JPH10306927A - Air handling unit type air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air handling unit type air conditioner, capable of obtaining an effective cooling and heating capacity without increasing a pressure loss or the axial power of a fan and the generation of noise, which are accompanied by the increase of the pressure loss, even when the size of height of a main body casing is reduced. SOLUTION: An air handling unit type air conditioner is provided with a main body casing 1, whose internal space is divided by a heat exchanging coil 3 into first and second flow passages 12, 13, while either one or both of outdoor air suction ports 10a, communicating with outdoor space, and an indoor air ventilating port 10b, communicating with indoor space, are provided on the upper part of the first flow passage 12 and an air supplying port 10c, communicating with the indoor space, is provided on the upper part of the second flow passage 13. In such an air handling unit type air conditioner, a dual suction type centrifugal fan 6 is provided at the vicinity of a central part in the up-and- down direction of the second flow passage 13 while the air outlet port 6b of the fan 6 is connected to the upper side air supplying port 10c through a duct 21, whose sectional area of passage is enlarged gradually.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air handling unit type air conditioner.

[0002]

2. Description of the Related Art An air conditioner of an air handling unit type generally comprises a heat exchange coil for heating and cooling, a humidifier, etc. integrally incorporated in a main body casing. There is an inflatable type (for example, see JP-A-63-91438).

Conventionally, as such an air handling unit type air conditioner, there is a first conventional example shown in FIGS. 13 and 14, for example.

In this conventional example, as shown in the figure, a blower storage space a having a predetermined vertical width is left in an upper part in a box-shaped casing 1 which is long in the vertical and horizontal directions, and a heat exchange coil storage space b in a lower part. And a cold water coil 3A, a hot water coil 3 and a pre-filter 2A and a main filter 2B at a substantially central portion in the left-right direction of the lower heat exchange coil storage space b.
The heat exchange coil 3 made of B and the humidifier 4 are arranged substantially integrally and side by side. Thereby, the heat exchange coil storage space b is divided into two vertically long first and second flow paths (upstream-side ventilation space) 12 and a second flow path (downstream-side ventilation space) 13 therebetween. It is divided into spaces.

[0005] Further, the blower accommodating space a is provided above the main filter 2B and the chilled water coil 3A by a partition wall 5 through an external air supply duct 1 through an external air supply duct.
The space is divided into two spaces, an air suction space 11 for sucking the air from Oa and the recirculating inside air from the inside air return port 10b, and a blower installation space 14. The air suction space 11 communicates with the first flow path (upstream air blowing space) 12,
The first flow path (upstream air blowing space) is drawn by sucking air supplied from the outside air suction port 10a via the air supply duct and recirculating inside air supplied from the inside air return air port 10b.
12

[0006] In the blower installation space 14,
As shown in the figure, a centrifugal blower 6 is provided, and the centrifugal blower 6 removes air from the first flow path (upstream side ventilation space) 12 on the upstream side of the heat exchange coil 3 to the pre-filter 2.
A, main filter 2B, heat exchange coil (cold water coil 3
A, the hot water coil 3B), dust removal, heat exchange, and humidification through the humidifier 4 and then sucked from the second downstream flow path (downstream ventilation space) 13 as shown by a chain line arrow in FIG. The air is blown into the room from the air outlet 6b of the centrifugal blower 6 through the air supply duct.

The centrifugal blower 6 is formed by a double suction type having, for example, first and second two air suction ports 6c and 6d in the left-right axial direction, and the first and second suction ports 6c are formed. , 6d, a multi-blade blower (so-called sirocco fan) for blowing air from the air outlet 6b of the spiral rotor housing 6a having a tongue portion and a scroll portion in a direction substantially orthogonal to the rotation axis of the fan rotor. The rotation is driven by a fan drive motor 6e directly connected to the rotation axis of the fan rotor. FIG.
Shows an example of the structure of an actual product of the first conventional example.

That is, in the configuration of the first conventional example, as is apparent from the configurations of FIGS. 13 to 15, a blower installation space 14 having a predetermined vertical width is provided above the upper end of the heat exchange coil 3. A double suction centrifugal blower 6 and a fan drive motor 6e directly connected thereto are provided.

However, in the case of an air handling unit type air conditioner having such a structure, the height of the blower housing space a is added in addition to the height of the heat exchange coil 3, so that the overall height is considerably high. There are disadvantages that can be significant. Further, the air flow flowing from above through the outside air suction port 10a and the inside air return air port 10b into the first flow path 12 which is the upstream side ventilation space cannot change its direction suddenly. A region having a low passing flow velocity is generated near the upper part (a) of the heat exchange coil 3.

