JPH055536A - Air conditioner - Google Patents

Abstract

(57) [Abstract] [Purpose] To improve the wind speed distribution for the heat exchanger to reduce operating noise and save energy. [Structure] An annular heat exchanger 3 is provided for an impeller 20, an inner peripheral surface 3c of the heat exchanger 3 and an outer peripheral surface 20a of the impeller 20.
Is arranged so that the interval between the impeller 20 and the impeller 20 gradually increases toward the front side in the rotational direction of the impeller 20, and this interval part functions as a kind of scroll, whereby the flow of air from the impeller 20 toward the heat exchanger 3 is increased. To increase the static pressure and suppress the fan operating noise. Further, the heat transfer area is substantially increased by appropriately superimposing the end portion of the heat exchanger 3 in the circumferential direction, and power saving is achieved by reducing the internal resistance. Furthermore, by configuring the heat exchanger 3 with a plurality of heat exchangers 3A and 3B, the heat transfer area is further expanded, and the refrigerant circulation amount of each of the heat exchangers 3A and 3B is independently controlled. If possible, increase the commercial value of the air conditioner by facilitating adjustment of air conditioning capacity.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner having an annular heat exchanger on the outer peripheral side of a centrifugal fan or a mixed flow fan.

[0002]

2. Description of the Related Art Generally, a centrifugal fan type blower having a moving blade (blade) is designed to realize a blowing function by using the lifting force of the moving blade. The transmission and conversion efficiency is extremely high, and it has been widely used as a blower for an air conditioner.

Recently, as a type of air conditioner, a ceiling-embedded air conditioner has been increasingly adopted particularly from the viewpoints of advantages of installation space and freedom in interior design. In the embedded type air conditioner, for example, as shown in Japanese Patent Application Laid-Open No. 62-194128, among various blowers, it is generally the centrifugal fan or a kind thereof as described above from the viewpoint of its airflow direction converting function. It is customary to use a mixed flow fan and dispose an annular heat exchanger on the outer peripheral side of the centrifugal fan or mixed flow fan.

[0004]

However, in the conventional air conditioner composed of such a combination of the centrifugal fan or the mixed flow fan and the annular heat exchanger, the operating noise is relatively low due to the reasons described below. There is a problem that it is expensive and it is difficult to make it compact.

That is, as shown in FIGS. 5 and 6, in this type of air conditioner Z ₀ , the impeller 20 is usually provided in the center of the casing 1 fixedly arranged on the lower surface side of the ceiling surface 10. The centrifugal fan 2 provided with is arranged such that the fan suction port 24 faces the air suction port 5 formed on the lower surface of the casing 1, and the air outlet formed from the impeller 20 on the outer peripheral lower surface side of the casing 1. 6, 6, ...
An annular heat exchanger 3 in which one end 3a and the other end 3b thereof are close to each other in the ventilation passage 9 provided between
Are arranged so as to surround the outer peripheral side of the impeller 20. In this case, the heat exchanger 3 has a circular inner peripheral surface and is arranged concentrically with the outer peripheral surface of the impeller 20.

In the air conditioner Z ₀ thus constructed, the outer peripheral surface of the impeller 20 and the inner peripheral surface of the heat exchanger 3 are concentric with each other, so that the air is blown out from the impeller 20. The air flow toward the inner peripheral surface side of the heat exchanger 3 cannot be expected to be a smooth decelerating flow as in a scroll, for example.

Therefore, the dynamic pressure of the flow velocity of the impeller 20 is hardly expected to be restored to the static pressure, and the internal resistance is dealt with only by increasing the static pressure obtained in the impeller 20. ing. Therefore, in general, the impeller 20 having a smaller reaction degree has a smaller specific noise and can be operated quietly, but the impeller 20 having a larger reaction degree is adopted, and as a result, the specific noise is increased. is there
(See curves L _{01 to} L _{03 in} FIG. 4).

The reaction degree is defined by "reaction degree = impeller wheel static pressure increase / impeller total pressure increase", and the smaller the blade outlet angle, the greater the reaction degree.

On the other hand, since the turbulence of the air blown out from the impeller 20 is large, it is necessary to rectify this and introduce it into the heat exchanger 3 side. There is no choice but to take a relatively large distance from the peripheral surface, and as a result, the air conditioner Z ₀ is prevented from becoming a compact.

