contacts the grinding section 1g during transport, the outer circumferential edge of the turbo fan 3 does not make precise contact with the grinding section 1g. More specifically, the shape of the inclined side surface 1h is a polygonal shape, so that the hub makes a linear contact or a surface contact with the outer circumferential edge of the turbo fan 3, as shown in Fig. 18.

By providing the grinding section 1g, which has the structure described above, it is prevented that a flow C2 ejected from an outlet 3i of the turbo fan 3, and inverted in a direction towards the gap E1 between the main plate 3b and the thermal insulating material 1e side of the top panel, flow excessively into the air passage 3f on the side of the engine. Therefore, the volume of air flow flowing out from the openings 3d to the air passage 3e inside the fan can be reduced, the air is prevented from interfering with the flow B of air entering the fan and suppressed shear distortion generation. In this way, noise can be reduced.

Next, with reference to the following Fig. 19, the dimensional design of the grinding section 1g will be described, in order to obtain, in a sufficient manner, a cooling effect of the motor 4 and a noise reduction effect.

Fig. 19 (a) illustrates the change in the noise value corresponding to E1 / D1 (proportion of the minimum hole E1 between the grinding section 1g and the main plate 3b in the gap D1 between the thermal thermal insulating material 1e of the upper panel and the main plate 3b, in the direction of the height) under the condition that the air supply volumes are equal. Fig. 19 (b) illustrates the engine cooling efficiency corresponding to E1 / D1 when the air supply volumes are equal.

If E1 / D1 is too small, the resistance to the flow of the gap D1 is large, causing the air to not flow. As a result, the noise is reduced, as shown in Fig. 19 (a). At the same time, the volume of flow to the surface of the engine 4 is reduced, causing the engine 4 to not cool sufficiently. As a result, the engine cooling efficiency deteriorates, as shown in Fig. 19 (b). On the other hand, if E1 / D1 is too large, excessive air flows into the gap D1, making the noise large, as shown in Fig. 19 (a). At the same time, sufficient air flows to the surface of the engine 4, increasing the cooling efficiency of the engine 4.

Accordingly, in this embodiment, E1 / D1 is set between 0.3 and 0.7 to balance the cooling effect of the engine 4 and the noise reduction effect. In this way, the cooling efficiency of the engine is increased and, in this way, damage due to the heat generated in the engine 4 can be prevented and the noise values can be reduced.

In this way, according to the second embodiment, the same advantages that are obtained according to the first embodiment are achieved. Also, according to the second embodiment, because the rectifier section 1g, which has the form described above, is provided, it is prevented that the flow C2 of air expelled from the outlet 3i of the turbo fan 3, and inverted in a direction towards the gap E1 between the main plate 3b and the thermal insulating material 1e side of the upper panel, flow excessively into the air passage 3f of the motor side. Therefore, the volume of air flow flowing out of the openings 3d to the air passage 3e inside the fan can be reduced, the air is prevented from interfering with the flow B of the fan inlet air and is suppressed shear distortion generation. In this way, noise can be reduced.

Because, in the event that the main plate 3b of the turbo fan 3 contacts the thermal insulating material 1e of the upper panel during transport, the manner of contact is not a point contact, such as in the case of a known apparatus , but is a linear contact or a surface contact, as indicated by J in Fig. 17, the concentration of stress on the main plate 3b due to impact can be avoided, and can

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prevent damage to the turbo fan 3. In addition, there is an advantage in that the grinding section 1g can be formed as a single unit using the thermal insulating material 1, which constitutes the passage of air, when the insulating material 1c is molded thermal. In this way, other components do not have to be composed and the assembly procedure can be simplified. As a result, an air conditioner of the type recessed in the ceiling, highly reliable and with low noise, capable of preventing engine damage by improving the cooling efficiency of the engine and providing a comfortable environment for a resident can be obtained.

Because E1 / D1 is set between 0.3 and 0.7, an air conditioner, of the type recessed in the ceiling, which has a cooling effect of the motor 4 and a noise reduction effect can be obtained.

The lateral surface of the grinding section 1g according to this embodiment, is shaped in a polygonal shape. However, the shape is not limited as long as the lateral surface of the grinding section 1g is shaped so that the outer circumferential edge of the turbo fan 3 can be brought into linear contact or surface contact. In other words, the shape may be that illustrated in Fig. 20, as described below.

Fig. 20 illustrates a perspective view of another example of a grinding section 1g having a different shape. In this example, the lateral surface 1h of the grinding section 1g is shaped as the inclined surface of a truncated cone. In this case, too, because at least the main plate 3b and the lateral surface 1h make linear contact, the stress concentration due to the impact imposed on the main plate 3b can be avoided and damage to the turbo fan 3 can be prevented. When this form is used, similar to the previous one, if E1 / D1 is from 0.3 to 0.7, an air conditioner, of the type embedded in the ceiling, can be obtained which has a cooling effect of the motor 4 and a noise reduction effect.

