JPH10246456A - Air handling unit type air-conditioning equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the installation area by installing a both-suction-type centrifugal blower at a second channel so that one of suction ports faces a heat exchange coil, at the same time a blow-off port faces a air-supply port, and a position in height direction at the body casing of the suction port center is located at an upper position than the center part of the heat exchange coil. SOLUTION: An external air suction port 10a, an inner air returning port 10b, and an air supply port 10c are provided at the upper part of first and second channels 12 and 13. A multiple-wing-both-suction-type centrifugal blower 6 is installed at the second channel 13 so that a second air suction port 6d of first and second suction ports 6c and 6d faces a heat exchange coil 3 and the air discharge port 6b faces an air supply port 10c and a position in center height direction of the first and second air suction ports 6c and 6d is at the upper part than the center part of the heat exchange coil 3. For example, in the heat exchange coil 3 where the dimensions in width and depth directions of a body casing 1 is reduced and an aspect ratio is large, air can be sucked from the upper part of the heat exchange coil 2 in this configuration and is sucked into a first air suction port 6 even from a lower part, thus making uniform the flow-rate distribution of a passing flow.

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, JP-A-63-91438).

Conventionally, as such an air handling unit type air conditioner, there is a first conventional example shown in FIGS. 6 and 7, 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 sucks in from the downstream second flow path (downstream blower 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 is formed by a multi-blade blower (a so-called sirocco fan) which blows out the air sucked from the air outlet 6b of the spiral rotor housing 6a having the tongue portion and the 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 shaft of the fan rotor.

That is, in the configuration of the first conventional example, the blower installation space 14 having a predetermined upper and lower width is provided above the upper end of the heat exchange coil 3 as described above, and the two suction type centrifugal blowers 6 and And a fan drive motor 6e directly connected to the fan drive motor 6e.

In the air handling unit type air conditioner having such a structure, in order to reduce the installation area, the size of the main casing 1 in the width direction and the depth direction is reduced so that the heat exchange coil 3 having a large aspect ratio is obtained. Is used, the first flow path 12 which is the upstream side ventilation space is used.
The flow area of the air flowing from the outside air suction port 10a and the inside air return air port 10b side increases,
The flow direction cannot be suddenly changed, and a region where the flow velocity is low is generated near the upper part (a) of the heat exchange coil 3.

Further, since the heat exchange coil 3 has a vertically long dimension in the height direction as compared with the width direction, the centrifugal blower 6 is located above the main body casing 1.
The air cannot pass around the lower part (b) of the heat exchange coil 3 and flow therethrough, and a region where the flow velocity is low also occurs near the lower part (b) of the heat exchange coil 3. As a result, a greatly distorted velocity distribution is generated in the flow passing through the heat exchange coil 3, which eventually causes an increase in pressure loss.

A first flow path 1 which is an upstream air blowing space
2 and the second flow path 13 that is the downstream side ventilation space, the cross-sectional area of the flow path decreases and the flow velocity increases because of the reduction in the width and depth dimensions of the main casing 1. There is a problem that pressure loss increases, and as a result, shaft power and noise of the blower increase.

In order to solve such a problem, there is a second conventional example as shown in FIGS. 8 and 9, for example. That is, in this configuration, the internal space of the main body casing 1 has the height from the bottom plate 1a to the vicinity of the top plate 1b, and the heat exchange coil 3 having a high aspect ratio has a first and a first space.
The first flow path 12 is divided into two second flow paths 12 and 13.
One or both of 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 are provided at an upper portion of the second passage 13, and an air supply port 10c communicating with the inside of the room is provided above the second flow path 13. On the other hand, the air outlet 6b of the above-mentioned double suction type centrifugal blower 6 is opposed to the upper part of the downstream side of the heat exchange coil 3 and the first and second two air inlets 6c, 6d are formed. The air inlet 10c is fitted and installed so that the opening direction is parallel to the heat exchange coil 3.

