Air conditioner

CROSS-REFERENCE TO RELATED APPLICATIONS

This U.S. National stage application claims priority under 35 U.S.C. §119(a) to Japanese Patent Application Nos. 2004-282115, filed in Japan on Sep. 28, 2004, and 2005-139411, filed in Japan on May 12, 2005, the entire contents of which are hereby incorporated herein by reference.

TECHNICAL FIELD

The present invention relates to an air conditioner, and particularly to an air conditioner disposed with a unit casing partitioned by a partition member into a fan chamber and a heat exchanger chamber, with a centrifugal fan that includes an impeller and a scroll casing housing the impeller being disposed inside the fan chamber and a heat exchanger being disposed inside the heat exchanger chamber so as to face a scroll blowout opening in the scroll casing.

BACKGROUND ART

Conventionally, there has been an air conditioner disposed with a unit casing where a centrifugal fan that includes impellers and scroll casings housing the impellers and a heat exchanger are partitioned by a partition member into a heat exchanger chamber and a fan chamber, with the centrifugal fan that includes the impellers and the scroll casings housing the impellers being disposed inside the fan chamber and the heat exchanger being disposed inside the heat exchanger chamber so as to face scroll blowout openings in the scroll casings.

As one example of such an air conditioner, there is a ceiling-hung type air conditioner. A ceiling-hung type air conditioner is mainly disposed with a unit casing capable of being hung from a ceiling, a centrifugal fan that sucks air into the unit casing via a unit suction opening and blows out air from a unit blowout opening, and a heat exchanger.

The unit suction opening is formed in the bottom surface of the unit casing, and the unit blowout opening is formed in the front surface of the unit casing. Further, a partition member comprising a plate-like member that is long from side to side and disposed upright is disposed in the unit casing to partition the space inside the unit casing into a fan chamber at the rear surface side that is communicated with the unit suction opening and a heat exchanger chamber at the front surface side that is communicated with the unit blowout opening. More specifically, the partition member includes a flat plate section that runs parallel to the front surface and the rear surface of the unit casing (i.e., orthogonal to the side surfaces of the unit casing). Communication openings that allow the fan chamber and the heat exchanger chamber to be communicated are formed in the flat plate section.

The centrifugal fan is disposed inside the fan chamber and mainly includes impellers, scroll casings housing the impellers, and a motor that drives the impellers to rotate. The impellers are, for example, double suction type sirocco fan rotors whose rotational axis is disposed facing the sides of the unit casing. The scroll casings include scroll body sections, which include scroll suction openings that open in the direction of the rotational axis of the impellers, and cylindrical scroll outlet sections, which include scroll blowout openings formed so as to blow out air in a direction intersecting the scroll suction openings and disposed so as to correspond to the communication openings in the partition member. In such an air conditioner, oftentimes the impellers and the scroll casings are disposed plurally juxtaposed in the rotational axis direction—that is, facing the sides of the unit casing—and in this case, the plural impellers are collectively driven to rotate by a single motor.

The heat exchanger is disposed inside the heat exchanger chamber so as to face the scroll blowout openings—and more specifically, so as to face substantially the entire flat plate section of the partition member—and is a device for cooling and heating air whose pressure has been boosted by the centrifugal fan inside the fan chamber and which has been blown out into the heat exchanger chamber from the scroll blowout openings in the scroll casings.

In such an air conditioner, when the centrifugal fan is actuated, air is sucked into the fan chamber of the unit casing via the unit suction opening, and the air that has been sucked into the fan chamber is sucked into the scroll casings through the scroll suction openings and is blown out from the inner peripheral sides to the outer peripheral sides of the impellers. The air that has been blown out to the outer peripheral sides of the impellers and whose pressure has been boosted is blown out into the heat exchanger chamber from the scroll blowout openings disposed so as to correspond to the communication openings in the partition member. Then, the air that has been blown out into the heat exchanger chamber from the scroll blowout openings is cooled or heated as a result of heat exchange being performed with refrigerant flowing inside a heat transfer tube of the heat exchanger and is blown out into the room from the unit blowout opening (e.g., see Japanese Patent JP-A No. 2002-106945).

However, in the above-described conventional air conditioner, whereas the heat exchanger faces substantially the entire flat plate section of the partition member, the communication openings in the flat plate section—that is, the scroll blowout openings in the scroll casings—are only disposed partially in the flat plate section of the partition member, so problems occur in which the air blown out into the heat exchanger chamber from the scroll blowout openings passes through the heat exchanger without being diffused, nonuniformity in the flow of air passing through the heat exchanger occurs, ventilation resistance in the heat exchanger increases, and blowing capability and heat exchange capability are reduced. Particularly in the case of a configuration where impellers and scroll casings are disposed plurally juxtaposed as in the above-described conventional air conditioner, this problem occurs in each scroll blowout opening.

With respect to this, an air conditioner disposed with scroll casings where the size of the scroll outlet sections in the direction of the rotational axis of the impellers is enlarged has been proposed (see Japanese Patent JP-A No. 5-99444).

SUMMARY OF THE INVENTION

In the above-described latter air conditioner, the problem of nonuniformity in the flow of air passing through the heat exchanger is reduced because the size of the scroll blowout openings is enlarged, but because the size of the scroll outlet sections is much larger than the size of the impellers, this hinders the scroll suction openings such that dynamic pressure recovery in the scroll outlet sections becomes difficult and, as a result, there is the potential for this to cause the blowing capability to be reduced.

Further, when there is enough space inside the fan chamber to be able to enlarge the size of the scroll outlet sections, it suffices to enlarge the sizes of the impellers and the scroll casings themselves, so it is difficult to apply the configuration of the above-described latter air conditioner when there is no extra space inside the fan chamber or when the unit casing must be made compact.

It is an object of the present invention to control nonuniformity in the flow of air passing through a heat exchanger while controlling a reduction in blowing capability in an air conditioner disposed with a unit casing partitioned by a partition member into a fan chamber and a heat exchanger chamber, with a centrifugal fan that includes an impeller and a scroll casing housing the impeller being disposed inside the fan chamber and a heat exchanger being disposed inside the heat exchanger chamber so as to face a scroll blowout opening in the scroll casing.

An air conditioner pertaining to a first aspect of the present invention is disposed with a unit casing, a partition member, an impeller, a scroll casing, and a heat exchanger. The unit casing includes a unit suction opening and a unit blowout opening. The partition member partitions the space inside the unit casing into a fan chamber communicated with the unit suction opening and a heat exchanger chamber communicated with the unit blowout opening and includes a flat plate section in which a communication opening that allow the fan chamber and the heat exchanger chamber to be communicated is formed. The impeller is disposed in the fan chamber. The scroll casing includes a scroll body section that includes a scroll suction opening and house the impeller and a cylindrical scroll outlet section that includes a scroll blowout opening disposed in correspondence to the communication opening. The heat exchanger is disposed inside the heat exchanger chamber so as to face the scroll blowout opening such that air that has been blown out into the heat exchanger chamber from the scroll blowout opening is blown out from the unit blowout opening after passing through the heat exchanger. A wall section that projects from the heat exchanger side of the flat plate section is disposed outside the scroll outlet section.

In this air conditioner, the wall section that projects from the heat exchanger side of the flat plate section is disposed outside the scroll outlet section, so that inside the heat exchanger chamber, a portion whose pressure is lower (called a negative pressure portion below) than the pressure of the air that has been blown out into the heat exchanger chamber from the scroll blowout opening is formed in the outside vicinity of the scroll blowout opening. Additionally, the air blown out into the heat exchanger chamber from the scroll blowout opening flows so as to be pulled into the negative pressure portion, so that the air is diffused to the outside of the scroll blowout opening. Thus, nonuniformity in the flow of air passing through the heat exchanger can be controlled while controlling a reduction in blowing capability.

An air conditioner pertaining to a second aspect of the present invention comprises the air conditioner pertaining to the first aspect of the present invention, wherein a distance between the portion where the scroll outlet section and the surface of the flat plate section on the heat exchanger side intersect and the portion where the wall section and the surface of the flat plate section on the heat exchanger side intersect is equal to or less than 0.5 times a rotor width of the impeller.

In this air conditioner, the distance between the portion where the scroll outlet section and the surface of the flat plate section on the heat exchanger side intersect and the portion where the wall section and the surface of the flat plate section on the heat exchanger side intersect is made equal to or less than 0.5 times a rotor width of the impeller, so that the negative pressure portion can be reliably formed in the outside vicinity of the scroll blowout opening.