In this embodiment, the grinding section 1g is formed by the lateral thermal insulating material 1e of the upper panel. However, for example, as shown in Fig. 21, the grinding section 1g can be formed by deforming a section of the area 1f corresponding to the main fan plate of the upper panel 1b of the chassis. In that case, even if the side thermal insulating material 1e of the upper panel is not provided inside the air passage of the upper panel 1b, the grinding section 1g may be provided as a single unit with the upper panel 1b of the chassis without the 1e thermal insulating material of the upper panel, so that the cost can be reduced.

Third realization

Next, it will be described, with reference to Figs. 22 and 23, an air conditioner, of the type embedded in the ceiling, according to a third embodiment of the present invention.

Fig. 22 illustrates a longitudinal cross-sectional view of the interior of the air conditioner according to the third embodiment of the present embodiment. Fig. 23 illustrates a perspective view of a grinding plate 19 shown in Fig. 22. In these drawings, the same components as those corresponding to the first embodiment shown in Figs. 1 to 4 are represented by the same reference numbers, and their descriptions are omitted.

The third embodiment is the same as the second embodiment shown in Fig. 14, except that, instead of forming the grinding section 1g on the lateral thermal insulating material 1e of the upper panel, a grinding plate 19, which has a shape corresponding to the rectifier section 1g and which works in the same way as the rectifier section 1g, is removably installed. The grinding plate 19 is composed of a laminated metal member or a plastic member and is fixed to the lateral thermal insulating material 1e of the upper panel and the upper panel 1b of the chassis with screws.

By using said structure, the same advantages are achieved as those achieved according to the first and second embodiments and the rectifier plate 19 becomes replaceable. Therefore, changes in flow resistance due to a partial change in the specifications of the structural components, such as heat exchanger 6 and filter 14, the volume of flow of the gap E2 between the main plate 3b and the plate grinding machine 19 can be adjusted appropriately according to the model, simply by changing the grinding plate 19.

The shape of the grinding plate 19, similar to the grinding section 1g described above, is not limited to the shape illustrated in the drawings and the shape may be that illustrated in Fig. 24 below.

In this example, the lateral surface 1h of the grinding plate 19 is shaped as the inclined surface of a truncated cone. In this case too, because at least the main plate 3b and the lateral surface 1h are put in linear contact, the stress concentration due to the impact imposed on the main plate 3b can be avoided and damage to the turbo fan 3 is prevented. As described above, if E1 / D1 = 0.3 to 0.7, an air conditioner, of the type embedded in the ceiling, which has a cooling effect of the motor 4 and a reduction effect can be obtained of noise

Fourth realization

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Next, it will be described, with reference to Figs. 25 and 32, an air conditioner, of the type embedded in the ceiling, according to a third embodiment of the present invention.

Fig. 25 is a longitudinal cross-sectional view of the interior of an air conditioner according to the fourth embodiment of the present invention. Fig. 26 illustrates a cross-sectional view z-z. Fig. 27 illustrates the exterior of an upper panel seen from an arrow S in Fig. 25. Fig. 28 illustrates a partially enlarged view of the turbo fan 3 and its vicinity illustrated in Fig. 25. Fig. 29 illustrates a perspective cross-sectional view taken along line vv in Fig. 26. Fig. 30 illustrates a side cross-sectional view of a motor 4. Fig. 31 illustrates a schematic view of a built-in drive substrate in the engine 4. Fig. 32 illustrates the results of the measurement experiments of the surface temperature of the engine and the noise value corresponding to the positional relationship between the passage 1k of radially positioned air guidance and the turbo fan 3, shown in Fig. 25. In these drawings, the same components as the components according to the first embodiment shown in Figs. 1 to 4 are represented by the same reference numbers, and their descriptions are omitted.

The fourth embodiment is the same as the first embodiment shown in Fig. 1, except that a plurality of reinforcing ribs 1i are provided in the upper panel 1b of the chassis to improve the resistance of the upper panel 1b of the chassis and there is a material 1ea lateral thermal insulator of the upper panel provided in the reinforcement ribs 1i and the upper chassis panel 1b, to form an air-guided passage 1k, radially positioned, to guide a flow C2 to the motor 4, to improve the cooling efficiency of the engine 4.

A plurality of reinforcing ribs 1i are provided in the upper panel 1b of the chassis, in an area corresponding to the inner side of the heat exchanger 6, in a manner in which the reinforcing ribs 1i extend from the outer peripheral portion of a area opposite the motor 4 towards the side panels 1a of the chassis and protrude towards the inner side of the body. On the inner side of the upper panel 1b of the chassis and the side panels 1a of the chassis having said reinforcing ribs 1i, a thermal insulating material 1ca, which has substantially an overall box shape, is arranged so that it constitutes a wall surface of air passage. The thermal insulating material 1ca includes a lateral thermal insulating material 1a of the upper panel disposed flush with the part of or with the entire inner surface of the upper panel 1b of the chassis and a lateral thermal insulating material 1d of the side panel, which is the same as the previously described. Because the fourth embodiment is characterized by the lateral thermal insulating material of the upper panel, the shape of the lateral thermal insulating material of the upper panel will be described in detail later.