In the air handling type air conditioner having such a structure, in order to reduce the installation area as described above, the dimensions of the main casing 1 in the width direction and the depth direction are reduced so that heat exchange with a large aspect ratio is achieved. Even if the coil 3 is used, the centrifugal blower 6 approaches the lower part (b) of the heat exchange coil 3 so that air can flow around this part.

[0014]

However, in the case of the configuration of the second conventional example, the rotor housing 6a of the centrifugal blower 6 exists immediately after the heat exchange coil 3 near the upper part (a). Therefore, the air passing through the portion of the heat exchange coil 3 immediately before the rotor housing 6a is
For example, as shown in an enlarged view in FIG. 12, the outer periphery of the rotor housing 6a must be largely wrapped around in the directions of the first and second air suction ports 6c and 6d. It is not possible to prevent a region where the flow velocity is small in the upper region (a) of the heat exchange coil 3 due to an increase in the flow velocity of the air flowing from the air port 10b and a sudden change in direction. Therefore, the flow passing through the heat exchange coil 3 also has a greatly distorted velocity distribution, and the pressure loss of the heat exchange coil 3 increases.

In addition, since the aspect ratio of the heat exchange coil 3 is large, the suction space in the axial direction of the centrifugal blower 6 is inevitably narrowed, as shown in FIG. Therefore, the pressure loss further increases, and the performance of the blower itself deteriorates.

Further, as described above, the first flow path 12 which is the upstream-side ventilation space and the second flow path 13 which is the downstream-side ventilation space have the same size as that of the main casing 1 in the width direction and the depth direction. As the passage area increases and the flow velocity increases, the pressure loss increases due to the reduction. As a result, the shaft power and noise of the blower increase.

As described above, when the width and depth dimensions of the main casing are reduced and a heat exchange coil having a large aspect ratio is used, the greatly distorted velocity distribution generated in the flow passing through the heat exchange coil is as follows. , Resulting in deterioration of cooling and heating capacity. In addition, an increase in pressure loss due to a greatly distorted velocity distribution generated in the heat exchange coil and an increase in passage flow velocity and an increase in pressure loss due to a decrease in the flow path area due to a decrease in the width and depth dimensions of the main body casing are caused by a blower. This causes the shaft power and noise to rise.

The present invention has been made in view of such circumstances, and even when a heat exchange coil having a large aspect ratio is used by reducing the dimensions of the main body casing in the width direction and the depth direction as described above, the pressure loss can be reduced. It is an object of the present invention to provide an air-handling unit type air conditioner that can reduce the installation area without causing an increase in the shaft power of the blower or the noise generated thereby.

[0019]

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, the inside of the main body casing has a height from the bottom plate to the vicinity of the top plate, and the first and second heat exchange coils have a large aspect ratio. 2 and 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 above the first channel, and In an air handling unit type air conditioner provided with an air supply port communicating with a room at an upper part, a double suction type centrifugal blower is provided in the second flow path, and one of the suction ports faces a heat exchange coil, The air outlet is opposed to the air supply port, and a position in the height direction of the center of the suction port in the main body casing is provided so as to be located slightly above the central portion of the heat exchange coil. .

As described above, the air conditioner according to the present invention firstly divides the internal space of the main body casing from the bottom plate to the vicinity of the top plate by the heat exchange coils having a high aspect ratio and a large height. Divided into two second flow paths, and 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 above the first flow path,
In an air handling unit type air conditioner provided with an air supply port communicating with a room at the upper part of the second flow path, both suction-type centrifugal blowers are connected to the downstream side front of the heat exchange coil with respect to the suction port of the heat exchange coil. One of the heat exchange coils is opposed to the heat exchange coil, and is disposed so that the height position of the center of the suction port is slightly higher than the center of the heat exchange coil, so that the heat exchange coil having a large aspect ratio is provided. Even if the width and depth dimensions of the main body casing are reduced by using, the centrifugal blower can suck air well from the conventional low flow velocity region above the heat exchange coil. In the same configuration, the air is effectively sucked from the lower part of the heat exchange coil into the suction port on the opposite side of the heat exchange coil of the centrifugal blower. Becomes uniform. As a result, the installation area can be reduced without increasing the pressure loss, concomitant increase in the power of the blower shaft, and increase in generated noise.