Furthermore, despite the fact that the dimension of the heat exchange coil 3 in the height direction is originally longer than that in the width direction,
Since the centrifugal blower 6 is located above the main body casing 1, air cannot pass around the lower part (b) of the heat exchange coil 3 and flow therethrough. (B) also has a region where the flow velocity is low.
As a result, a velocity distribution in which the difference between the maximum passage velocity and the minimum passage velocity is large occurs in the flow passing through the heat exchange coil 3, resulting in an increase in pressure loss.

In order to solve such a problem, there is a second conventional example shown in FIGS. That is, in the configuration of the conventional example, for example, the internal space of the entire main body casing 1 is changed to, for example, the bottom plate 1a.
Is divided into first and second two flow paths 12 and 13 by a heat exchange coil 3 having a height from
Outside air suction port 10 communicating with the outside of the room above the first flow path 12
a and one or both of the inside air return air ports 10b communicating with the inside of the room and the air supply port 10c communicating with the inside of the room at the upper part of the second flow path 13, while the double suction centrifugal blower 6 described above is provided. Is driven by the lower fan motor 6e via the belt 6f to shorten the axial length, so that the scroll side of the rotor housing 6a is arranged above the downstream side of the heat exchange coil 3 so as to face the rear side. The air outlet 6b is fitted and installed in the air supply port 10c such that the air outlet 6b is substantially equal to the upper end position of the heat exchange coil 3.

With such a configuration, the space for installing the blower as in the first conventional example is eliminated and the blower can be lowered, so that the size of the main body casing 1 in the height direction can be reduced. Can be. Then, the centrifugal blower 6 is moved in the lower (b) direction of the heat exchange coil 3.
As shown in the figure, air can flow around the lower (b) portion of the heat exchange coil 3 as shown in FIG.

[0013]

However, in the case of the configuration of the second conventional example, if the depth dimension of the main body casing 1 is not enlarged for compactness, the centrifugal blower 6
The front and rear side walls of the main body casing 1 exist immediately before the air suction ports 6c and 6d.
The suction pressure loss increases due to the small interval between the heat exchange coil 3 and the side wall portion, while the scroll wall of the rotor housing 6a of the centrifugal blower 6 exists immediately near the upper part (a) of the heat exchange coil 3. Therefore, the air passing through the portion immediately before the rotor housing 6a through the heat exchange coil 3 flows around the outer periphery of the scroll wall of the rotor housing 6a as shown in, for example, an enlarged view of FIG. Therefore, it is necessary to turn around at a steep angle in the direction of the air inlets 6c and 6d, so that it is impossible to prevent the generation of the area where the flow velocity is small in the upper area (a) of the heat exchange coil 3 as well. Therefore, the flow passing through the heat exchange coil 3 has a velocity distribution, and the pressure loss of the heat exchange coil 3 increases. Reference numeral 6g in the figure indicates a fan rotor of the centrifugal blower 6.

[0014] Such a velocity distribution generated in the flow passing through the heat exchange coil unit causes deterioration of the cooling and heating capacity.

The present invention has been made in view of the above circumstances, and even when the size in the height direction of the main body casing is reduced as described above, the suction pressure loss increases, the air flow velocity distribution deteriorates, and It is an object of the present invention to provide an air handling unit type air conditioner capable of reducing the height dimension of a main body casing without causing a decrease in cooling / heating capacity, an increase in blower shaft power, an increase in generated noise, and the like. Is what you do.

[0016]

Means for Solving the Problems In order to achieve the above object, the present invention is provided with the following means for solving the problems.

That is, in the air handling unit type air conditioner of the present invention, as shown in FIGS. 1 to 12, for example, the internal space of the main body casing is divided into first and second two flow paths by a heat exchange coil. One or both of an outside air suction port communicating with the outside of the room and an inside air return air port communicating with the inside of the room are provided at the upper part of the first flow path, and a supply path communicating with the room at the upper part of the second flow path is provided. In an air handling unit type air conditioner provided with air vents, a double suction type centrifugal blower is provided near the center in the vertical direction of the second flow path, and the air outlet of the air suction port is provided to the upper air supply port. , Which are connected via a duct that gradually increases the cross-sectional area of the passage.

As described above, the air conditioner according to the present invention first divides the internal space of the main body casing into first and second flow paths by means of a heat exchange coil, and One or both of an outside air suction port communicating with the outside and an inside air return port communicating with the inside of the room are provided, and an air handling unit type having an air supply port communicating with the inside of the room above the second flow path. In the air conditioner, the second
A double suction centrifugal blower is provided in the vicinity of the center in the vertical direction of the flow path, and its air outlet is connected to the upper air supply port via a duct that gradually enlarges the cross-sectional area of the passage.