An air conditioner pertaining to a third aspect of the present invention comprises the air conditioner pertaining to the first or second aspect of the present invention, wherein a distance from the surface of the flat plate section on the heat exchanger side to an end portion of the scroll outlet section on the heat exchanger side is greater than 0 and equal to or less than 0.3 times a rotor diameter of the impeller.

In this air conditioner, by making the distance from the surface of the flat plate section on the heat exchanger side to the end portion of the scroll outlet section on the heat exchanger side greater than 0—that is, by allowing the end portion of the scroll outlet section on the heat exchanger side to project toward the heat exchanger chamber—the negative pressure portion comprising a space interposed between the wall section and the end portion of the scroll outlet section on the heat exchanger side can be formed in the outside vicinity of the scroll blowout opening where the effect of causing the air blown out into the heat exchanger chamber from the scroll blowout opening to be diffused outside the scroll blowout opening is large. Moreover, by making the distance from the surface of the flat plate section on the heat exchanger side to the end portion of the scroll outlet section on the heat exchanger side equal to or less than 0.3 times the rotor diameter of the impeller, a distance that is sufficient for the air blown out into the heat exchanger chamber from the scroll blowout opening to diffuse outside the scroll blowout opening can be ensured between the scroll blowout opening and the heat exchanger.

An air conditioner pertaining to a fourth aspect of the present invention comprises the air conditioner pertaining to the third aspect of the present invention, wherein a distance from the surface of the flat plate section on the heat exchanger side to an end portion of the wall section on the heat exchanger side is equal to or greater than the distance from the surface of the flat plate section on the heat exchanger side to the end portion of the scroll outlet section on the heat exchanger side and is equal to or less than 0.5 times the rotor diameter of the impeller.

In this air conditioner, by making the distance from the surface of the flat plate section on the heat exchanger side to the end portion of the wall section on the heat exchanger side equal to or greater than the distance from the surface of the flat plate section on the heat exchanger side to the end portion of the scroll outlet section on the heat exchanger side—that is, by allowing the end portion of the wall section to project further toward the heat exchanger than the end portion of the scroll outlet section on the heat exchanger side—the difference in pressure between the pressure of the negative pressure portion comprising a space interposed between the wall section and the end portion of the scroll outlet section on the heat exchanger side and the pressure of the air blown out into the heat exchanger chamber from the scroll blowout opening can be made greater, so that the effect of causing the air blown out into the heat exchanger chamber from the scroll blowout opening to be diffused outside the scroll blowout opening can be raised. Moreover, by making the distance from the surface of the flat plate section on the heat exchanger side to the end portion of the wall section on the heat exchanger side equal to or less than 0.5 times the rotor diameter of the impeller, it can be ensured that the flow of air to be diffused by the negative pressure portion to the outside of the scroll blowout opening is, as much as possible, not restricted by the wall section, so that the air blown out into the heat exchanger chamber from the scroll blowout opening can be further diffused outside the wall section.

An air conditioner pertaining to a fifth aspect of the present invention comprises the air conditioner of any of the first to fourth aspects of the present inventions, wherein an angle formed by the wall section and the surface of the flat plate section on the heat exchanger side is greater than 30° and equal to or less than 90°.

In this air conditioner, by making the angle formed by the wall section and the surface of the flat plate section on the heat exchanger side greater than 30°, the negative pressure portion can be reliably formed in the outside vicinity of the scroll blowout opening. Moreover, by making the angle formed by the wall section and the surface of the flat plate section on the heat exchanger side equal to or less than 90°, it can be ensured that the air blown out into the heat exchanger chamber from the scroll blowout opening is reliably diffused to the outside of the scroll blowout opening.

An air conditioner pertaining to a sixth aspect of the present invention comprises the air conditioner of any of the first to fifth aspects of the present inventions, wherein serrations are disposed in the end portion of the wall section on the heat exchanger side.

In this air conditioner, serrations are disposed in the end portion of the wall section on the heat exchanger side, so that variations in the pressure of the air blown out into the heat exchanger chamber from the scroll blowout opening at the end portion of the wall section on the heat exchanger side can be controlled. Thus, the occurrence of noise resulting from pressure variations at the end portion of the wall section on the heat exchanger side can be controlled.

An air conditioner pertaining to a seventh aspect of the present invention comprises the air conditioner pertaining to any of the first to sixth aspects of the present inventions, wherein plural dimples are disposed in the surface of the wall section on the side of the scroll outlet section.

In this air conditioner, plural dimples are disposed in the surface of the wall section on side of the scroll outlet section, so that the air blown out into the heat exchanger chamber from the scroll blowout opening can be matched to the surface of the wall section on the side of scroll outlet section. Thus, the effect of causing the air blown out into the heat exchanger chamber from the scroll outlet section to be diffused to the outside of the scroll blowout opening can be raised.

An air conditioner pertaining to an eighth aspect of the present invention comprises the air conditioner pertaining to any of the first to sixth aspects of the present inventions, wherein plural through holes are disposed in the wall section.

In this air conditioner, plural through holes are disposed in the wall section, so that the air blown out into the heat exchanger chamber from the scroll blowout opening can be matched to the surface of the wall section on the scroll outlet section. Thus, the effect of causing the air blown out into the heat exchanger chamber from the scroll blowout opening to be diffused to the outside of the scroll blowout opening can be raised.

An air conditioner pertaining to a ninth aspect of the present invention comprises the air conditioner pertaining to any of the first to eighth aspects of the present inventions, wherein the impeller is disposed so as to rotate about a rotational axis along the flat plate section. The air conditioner further includes a motor that is disposed on the rotational axis direction side of the scroll casing inside the fan chamber and which drives the impeller to rotate. The scroll outlet section extends toward the communication opening while slanting toward the motor but without its size in the rotational axis direction being enlarged.

In an air conditioner having this configuration, the air that has been blown out into the heat exchanger chamber from the scroll blowout opening in the scroll casing mainly ends up passing through the portion of the heat exchanger facing the scroll casing with the flat plate section interposed therebetween and it becomes difficult for the air to pass through the portion of the heat exchanger facing the motor with the flat plate section interposed therebetween, so it becomes easy for problems to occur in which nonuniformity in the flow of air passing through the heat exchanger occurs, ventilation resistance in the heat exchanger increases, and blowing capability and heat exchange capability decrease.

With respect to this, in the air conditioner pertaining to the aspect of the present invention, the scroll outlet section extends toward the communication opening while slanting toward the motor but without its size in the rotational axis direction being enlarged, so it becomes easier for the air to also pass through the portion of the heat exchanger facing the motor with the flat plate section interposed therebetween, and nonuniformity in the flow of air passing through the heat exchanger can be controlled. Moreover, because it is ensured that the size of the scroll outlet section in the rotational axis direction is not enlarged, it also becomes difficult for drawbacks such as dynamic pressure recovery in the scroll outlet section becoming difficult to occur, and a reduction in blowing performance can be controlled.

An air conditioner pertaining to a tenth aspect of the present invention comprises the air conditioner pertaining to any of the first to eighth aspects of the present inventions, wherein the impeller is disposed so as to rotate about a rotational axis along the flat plate section. The wall section is disposed outside the scroll outlet section in the rotational axis direction.

In an air conditioner disposed with a unit casing partitioned by a partition member into a fan chamber and a heat exchanger chamber, with a centrifugal fan that includes an impeller and a scroll casing housing the impeller being disposed inside the fan chamber and a heat exchanger being disposed inside the heat exchanger chamber so as to face a scroll blowout opening in the scroll casing, when the impeller is disposed so as to rotate about a rotational axis along a flat plate section of the partition member, there is a strong tendency for it to be difficult for the air blown out to the heat exchanger chamber from the scroll outlet section opening in the direction intersecting the rotational axis to be diffused in the direction along the rotational axis.

However, in this air conditioner, the wall section is disposed outside in the rotational axis direction, so that inside the heat exchanger chamber, the negative pressure portion is formed in the outside vicinity of the scroll blowout opening in the rotational axis direction. Additionally, the air blown out into the heat exchanger chamber from the scroll blowout opening flows so as to be pulled into the negative pressure portion, so that it becomes easier for the air to be diffused to the outside of the scroll blowout opening in the rotational axis direction. Thus, nonuniformity in the flow of air passing through the heat exchanger can be controlled while controlling a reduction in blowing capability.