Therefore, according to the present invention, in an air conditioner including a centrifugal fan or a mixed flow fan and a heat exchanger arranged so as to surround the fan, the wind speed distribution with respect to the heat exchanger is improved to reduce the operating noise. And to improve energy efficiency.

[0011]

Each invention of the present application employs a joint-like structure as a specific means for solving such problems.

(1) In the invention according to claim 1, as illustrated in FIGS. 1A and 1B, the air suction port 5 is provided on the lower surface 1a,
A centrifugal fan or a mixed flow fan 2 having an impeller 20 having a plurality of blades 23, 23, ... Is provided in a casing 1 having an air outlet 6 formed in an outer peripheral portion 1b of a side surface or a lower surface 1a. While being attached to the suction port 5 so as to be opposed to each other, the heat is formed on the outer peripheral side of the centrifugal fan or the mixed flow fan 2 so that one end 3a and the other end 3b of the centrifugal fan or the mixed flow fan 2 are wound in an annular shape. The exchanger 3 is arranged so as to surround the outer peripheral side of the centrifugal fan or the mixed flow fan 2,
In the air conditioner in which the air blown radially outward from the centrifugal fan or the mixed flow fan 2 is blown out to the indoor side from the air outlet 6 via the heat exchanger 3, the centrifugal fan or Impeller 20 of mixed flow fan 2
The distance between the outer peripheral surface 20a of the heat exchanger 3 and the inner peripheral surface 3c of the heat exchanger 3 is small on one end 3a side of the heat exchanger 3 located on the front side in the rotation direction of the impeller 20 and on the rear side. It is characterized in that it is set to be large on the end 3b side.

(2) In the invention described in claim 2, as shown in FIGS. 1A and 2, in the air conditioner described in claim 1, one end 3a and the other end 3b of the heat exchanger 3 are arranged around the circumference thereof. It is characterized in that they are configured so as to be polymerized with each other in the direction.

(3) In the invention described in claim 3, FIG.
As illustrated in FIG. 2, the air conditioner according to claim 1 or 2 is characterized in that the shape of the inner peripheral surface 3c of the heat exchanger 3 is a logarithmic spiral curve.

(4) In the invention according to claim 4, as illustrated in FIG. 3, inside the casing 1 in which the air inlet 5 is formed on the lower surface 1a and the air outlet 6 is formed on the side surface or the outer peripheral portion 1b of the lower surface 1a. , A centrifugal fan or a mixed flow fan 2 having an impeller 20 provided with a plurality of blades 23, 23, ... Is attached to the air suction port 5 in a state of being opposed to the centrifugal fan or mixed flow fan. The heat exchanger 3 is arranged on the outer peripheral side of the centrifugal fan or the mixed flow fan 2 so as to surround the outer peripheral side of the centrifugal fan or the mixed flow fan 2, and the air blown from the centrifugal fan or the mixed flow fan 2 outward in the radial direction thereof. In the air conditioner in which the air is blown from the air outlet 6 to the indoor side through the heat exchanger 3, the heat exchanger 3 is composed of a plurality of heat exchangers 3A and 3B curved in an arc shape. In addition, each heat exchanger 3A, 3 B is the inner surface 3 of each
One end 3Aa, 3 of each of the heat exchangers 3A, 3B located at the front side in the rotation direction of the impeller 20 is such that the distance between Ac, 3Bc and the outer circumference of the impeller 20 of the centrifugal fan or mixed flow fan 2 is set.
It is small on the Ba side and large on the other end 3Ab, 3Bb side located on the rear side in the rotational direction, and one end 3Aa, 3Ba of each heat exchanger 3A, 3B is rearward in the rotational direction of the impeller 20 in the circumferential direction. Side heat exchangers 3A, 3
It is characterized in that the other ends 3Ab and 3Bb of B are appropriately polymerized.

(5) According to the invention of claim 5, claim 4
In the air conditioner described, the plurality of heat exchangers 3
It is characterized in that the refrigerant circulation amounts of A and 3B can be independently controlled.