That is, in this configuration, the double suction type centrifugal blower is installed in the second flow path in a state where the position in the height direction is located near the center of the heat exchange coil. Therefore, the height dimension of the main casing can be sufficiently reduced. Moreover, the space formed between the air outlet of the lower centrifugal blower and the air supply port at the upper part of the upper main body casing is connected by a duct having a diffuser structure that gradually enlarges the cross-sectional area of the passage. The flow velocity of the air blown out from the air outlet of the blower is reduced in the duct portion where the cross-sectional area of the passage gradually increases, and the dynamic pressure on the outlet side of the centrifugal blower is efficiently converted to static pressure. This makes it possible to compensate for the increase in the suction pressure loss at the air suction port described above, thereby preventing deterioration in the speed distribution and increases in the power of the blower shaft and noise.

Further, since the centrifugal blower is located near the center of the heat exchange coil, the streamline of the air passing through the upper part of the heat exchange coil and reaching the blower becomes gentler, and the heat exchange coil can be more effectively formed. The flow velocity distribution of the passing air can be made uniform. Further, in the portion where the rotor housing of the centrifugal blower is located immediately after the heat exchange coil, it becomes easier for air to flow around the centrifugal blower while avoiding the rotor housing toward the air suction port. The flow velocity distribution can be made even more uniform.

As a result, the installation area can be reduced without increasing the pressure loss, consequently increasing the power of the blower shaft and increasing the noise generated.

Further, in the above configuration, if a round surface is formed in the rotor housing corner portion of the centrifugal blower main body as shown in FIG. 3, for example, the above-mentioned air stream line becomes more gentle, and the above-described operation is more effectively performed. Can be obtained effectively. Therefore, the apparatus can be made more compact.

In the case where the duct is provided as described above, the duct is formed separately from the rotor housing of the centrifugal blower as shown in FIGS. 1 and 2, for example. The base end having the smaller passage cross-sectional area may be connected to the air outlet of the rotor housing, or may be formed integrally with the rotor housing itself as shown in FIGS. With the former configuration, the duct itself is relatively easy to manufacture, and with the latter configuration, the configuration is simple, the number of parts is reduced, and connection work with the rotor housing is unnecessary.

Further, in the case where the above-described configuration is employed, the air inlet of the centrifugal blower rotor housing is swaged at its edge as shown in FIGS. Are integrally formed, or a bell mouth formed by a separate member is attached as shown in FIG. By doing so, separation of the flow of the air sucked from the air suction port of the rotor housing to the fan rotor side is reduced, the flow velocity distribution is made uniform, and the air suction resistance is reduced. Therefore, the blowing performance is improved and the noise is reduced.

[0025]

As described above, according to the air handling unit type air conditioner of the present invention, even when the size of the main casing is reduced in the height direction, the pressure loss of the heat exchange coil portion increases and the flow velocity distribution accompanying the pressure loss increases. It is possible to provide a compact and low-cost air-handling unit type air conditioner that can have a sufficiently small installation area without causing non-uniformity of the air conditioner, an increase in blower shaft power and noise, and the like. .

[0026]

BEST MODE FOR CARRYING OUT THE INVENTION

(Embodiment 1) FIGS. 1 to 3 show a configuration of an air handling unit type air conditioner according to Embodiment 1 of the present invention.

In the drawing, reference numeral 1 denotes a flat box-shaped main body casing of the air conditioner, and the internal space of the main body casing 1 has a height from the vicinity of the bottom plate 1a to the vicinity of the top plate 1b. Chilled water coil 3A having a large aspect ratio
And the heat exchange coil 3 composed of the hot water coil 3B,
It is divided into an upstream first flow path 12 and a downstream second flow path 13. A filter section composed of a pre-filter 2A and a main filter 2B is provided immediately before the heat exchange coil 3, and a humidifier 4 is provided immediately after the heat exchange coil 3 in a substantially integrated structure in a side-by-side state. is set up. The heat exchange coil 3 is further appropriately provided with a distribution header, a cold / hot water pipe, a two-way valve, etc., but is omitted in each figure for simplification of description.

An outside air suction port 10a communicating with the outside of the room and an inside air return air port 10b communicating with the inside of the room (or any one of them) are provided above the first flow path 12, and a second flow path 13 is provided. Are provided with air supply ports 10c communicating with the room. Further, in the second flow path 13, the multi-blade double-suction centrifugal blower 6 provided with the first and second two air suction ports 6c and 6d on both sides of the rotor housing 6a similar to the conventional one is provided with the above-described first flow path. 1, second air suction port 6c, 6
d face the front and rear side plates of the main body casing 1, respectively, and the air outlet 6b is connected to the upper air supply port 10c.
, And in the main body casing 1,
The air suction ports 6c and 6d are installed such that the position in the height direction of the center of the air suction ports 6c and 6d is located slightly above the center of the heat exchange coil 3. Here, the centrifugal blower 6
Is fixed to, for example, a mount having a frame structure with good ventilation, but is omitted in the figure. The bearings and the like for supporting the rotating shaft 15 of the centrifugal blower 6 are also not shown in detail in the drawing.