An air conditioner pertaining to an eleventh aspect of the present invention comprises the air conditioner pertaining to the tenth aspect of the present invention, wherein the impellers and the scroll casings are disposed plurally juxtaposed in the rotational axis direction. The wall sections are disposed on adjacent scroll casing sides of the outside of the scroll outlet sections.

In an air conditioner disposed with a unit casing partitioned by a partition member into a fan chamber and a heat exchanger chamber, with a centrifugal fan that includes impellers and scroll casings housing the impellers being disposed inside the fan chamber and a heat exchanger being disposed inside the heat exchanger chamber so as to face scroll blowout openings in the scroll casings, when the impellers are disposed so as to rotate about a rotational axis along a flat plate section of the partition member and the impellers and scroll casings are plurally juxtaposed in the rotational axis direction, a clearance is formed between adjacent scroll casings and it becomes difficult for the air that has been blown out into the heat exchanger chamber from the scroll outlet sections to pass through the portion corresponding to this clearance.

However, in this air conditioner, the wall sections are disposed on adjacent scroll casing sides of the outside of the scroll outlet sections, so that inside the heat exchanger chamber, the negative pressure portions are formed on adjacent scroll casings sides of the scroll blowout openings. Additionally, the air blown out into the heat exchanger chamber from the scroll blowout openings flows so as to be pulled into the negative pressure portions, so that it becomes easier for the air to be diffused to the adjacent scroll casing sides of the scroll blowout openings. Thus, nonuniformity in the flow of air passing through the heat exchanger can be controlled while controlling a reduction in blowing capability.

An air conditioner pertaining to a twelfth aspect of the present invention comprises the air conditioner pertaining to the tenth or eleventh aspect of the present invention, wherein the air conditioner further includes a motor that is disposed on the rotational axis direction side of the scroll casing inside the fan chamber and which drives the impeller to rotate. The wall section is disposed on the motor side of the outside of the scroll outlet section.

In an air conditioner disposed with a unit casing partitioned by a partition member into a fan chamber and a heat exchanger chamber, with a centrifugal fan that includes an impeller and a scroll casing housing the impeller being disposed inside the fan chamber and a heat exchanger being disposed inside the heat exchanger chamber so as to face a scroll blowout opening in the scroll casing, when the impeller is disposed so as to rotate about a rotational axis along a flat plate section of the partition member and the motor that drives the impeller to rotate is disposed on the rotational axis direction side of the scroll casing, the air that has been blown out into the heat exchanger chamber from the scroll blowout opening mainly ends up passing through the portion of the heat exchanger facing the scroll casing with the flat plate section interposed therebetween, and it becomes difficult for the air to pass through the portion of the heat exchanger facing the motor with the flat plate section interposed therebetween.

However, in this air conditioner, the wall section is disposed on the motor side of the outside of the scroll outlet section, so that inside the heat exchanger chamber, the negative pressure portion is formed on the motor side of the scroll blowout opening. Additionally, the air blown out into the heat exchanger chamber from the scroll blowout opening flows so as to be pulled into the negative pressure portion, so that it becomes easier for the air to be diffused to the motor side of the scroll blowout opening. Thus, nonuniformity in the flow of air passing through the heat exchanger can be controlled while controlling a reduction in blowing capability.

An air conditioner pertaining to a thirteenth aspect of the present invention comprises the air conditioner pertaining to the twelfth aspect of the present invention, wherein the scroll outlet section extends toward the communication opening while slanting toward the motor but without its size in the rotational axis direction being enlarged.

In this air conditioner, the scroll outlet section extends toward the communication opening while slanting toward the motor but without its size in the rotational axis direction being enlarged, so it becomes easier for the air to also pass through the portion of the heat exchanger facing the motor with the flat plate section interposed therebetween, and nonuniformity in the flow of air passing through the heat exchanger can be further controlled. Moreover, because it is ensured that the size of the scroll outlet section in the rotational axis direction is not enlarged, it also becomes difficult for drawbacks such as dynamic pressure recovery in the scroll outlet section becoming difficult to occur, and a reduction in blowing performance can be controlled.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a side sectional view of a ceiling-hung type air conditioner serving as a first embodiment of an air conditioner pertaining to the present invention.

FIG. 2 is a plan sectional view of the ceiling-hung type air conditioner serving as the first embodiment of the air conditioner pertaining to the present invention.

FIG. 3 is an enlarged view of FIG. 2 showing the structure of the vicinity of an impeller and a scroll casing.

FIG. 4 is an enlarged view of FIG. 1 showing the structure of the vicinity of the impeller and the scroll casing.

FIG. 5 is a view showing the structure of the vicinity of a scroll outlet section in an air conditioner pertaining to a first modification of the first embodiment.

FIG. 6 is a view showing the structure of the vicinity of a scroll outlet section in an air conditioner pertaining to a second modification of the first embodiment.

FIG. 7 is a view showing the structure of the vicinity of the scroll outlet section in the air conditioner pertaining to the second modification of the first embodiment.

FIG. 8 is a view showing the structure of the vicinity of a scroll outlet section in an air conditioner pertaining to a third modification of the first embodiment.

FIG. 9 is a view corresponding to FIG. 2 and showing an air conditioner pertaining to a fourth modification of the first embodiment.

FIG. 10 is a side view (seen from arrow A in FIG. 11) of a duct type air conditioner serving as a second embodiment of the air conditioner pertaining to the present invention.

FIG. 11 is a plan sectional view of the duct type air conditioner serving as the second embodiment of the air conditioner pertaining to the present invention.

FIG. 12 is an enlarged view of FIG. 11 showing the structure of the vicinity of an impeller and a scroll casing.

FIG. 13 is a view showing the structure of the vicinity of a scroll outlet section in an air conditioner pertaining to a first modification of the second embodiment.

FIG. 14 is a view showing the structure of the vicinity of the scroll outlet section in the air conditioner pertaining to the first modification of the second embodiment.

FIG. 15 is a view showing the structure of the vicinity of the scroll outlet section in the air conditioner pertaining to the first modification of the second embodiment.

FIG. 16 is a view showing the structure of the vicinity of the scroll outlet section in the air conditioner pertaining to the first modification of the second embodiment.

FIG. 17 is a view corresponding to FIG. 11 and showing an air conditioner pertaining to a second modification of the second embodiment.

DETAILED DESCRIPTION OF THE INVENTION

Embodiments of an air conditioner pertaining to the present invention will be described below on the basis of the drawings.

First Embodiment

(1) Basic Structure of Air Conditioner

FIG. 1 and FIG. 2 show a ceiling-hung type air conditioner 1 serving as a first embodiment of the air conditioner pertaining to the present invention. Here, FIG. 1 is a side sectional view (showing the cross section of a scroll casing 32b) of the air conditioner 1. FIG. 2 is a plan sectional view of the air conditioner 1.

The air conditioner 1 is disposed hanging from a ceiling in an air-conditioned room and is connected via refrigerant communication pipes (not shown) to an outdoor unit (not shown) disposed outdoors.

The air conditioner 1 is mainly disposed with a unit casing 2, a centrifugal fan 3, and a heat exchanger 4.

The unit casing 2 is shaped like a thin box overall that is long from side to side and is formed such that its dimension in the height direction becomes smaller from the rear surface side to the front surface side. A unit suction opening 2a that sucks room air into the unit casing 2 is disposed in a portion at the rear surface side of the bottom surface of the unit casing 2. Further, a unit blowout opening 2b that blows cooled or heated air into the room from the inside of the unit casing 2 is disposed in the front surface of the unit casing 2.

More specifically, the unit casing 2 mainly includes a top plate section 21 capable of being hung from the ceiling, a bottom plate section 22 disposed facing the portion at the front surface side of the top plate section 21, and a suction grill 23 disposed facing the portion at the rear surface side of the top plate section 21. The top plate section 21 is a metal plate-like member formed as a result of its pair of side surfaces and its rear surface being folded by sheet metal processing. The suction grill 23 is detachably attached to the top plate section 21 and configures the suction opening 2a.