As described above, the upper panel thermal insulation material 1a upper panel is arranged flush with part of or with the entire inner surface of the upper panel 1b of the chassis, but, according to this embodiment, the lateral thermal insulating material 1a of the upper panel It is arranged flush with part of the inner surface of the upper panel 1b of the chassis. In other words, the reinforcing ribs 1i are provided in the upper panel 1b of the chassis in a manner in which the reinforcing ribs 1i protrude towards the inner length of the body, and the lateral thermal insulating material 1a of the upper panel is formed of so that it is arranged flush with the entire protruding surface 1 based on the protruding surface 1ia (reference to Fig. 29). The lateral thermal insulating material 1e of the upper panel is formed flush with part (several) of the radially positioned areas 1ib from among a plurality of radially positioned areas (i.e., the triangular area (one of which is a longitudinal area) 1ib positions outside the protruding surface 1ia and located between the adjacent reinforcing ribs 1i in the upper panel 1b of the chassis) in an outstanding manner.

According to this embodiment, as shown in Fig. 26, the lateral thermal insulating material 1a of the upper panel is arranged flush with four of the radially positioned areas 1ib and, for the other areas, the lateral thermal insulating material of the upper panel It is provided flat without being arranged flush with the areas 1ib positioned radially. Therefore, as shown in Figs. 26 and 29, the other radially positioned areas 1ib, different from the four radially positioned areas 1ib, are hidden, covered with the flat portion of the thermal insulating material of the upper panel.

The lateral thermal insulating material 1e of the upper panel, which has said structure, forms an area corresponding to the radially positioned areas 1ib (reference to Fig. 29) so that the radially positioned air guide passage 1k has a distance of gap to the main plate 3b that is greater than the gap distance between the reinforcing ribs 1i and the main plate 3b.

Next, it will be described, with reference to Figs. 30 and 31, the structure of the engine 4 to be cooled and the installation of the engine 4.

The engine 4 is constituted in a manner that has a substrate 4h incorporated in the engine, which has a 4d actuator circuit and a control circuit 4e mounted inside the engine, on the side of the upper chassis panel (side opposite the turbo fan ) or, more specifically, it consists of a DC motor. The substrate 4h incorporated in the motor is fixed inside the motor 4. The rotor 4g is fixed to the rotary axis 4a. A stator 4f, which includes a coil and a core, is arranged around the rotor 4g. Stator 4f is molded and shaped

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As a single unit with a 4k molding material. The DC motor is formed by arranging the rotor 4g in a hollow portion formed in the stator 4f and maintaining the rotor 4g, in a way that it can rotate freely, by means of the edge of the hollow portion and a bearing 4i snapped into a support 4l . In addition, the 4g rotor is formed by molding a plastic magnetic material in a cylindrical shape and has magnetic fields that have N and S poles on the outer periphery.

In the substrate 4h incorporated in the motor, a hole element 4j is mounted to detect the magnetic field of the rotor 4g and generate a revolution signal, the control circuit 4e to receive the revolution signal and transmit a voltage signal that orders a revolution, and the 4d actuator circuit to control the electric power applied to the magnetic field of the stator 4f, based on the revolution order signal. In the 4d substrate actuator circuit 4h incorporated in the motor, a 4M power element is mounted and is in contact with the support 4L with the intervention of an insulating plate and a heat-radiating silicone.

The substrate 4h incorporated in the motor is connected to an electronic substrate 25 inside a box 24 of electrical components, as illustrated in Fig. 25, by wiring. As shown in Fig. 31, on the electronic substrate 25, an AC / DC converter 25a is mounted to convert a voltage (for example, 200 V) of an AC power supply 26 to a DC voltage and adapt it to supply this DC voltage to the 4d actuator circuit and a power supply 25b for the control circuit, to supply power to the control circuit 4e.

In the motor 4, which has said structure, the temperature of the heat generated in the power element 4M becomes higher than that of the other components, such as the stator coil 4f, and, thus, the heat is transmitted by means of the heat-radiating silicone, to increase the temperature of the support 4L and a lateral surface 4c on the side of the upper panel of the engine chassis 4. Therefore, if the support 4L and the lateral surface 4c on the side of the panel The upper part of the engine chassis 4 does not radiate heat, the power element 4M will be damaged by the heat generated, and the engine 4 will fail. In other words, to prevent damage to the engine 4, it is necessary to mainly cool the support 4L and the lateral surface 4c on the side of the upper panel of the engine chassis 4.