The centrifugal blower 6 has a fan drive motor 6e provided at a lower portion of the main body of the centrifugal blower 6 by a predetermined distance, and is driven by a belt 6f and pulleys 19A and 19B. The fan drive motor 6e is fixed to, for example, a frame-structured base similarly to the centrifugal blower 6, but is also omitted in the drawings for simplification of description. Similarly, a table for fixing the pulley 19B is also omitted from the drawing. With such a belt drive configuration, the axial length of the fan rotor of the centrifugal blower 6 is reduced, and the centrifugal blower 6
, The air is easily sucked into the second air suction port 6d.

The belt 6f may be of any type, such as a V-belt or a toothed belt, but it is needless to say that the belt 6f preferably has high transmission efficiency and low driving noise.

The pulley 19A on the centrifugal blower 6 side
Have a plurality of fan-shaped holes 20, 20.
.. The structure is formed with As a result, the air sucked from the second air suction port 6d is removed from the holes 2d.
2 and 3, the pulley 19A is installed immediately before the second air suction port 6d of the centrifugal blower 6 as much as possible, as shown in FIGS. Even if the axial length is shortened, the effect of equalizing the flow velocity distribution of the flow passing through the centrifugal blower 6 can be maintained, and the blower performance does not deteriorate.

Then, the centrifugal blowers 6 opposed to each other
As shown in FIGS. 1 and 2, the passage cross-sectional area is gradually increased upward by inclining the tongue side wall surface 22 between the air outlet 6b and the air supply port 10c in the upper part of the main body casing 1. Are connected by a duct 21 having a diffuser structure. As a result, the air outlet 6 of the centrifugal blower 6
The flow velocity of the air blown from b is reduced in the duct 21 and the dynamic pressure at the outlet side of the centrifugal blower 6 is efficiently converted into static pressure. It will be higher than the static pressure of the centrifugal blower 6 alone. As a result, an increase in suction pressure loss due to a narrow flow passage area between the air suction ports 6c and 6d and the front and rear side plates of the main casing 1 can be compensated.

Further, since the centrifugal blower 6 is located near the center of the heat exchange coil 3, the flow line of the air passing through the upper part of the heat exchange coil 3 and reaching the centrifugal blower 6 becomes gentler, so that it is more effective. Thus, the flow velocity distribution of the air passing through the heat exchange coil 3 can be made uniform. Further, in a portion where the rotor housing 6a of the centrifugal blower 6 exists immediately after the heat exchange coil 3, air is
Toward the air suction ports 6c and 6d of the rotor housing 6
Since it is easy to turn around while avoiding a, the flow velocity distribution of the air passing through the heat exchange coil can be further uniformed.

As a result, the installation area can be reduced without increasing the pressure loss, concomitantly increasing the power of the blower shaft and increasing the noise generated.

In the above case, if the corner portion on the heat exchange coil 3 side of the rotor housing 6a of the centrifugal blower 6 is formed on a round surface as shown in FIG. 3, for example, the heat exchange coil 3 is connected to the air inlets 6c and 6d. The streamline of the incoming air becomes gentle, and the above operation becomes more effective.

By the way, in the configuration of the first embodiment shown in FIG. 1, the duct 21 inclines and scrolls on the tongue side between the air outlet 6b of the centrifugal blower 6 and the air supply port 10c on the upper part of the main body casing 1. Although it is straightly connected on the side, this shape can be changed to any shape as long as the static pressure conversion performance of the duct 21 is not impaired.

For example, the passage cross-sectional area of the duct 21 may be expanded in both the left and right width directions of the main body casing 1, or may be expanded in one or both of the front and rear depth directions. The former case is effective when the aspect ratio of the heat exchange coil 3 is considerably large and the depth dimension cannot be increased.

Further, for the same purpose, one of the tongue side wall surface and the scroll side wall surface of the rotor housing 6a of the centrifugal blower 6 of the duct 21 or both of them is substantially arc-shaped in the downstream direction of the flow path. The diameter can also be increased so as to have a shape. In such a thing,
Due to the Coanda effect in the downstream direction of the air flow, the separation of the flow from the wall surface is suppressed, and the area ratio of the inlet and the outlet of the duct 21 in the depth direction of the main casing 1 can be further increased. The effect is improved.

Further, in the above configuration, the centrifugal blower 6 is installed so that the scroll side wall surface faces the heat exchange coil 3 in order to swirl the inflow air in the rotation direction of the fan rotor. On the contrary, it can be installed so that the tongue side walls face each other. Also,
The radius of the corner of the rotor housing 6a is as follows:
As shown in FIG. 3, it is preferable to form it on both the scroll side and the tongue side.

(Embodiment 2) FIGS. 4 to 8 show the configuration of an air handling unit type air conditioner according to Embodiment 2 of the present invention.