[0017]

With each of the inventions of the present application having such a configuration, the following actions can be obtained.

(I) In the air conditioner according to the first aspect of the present invention, the distance between the inner circumference of the heat exchanger 3 and the outer circumference of the impeller 20 is located on the front side in the rotation direction of the impeller 20 of the heat exchanger 3. End 3
Since it is set to be small on the a side and large on the other end 3b side located on the rear side, the inner peripheral surface of the heat exchanger 3 acts on the impeller 20 as a scroll portion, Since the air blown out from 20 becomes a swirling flow and smoothly flows toward the heat exchanger 3 side,
Recovery of the dynamic pressure of the flow velocity of the impeller 20 to the static pressure is promoted, and together with the increase in the static pressure obtained in the impeller 20,
A larger static pressure will be obtained (see curve L _{2 in} FIG. 4).

Further, since the inner peripheral surface of the heat exchanger 3 acts as a scroll portion and the air blown out from the impeller 20 becomes a swirling flow, and the distance until it reaches the heat exchanger 3 is long, for example, the impeller. Even if the turbulence of the air blown out of 20 is large, this is sufficiently rectified before reaching the heat exchanger 3 side, and the turbulence is minimized as much as possible.

(Ii) In the air conditioner according to claim 2,
In addition to the operation described above, the one end 3a and the other end 3b of the heat exchanger 3 are configured to be superposed in the circumferential direction, so that, for example, the one end 3a and the other end 3b are opposed to each other in the circumferential direction. In comparison with the above case, the circumferential length of the heat exchanger 3 is increased and the heat transfer area of the heat exchanger 3 is substantially expanded.

(Iii) In the air conditioner according to claim 3,
In addition to the above and described actions, since the shape of the inner peripheral surface of the heat exchanger 3 is a logarithmic spiral curve, the impeller 20
The swirling flow of the air blown out from the blade becomes smoother, and the recovery of the dynamic pressure of the blowout flow velocity of the impeller 20 to the static pressure is further promoted.

(Iv) In the air conditioner according to claim 4,
The plurality of heat exchangers 3A, 3B are both formed in a semi-circular shape, and the inner peripheral surface 3A of the plurality of heat exchangers 3A, 3B goes from one end to the other end.
Since the distance between c and 3Bc and the outer peripheral surface 20a of the impeller 21 is gradually increased, the impeller 20 to the heat exchangers 3A and 3A are similar to the air conditioner according to claim 1.
In addition to smoothing the flow of air toward B to secure a larger static pressure, each heat exchanger 3A, 3B is superposed in the circumferential direction with another heat exchanger 3A, 3B at both ends thereof. Therefore, it is possible to ensure a larger heat transfer area than in the case where the heat exchanger 3 has only one overlapping position in the circumferential direction as in the air conditioner according to the second aspect.

(V) In the air conditioner according to the fifth aspect, in addition to obtaining the action described in (iv) above, the impeller 25
Heat exchangers 3A, 3 arranged so as to surround the outside of the
Since the amount of circulating refrigerant of B can be controlled independently of each other, for example, the temperature of the air blown out via the heat exchangers 3A and 3B corresponding to the difference in the heating / cooling demand at each location in the room. Can be adjusted arbitrarily.

[0024]

Therefore, according to the air conditioner of each invention of the present application, the following effects can be obtained.

According to the air conditioner of the first aspect, the recovery of the dynamic pressure of the blowout flow velocity of the impeller 20 to the static pressure is promoted, and together with the increase in the static pressure obtained in the impeller 20, Since a larger static pressure can be obtained (curve L _{2 in} FIG.
(Refer to), it is possible to secure the required air blowing performance at a lower rotational speed (in other words, at a lower blade peripheral speed) compared with the conventional one, and thereby increase in proportion to the sixth power of the peripheral speed at the blade outlet. The noise generated by the fan is reduced, and the operating noise of the air conditioner as a whole is further reduced (see the curve L _{1 in} FIG. 4).