As another example of the motor 4, if the motor 4 is a DC motor that indicates the actuator circuit 4d and the control circuit 4e mounted on the electronic substrate 25, accommodated in the box 24 of electrical components, outside the motor, the rotary axis 4a is heated by the heat transmitted from the stator 4f, which has the highest temperature in the motor 4, the lubricating oil of the bearing 4i is degraded by the high temperature, and the bearing 4i is seized, causing the motor 4 to be damaged. . In other words, also for this case, to prevent damage to the motor 4, it is necessary to mainly cool a portion 4P corresponding to the bearing (reference to Fig. 28) on the surface of the motor and the support 4L in contact with the bearing 4i. The portion 4P corresponding to the bearing is a portion of the outer surface of the bearing 4i of the motor 4.

Next, the cooling effect of the engine 4 will be described by checking the air guide steps 1k, positioned radially.

In the thermal insulating material 1a, lateral of the upper panel, the portion that is disposed flush with the radially positioned areas 1ib, and which constitute the radially positioned air guideways 1k, has a greater gap distance E1 compared to other portions (ie, the flat portion formed according to the protruding surface 1 of the reinforcing ribs 1i).

Therefore, the speed and volume of flow of part of the flow C2 of air dissipated from the turbo fan 3 can be increased when the air is taken to the engine 4. Consequently, the cooling effect on the engine 4 is increased.

The direction of the flow C2, which rotates between the main plate 3b and the lateral thermal insulating material 1a of the upper panel and which is carried towards the motor 4, is changed by contacting a lateral surface 1ka of the air guided passage 1k, positioned radially, as shown in Fig. 29. In this way, the lateral surface 4c of the engine 4 on the side of the upper chassis panel and the support 4L on the upper surface of the motor 4 on the side of the upper panel are cooled of the chassis.

According to this example, the thermal insulating material 1e of the side of the upper panel is arranged flush only with part of the areas 1ib, positioned radially, of all the areas 1ib, positioned radially. The thermal insulating material 1 on the side of the upper panel is not arranged flush with all areas 1ib, positioned radially, since if all the thermal insulating material 1e on the side of the upper panel is arranged flush with all areas 1ib, positioned radially, the noise may increase.

As shown in Fig. 28, the air C2 passing through the gap E1 between the main plate 3b and the thermal insulating material 1eb from the side of the upper panel and flowing into the air passage 3f from the motor side , flows around the motor 4 and is then emitted from the openings 3d to the air passage 3e inside the fan. At this time, because the air flow passes through the portion 4P corresponding to the bearing on the surface of the engine, the portion 4p corresponding to the bearing can be cooled. In this way, the 4P portion corresponding to the bearing can be sufficiently cooled. Because the engine 4 can be cooled sufficiently in this way, the turbo fan 3 can be rotated until the engine is reached.

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Kmite temperature of the 4M power element. In this way, the volume of air supply can be increased, and the heat exchange capacity of the heat exchanger 6 can be improved. In addition, because the loss of the internal circuit of the 4M power element can be reduced, the efficiency of the motor is improved and energy can be conserved.

Next, the positional relationship between an air-guided passage 1k, radially positioned, and the turbo fan 3 to obtain a high cooling effect of the engine 4 and a high noise reduction effect is described.

If an inner circumferential edge 1kb of the radially arranged air guide passage 1k is disposed separate from the engine 4, it becomes difficult to carry a flow towards the lateral surface 4c of the side of the upper panel of the engine chassis 4 and the support 4L, causing insufficient refrigeration. If an outer circumferential edge 1kc of the air-guided passage 1k, positioned radially, is disposed more outward than the outer circumference of the turbo fan 3, the flow C1 dissipated, instead of the flow C2 passing through the gap E1 and which It is directed towards the air passage 3f on the side of the engine, directly collides with the lateral surface 1ka of the air-guided passage 1k, positioned radially, causing an increase in noise. When the dissipated flow C1 collides directly with the lateral surface 1ka of the air-guided passage 1k, positioned radially, and its direction is changed towards the motor 4, the volume of flow towards the motor 4 increases, while the volume of flow towards heat exchanger 6 is reduced. Therefore, the air flow must be increased to increase the heat exchange capacity, and, as a result, the noise worsens.

Considering the above, the optimal positioning of the inner circumferential edge 1kb and the outer circumferential edge 1kc of the air guided passage 1k, positioned radially, to improve both the cooling effect and the noise reduction effect will be described.

Fig. 32 (a) illustrates the relationship between the position of the inner circumferential edge 1kb of the air-guided passage 1k, positioned radially, and the surface temperature T1 of the support 4L arranged on the side of the upper panel of the engine chassis 4, after it worked for the same amount of time. Fig. 32 (b) illustrates the relationship between the position of the outer circumferential edge 1kc of the air guided passage 1k, positioned radially, and the noise SP value, in the same flow volumes. Fig. 32 (c) illustrates the relationship between the position of the outer circumferential edge 1kc of the air-guided passage 1k, positioned radially, and the surface temperature T1 of the support 4L arranged on the side of the upper panel of the engine chassis 4, after running for the same amount of time.