Further, a partition member 24 comprising a plate-like member that is long from side to side and disposed upright is disposed between the bottom plate section 22 and the suction grill 23 of the unit casing 2. The partition member 24 partitions the space inside the unit casing 2 into a fan chamber S1 at the rear surface side that is communicated with the unit suction opening 2a and a heat exchanger chamber S2 at the front surface side that is communicated with the unit blowout opening 2b. More specifically, in the present embodiment, the partition member 24 includes a flat plate section 25 that runs parallel to the front surface and the rear surface of the unit casing 2 (i.e., orthogonal to the side surfaces of the unit casing 2). Additionally, four communication openings 25a to 25d that correspond to scroll blowout openings 35a to 35d (described later) of four scroll casings 32a to 32d configuring the centrifugal fan 3 and allow the fan chamber S1 and the heat exchanger chamber S2 to be communicated are formed in the flat plate section 25. The four communication openings 25a to 25d are disposed juxtaposed in the longitudinal direction of the flat plate section 25 and, in the present embodiment, are rectangular holes.

The front surface, the side surfaces, and the bottom surface of the unit casing 2 are covered by an outer member 26 made of synthetic resin. A heat insulating member 27 comprising styrene foam, for example, is attached to the top plate section 21 in the vicinity of the unit blowout opening 2b. Further, a drain pan 28 comprising styrene foam, for example, is attached to the inside portion of the bottom plate section 22. The unit blowout opening 2b that is substantially rectangular and long from side to side is configured by the portions of the unit casing 2 at the front surface side including the portions of the outer member 26 and the heat insulating member 27 at the front surface side, and the portion of the drain pan 28 at the front surface side.

A first flap 29 that swings up and down and plural second flaps 30 that swing right and left are disposed in the unit blowout opening 2b. The first flap 29 comprises a plate-like member that is long from side to side, and is supported by the unit casing 2 so as to freely swing about a first axis X1 along the longitudinal direction of the unit blowout opening 2b. The plural second flaps 30 are supported by the unit casing 2 so as to freely swing about second axes X2 that cross the first axis X1 at positions on the rear surface side of the first axis X1.

The centrifugal fan 3 is disposed inside the fan chamber S1 and is a device for sucking air into the fan chamber S1 from the unit suction opening 2a, boosting the pressure of the air, and blowing out the air to the heat exchanger chamber S2 through the communication openings 25a to 25d in the partition member 24. Additionally, the centrifugal fan 3 mainly includes four impellers 31a to 31d, four scroll casings 32a to 32d housing the impellers 31a to 31d, and a motor 33 that drives the impellers 31a to 31d to rotate.

First, the impellers 31a to 31d will be described using FIG. 1 and FIG. 2. In the present embodiment, the impellers 31a to 31d are double suction type sirocco fan rotors and are disposed juxtaposed such that their rotational axis O faces the sides of the unit casing 2 (i.e., along the flat plate section 25 of the partition member 24). It will be noted that, because the impellers 31a to 31d all have the same structure, just the configuration of the impeller 31b will be described here, and in regard to the configurations of the impellers 31a, 31c, and 31d, the letters a, c, and d will be added instead of the letter b representing the respective parts of the impeller 31b and description of those respective parts will be omitted.

The impeller 31b mainly includes a discoid main plate 41b that rotates about the rotational axis O, numerous blades 42b that are disposed annularly around the rotational axis O on both sides of the outer peripheral portion of the main plate 41b with one end of each blade being fixed to the main plate 41b, and a pair of side plates 43b that are disposed on both rotational axis O direction sides of the main plate 41b and join together the other ends of the numerous blades 42b.

Next, the scroll casings 32a to 32d will be described. It will be noted that, because the scroll casings 32a to 32d all have the same structure, just the configuration of the scroll casing 32b will be described here, and in regard to the configurations of the scroll casings 32a, 32c, and 32d, the letters a, c, and d will be added instead of the letter b representing the respective parts of the scroll casing 32b and description of those respective parts will be omitted.

The scroll casing 32b includes two scroll suction openings 34b formed in both side surfaces in order to configure a double suction type centrifugal fan and a scroll blowout opening 35b formed so as to blow out air in the direction intersecting the scroll suction openings 34b. Here, the scroll suction openings 34b open in the direction of the rotational axis O of the impeller 31b. For this reason, the unit suction opening 2a opens in the direction intersecting (more specifically, the direction orthogonal to) the opening direction of the scroll suction openings 34b. Further, the scroll blowout opening 35b is disposed so as to correspond to the communication opening 25b in the partition member 24.

More specifically, in the present embodiment, the scroll casing 32b is a member made of resin and has a divided structure comprising a scroll lower member 45b that covers the impeller 31b from below and a scroll upper member 44b that covers the impeller 31b from above. Additionally, by attaching these members 44b and 45b to each other, a scroll body section 36b that includes the two scroll suction openings 34b and houses the impeller 31b and a scroll outlet section 37b that includes the scroll blowout opening 35b and is communicated with the scroll body section 36b are configured. Two bellmouth sections 38b that surround the scroll suction openings 34b are formed in the scroll body section 36b. Inner peripheral end portions of the bellmouth sections 38b curve in bell shapes toward the impeller 31b. The scroll outlet section 37b is a portion shaped like a square cylinder that is communicated with the portion at the partition member 24 side of the scroll body section 36b, and the distal end portion of the scroll outlet section 37b is inserted into the communication opening 25b formed in the flat plate section 25 of the partition member 24 and projects toward the heat exchanger 4 from the flat plate section 25 of the partition member 24. The scroll outlet section 37b extends directly in a direction substantially orthogonal to the flat plate section 25—that is, in a direction orthogonal to the rotational axis O—when the unit casing 2 is seen in plan view and slants somewhat downward so as to blow out air a little downward when the unit casing 2 is seen in side view.

It will be noted that, although there are four impellers and four scroll casings in the present embodiment, the number of impellers and scroll casings is not limited to this and may also be one, two, or four or more. Further, although the impellers and the scroll casings are a double suction type in the present embodiment, they may also be a single suction type.

In the present embodiment, the motor 33 is disposed between the scroll casing 32b and the scroll casing 32c (i.e., on the rotational axis O direction sides of the scroll casing 32b and the scroll casing 32c) when the unit casing 2 is seen in plan view, and is fixed to the partition member 24 and the unit casing 2 via a support member 33a. For this reason, just the distance between the scroll casing 32b and the scroll casing 32c is larger in comparison to the distances between the other scroll casings (more specifically, the distance between the scroll casing 32a and the scroll casing 32b and the distance between the scroll casing 32c and the scroll casing 32d). Additionally, the four impellers 31a to 31d are all coupled to the motor 33 so that they can be collectively driven to rotate.

When the centrifugal fan 3 is actuated, air is sucked into the fan chamber S1 of the unit casing 2 via the unit suction opening 2a, and the air that has been sucked into the fan chamber S1 is sucked into the scroll casings 32a to 32d through the scroll suction openings 34a to 34d and blown out from the inner peripheral sides to the outer peripheral sides of the impellers 31a to 31d. The air that has been blown out to the outer peripheral sides of the impellers 31a to 31d and whose pressure has been boosted is blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d in the scroll casings 32a to 32d disposed so as to correspond to the communication openings 25a to 25d in the partition member 24.

The heat exchanger 4 is disposed inside the heat exchanger chamber S2 and is a device for cooling or heating the air whose pressure has been boosted by the centrifugal fan 3 inside the fan chamber S1 and which has been blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d in the scroll casings 32a to 32d. In the present embodiment, the heat exchanger 4 is a cross fin tube type heat exchanger and is disposed facing, and parallel to, substantially the entire flat plate section 25 of the partition member 24. For this reason, the heat exchanger 4 is disposed facing the scroll blowout openings 35a to 35d in the scroll outlet sections 37a to 37d. Further, the heat exchanger 4 is disposed such that its upper portion slants toward the unit blowout opening 2b. Additionally, the drain pan 28 is disposed below the heat exchanger 4 so that condensation water generated by the heat exchanger 4 can be received.

Thus, the air that has been blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d is cooled or heated as a result of heat exchange being performed with refrigerant flowing inside a heat transfer tube of the heat exchanger 4 and is blown out into the room from the unit blowout opening 2b.

In the air conditioner 1 disposed with the above-described configuration, wall sections 61a to 61d are further disposed. These wall sections 61a to 61d will be described below using FIG. 1 to FIG. 4. Here, FIG. 3 is an enlarged view of FIG. 2 and shows the structure of the vicinity of the impeller 31b and the scroll casing 32b. FIG. 4 is an enlarged view of FIG. 1 and shows the structure of the vicinity of the impeller 31b and the scroll casing 32b.