Further, even if the turbulence of the air blown out from the impeller 20 is large, it is sufficiently rectified by the time it reaches the heat exchanger 3 side, and the turbulence is minimized as much as possible. The one end 3a of the heat exchanger 3 can be arranged closer to the outer circumference of the impeller 20 without worrying about the turbulence of the air flow.
Even if it is largely separated from the outer periphery of 0, for example, the impeller and the heat exchanger are concentrically arranged as in the above-mentioned conventional example, and the space between them is large from the viewpoint of securing a space for rectification. It is possible to reduce the overall radial dimension as compared with the set configuration, and the air conditioner can be made compact accordingly.

According to the air conditioner of claim 2, in addition to the effects described above, one end 3a of the heat exchanger 3
Since the heat transfer area of the heat exchanger 3 can be substantially expanded by making the other end 3b and the other end 3b superposed in the circumferential direction, for example, when the capacity of the heat exchanger 3 is made constant. Can reduce the thickness dimension in the ventilation direction of the heat exchanger 3 to that extent to reduce the in-machine resistance (see the curve L _{2 in} FIG. 4), and as a result, reduce the operating noise.
(Refer to the curve L _{1 in} FIG. 4) or the axial power of the centrifugal fan 2 can be reduced.

According to the air conditioner of the third aspect, in addition to the above and the effects described above, the swirling flow of the air blown out from the impeller 20 is formed by using the shape of the inner peripheral surface of the heat exchanger 3 as a logarithmic spiral curve. Smoother and the impeller 20
By further accelerating the recovery of the dynamic pressure of the blowout flow velocity of the air conditioner to the static pressure, it is possible to further suppress the operation of the air conditioner.

According to the air conditioner of the fourth aspect, in addition to the same effects as the above-described effects, the heat transfer area is increased by increasing the number of circumferentially overlapping portions of the heat exchangers 3A, 3B. Thus, it is possible to secure a still higher static pressure to further reduce the operating noise, and further reduce the internal resistance to achieve power saving.

According to the air conditioner of the fifth aspect, in addition to the above-described effects, more comfortable cooling and heating can be realized by controlling the outlet temperature corresponding to the demand for cooling and heating of the room. It is possible to obtain the effect of further increasing the commercial value of.

[0031]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the accompanying drawings.

First Embodiment FIGS. 1A and 1B show an air conditioner Z _{1 according} to an embodiment of the invention described in claims 1 and 3 of the present application.
The air conditioner Z ₁ is a so-called ceiling-embedded air conditioner that is embedded in the ceiling surface 10 and has a casing 1 that is fixedly arranged in the ceiling surface 10. The casing 1 is provided with a bottom wall member 4 having an air suction port 5 at the center of the lower surface 1a and an outer edge portion 1b of the lower surface 1a.
, Are formed with air outlets 6, 6 ... Inside the casing 1, a centrifugal fan 2 including a motor 8 fixedly supported on the upper surface 1c of the casing 1 and an impeller 20 described later fixed to a rotating shaft 8a of the motor 8 is provided. It is arranged in a state of being located on the axial center of the air suction port 5.

The impeller 20 has a main plate 21 fixed to the rotary shaft 8a of the motor 8 and a side plate 2 having a fan suction port 24 corresponding to the air suction port 5 formed in the central portion thereof.
2 are arranged to face each other at a predetermined interval, and a plurality of curved plate-shaped blades 23, 2 are provided between the main plate 21 and the side plate 22.
.. are arranged at predetermined intervals in the circumferential direction. When the impeller 20 is arranged in the casing 1, the air outlets 6, 6,
· Ventilation path 9 leading to ··· is formed.

Further, a heat exchanger 3 which will be described later is arranged in the casing 1 so as to cross the ventilation passage 9. This heat exchanger 3 has a height dimension H (see FIG. 1A),
The cross fin having a width dimension S (see FIG. 1B) and a predetermined length is wound in an annular shape. In this embodiment, the inner peripheral surface 3c has a logarithmic spiral curve. To form an annular body in which one end 3a and the other end 3b face each other at a predetermined interval by spirally winding from one end 3a to the other end 3b in the lengthwise direction, and a seal plate is provided between the one end 3a and the other end 3b. They are connected by 25. The fin shape of the heat exchanger 3 is preferably a mesh fin with less air collision loss.