In the figure, reference numeral 1 denotes a flat box-shaped main body casing similar to that of the first embodiment of the air conditioner, and the inner space of the main body casing 1 is
a cold water coil 3A and a hot water coil 3B having a height from near a to near the top plate 1b and having a large aspect ratio.
The upstream first flow path 12 is formed by the heat exchange coil 3 composed of
And a second downstream flow path 13. A filter section composed of a pre-filter 2A and a main filter 2B is provided immediately before the heat exchange coil 3, and a humidifier 4 is provided immediately after the heat exchange coil 3 in a substantially integrated structure in a side-by-side state. is set up. The heat exchange coil 3 is further appropriately provided with a distribution header, a cold / hot water pipe, a two-way valve, etc., but is omitted in each figure for simplification of description.

An upper portion of the first flow path 12 has an outside air suction port 10a communicating with the outside of the room and an inside air return air port 10b (or one of them) communicating with the inside of the room, and a second flow path 13a. Are provided with air supply ports 10c communicating with the room. Further, in the second flow path 13, a multi-blade double suction centrifugal blower 6 having first and second two air suction ports 6c and 6d provided on both side plates of a rotor housing 6a similar to the conventional one is provided. Have been. The centrifugal blower 6
The first and second air suction ports 6c and 6d face the front and rear side plates of the main body casing 1, respectively, and the air outlet 6b is connected to the upper air supply port 10c via a duct 21 described later. And the center of the first and second air suction ports 6c and 6d in the body casing 1 in the height direction is positioned slightly higher than the center of the heat exchange coil 3. Installed. The edge portions of the first and second air suction ports 6c and 6d are swaged inwardly as shown in FIG. 7 to form bell mouths 41 and 41. Here, the centrifugal blower 6 is fixed to a mount having a frame structure having good ventilation, for example, but is omitted in the figure. The bearings and the like for supporting the rotating shaft 15 of the centrifugal blower 6 are also not shown in detail in the drawing.

The centrifugal blower 6 has a fan drive motor 6e installed at a lower portion of the main body of the centrifugal blower 6 by a predetermined distance, and is driven by a belt 6f and pulleys 19A and 19B. The fan drive motor 6e is fixed to, for example, a frame-structured base similarly to the centrifugal blower 6, but is also omitted in the drawings for simplification of description. Similarly, a table for fixing the pulley 19B is also omitted from the drawing. With such a belt drive configuration, the axial length of the fan rotor of the centrifugal blower 6 is reduced, and the centrifugal blower 6
, The air is easily sucked into the second air suction port 6d.

The belt 6f may be of any type, such as a V-belt or a toothed belt, but it is needless to say that the belt 6f preferably has high transmission efficiency and low driving noise.

The pulley 19A on the centrifugal blower 6 side
Have a plurality of fan-shaped holes 20, 20.
.. The structure is formed with As a result, the air sucked from the second air suction port 6d is removed from the holes 2d.
4 and 5, the pulley 19A is installed immediately before the second air suction port 6d of the centrifugal blower 6, as shown in FIGS. Even if the axial length is shortened, the effect of equalizing the flow velocity distribution of the flow passing through the centrifugal blower 6 can be maintained, and the blower performance does not deteriorate.

A connection passage extending from the air outlet 6b of the rotor housing 6a of the centrifugal blower 6 to the air supply port 10c on the upper part of the main body casing 1 has a rotor as shown in FIGS. 4 and 5, for example. A duct 21 having a diffuser structure in which the cross-sectional area of the passage is gradually increased upward by gradually inclining the tongue side wall surface 22 of the housing 6a to the side is provided. The duct 21 is formed integrally with the rotor housing 6a as shown in FIGS. As a result, the flow rate of the air blown from the air outlet 6b of the centrifugal
The static pressure at the outlet of the duct 21 is higher than the static pressure of the centrifugal blower 6 alone, since the internal pressure is decelerated and the dynamic pressure at the outlet side of the centrifugal blower 6 is efficiently converted into static pressure. Will be. As a result, it is possible to compensate for an increase in suction pressure loss caused by a narrow flow passage area between the first and second air suction ports 6c and 6d and the front and rear side plates of the main body casing 1.

Further, since the centrifugal blower 6 is located near the center of the heat exchange coil 3, the streamline of the air passing through the upper part of the heat exchange coil 3 and reaching the centrifugal blower 6 becomes gentler, which is more effective. Thus, the flow velocity distribution of the air passing through the heat exchange coil 3 can be made uniform. Further, in a portion where the rotor housing 6a of the centrifugal blower 6 exists immediately after the heat exchange coil 3, air is
It is easy to wrap around the first and second air suction ports 6c and 6d while avoiding the rotor housing 6a, so that the flow velocity distribution of the air passing through the heat exchange coil can be further uniformed. it can.

As a result, the installation area can be reduced without increasing the pressure loss, the accompanying increase in the power of the blower shaft, and the increase in generated noise.

Further, in the above configuration, since the duct 21 is formed integrally with the rotor housing 6a of the centrifugal blower 6, the configuration can be simplified, the cost can be reduced, and the number of assembly steps can be reduced. it can.