As shown in FIG. 2, FIG. 3, and FIG. 4, the wall sections 61a to 61d are portions that project from the heat exchanger 4 side of the flat plate section 25 of the partition member 24 disposed on the outside of the scroll outlet sections 37a to 37d. It will be noted that, because the wall sections 61a to 61d all have the same structure in the present embodiment, just the configuration of the wall section 61b will be described here, and in regard to the configurations of the wall sections 61a, 61c, and 61d, the letters a, c, and d will be added instead of the letter b representing the respective parts of the wall section 61b and description of those respective parts will be omitted.

In the present embodiment, the wall section 61b is a cylindrical portion disposed so as to surround the outside of the cylindrical scroll outlet section 37b and includes side wall sections 62 and 63 respectively disposed on the sides of both side surface portions 46 and 47 of the scroll outlet section 37b, an upper wall section 64 disposed above an upper surface portion 48 of the scroll outlet section 37b, and a lower wall section 65 disposed below a lower surface portion 49 of the scroll outlet section 37b. Additionally, the wall section 61b (specifically, the side wall sections 62 and 63, the upper wall section 64, and the lower wall section 65) at the fan chamber S1 side contacts a position outside the communication opening 25b on the flat plate section 25 of the partition member 24 and extends from there so as to project toward the heat exchanger 4. In the air conditioner 1 of the present embodiment, by disposing the wall section 61b, a portion (called negative pressure portion S3 below) whose pressure is lower than the pressure of the air blown out into the heat exchanger chamber S2 from the scroll blowout opening 35b is formed in the outside vicinity of the scroll blowout opening 35b. It will be noted that it is not necessary for the wall section 61b to be disposed around the outside of the entire scroll blowout opening 35b as in the present embodiment and that the wall section 61b may also be disposed just where the negative pressure portion S3 is to be formed in the outside vicinity of the scroll blowout opening 35b. For example, when the negative pressure portion S3 is to be formed just on the sides of the scroll blowout opening 35b, just the side wall sections 62 and 63 may be disposed without disposing the upper wall section 64 and the lower wall section 65.

Further, in the present embodiment, a distance c between the portion where the scroll outlet section 37b and the surface of the flat plate section 25 on the heat exchanger 4 side intersect and the portion where the wall section 61b and the surface of the flat plate section 25 on the heat exchanger 4 side intersect is equal to or less than 0.5 times a rotor width W of the impeller 31b. More specifically, a distance c between the portion where the outer surface of the side surface portion 46 of the scroll outlet section 37b (i.e., the surface on the side of the side wall section 62 of the wall section 61b) and the surface of the flat plate section 25 on the heat exchanger 4 side intersect and the portion where the inner surface of the side wall section 62 of the wall section 61b (i.e., the surface on the side of the side surface portion 46 of the scroll outlet section 37b) and the surface of the flat plate section 25 on the heat exchanger 4 side intersect, a distance c between the portion where the outer surface of the side surface portion 47 of the scroll outlet section 37b (i.e., the surface on the side of the side wall section 63 of the wall section 61b) and the surface of the flat plate section 25 on the heat exchanger 4 side intersect and the portion where the inner surface of the side wall section 63 of the wall section 61b (i.e., the surface on the side of the side surface portion 47 of the scroll outlet section 37b) and the surface of the flat plate section 25 on the heat exchanger 4 side intersect, a distance c between the portion where the outer surface of the upper surface portion 48 of the scroll outlet section 37b (i.e., the surface on the side of the upper wall section 64 of the wall section 61b) and the surface of the flat plate section 25 on the heat exchanger 4 side intersect and the portion where the inner surface of the upper wall section 64 of the wall section 61b (i.e., the surface on the side of the upper wall section 48 of the scroll outlet section 37b) and the surface of the flat plate section 25 on the heat exchanger 4 side intersect, and a distance c between the portion where the outer surface of the lower surface portion 49 of the scroll outlet section 37b (i.e., the surface on the side of the lower wall section 65 of the wall section 61b) and the surface of the flat plate section 25 on the heat exchanger 4 side intersect and the portion where the inner surface of the lower wall section 65 of the wall section 61b (i.e., the surface on the side of the lower surface portion 49 of the scroll outlet section 37b) and the surface of the flat plate section 25 on the heat exchanger 4 side intersect are equal to or less than 0.5 times the rotor width W of the impeller 31b. In the air conditioner 1 of the present embodiment, by making the distance c equal to or less than 0.5 times the rotor width W, the negative pressure portion S3 can be reliably formed in the outside vicinity of the scroll blowout opening 35b. It will be noted that, when the wall section 61b does not contact the flat plate section 25, the portion where the wall section 61b and the surface of the flat plate section 25 on the heat exchanger 4 side would intersect if the end portion of the wall section 61b on the flat plate section 25 side were to be extended corresponds to the portion where the wall section 61b and the surface of the flat plate section 25 on the heat exchanger 4 side intersect.

Further, in the present embodiment, a distance a from the surface of the flat plate section 25 on the heat exchanger 4 side to the end portion of the scroll outlet section 37b on the heat exchanger 4 side is greater than 0 and equal to or less than 0.3 times a rotor diameter D of the impeller 31b. More specifically, a distance a from the surface of the flat plate section 25 on the heat exchanger 4 side to the end portions of both side surface portions 46 and 47 of the scroll outlet section 37b on the heat exchanger 4 side, a distance a from the surface of the flat plate section 25 on the heat exchanger 4 side to the end portion of the upper surface portion 48 of the scroll outlet section 37b on the heat exchanger 4 side, and a distance a from the surface of the flat plate section 25 on the heat exchanger 4 side to the end portion of the lower surface portion 49 of the scroll outlet section 37b on the heat exchanger 4 side are greater than 0 and equal to or less than 0.3 times the rotor diameter D of the impeller 31b. In the air conditioner 1 of the present embodiment, by making the distance a greater than 0—that is, by allowing the end portion of the scroll outlet section 37b on the heat exchanger 4 side to project toward the heat exchanger chamber S2—the negative pressure portion S3 comprising space interposed between the wall section 61b and the end portion of the scroll outlet section 37b on the heat exchanger 4 side can be formed in the outside vicinity of the scroll blowout opening 35b.

Further, in the present embodiment, a distance b from the surface of the flat plate section 25 on the heat exchanger 4 side to the end portion of the wall section 61b on the heat exchanger 4 side is equal to or greater than the distance a and equal to or less than 0.5 times the rotor diameter D of the impeller 31b. More specifically, a distance b from the surface of the flat plate section 25 on the heat exchanger 4 side to the end portions of the side wall sections 62 and 63 of the wall section 61b on the heat exchanger 4 side, a distance b from the surface of the flat plate section 25 on the heat exchanger 4 side to the end portion of the upper wall section 64 of the wall section 61b on the heat exchanger 4 side, and a distance b from the surface of the flat plate section 25 on the heat exchanger 4 side to the end portion of the lower wall section 65 of the wall section 61b on the heat exchanger 4 side are equal to or greater than the distance a and equal to or less than 0.5 times the rotor diameter D of the impeller 31b. In the air conditioner 1 of the present embodiment, by making the distance b equal to or greater than the distance a—that is, by allowing the end portion of the wall section 61b to project further toward the heat exchanger 4 than the end portion of the scroll outlet section 37b on the heat exchanger 4 side—the difference in pressure between the pressure of the negative pressure portion S3 comprising space interposed between the wall section 61b and the end portion of the scroll outlet section 37b on the heat exchanger 4 side and the pressure of the air blown out into the heat exchanger chamber S2 from the scroll blowout opening 35b can be made greater.

Further, in the present embodiment, an angle θ formed by the wall section 61 and the surface of the flat plate section 25 on the heat exchanger 4 side is greater than 30° and equal to or less than 90°. More specifically, the angle θ formed by the inner surfaces of the side wall sections 62 and 63 of the wall section 61b (i.e., the surfaces on the sides of the side surface portions 46 and 47 of the scroll outlet section 37b) and the portion of the surface of the flat plate section 25 on the heat exchanger 4 side outside the side wall sections 62 and 63 of the wall section 61b, the angle θ formed by the inner surface of the upper wall section 64 of the wall section 61b (i.e., the surface on the side of the upper surface portion 48 of the scroll outlet section 37b) and the portion of surface of the flat plate section 25 on the heat exchanger 4 side outside the upper wall section 64 of the wall section 61b, and the angle θ formed by the inner surface of the lower wall section 65 of the wall section 61b (i.e., the surface on the side of the lower surface portion 49 of the scroll outlet section 37b) and the portion of the surface of the flat plate section 25 on the heat exchanger 4 side outside the lower wall section 65 of the wall section 61b are greater than 30° and equal to or less than 90°. In the air conditioner 1 of the present embodiment, by making the angle formed by the wall section 61b and the surface of the flat plate section 25 on the heat exchanger 4 side greater than 30°, the negative pressure portion S3 can be reliably formed in the outside vicinity of the scroll blowout opening 35b.