The heat exchanger 3 having the above-mentioned structure
Are arranged on the outer peripheral side of the impeller 20 so as to surround them. In this case, in this embodiment, the relative mounting positions of the heat exchanger 3 and the impeller 20 are set to the heat exchanger 3
One end 3a of which is located on the front side in the rotational direction of the impeller 20, and the distance between the inner peripheral surface 3c of the heat exchanger 3 and the outer peripheral surface 20a of the impeller 20 is equal to that of the heat exchanger 3. One end 3a
It is set to be smallest on the side and largest on the other end 3b side. Therefore, in the state in which the heat exchanger 3 is arranged on the outer peripheral side of the impeller 20, the distance between the two goes from the one end 3a of the heat exchanger to the other end 3b of the heat exchanger (in other words, the impeller). It is designed to gradually expand (as it goes to the front side in the rotation direction of 20).

In the air conditioner Z ₁ thus constructed, when the centrifugal fan 2 is operated, the air suction port 5
The air sucked from the impeller 20 to the impeller 20 side has a higher static pressure in the impeller 20 and is blown radially outward from the impeller 20 with a predetermined dynamic pressure. The air blown out from the impeller 20 is
As shown by the streamline A ₁ in FIG. ₁ , after flowing into the heat exchanger 3 side and exchanging heat there to become hot air or cold air, the air is blown toward the indoor side through the air outlets 6, 6 ,. Blown out.

In this case, the inner peripheral surface 3c of the heat exchanger 3 located on the outer side of the impeller 20 is curved in a logarithmic spiral curve which gradually and smoothly departs from the inner peripheral surface 3c toward the front side in the rotational direction of the impeller 20. Since the impeller 20 acts as a kind of scroll portion on the impeller 20, the air blown out from the impeller 20 follows the inner peripheral surface 3c as shown by the streamline A ₂ in FIG. 1B. It becomes a turning flow. As a result, the recovery of the dynamic pressure of the flow velocity of the impeller 20 to the static pressure is promoted, and the static pressure of the air is the sum of the amount of increase in the impeller 20 and the amount of recovery from this dynamic pressure, The blown air has a higher static pressure than in the case of a structure in which the recovery of the dynamic pressure to the static pressure can hardly be expected as in the conventional case. Therefore, when the air blowing performance of the centrifugal fan 2 is constant, the rotational speed of the centrifugal fan 2 can be reduced to lower the peripheral speed of the impeller 20 as compared with that of the conventional structure, and as a result, the noise generated by the fan is reduced. The operating noise of the air conditioner Z ₁ as a whole is reduced as much as possible.

On the other hand, since the air blown out from the impeller 20 becomes a swirling flow and it takes a relatively long time to reach the inner peripheral surface 3c of the heat exchanger 3, for example, the impeller 2
Even if the turbulence of the air blown out from 0 is large, it will be sufficiently rectified by the time it reaches the inner peripheral surface 3c of the heat exchanger 3. Therefore, in order to rectify the flow between the impeller 20 and the heat exchanger 3 in a direction close to the radial direction of the impeller 20 (see streamline A _{0 in} FIG. 6) as in the conventional air conditioner. It is not necessary to provide a relatively large space for the outer peripheral surface 2 of the impeller 20 so that the one end 3a side of the heat exchanger 3 is further extended.
It can approach 0a. As a result, even if the gap between the impeller 20 and the heat exchanger 3 is open on the side of the other end 3b of the heat exchanger 3, as a whole, the impeller 20 and the portion of the heat exchanger 3 in the radial direction are viewed. The size can be reduced, and the air conditioner Z ₁ can be made compact accordingly.

Second Embodiment FIG. 2 shows an air conditioner Z _{2 according} to an embodiment of the invention described in claims 1 to 3 of the present application. The structure of this embodiment is basically the same as that of the first embodiment,
From the viewpoint of enlarging the heat transfer area of the heat exchanger 3 and lowering the internal resistance thereof, the invention of claim 3 is applied to devise the shape of the heat exchanger 3.

That is, in the heat exchanger 3 of this embodiment, the one of the first embodiment has one end 3a and the other end 3b of the heat exchanger 3 opposed to each other at a predetermined interval in the circumferential direction (in other words, The heat exchanger 3 is provided only in an angular range of 360 ° or less around the axis of the centrifugal fan 2), while the one end 3a and the other end 3b of the heat exchanger 3 are appropriately arranged in the circumferential direction. The heat exchanger 3 is formed so as to be superposed on the centrifugal fan 2 in an angular range of 360 ° or more around the axis of the centrifugal fan 2.