Further, in the above configuration, FIGS.
As shown in the figure, the rotor housing 6a of the centrifugal blower 6
Of the first and second air suction ports 6c and 6d are formed with a round surface on the inside to form a bell mouth of an integral structure. Separation of the air flow reaching the fan rotor via the second air inlets 6c and 6d is reduced, the flow velocity distribution is made uniform, and the air resistance is reduced. As a result, the above action becomes more effective.

In the above case, if the corner portion on the heat exchange coil 3 side of the rotor housing 6a of the centrifugal blower 6 is formed on the round surface in the same manner as in the case of FIG. The streamlines of the air from the coil 3 to the first and second air suction ports 6c and 6d become gentle, so that the above-described operation is more effective.

In the above configuration, the duct 21 connects the air outlet 6b of the centrifugal blower 6 and the air supply port 10c in the upper part of the main body casing 1 at the tongue side and straightly at the scroll side. However, this shape can be changed to an arbitrary shape as long as the static pressure conversion performance of the duct 21 is not impaired.

For example, the passage cross-sectional area of the duct 21 may be expanded in both the left and right width directions of the main body casing 1 or may be expanded in one or both of the front and rear depth directions. The former case is effective when the aspect ratio of the heat exchange coil 3 is considerably large and the depth dimension cannot be increased.

Further, for the same purpose, either one of the tongue side wall surface and the scroll side wall surface of the rotor housing 6a of the centrifugal blower 6 of the duct 21 or both of them are substantially arc-shaped in the downstream direction of the flow path. The diameter can also be increased so as to have a shape. In such a thing,
Due to the Coanda effect in the downstream direction of the air flow, separation from the wall surface of the flow is suppressed, and the area ratio between the inlet and the outlet of the duct 21 in the depth direction of the main casing 1 can be further increased. The effect is improved.

Furthermore, in the above configuration, the centrifugal blower 6 is installed so that the scroll side wall surface faces the heat exchange coil 3 in order to swirl the inflow air in the rotation direction of the fan rotor. On the contrary, it can be installed so that the tongue side walls face each other. Also,
The radius of the corner of the rotor housing 6a is as follows:
Preferably, it is formed on both the scroll side and the tongue side.

Further, the above-mentioned bell mouth 41 provided at the first and second air suction ports 6c and 6d,
For example, as shown in FIG. 8, the air inlet openings 40, 40 formed in the both side plates 39, 39 of the rotor housing 6a are provided with a round surface shape inside the same rotor housing previously formed by a separate member. The bell mouths 41, 41 may be provided by screwing each other with bolts 42, 42 and nuts 43, 43.

(Embodiment 3) FIGS. 9 and 10 show the configuration of an air handling unit type air conditioner according to Embodiment 3 of the present invention.

In the figure, reference numeral 1 denotes a flat box-shaped main body casing of the air conditioner. The internal space of the main body casing 1 has a height from the vicinity of the bottom plate 1a to the vicinity of the top plate 1b. Chilled water coil 3A having a large aspect ratio
And the heat exchange coil 3 composed of the hot water coil 3B,
It is divided into an upstream first flow path 12 and a downstream second flow path 13. A filter section composed of a pre-filter 2A and a main filter 2B is provided immediately before the heat exchange coil 3, and a humidifier 4 is provided immediately after the heat exchange coil 3 in a substantially integrated structure in a side-by-side state. is set up. The heat exchange coil 3 is further appropriately provided with a distribution header, a cold / hot water pipe, a two-way valve, etc., but is omitted in each figure for simplification of description.

An upper portion of the first flow path 12 is provided with an outside air suction port 10a communicating with the outside of the room and an inside air return air port 10b (or any one of them) communicating with the inside of the room. In the upper part of the air supply port, an air supply port 10c is provided, which communicates and opens into the room. And further, the second flow path 1
3, a multi-blade double-suction centrifugal blower 6 having first and second two air suction ports 6c and 6d on both sides of a rotor housing 6a similar to the conventional one is provided with the first and second air suction ports. 6
The second air suction port 6d on one side of the first and second air suction ports 6c and 6d faces the heat exchange coil 3, and the air outlet 6b faces the upper air supply port 10c. The two air suction ports 6c and 6d are installed such that the center in the height direction is located slightly above the center of the heat exchange coil 3. The rims of the first and second air suction ports 6c and 6d are caulked by drawing a round surface inside in the same manner as that of the second embodiment shown in FIG. Has formed.
Here, the centrifugal blower 6 is fixed to a mount having a frame structure having good ventilation, for example, but is omitted in the figure. The bearings and the like for supporting the rotating shaft of the centrifugal blower 6 are also omitted in the drawings.