(2) Operation of Air Conditioner

Next, operation of the air conditioner 1 of the present embodiment will be described using FIG. 1 to FIG. 4.

When the motor 33 is started to actuate the centrifugal fan 3, air is sucked into the fan chamber S1 of the unit casing 2 via the unit suction opening 2a, and the air that has been sucked into the fan chamber S1 is sucked into the scroll casings 32a to 32d through the scroll suction openings 34a to 34d and is blown out from the inner peripheral sides to the outer peripheral sides of the impellers 31a to 31d. The air that has been blown out to the outer peripheral sides of the impellers 31a to 31d and whose pressure has been boosted is blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d disposed so as to correspond to the communication openings 25a to 25d in the partition member 24. Then, the air that has been blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d is cooled or heated as a result of heat exchange being performed with refrigerant flowing inside the heat transfer tube of the heat exchanger 4 and is blown out into the room from the unit blowout opening 2b.

Here, in the air conditioner 1 of the present embodiment, the wall sections 61a to 61d that project from the heat exchanger 4 side of the flat plate section 25 are disposed outside the scroll outlet sections 37a to 37d, so that the negative pressure portions S3 whose pressure is lower than the pressure of the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d are formed in the outside vicinities of the scroll blowout openings 35a to 35d. Additionally, the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d (see arrow F in FIG. 3 and in FIG. 4) flows so as to be pulled into the negative pressure portions S3, so that the air is diffused to the outsides of the scroll blowout openings 35a to 35d in comparison to when wall sections are not disposed in the scroll outlet sections (see arrow f showing the flow of air when wall sections are not disposed in the scroll outlet sections). Thus, nonuniformity in the flow of air passing through the heat exchanger 4 can be controlled while controlling a reduction in blowing capability.

Further, in the air conditioner 1 of the present embodiment, by making the distance c equal to or less than 0.5 times the rotor width W of the impellers 31a to 31d, the negative pressure portions S3 can be reliably formed in the outside vicinities of the scroll blowout openings 35a to 35d.

Further, in the air conditioner 1 of the present embodiment, by making the distance a greater than 0—that is, by allowing the end portions of the scroll outlet sections 37a to 37d on the heat exchanger 4 side to project toward the heat exchanger chamber S2—the negative pressure portions S3 comprising spaces interposed between the wall sections 61a to 61d and the end portions of the scroll outlet sections 37a to 37d on the heat exchanger 4 side can be formed in the outside vicinities of the scroll blowout openings 35a to 35d where the effect of causing the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d to be diffused outside the scroll blowout openings 35a to 35d is large. Moreover, by making the distance a equal to or less than 0.3 times the rotor diameter D of the impellers 31a to 31d, a distance that is sufficient for the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d to diffuse outside the scroll blowout openings 35a to 35d can be ensured between the scroll blowout openings 35a to 35d and the heat exchanger 4.

Further, in the air conditioner 1 of the present embodiment, by making the distance b equal to or greater than the distance a—that is, by allowing the end portions of the wall sections 61a to 61d to project further toward the heat exchanger 4 than the end portions of the scroll outlet sections 37a to 37d on the heat exchanger 4 side—the difference in pressure between the pressure of the negative pressure portions S3 comprising spaces interposed between the wall sections 61a to 61d and the end portions of the scroll outlet sections 37a to 37d on the heat exchanger 4 side and the pressure of the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d can be made greater, so that the effect of causing the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d to be diffused to the outsides of the scroll blowout openings 35a to 35d can be raised. Moreover, by making the distance b equal to or less than 0.5 times the rotor diameter D of the impellers 31a to 31d, it can be ensured that the flow of air to be diffused by the negative pressure portions S3 to the outsides of the scroll blowout openings 35a to 35d is, as much as possible, not restricted by the wall sections 61a to 61d, so that the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d can be further diffused to the outsides of the wall sections 61a to 61d.

Further, in the air conditioner 1 of the present embodiment, by making the angle θ greater than 30°, the negative pressure portions S3 can be reliably formed in the outside vicinities of the scroll blowout openings 35a to 35d. Moreover, by making the angle θ equal to or less than 90°, it can be ensured that the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d is reliably diffused to the outsides of the scroll blowout openings 35a to 35d.

In this manner, in the air conditioner 1 of the present embodiment, whereas the heat exchanger 4 faces substantially the entire flat plate section 25 of the partition member 24, the communication openings 25a to 25d in the flat plate section 25—that is, the scroll blowout openings 35a to 35d in the scroll casings 32a to 32d—are only disposed partially in the flat plate section 25 of the partition member 24, but by disposing the wall sections 61a to 61d as described above, the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d can be diffused to the outsides of the scroll blowout openings 35a to 35d and allowed to pass through the heat exchanger 4 without having to increase the size of the scroll blowout openings 35a to 35d, and nonuniformity in the flow of air passing through the heat exchanger 4 can be controlled.

Moreover, because the wall sections 61a to 61d are disposed on the heat exchanger chamber S2 side of the flat plate section 25 of the partition member 24, problems do not arise where the wall sections 61a to 61d hinder the scroll suction openings 34a to 34d such that dynamic pressure recovery in the scroll outlet sections 37a to 37d becomes difficult, and the wall sections 61a to 61d are effective as means to control nonuniformity in the flow of air passing through the heat exchanger 4 when there is no extra space inside the fan chamber S1 or when the unit casing 2 must be made compact.

(3) Modification 1

Further, serrations may be disposed in the end portions of the wall sections 61a to 61d on the heat exchanger 4 side. To describe using the wall section 61b as an example, as shown in FIG. 5, it is possible to dispose triangular wave-shaped serrations 71 in the end portion of the wall section 61b on the heat exchanger 4 side (in FIG. 5, there is shown a drawing where the serrations 71 are disposed in the side wall section 62, but the same serrations 71 may also be disposed in the other wall sections 63 to 65).

In this manner, by disposing the serrations 71 in the end portions of the wall sections 61a to 61d on the heat exchanger 4 side, variations in the pressure of the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d at the end portions of the wall sections 61a to 61d on the heat exchanger 4 side can be controlled. Thus, the occurrence of noise resulting from pressure variations at the end portions of the wall sections 61a to 61d on the heat exchanger 4 side can be controlled.

(4) Modification 2

Further, plural dimples may be disposed in the inner surfaces of the wall sections 61a to 61d—that is, the surfaces of the wall sections 61a to 61d on the sides of the scroll outlet sections 37a to 37d. To describe using the wall section 61b as an example, as shown in FIG. 6, it is possible to dispose plural dimples 72 in the inner surface of the wall section 61b—that is, the surface of the wall section 61b on the scroll outlet section 37b side (in FIG. 6, there is shown a drawing where the plural dimples 72 are disposed in the side wall section 62, but the same plural dimples 72 may also be disposed in the other wall sections 63 to 65).

In this manner, by disposing the plural dimples 72 in the inner surfaces of the wall sections 61a to 61d—that is, the surfaces of the wall sections 61a to 61d on the sides of the scroll outlet sections 37a to 37d—the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d can be matched to the surfaces of the wall sections 61a to 61d on the sides of the scroll outlet sections 37a to 37d. Thus, the effect of causing the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d to be diffused to the outsides of the scroll blowout openings 35a to 35d can be raised.

Further, in order to obtain the same effect as disposing plural dimples in the inner surfaces of the wall sections 61a to 61d—that is, the surfaces of the wall sections 61a to 61d on the sides of the scroll outlet sections 37a to 37d—plural through holes 73 may be disposed in the wall sections 61a to 61d. To describe using the wall section 61b as an example, as shown in FIG. 7, it is possible to dispose the plural through holes 73 in the wall section 61b (in FIG. 7, there is shown a drawing where the plural through holes 73 are disposed in the side wall section 62, but the same plural through holes 73 may also be disposed in the other wall sections 63 to 65).