If 0 <L2 <0.3xL1, as shown in Fig. 32 (a), where L1 represents the outside diameter of the turbo fan 3, L0 represents the distance between the center 4ac of the rotary axis of the engine 4 and the edge 1kc outer circumferential of the air guided passage 1k, positioned radially, and L2 represents the distance between the center 4ac of the rotary axis of the motor 4 and the inner circumferential edge 1kb of the air guided steps 1k, positioned radially, the motor 4 it is sufficiently cooled compared to the case in which the radially positioned air guide steps 1k are not provided (i.e., when L2 = 0.5xL1). This is supposed to be true since a large area for the lateral surface 1ka of the air-guided passages 1k can be obtained, and the air flow to the engine 4 can be increased.

As shown in Fig. 32 (b), if L0 <0.6xL1, the noise value is only getting worse. As shown in Fig. 32 (c), if 0.5xL1 <L0, that is, if the outer circumferential edge 1kc of the air-guided passage 1k, positioned radially, is farther out than the main plate 3b, Engine 4 will be cooled sufficiently.

Consequently, by setting the dimensions within the intervals 0.5xL1 <L0 <0.6xL1 and 0 <L2 <0.3xL1, the motor 4 will be cooled sufficiently and the noise value does not worsen, allowing to obtain an air conditioner, of type recessed in the ceiling, high quality.

As described above, according to the fourth embodiment, because the reinforcing ribs 1i are formed in the upper panel 1b of the chassis in a manner in which they protrude into the body, the resistance can be increased without increasing the height of the body. In this way, the thickness and weight of the upper panel 1b of the chassis can be reduced. Also, because the radially positioned air guide passage 1k, which has the ability to change the direction of the flow C2 towards the motor 4, is formed with the thermal insulating material 1 on the side of the upper panel provided on the inner side From the top panel 1b of the chassis, the engine 4 can be effectively cooled and damage to the engine can be prevented.

Because the thermal insulating material (thermal insulating material 1 on the side of the upper panel) is provided on the inner surface of the upper panel 1b of the chassis, even when the heat exchanger 6 is cooled during the cooling operation, the atmosphere in the The inside of the body is also cooled, and the humidity of the area under the roof where the body 1 of the air conditioner is installed is high, a condensation of rolling over the surface of the upper panel 1b of the chassis can be prevented. In this way, the rock does not fall on the floor of the room dirtying the floor, and the cleanliness of the floor is maintained.

By setting the dimensions within the ranges of 0.5xL1 <L0 <0.6xL1 and 0 <L2 <0.3xL1, you can obtain an air conditioner, of the type recessed in the ceiling, of high quality and low noise, capable to improve the cooling efficiency of the engine 4 and to suppress the worsening of the noise value and able to prevent heat damage

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generated in engine 4.

Because the substrate 4h incorporated in the motor, which includes the actuator circuit 4d and the control circuit 4e, is stored inside the motor 4, the size of the electrical component box 24 can be reduced in comparison with the size of a box 24 of electrical components that includes the 4d actuator circuit and the control circuit 4e. In this way, the flaring 5 and the passage 11 of air entering the body are not partially blocked. Therefore, a reduction in resistance to flow and a prevention of a drift from the inlet are possible, and a reduction in noise is possible.

If the height of the upper surface (support surface 4L of the engine 4) of the motor 4 on the side of the upper panel 1b of the engine chassis 4 is lower (closer to the turbo fan 3) than the height of the surface of the material 1ea Thermal insulator on the side of the upper panel, shown in a dotted line in Fig. 28, a space is formed in the vicinity of the support 4L, which allows the flow C2 to flow easily into the support 4L. Therefore, the cooling effect can be improved and, as a result, the efficiency of the engine is improved, allowing a high-quality air conditioning device of the ceiling type, capable of excellent energy savings, to be obtained. .

Fifth realization

Next, it will be described, with reference to Figs. 33 to 35, an air conditioner, of the type embedded in the ceiling, according to a fifth embodiment of the present invention.

Figs. 33 and 34 illustrate the same body as the fourth embodiment, except that the radially arranged reinforcing ribs 1i protrude outward from the body. Fig. 33 illustrates the upper panel 1b of the chassis, seen from the side of a thermal insulating material 1eb from the side of the upper panel. A cross-sectional view Y-Y of Fig. 33 is substantially the same as Fig. 28. Fig. 34 illustrates a plan view of the exterior of the upper panel 1b of the chassis. Fig. 35 illustrates a perspective cross-sectional view taken along line V-V in Fig. 33. In these drawings, the same components as those of the first embodiment, shown in Figs. 1 to 4, and those of the fourth embodiment, shown in Figs. 25 to 32, are represented by the same reference numbers, and their descriptions are omitted.