In the air handling unit type air conditioner of the present invention, the fan drive motor of the centrifugal blower is installed below the centrifugal blower main body, and the fan of the centrifugal blower main body is driven by a belt through a belt and a pulley. With this configuration, there is no obstacle near the air inlet of the centrifugal blower, which has a large air resistance as seen with the conventional directly connected fan drive motor, and the air suction becomes easier, so the blower performance deteriorates. Can be prevented, and the effect of equalizing the flow velocity distribution of the flow passing through the heat exchange coil can be further enhanced.

In the same construction, if the pulley on the main body of the centrifugal blower is formed into a shape having a hole around the rotation shaft, the suction air can pass through the hole more easily. Even when approaching the suction port of the impeller, the effect of equalizing the flow velocity distribution of the flow passing through the heat exchange coil can be sufficiently maintained, and the deterioration of the blower performance can be further prevented. As a result, the apparatus can be made more compact.

In the above configuration, the fan drive motor may be inserted into the fan impeller of the centrifugal blower main body, or the fan drive motor may be integrated with the fan impeller of the centrifugal blower main body as an outer rotor motor. Thus, the same effect as above can be obtained more effectively. Therefore, the apparatus can be made more compact.

Further, according to the present invention, the space formed between the air outlet of the centrifugal blower and the air supply port on the upper part of the main body casing is connected by a duct having a diffuser structure for gradually increasing the cross-sectional area of the passage. The flow velocity of the air blown out from the air outlet of the centrifugal blower is gradually reduced in the gradual passage cross-section enlarged duct, and the dynamic pressure at the outlet of the centrifugal blower is efficiently converted to static pressure. With the reduction in the width and depth dimensions, the flow path area decreases and the flow velocity increases, which can compensate for the increase in pressure loss in the flow path before and after the heat exchange coil, and reduces the power of the blower shaft and the noise generated. You can prevent the rise.

[0026]

As described above, according to the air handling unit type air conditioner of the present invention, even when the heat exchange coil having a large aspect ratio is used by reducing the width and depth dimensions of the main body casing, the pressure loss is reduced. It is possible to provide a compact, low-cost air-handling unit type air conditioner that can sufficiently reduce the installation area without causing an increase in the shaft power of the blower and the noise generated thereby. Become.

[0027]

BEST MODE FOR CARRYING OUT THE INVENTION

(Embodiment 1) FIGS. 1 and 2 show a configuration of an air handling unit type air conditioner according to Embodiment 1 of the present invention.

In the figure, 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. 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. 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.

First, as described above, the second air suction port 6d of the centrifugal blower 6 is configured to directly face the heat exchange coil 3, so that the size of the main body casing 1 in the width direction and the depth direction can be reduced. Thus, even if the heat exchange coil 3 having a large aspect ratio is used, the centrifugal blower 6 can satisfactorily blow air from the region of the upper portion of the heat exchange coil 3 where the flow velocity is small (the conventional (a) region) as shown in the figure. Inhalation becomes possible (see chain line arrow). 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 construction, 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 like the centrifugal blower 6 but
This is also omitted in the figure for simplification of the 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. Here, in FIGS. 1 and 2, 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, but this is installed on the side opposite to the heat exchange coil 3. Of course, it is good. If the belt 6f is installed outside the main casing 1 as another configuration, it is expected that the effects of the present invention can be further improved.

The air outlet 6b of the centrifugal blower 6
Between the air supply port 10c in the upper part of the main body casing 1 and
As shown in FIG. 2, the ducts 21 are connected by a duct 21 having a diffuser structure in which a passage cross-sectional area is gradually increased upward. Thereby, the flow velocity of the air blown out from the air outlet 6b of the centrifugal blower 6 is reduced in the duct 21 so that the exit side dynamic pressure of the centrifugal blower 6 is efficiently converted to static pressure. Therefore, the static pressure at the outlet of the duct 21 is higher than the static pressure of the centrifugal 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.