(5) Modification 3

Further, the serrations pertaining to modification 1 and the plural dimples or through holes pertaining to modification 2 may be simultaneously disposed in the wall sections 61a to 61d. To describe using the wall section 61b as an example, as shown in FIG. 8, it is possible to dispose the triangular wave-shaped serrations 71 in the end portion of the wall section 61b on the heat exchanger 4 side and to dispose the plural dimples 72 in the inner surface of the wall section 61b—that is, the surface of the wall section 61b on the scroll outlet section 37b side (in FIG. 8, there is shown a drawing where the serrations 71 are disposed in the side wall section 62 and where the plural dimples 72 are disposed in the side wall section 62, but the same serrations 71 and plural dimples 72 may also be disposed in the other wall sections 63 to 65; further, plural through holes may be disposed instead of the plural dimples 72).

Thus, the effects of both modification 1 and modification 2 can be obtained.

(6) Modification 4

Further, in the air conditioner 1 of the above first embodiment (including modifications 1 to 3), the impellers 31a to 31d are disposed so as to rotate about the rotational axis O along the flat plate section 25 of the partition member 24, and the motor 33 that drives the impellers 31a to 31d to rotate is disposed on the rotational axis O direction sides of the scroll casings 32a to 32d inside the fan chamber S1.

For this reason, the air blown out into the heat exchanger chamber S2 from the scroll blowout openings 35a to 35d in the scroll casings 32a to 32d mainly ends up passing through the portions of the heat exchanger 4 facing the scroll casings 32a to 32d with the flat plate section 25 interposed therebetween and it becomes difficult for the air to pass through the portion of the heat exchanger 4 facing the motor 33 with the flat plate section 25 interposed therebetween (specifically, the portion between the scroll casing 32b and the scroll casing 32c), so it becomes easy for problems to occur in which nonuniformity in the flow of air passing through the heat exchanger 4 occurs, ventilation resistance in the heat exchanger 4 increases, and blowing capability and heat exchange capability decrease.

With respect to this, in the air conditioner 1 of the present modification, as shown in FIG. 9, the scroll outlet sections 37b and 37c of the scroll casings 32b and 32c extend toward the communication openings 25b and 25c while slanting toward the motor 33 but without their size L in the rotational axis O direction being enlarged, so it becomes easier for the air blown out into the heat exchanger chamber S2 to also pass through the portion of the heat exchanger 4 facing the motor 33 with the flat plate section 25 interposed therebetween, and nonuniformity in the flow of air passing through the heat exchanger 4 can be controlled. Moreover, because it is ensured that the size L of the scroll outlet sections 37b and 37c in the rotational axis O direction is not enlarged, it also becomes difficult for drawbacks such as dynamic pressure recovery in the scroll outlet sections 37b and 37c becoming difficult to occur, and a reduction in blowing performance can be controlled.

Second Embodiment

(1) Basic Structure of Air Conditioner

FIG. 10 and FIG. 11 show a duct type air conditioner 101 serving as a second embodiment of the air conditioner pertaining to the present invention. Here, FIG. 10 is a side view (seen from arrow A in FIG. 11) of the air conditioner O11. FIG. 11 is a plan sectional view of the air conditioner 101. The air conditioner 101 has a duct structure and is disposed in the space behind a ceiling in an air-conditioned room. The air conditioner 101 is connected via refrigerant communication pipes (not shown) to an outdoor unit (not shown) disposed outdoors.

The air conditioner 101 is mainly disposed with a unit casing 102, a centrifugal fan 103, and a heat exchanger 104.

The unit casing 102 is a member shaped like a thin box overall that is long from side to side, with there being formed therein a fan chamber S101, which includes unit suction openings 102g and 102h in a lower surface 102a and in a rear surface 102b (the surface at the top of the page in FIG. 11) of the unit casing 102 and in which the centrifugal fan 103 is disposed, and a heat exchanger chamber S102, which includes a unit blowout opening 1021 in a front surface 102c (the surface at the bottom of the page in FIG. 11) and in which the heat exchanger 104 is disposed. It will be noted that the unit suction openings 102g and 102h are configured such that either one can be selected and used in accordance with the installation conditions of the space behind the ceiling. The fan chamber S101 and the heat exchanger chamber S102 are formed as a result of the space inside the unit casing 102 being partitioned front and back by a partition member 124 comprising a plate-like member that is long from side to side and disposed upright inside the unit casing 102. More specifically, in the present embodiment, the partition member 124 includes a flat plate section 125 that runs parallel to the front surface and the rear surface of the unit casing 102 (i.e., orthogonal to the side surfaces of the unit casing 102). Additionally, two communication openings 125a and 125b that correspond to scroll blowout openings 135a and 135b (described later) of two scroll casings 132a and 132b configuring the centrifugal fan 103 and allow the fan chamber S101 and the heat exchanger chamber S102 to be communicated are formed in the flat plate section 125. The two communication openings 125a and 125b are disposed juxtaposed in the longitudinal direction of the flat plate section 125 and, in the present embodiment, are rectangular holes.

The centrifugal fan 103 is disposed inside the fan chamber S101 and is a device for sucking air into the fan chamber S101 from the unit suction opening 102g or the unit suction opening 102h, boosting the pressure of the air, and blowing out the air to the heat exchanger chamber S102 through the communication openings 125a and 125b in the partition member 124. Additionally, the centrifugal fan 103 mainly includes two impellers 131a and 131b, two scroll casings 132a and 132b housing the impellers 131a and 131b, and a motor 133 that drives the impellers 131a and 131b to rotate.

First, the impellers 131a and 131b will be described using FIG. 10 and FIG. 11. In the present embodiment, the impellers 131a and 131b are double suction type sirocco fan rotors and are disposed juxtaposed such that their rotational axis O faces the sides of the unit casing 102 (i.e., along the flat plate section 125 of the partition member 124). It will be noted that, because the impellers 131a and 131b have the same structure, just the configuration of the impeller 131a will be described here, and in regard to the configuration of the impellers 131b, the letter b will be added instead of the letter a representing the respective parts of the impeller 131a and description of those respective parts will be omitted.

The impeller 131a mainly includes a discoid main plate 141a that rotates about the rotational axis O, numerous blades 142a that are disposed annularly around the rotational axis O on both sides of the outer peripheral portion of the main plate 141a with one end of each blade being fixed to the main plate 141a, and a pair of side plates 143a that are disposed on both sides of the main plate 141a in the rotational axis O direction and join together the other ends of the numerous blades 142a.

Next, the scroll casings 132a and 132b will be described. It will be noted that, because the scroll casings 132a and 132b have the same structure, just the configuration of the scroll casing 132a will be described here, and in regard to the configuration of the scroll casing 132b, the letter b will be added instead of the letter a representing the respective parts of the scroll casing 132a and description of those respective parts will be omitted.

The scroll casing 132a includes two scroll suction openings 134a formed in both side surfaces in order to configure a double suction type centrifugal fan and a scroll blowout opening 135a formed so as to blow out air in the direction intersecting the scroll suction openings 134a. Here, the scroll suction openings 134a open in the direction of the rotational axis O of the impeller 131a. For this reason, the unit suction opening 102g and the unit suction opening 102h open in the direction intersecting (more specifically, the direction orthogonal to) the opening direction of the scroll suction openings 134a. Further, the scroll blowout opening 135a is disposed so as to correspond to the communication opening 125a in the partition member 124.

More specifically, in the present embodiment, the scroll casing 132a is a member made of resin and has a divided structure comprising a scroll lower member 145a that covers the impeller 131a from below and a scroll upper member 144a that covers the impeller 131a from above. Additionally, by attaching these members 144a and 145a to each other, a scroll body section 136a that includes the two scroll suction openings 134a and houses the impeller 131a and a scroll outlet section 137a that includes the scroll blowout opening 135a and is communicated with the scroll body section 136a are configured. Two bellmouth sections 138a that surround the scroll suction openings 134a are formed in the scroll body section 136a. Inner peripheral end portions of the bellmouth sections 138a curve in bell shapes toward the impeller 131a. The scroll outlet section 137a is a member shaped like a square cylinder that is communicated with the portion of the scroll body section 136a on the partition member 124 side, and the distal end portion of the scroll outlet section 137a is inserted into the communication opening 125a formed in the flat plate section 125 of the partition member 124 and projects toward the heat exchanger 104 from the flat plate section 125 of the partition member 124. The scroll outlet section 137a extends directly in a direction substantially orthogonal to the flat plate section 125—that is, in a direction orthogonal to the rotational axis O—when the unit casing 102 is seen in plan view and slants somewhat downward so as to blow out air a little downward when the unit casing 102 is seen in side view.