As described above, when the second air suction port 6d of the centrifugal blower 6 is configured to directly face the heat exchange coil 3, for example, the dimensions of the main body casing 1 in the width direction and the depth direction are reduced. Even if the heat exchange coil 3 having a large aspect ratio is used, the centrifugal
However, air can be satisfactorily sucked also from the region of the upper portion of the heat exchange coil 3 where the flow velocity is low (the region (i)). Furthermore, with this configuration, air can be effectively sucked into the first air suction port 6c of the centrifugal blower 6 on the side opposite to the heat exchange coil 3 also from the lower part of the heat exchange coil 3 (conventional (b) area). As a result, the flow velocity distribution of the flow passing through the heat exchange coil 3 becomes uniform, and the installation area of the air conditioner can be reduced without increasing the pressure loss and the accompanying increase in the power of the blower shaft and the generated noise. Can be smaller.

In the same configuration, the centrifugal blower 6
Sets the fan drive motor 6e below the main body of the centrifugal blower 6 by a predetermined distance, and sets the belt 6f and the pulley 19
A, 19B belt drive configuration. The fan drive motor 6e is fixed to, for example, a frame-structured base similarly to the case of the centrifugal blower 6, but is also omitted in the drawings for simplification of description. A table for adjusting and fixing the belt tension via the pulley 19B is also omitted from the drawing. With this belt drive configuration, compared to the conventional case where the fan drive motor 6 e is directly connected to the fan rotor of the centrifugal blower 6, the air is sucked into the second air suction port 6 d of the centrifugal blower 6. This makes it easy to prevent the blower performance from deteriorating due to the presence of the fan drive motor 6e that hinders the air flow near the second air suction port 6d. The effect of equalizing the flow velocity distribution can be further enhanced. The belt 6f may be of any type such as a V-belt and a toothed belt, but it is needless to say that the belt 6f preferably has high transmission efficiency and low driving noise.

The pulley 19A on the centrifugal blower 6 side
Have a plurality of fan-shaped holes 20, 20.
..It has a formed structure. Thereby, the flowing air can smoothly pass through the holes 20, 20,... As shown in the drawing, so that the pulley 19A is installed immediately before the second air suction port 6d of the centrifugal blower 6 as shown in the drawing. Even so, the effect of equalizing the flow velocity distribution of the flow passing through the centrifugal blower 6 can be maintained, and the performance of the blower does not deteriorate.

As shown in the figure, a connection flow path from the air outlet 6b of the rotor housing 6a of the centrifugal blower 6 to the air supply port 10c at the upper part of the main body casing 1 has a tongue side of the rotor housing 6a as shown in the drawing. A duct 21 having a diffuser structure in which a passage cross-sectional area is gradually increased upward by gradually inclining a wall surface 22 forward is provided. This duct 21 is formed integrally with the rotor housing 6a as shown in FIGS.
And, thereby, the air outlet 6 of the centrifugal blower 6
b, the flow velocity of the air blown out of the duct 21 is reduced in the duct 21 and the dynamic pressure on the outlet side of the centrifugal blower 6 is efficiently converted into static pressure. This will be higher than the static pressure of the blower 6 alone. As a result, it is possible to compensate for an increase in the pressure loss due to an increase in the flow velocity due to a decrease in the flow path area in the first flow path 12 and the second flow path 13.

Further, in the above configuration, since the duct 21 itself is formed integrally with the rotor housing 6a of the centrifugal blower 6, the configuration is simplified, the cost is reduced, and the number of assembling steps is reduced. be able to.

Further, in the above configuration, as described above, the edge portions of the first and second air suction ports 6c and 6d of the rotor housing 6a of the centrifugal blower 6 are each formed with a curved surface inward. Since the bell mouth having an integral structure is formed by tightening, the first and second
The air flow reaching the fan rotor via the air inlets 6c and 6d is less separated, the flow velocity distribution is made uniform, and the air resistance is reduced. As a result, the above action becomes more effective.

In the present embodiment, the above-mentioned bell mouths provided at the first and second air suction ports 6c and 6d are also provided, for example, as shown in FIG. , 39, are formed with separate bell-shaped bell mouths 41, 41 on the inside of the rotor housing, which are previously formed by a separate member, with bolts 42, 42 and nuts 43, 43.
May be provided by screwing together.

(Embodiment 4) In the configuration of Embodiment 3 shown in FIGS. 9 and 10, the duct 21 is provided between the air outlet 6b of the centrifugal blower 6 and the air supply port 10c in the upper part of the main body casing 1. Are connected linearly, but the shape may be any shape as long as the static pressure conversion performance in the duct 21 is not impaired. 9 and FIG. 10, the belt 6f and the pulleys 19A and 19B are installed on the side of the centrifugal blower 6 facing the heat exchange coil 3. Of course, it may be installed on the opposite side. FIG. 11 shows a configuration of the third embodiment based on such a purpose.