The fifth embodiment is the same as the fourth embodiment, except that the reinforcing ribs 1i, arranged radially, protrude outward from the body, rather than into the interior of the body. On the inner surface side of the upper panel 1b of the chassis and the side panels 1a of the chassis having said reinforcing ribs 1i protruding outwardly, a thermal insulating material 1cb, substantially box-shaped, is provided to form a lateral surface of an air passage. The thermal insulating material 1cb includes a thermal insulating material 1e from the side of the upper panel disposed flush with part of or with the entire inner surface of the upper panel 1b of the chassis and a thermal insulating material 1d from the side of the upper side panel, which is the same than described above. Because the fifth embodiment is characterized by the thermal insulating material 1eb on the side of the upper panel, the shape of the thermal insulating material 1eb on the side of the upper panel will be described in detail below.

The thermal insulating material 1eb on the side of the upper panel, similar to the fourth embodiment, is arranged flush with part of the upper panel 1b of the chassis, instead of flush with the entire upper panel 1b of the chassis. More specifically, in the upper panel 1b of the chassis, the reinforcing ribs 1i are formed, which protrude outwards from the body, as shown in Fig. 34, and the thermal insulating material 1eb from the side of the upper panel is formed so that they are arranged flush with the total surface 1ic based on the protruding surface 1ic (reference to Fig. 35). The thermal insulating material 1eb on the side of the upper panel is formed flush with part (several) of the reinforcing ribs 1i from among all the reinforcing ribs 1i that protrude outward more than the surface 1ic, in an outstanding manner. According to this embodiment, as shown in Fig. 33, the thermal insulating material 1eb on the side of the upper panel is arranged flush with four of the reinforcing ribs 1i, and, for the other areas, the thermal insulating material 1eb on the side of the upper panel is provided flat, without being arranged flush with the reinforcing ribs 1i. Therefore, as shown in Fig. 33, the reinforcing ribs 1i, except for the four reinforcing ribs 1i, are hidden covered with the flat portion of the thermal insulating material 1eb on the side of the upper panel.

In the thermal insulating material 1eb, which has said structure, the area formed flush with the reinforcing ribs 1i constitutes radially positioned air guideways 1k ', which have a gap distance to the main plate 3b which is greater than the gap distance between the flat and non-flush formed area with the reinforcing ribs 1i and the main plate 3b.

By using said structure, similar to the fourth embodiment, in which the radially positioned air guide steps 1k are provided, a reduction in weight is possible by increasing the resistance and the guiding part of the flow C2 dissipated from the turbo fan 3 by middle of the 1k 'air guidance passage, positioned radially. In this way, it is possible to effectively cool the lateral surface 4c of the motor 4 on the side of the upper chassis panel and the support 4L.

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The air that passes through the gap E1 between the main plate 3b and the thermal insulating material 1eb from the side of the upper panel and flowing into the air passage 3f from the side of the engine, flows around the engine 4 and then It is emitted from the 3d openings towards the air passage 3e inside the fan. At this time, because the air flow passes through the portion 4P corresponding to the bearing on the surface of the engine, the portion 4P corresponding to the bearing can be sufficiently cooled and damage can be prevented therein. Because the engine 4 is sufficiently cooled in this way, the turbo fan 3 can be rotated until the limit temperature of the power element 4M is reached. In this way, the volume of air supply can be increased, and the heat exchange capacity of the heat exchanger 6 can be improved. In addition, because the loss of the internal circuit of the 4M power element can be reduced, the efficiency of the motor is improved and energy can be saved.

Because the inner side of the upper panel 1b of the chassis is covered with the thermal insulating material 1eb from the side of the upper panel, even if some of the air cooled in the heat exchanger 6 flows into the interior of the motor 4, condensation can be prevented, allowing to obtain an air conditioner, of the type embedded in the ceiling, of high quality.

According to the previous description, in the fourth embodiment, such satisfy 0.5xL1 <L0 <0.6xL1 and 0 <L2 <0.3xL1 are effective advantages are also achieved in the fifth embodiment.

Reference numbers

1: air conditioner body,

 1st:

 chassis side panels

 1 B:

 upper chassis panel

 1c, 1ca and 1cb:

 thermal insulating material

 1e, 1ea and 1eb:

 thermal insulating material on the side of the upper panel

 1f:

 area corresponding to the main plate of the fan

 1g:

 grinding section

 1 hour:

 lateral surface

 1i:

 booster nerves

 1st:

 protruding surface

 1ib:

 radially positioned areas

 1k:

 radially positioned air guide passage

 1kb:

 inner circumferential edge

 1kc:

 outer circumferential edge

 3:

 turbo fan

 3rd:

 Pallas

 3b:

 main board

 3c:

 Cube

 3rd:

 circumferential surface portion

 3cb:

 flat portion

 3cc:

 cylindrical portion

 3d:

 openings

 3e:

 air passage inside the fan

 3f:

 engine side air passage

 3g:

 cover

as shown in Fig. 32, dimensions to cool the engine 4 and reduce noise. The same

of the type embedded in the ceiling

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Four. Five

fifty

 3h:

 fixed portion

 3i:

 exit

 4:

 engine

 4th:

 rotary motor

 4ac:

 center of the rotary axis

 4b:

 lower edge surface of the engine

 4d:

 actuator circuit

 4e:

 control circuit

 4h:

 substrate incorporated into the engine

 5:

 flared

 6:

 heat exchanger

 18:

 air guiding cover

 18:

 flange portion

 18b:

 bottom edge opening

 18c:

 circumferential surface portion

 19:

 grinding plate

 23a:

 inlet air passage

 23b:

 air outlet fan outlet

The mother application claimed the following matter that is included here as part of the description, but is not claimed.

An air conditioning apparatus, of the type embedded in the ceiling, comprising: (a) a body (1) of the air conditioning apparatus, of the type embedded in the ceiling, which includes an upper panel (1b) of the chassis; (b) a motor (4) disposed in the body (1) of the air conditioning apparatus, of the type embedded in the ceiling, in a manner in which a rotating shaft (4a) of the motor is arranged at right angles to the upper panel (1b) of the chassis; (c) a turbo fan (3) that includes a hub (3c) that protrudes downward, that covers the engine (4) and that fixes the rotating shaft (4a) of the engine in place, a main plate (3b) that it extends from the periphery of an upper opening of the hub (3c), such that it opposes the upper panel (1b) and has a plurality of blades (3a) fixed to a surface of the main plate (3b) opposite the another surface opposite the upper panel (1b), and a cover (3g) opposite the main plate (3b) and constituting a guide channel for the blades (3a), the turbo fan (3) that expels air collected from the side of the cover through an air passage (3e) of the inside of the fan, formed on the side opposite to the side of the hub motor (3c); and (d) an air guide cover (18) for guiding air flowing from a gap formed between the upper panel (1b) of the chassis and the main plate (3b) and into the air passage (3f) of the side of the engine, the air guide cover (18), being provided on the side of the hub motor (3c), to form the air passage (3f) on the side of the engine between the engine (4) and the cover ( 18) for air guidance, in which the air guidance cover (18) includes a portion (18c) of circumferential surface extending downward from the side of the main plate (3b), the height position of the opening (18b) of the lower edge of the circumferential surface portion (18c) is positioned lower than the surface of the lower edge of the motor (4), and the hub (3c) includes a plurality of openings (3d) to allow the air flowing from the gap into the air passage (3f) of the side of the engine and then from the opening of the lower edge to the c air guide (18) inside a gap between the air guide cover (18) and the hub (3c) to flow out into the air passage (3e) inside the fan. Such an air conditioner, of the type embedded in the ceiling, in which a plurality of openings (3d) are formed in the hub (3c) in the vicinity of a main plate (3b). Such an air conditioner, of the type embedded in the ceiling, in which the portion (18c) of the circumferential surface of the air guiding cover (18) is formed such that the cross-sectional area of the passage (3f) of air from the side of the engine is reduced towards the opening (18b) of the lower edge. Such an air conditioner, of the type embedded in the ceiling, in which the cube (3c) and the circumferential surface portion (18c) of the air guiding cover (18) are both formed as truncated cones, with substantially the same inclination. Such an air conditioning apparatus, of the type embedded in the ceiling, in which the circumferential surface portion (18c) of the air guiding cover (18) includes a cylindrical portion in line with the outer peripheral surface of the motor (4) . Such an air conditioner, of the type embedded in a ceiling,