In this case, the effective length of the heat exchanger 3 is increased and its substantial heat transfer area is expanded, as compared with the case of the structure of the first embodiment, for example. Therefore, for example, when the heat exchange capacity is constant, the thickness dimension S ₀ in the ventilation direction can be reduced by the expansion of the heat transfer area to reduce the in-machine resistance. As a result, it is possible to reduce the rotational speed of the centrifugal fan 2, suppress the fan-generated sound (that is, the operating sound of the air conditioner Z ₂ ), and reduce the shaft power thereof.

Third Embodiment FIG. 3 shows an air conditioner Z _{3 according} to an embodiment of the present invention as defined in claims 4 and 5 of the present application. In the air conditioner Z ₃ of this embodiment, the heat exchanger 3 of the second embodiment is used.
From the standpoint of expanding the heat transfer area of the heat exchanger and lowering the internal resistance thereof, one end 3a and the other end 3b of the annular heat exchanger 3 were appropriately polymerized in the circumferential direction. In order to further promote the effect of expanding the heat transfer area due to the polymerization of the exchanger, the invention according to claim 4 is applied to the heat exchangers, that is, the first heat exchanger 3A and the second heat exchanger that are curved in a substantially semi-circular shape. The heat exchanger 3B is composed of two heat exchangers, and the inner peripheral surfaces 3Ac, 3Bc of the heat exchangers 3A, 3B gradually move toward the other ends 3Aa, 3Ba toward the other ends 3Ab, 3Bb. The one end 3Aa of the first heat exchanger 3A and the other end 3Bb of the second heat exchanger 3B, and the one end 3Ba of the second heat exchanger 3B and the first heat exchanger 3A are moved away from the outer peripheral surface of the vehicle 20. The other end 3Ab is overlapped with each other by an appropriate size in the circumferential direction. It is arranged like this.

In the case of such a configuration, the outer peripheral surface 20a of the impeller 20 and each of the heat exchangers 3 as in the above embodiments.
The air blown out from the impeller 20 is smoothly heated without causing turbulence in the flow by gradually increasing the distance between the inner peripheral surfaces 3Ac and 3Bc of A and 3B toward the front in the impeller rotation direction. It goes without saying that a higher static pressure is ensured by flowing into the exchangers 3A, 3B and the noise generated by the fan can be reduced as much as possible, but in addition to this, the heat exchangers 3A, 3B are also added.
Since the overlapping portions of the two heat exchangers 3A and 3B are located at both ends of the heat exchangers 3A and 3B, the heat transfer is larger than the case where the overlapping portion of the heat exchanger is a single portion as in the second embodiment. It is possible to secure an area, and as a result, it is possible to further reduce the fan-generated noise and the shaft power by lowering the in-machine resistance more than that of the second embodiment due to the large heat transfer area. Is.

On the other hand, in this embodiment, the invention described in claim 5 is applied so that the amount of circulating refrigerant in each of the heat exchangers 3A and 3B can be independently controlled. In such a case, for example, when the degree of demand of heating and cooling in the room is different in each part, a large amount of refrigerant is circulated through the heat exchanger 3A or 3B corresponding to the portion with the high demand of heating and cooling. Heat exchanger 3B that enhances the capacity and, conversely, corresponds to the part with a small degree of demand
Alternatively, by circulating a small amount of refrigerant in the same 3A to suppress the cooling / heating capacity, comfortable cooling / heating operation that meets actual cooling / heating requirements can be achieved, which in turn can contribute to improving the commercial value of the air conditioner Z _3. Is.

In this embodiment, the first heat exchanger 3
Although A and the second heat exchanger 3B constitute a ring-shaped heat exchanger, in another embodiment, it may be constituted by three or more heat exchangers.

[Brief description of drawings]

FIG. 1A is a vertical cross-sectional view of an air conditioner according to a first embodiment of the present invention.

1B is a view taken in the direction of arrows I-I in FIG. 1A.