(Embodiment 2) In the configuration of Embodiment 1 shown in FIG. 1, the dimensions of the air outlet 6b of the centrifugal blower 6 and the air inlet 10c in the width direction of the main casing 1 are substantially the same. However, it is not necessary that the two dimensions match each other, and they may be different from each other.

(Embodiment 3) In the configuration of Embodiment 1 shown in FIG. 1, the duct 21 extends linearly 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. However, the shape may be any shape as long as the static pressure conversion performance of the duct 21 is not impaired. Duct 21 based on such a purpose
FIG. 3 shows a configuration of the third embodiment in which the shape is different.

That is, the third embodiment shown in FIG.
The width of the duct 21 in the axial direction is increased in the width direction of the main casing 1, and is effective when the aspect ratio of the heat exchange coil 3 is considerably large and the depth dimension cannot be expanded. Become.

(Embodiment 4) Next, FIG.
For the same purpose as described above, the tongue side wall surface 22 of the rotor housing 6a of the centrifugal blower 6 of the duct 21 is formed in a substantially circular arc shape toward the inside of the flow path, and the flow is separated from the wall surface by the Coanda effect downstream of the tongue. Is suppressed, and the area ratio between the inlet and the outlet of the duct 21 in the depth direction of the main body casing 1 can be further increased, so that the diffuser effect is improved.

(Embodiment 5) Further, FIG.
The fan drive motor 6e of the centrifugal blower 6 is incorporated in an impeller of a fan rotor 6g, characterized in that it is more compact and the air resistance at the time of air intake is reduced as much as possible. It is.

The support structure of the fan drive motor is not shown.

(Embodiment 6) Although not shown,
The fan drive motor 6e can be integrated with an impeller of the fan rotor 6g as an outer rotor motor.

[Brief description of the drawings]

FIG. 1 is a 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 sectional view showing a configuration of an air handling unit type air conditioner according to Embodiment 3 of the present invention.

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

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

FIG. 6 is a sectional view showing a configuration of an air handling unit type air conditioner according to a first conventional example.

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

FIG. 8 is a sectional view showing a configuration of an air handling unit type air conditioner according to a second conventional example.

FIG. 9 is a sectional view taken along the line BB of FIG. 8;

FIG. 10 is a cross-sectional view showing a problem of the second conventional example.

[Explanation of symbols]

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

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Yoshimasa Kikuchi 1304 Kanaokacho, Sakai-shi, Osaka Daikin Industries Inside the Kanaoka Plant of Sakai Seisakusho Co., Ltd. (72) Inventor Kazuyuki Hamada, 1304 Kanaokacho, Sakai City, Osaka Daikin Industries, Ltd.

Claims (6)

[Claims] The internal space of the main body casing is divided into first and second flow paths by a heat exchange coil having a height from the bottom plate to the vicinity of the top plate and having a large aspect ratio. Either 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 above the first flow path, and an air supply port communicating with the inside of the room is provided above the second flow path. In the air-conditioning unit of the air handling unit type, both suction-type centrifugal blowers are provided in the second flow path, and one of the suction ports faces the heat exchange coil and the blowout port faces the air supply port. An air handling unit type air conditioner, wherein a position of a center of the suction port in a height direction of the main body casing is located slightly above a central portion of the heat exchange coil. 2. The air handling unit type air conditioner according to claim 1, wherein the fan drive motor is installed below the centrifugal blower main body, and the fan is driven by a belt via a belt and a pulley. 3. The centrifugal blower main body-side pulley has a shape having a hole around a rotation shaft.
The air handling unit type air conditioner according to the above. 4. The air handling unit type air conditioner according to claim 1, wherein the fan drive motor is inserted into the fan impeller of the centrifugal blower main body and is directly connected to the fan impeller. Machine. 5. The air handling unit type air conditioner according to claim 1, wherein the fan drive motor is integrated with a fan impeller of a centrifugal blower main body as an outer rotor motor. 6. The air outlet of the centrifugal blower main body and the air supply port of the upper part of the main body casing are connected by a duct that gradually enlarges the cross-sectional area of the passage.
The air conditioner according to 4 or 5.