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in which k represents the minimum gap between the air guide cover (18) and the lower edge of the engine (4), G5 represents the area of an air outlet of the turbo fan (3), G1 represents an area G1 of circular opening in a gap of space E2 mm between the air guide cover (18) and the hub (3c), and G4 represents the total opening area of the openings (3d), each of the relevant components maintains relations so that the gap mm mm k is between 8 mm and 25 mm, G4 / G1 is 40% or more, and G4 / G5 is between 0.5% and 10%. Such an air conditioner, of the type embedded in the ceiling, in which the air guidance cover (18) is formed of a metal member with a high thermal conductivity and is fixed to the turbo fan (3) so that it rotates together With the turbo fan. Such an air conditioner, of the type embedded in the ceiling, in which a grinding section (1g) is provided in a gap between an area (1f) corresponding to the main fan plate in the upper panel (1b) of the opposite chassis to the main plate (3b) and the main plate (3b) in a manner in which the gap becomes thinner towards the center of the main plate (3b). Such an air conditioner, of the type embedded in the ceiling, in which a lateral surface of the grinding section (1g) is formed at an angle so that, when the turbo fan (3) makes contact with the grinding section (1g ), pivoting at a support point in a fixed portion (3h) of the hub (3c) and the rotating shaft (4a) of the engine during transport, the outer circumferential edge of the turbo fan (3) does not make contact with the lateral surface of the rectifying section (1g). Such an air conditioner, of the type embedded in the ceiling, in which the grinding section (1g) is shaped in a polygonal manner such that, when the turbo fan (3) makes contact with the rectifying section (1g), pivoting at a support point in a fixed portion (3h) of the hub (3c) and the rotary axis (4a) of the engine during transport, the turbo fan (3) makes linear contact or surface contact with the grinding section (1g). Such an air conditioner, of the type embedded in the ceiling, in which the rectifying section (1g) is formed as a truncated cone so that, when the turbo fan (3) makes contact with the rectifying section (1g), pivoting at a support point in a fixed portion (3h) of the hub (3c) and the rotary axis (4a) of the engine during transport, the turbo fan (3) makes linear contact with the grinding section. Such an air conditioner, of the type embedded in the ceiling, in which, on the side of the main plate of the upper panel (1b) of the chassis, a thermal insulating material (1e, 1ea, 1eb) is provided on the side of the panel upper, which defines an air passage on the inner side of the upper panel (1b) of the chassis, and the grinding section (1g) is formed as a single unit with the thermal insulating material (1eb) on the side of the upper panel. Such an air conditioner, of the type embedded in the ceiling, in which the grinding section (1g) is formed by deforming the area (1f) corresponding to the main fan plate of the upper panel (1b) of the chassis. Such an air conditioner, of the type embedded in the ceiling, in which the grinding section (1g) is a grinding plate (19) fixed, so that it can be disassembled, directly or indirectly on the upper panel (1b) of the chassis . Such an air conditioner, of the type embedded in the ceiling, in which an E1 / D1 ratio of a hole E1 mm between the grinding section (1g) and the main plate (3b) in a hole D1 between the thermal insulating material of the side of the upper panel and the main plate (3b), in the direction of height, is 0.3 to 0.7.

Claims (6)

5 10 fifteen twenty 25 30 35 40 1. An air conditioner, of the type embedded in the ceiling, comprising: (a) a body (1) of the air conditioning apparatus, of the type embedded in the ceiling, which includes an upper panel (1b) of the chassis; (b) a motor (4) disposed in the body (1) of the air conditioning apparatus, of the type embedded in the ceiling, in such a way that a rotating shaft (4a) is orthogonal to the upper panel (1b) of the chassis, Y (c) a turbo fan (3) that includes a hub (3c) protruding downward, which covers the motor (4) and to which the rotary axis (4a) of the motor is fixed, a main plate (3b) extending from the periphery of an upper opening of the hub (3c), opposite the upper panel (1b) and has a plurality of blades (3a) fixed to an opposite surface of the main plate (3b) to the other surface opposite the upper panel (1b) of the chassis, and a cover (3g), opposite the main plate (3b) and constituting a guided flow channel of the blades (3a), and that expels air introduced from the side of the cover through the air passage (3e) of the interior of the fan formed on the opposite side of the motor side of the hub (3c), characterized in that a grinding section (1g) is provided in an area (1f) corresponding to the main plate of the fan, opposite to the main plate (3b) of a thermal insulating material (1e) lateral of the upper panel provided within the upper panel (1b) of the chassis, so that a gap with the main plate (3b) is a predetermined distance, and the ratio E1 / D1 of a hole E1 mm between the grinding section (1g) and the main plate (3b) of a hole D1 between the thermal insulating material (1e) on the side of the upper panel and the main plate (3b), in The height direction is 0.3 to 0.7. 2. The air conditioner, of the type embedded in the ceiling, according to claim 1, wherein the grinding section (1g) is formed in a ring shape protruding towards the side of the main plate (3b), 3. The air conditioning apparatus, of the type embedded in the ceiling, according to claim 1 or 2, wherein an insulating material (1e) is provided on the side of the main plate of the upper plate (1b) of the chassis thermal from the side of the upper panel that defines an air passage on the inner side of the upper plate (1b) of the chassis, and the grinding section (1g) is formed integrally by the thermal insulating material (1e) of the side of the upper panel. 4. The air conditioner, of the type embedded in the ceiling, according to any one of claims 1 to 3, wherein between the area corresponding to the main plate of the fan, opposite to the main plate (3b) of the top plate (1b) of the chassis and the main plate (3b), the grinding section (1g) is formed inclined so that the gap with the main plate (3b) becomes narrower as it approaches the center of the main plate (3b) ). 5. The air conditioner, of the type embedded in the ceiling, according to any one of claims 1 to 4, wherein the grinding section (1g) is formed in the form of a polygon. 6. The air conditioner, of the type embedded in the ceiling, according to any of claims 1 to 4, wherein the grinding section (1g) is formed in the shape of a truncated cone.