FIG. 2 is a sectional view of an essential part of an air conditioner according to a second embodiment of the present invention.

FIG. 3 is a sectional view of an essential part of an air conditioner according to a third embodiment of the present invention.

FIG. 4 is an air volume-static pressure / specific noise characteristic diagram.

FIG. 5 is a vertical cross-sectional view of a conventional air conditioner.

6 is a view taken along the line VI-VI in FIG.

[Explanation of symbols]

1 is a casing, 2 is a centrifugal fan, 3, 3A and 3B are heat exchangers, 4 is a bottom wall member, 5 is an air inlet, 6 is an air outlet, 8 is a motor, 9 is an air passage, 10 is a ceiling surface. , 20
Is an impeller, 21 is a main plate, 22 is a side plate, 23 is a blade, 24
Is a fan suction port, and 25 is a seal plate.

Claims (1)

Claims: 1. A casing (1) having an air inlet (5) formed on a lower surface (1a) and an air outlet (6) formed on a side surface or an outer peripheral portion (1b) of the lower surface (1a). Inside, multiple blades (23), (23),
A centrifugal fan or a mixed flow fan (2) having an impeller (20) provided with is installed while facing the air suction port (5), while the centrifugal fan or mixed flow fan (2) is installed.
A heat exchanger (3) formed by winding in an annular shape on the outer peripheral side so that one end (3a) and the other end (3b) thereof are close to each other.
Are arranged so as to surround the outer peripheral side of the centrifugal fan or the mixed flow fan (2), and the air blown from the centrifugal fan or the mixed flow fan (2) outward in the radial direction is transferred to the heat exchanger. An air conditioner adapted to blow out from the air outlet (6) to the indoor side via (3), the outer peripheral surface (20a) of an impeller (20) of the centrifugal fan or mixed flow fan (2).
The distance between the heat exchanger (3) and the inner peripheral surface (3c) of the heat exchanger (3) is small at one end (3a) side of the heat exchanger (3) located on the front side in the rotation direction of the impeller (20), An air conditioner characterized in that it is set to be larger on the other end (3b) side located on the rear side in the rotation direction. 2. The air according to claim 1, wherein one end (3a) and the other end (3b) of the heat exchanger (3) are configured to overlap each other in the circumferential direction. Harmony device. 3. The air conditioner according to claim 1, wherein the inner peripheral surface (3c) of the heat exchanger (3) has a logarithmic spiral curve. 4. A casing (1) having an air inlet (5) on the lower surface (1a) and an air outlet (6) on the side surface or the outer peripheral portion (1b) of the lower surface (1a). Wings (23), (23),
A centrifugal fan or a mixed flow fan (2) having an impeller (20) provided with is installed while facing the air suction port (5), while the centrifugal fan or mixed flow fan (2) is installed.
A heat exchanger (3) is arranged on the outer peripheral side of the centrifugal fan or the mixed flow fan (2) so as to surround the outer peripheral side of the centrifugal fan or the mixed flow fan (2), and the heat exchanger (3) is radially outward from the centrifugal fan or the mixed flow fan (2). Air blown to the air is blown through the heat exchanger (3) into the air outlet.
An air conditioner adapted to blow out from (6) to the indoor side, wherein the heat exchanger (3) is composed of a plurality of heat exchangers (3A) and (3B) curved in an arc shape. , The heat exchangers (3A) and (3B) have inner surface (3A)
c), (3Bc) and the outer circumference of the impeller (20) of the centrifugal fan or mixed flow fan (2) are such that the heat exchangers (3A), (3)
B) is small on one end (3Aa), (3Ba) side located on the front side in the rotation direction of the impeller (20), and is large on the other end (3Ab), (3Bb) side located on the rear side in the rotation direction, Further, in the circumferential direction, one end (3Aa), (3Ba) of each heat exchanger (3A), (3B) is located on the rear side in the rotation direction of the impeller (20) from the heat exchanger (3A), (3B). ) Other end (3A
An air conditioner characterized in that b) and (3Bb) are appropriately polymerized. 5. The plurality of heat exchangers (3) according to claim 4,
An air conditioner characterized in that the refrigerant circulation amounts of A) and (3B) can be independently controlled.