That is, in the fourth embodiment shown in FIG. 11, the belt 6f and the pulleys 19A and 19B are provided on the side opposite to the heat exchange coil 3, and the width of the duct 21 in the axial direction is the same as that of the main casing 1 in the width direction. Such a duct shape is effective when the aspect ratio of the heat exchange coil 3 is considerably large and the depth dimension cannot be enlarged.

(Embodiment 5) In FIG. 12, the tongue side wall surface 22 of the rotor housing 6a of the centrifugal blower 6 of the duct 21 is used for the same purpose as in FIG.
Is formed into a substantially circular arc shape in the direction toward the inside of the flow channel. The Coanda effect at the downstream of the tongue suppresses the separation of the flow from the wall surface and reduces the area ratio between the inlet and the outlet of the duct 21 in the depth direction of the main casing 1. It can be made larger, and the diffuser effect is improved.

[Brief description of the drawings]

FIG. 1 is a schematic sectional view showing a configuration of an air handling unit type air conditioner according to Embodiment 1 of the present invention.

FIG. 2 is a sectional view taken along line CC of FIG.

FIG. 3 is a schematic cross-sectional view of the air handling unit type air conditioner according to Embodiment 1 of the present invention in a partially cut-away state showing the operation of the air conditioner.

FIG. 4 is a schematic sectional view showing a configuration of an air handling unit type air conditioner according to Embodiment 2 of the present invention.

FIG. 5 is a sectional view taken along line DD of FIG. 1;

FIG. 6 is a perspective view of a rotor housing part which is a main part of the air handling unit type air conditioner.

FIG. 7 is a sectional view taken along the line EE of FIG. 6;

FIG. 8 is an enlarged sectional view of a main part of a rotor housing portion according to a modification of the air handling unit type air conditioner according to Embodiment 2 of the present invention.

FIG. 9 is a schematic sectional view showing a configuration of an air handling unit type air conditioner according to Embodiment 3 of the present invention.

FIG. 10 is a sectional view taken along the line FF of FIG. 9;

FIG. 11 is a schematic sectional view showing a configuration of an air handling unit type air conditioner according to Embodiment 4 of the present invention.

FIG. 12 is a schematic sectional view showing a configuration of an air handling unit type air conditioner according to Embodiment 5 of the present invention.

FIG. 13 is a schematic sectional view showing a configuration of an air handling unit type air conditioner according to a first conventional example.

FIG. 14 is a sectional view taken along line AA of FIG.

FIG. 15 is a schematic perspective view showing an actual product example of the first conventional example.

FIG. 16 is a schematic sectional view showing a configuration of an air handling unit type air conditioner according to a second conventional example.

FIG. 17 is a sectional view taken along the line BB of FIG. 16;

FIG. 18 is a schematic sectional view showing a problem of the second conventional example.

[Explanation of symbols]

1 is a main body casing, 2A is a pre-filter, 2B is a main filter, 3 is a heat exchange coil, 3A is a cold water coil, 3
B is a hot water coil, 4 is a humidifier, 6 is a centrifugal blower, 6a is a rotor housing, 6b is an air outlet, 6c and 6d are first and second air inlets, 6f is a belt, 10a is an outside air inlet, 10b is an inside air return air port, 10c is an air supply port, 12 is a first flow path (upstream air flow path), 13 is a second flow path (downstream air flow path), and 21 is a duct.

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Kenjiro Kinoshita 1304 Kanaokacho, Sakai-shi, Osaka Daikin Industries Inside the Kanaoka Plant of Sakai Seisakusho Co., Ltd. Kishiwada Plant of Sakai Factory Co., Ltd.

Claims (6)

[Claims] 1. An internal space of a main body casing is divided into first and second flow paths by a heat exchange coil, and an upper portion of the first flow path communicates with an outside air suction port that communicates with the outside of the room. In one or both of the inside air return air ports, in an air handling unit type air conditioner having an air supply port communicating with the room above the second flow path, A double suction type centrifugal blower is provided near the center in the vertical direction, and the air outlet is provided for the upper air supply port,
An air handling unit type air conditioner, wherein the air handling unit is connected via a duct having a gradually increasing cross-sectional area. 2. The air handling unit type air conditioner according to claim 1, wherein a corner portion of a rotor housing of the centrifugal blower is formed on a round surface. 3. The centrifugal blower according to claim 1, wherein the duct is formed separately from the rotor housing of the centrifugal blower and is connected to the rotor housing air outlet of the centrifugal blower.
Or the air handling unit type air conditioner according to 2. 4. The air handling unit type air conditioner according to claim 1, wherein the duct is formed integrally with a rotor housing of the centrifugal blower. 5. The air handling unit type air conditioner according to claim 1, wherein a bell mouth is formed by caulking an edge of a rotor housing air suction port of the centrifugal blower. Machine. 6. The air handling unit type air conditioner according to claim 1, wherein a bell mouth having a separate structure is attached to an edge of a rotor housing air suction port of the centrifugal blower. .