In the present embodiment, the motor 133 is disposed between the scroll casing 132a and the scroll casing 132b (i.e., on the rotational axis O direction sides of the scroll casing 132a and the scroll casing 132b) when the unit casing 102 is seen in plan view, and is fixed to the partition member 124 and the unit casing 102 via a support member 133a. For this reason, a clearance corresponding to the size of the motor 133 is formed between the scroll casing 132a and the scroll casing 132b. Additionally, both of the two impellers 131a and 131b are coupled to the motor 133 so that they can be collectively driven to rotate.

When the centrifugal fan 103 is actuated, air is sucked into the fan chamber S101 of the unit casing 102 via the unit suction opening 102g or the unit suction opening 102h, and the air that has been sucked into the fan chamber S101 is sucked into the scroll casings 132a and 132b through the scroll suction openings 134a and 134b and is blown out from the inner peripheral sides to the outer peripheral sides of the impellers 131a and 131b. The air that has been blown out to the outer peripheral sides of the impellers 131a and 131b and whose pressure has been boosted is blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b in the scroll casings 132a and 132b disposed so as to correspond to the communication openings 125a and 125b in the partition member 124.

The heat exchanger 104 is disposed inside the heat exchanger chamber S102 and is a device for cooling or heating the air whose pressure has been boosted by the centrifugal fan 103 inside the fan chamber S101 and which has been blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b in the scroll casings 132a and 132b. In the present embodiment, the heat exchanger 104 is a cross fin tube type heat exchanger and is disposed facing, and parallel to, substantially the entire flat plate section 125 of the partition member 124. For this reason, the heat exchanger 104 is disposed facing the scroll blowout openings 135a and 135b in the scroll outlet sections 137a and 137b. Further, the heat exchanger 104 is disposed such that its upper portion slants toward the unit blowout opening 102i. Additionally, a drain pan 128 is disposed below the heat exchanger 104 so that condensation water generated by the heat exchanger 104 can be received.

Thus, the air that has been blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b is cooled or heated as a result of heat exchange being performed with refrigerant flowing inside a heat transfer tube of the heat exchanger 104 and is blown out into the room from the unit blowout opening 102i.

In the air conditioner 101 disposed with the above-described configuration, wall sections 161a and 161b are further disposed. These wall sections 161a and 161b will be described below using FIG. 10 to FIG. 12. Here, FIG. 12 is an enlarged view of FIG. 11 and shows the structure of the vicinity of the impeller 131a and the scroll casing 132a.

As shown in FIG. 11 and FIG. 12, the wall sections 161a and 161b are portions that project from the heat exchanger 104 side of the flat plate section 125 of the partition member 124 disposed outside the scroll outlet sections 137a and 137b. It will be noted that, because the wall sections 161a and 161b have the same structure in the present embodiment, just the configuration of the wall section 161a will be described here, and in regard to the configuration of the wall section 161b, the letter b will be added instead of the letter a representing the respective parts of the wall section 161a and description of those respective parts will be omitted.

In the present embodiment, the wall section 161a is disposed to the side of a side wall section 146 of the cylindrical scroll outlet section 137a. Additionally, the end portion of the wall section 161a on the fan chamber S101 side contacts a position on the flat plate section 125 of the partition member 124 outside the communication opening 125a and extends from there so as to project toward the heat exchanger 104.

In the air conditioner 101 of the present embodiment, by disposing the wall section 161a, a portion (called negative pressure portion S103 below) whose pressure is lower than the pressure of the air blown out into the heat exchanger chamber S102 from the scroll blowout opening 135a is formed in the outside vicinity of the scroll blowout opening 135a.

Specifically, the wall section 161a is disposed at a position to the side of the side wall section 146 of the scroll outlet section 137a—that is, outside the scroll outlet section 137a in the rotational axis O direction—so that inside the heat exchanger chamber S102, the negative pressure portion S103 is formed in the outside vicinity of the scroll blowout opening 135a in the rotational axis O direction. Moreover, the wall section 161a is disposed on the scroll casing 132b, which is the adjacent scroll casing, side of the outside of the scroll outlet section 137a, so that inside the heat exchanger chamber S102, the negative pressure portion S103 is formed on the scroll casing 132b side of the scroll blowout opening 135a. Further, the wall section 161a is disposed on the motor 133 side of the outside of the scroll outlet section 137a, so that inside the heat exchanger chamber S102, the negative pressure portion S103 is formed on the motor 133 side of the scroll blowout opening 135a.

Further, in the present embodiment, a distance c between the portion where the scroll outlet section 137a and the surface of the flat plate section 125 on the heat exchanger 104 side intersect and the portion where the wall section 161a and the surface of the flat plate section 125 on the heat exchanger 104 side intersect is equal to or less than 0.5 times a rotor width W of the impeller 131a. More specifically, a distance c between the portion where the outer surface of the side surface portion 146 of the scroll outlet section 137a (i.e., the surface on the side of the wall section 161a) and the surface of the flat plate section 125 on the heat exchanger 104 side intersect and the portion where the inner surface of the wall section 161a (i.e., the surface on the side of the side surface portion 146 of the scroll outlet section 137a) and the surface of the flat plate section 125 on the heat exchanger 104 side intersect is equal to or less than 0.5 times the rotor width W of the impeller 131a. In the air conditioner 101 of the present embodiment, by making the distance c equal to or less than 0.5 times the rotor width W, the negative pressure portion S103 can be reliably formed in the outside vicinity of the scroll blowout opening 135a. It will be noted that when the wall section 161a does not contact the flat plate section 125, the portion where the wall section 161a and the surface of the flat plate section 125 on the heat exchanger 104 side would intersect if the end portion of the wall section 161a on the flat plate section 125 side were to be extended corresponds to the portion where the wall section 161a and the surface of the flat plate section 125 on the heat exchanger 104 side intersect.

Further, in the present embodiment, a distance a from the surface of the flat plate section 125 on the heat exchanger 104 side to the end portion of the scroll outlet section 137a on the heat exchanger 104 side is greater than 0 and equal to or less than 0.3 times a rotor diameter D of the impeller 131a. More specifically, a distance a from the surface of the flat plate section 125 on the heat exchanger 104 side to the end portion of the side surface portion 146 of the scroll outlet section 137a on the heat exchanger 104 side is greater than 0 and equal to or less than 0.3 times the rotor diameter D of the impeller 131a. In the air conditioner 101 of the present embodiment, by making the distance a greater than 0—that is, by allowing the end portion of the scroll outlet section 137a on the heat exchanger 104 side to project toward the heat exchanger chamber S102—the negative pressure portion S103 comprising space interposed between the wall section 161a and the end portion of the scroll outlet section 137a on the heat exchanger 104 side can be formed in the outside vicinity of the scroll blowout opening 135a.

Further, in the present embodiment, a distance b from the surface of the flat plate section 125 on the heat exchanger 104 side to the end portion of the wall section 161a on the heat exchanger 104 side is equal to or greater than the distance a and equal to or less than 0.5 times the rotor diameter D of the impeller 131a. More specifically, a distance b from the surface of the flat plate section 125 on the heat exchanger 104 side to the end portion of the wall section 161a on the heat exchanger 104 side is equal to or greater than the distance a and equal to or less than 0.5 times the rotor diameter D of the impeller 131a. In the air conditioner 101 of the present embodiment, by making the distance b equal to or greater than the distance a—that is, by allowing the end portion of the wall section 161a to project further toward the heat exchanger 104 than the end portion of the scroll outlet section 137a on the heat exchanger 104 side—the difference in pressure between the pressure of the negative pressure portion S103 comprising space interposed between the wall section 161a and the end portion of the scroll outlet section 137a on the heat exchanger 104 side and the pressure of the air blown out into the heat exchanger chamber S102 from the scroll blowout opening 135a can be made greater.

Further, in the present embodiment, an angle θ formed by the wall section 161a and the surface of the flat plate section 125 on the heat exchanger 104 side is greater than 30° and equal to or less than 90°. More specifically, the angle θ formed by the inner surface of the wall section 161a (i.e., the surface on the side of the side surface portion 146 of the scroll outlet section 137a) and the portion of the surface of the flat plate 125 on the heat exchanger 104 side outside the wall section 161a is greater than 30° and equal to or less than 90°. In the air conditioner 101 of the present embodiment, by making the angle formed by the wall section 161a and the surface of the flat plate section 125 on the heat exchanger 104 side greater than 30°, the negative pressure portion S103 can be reliably formed in the outside vicinity of the scroll blowout opening 135a. Moreover, by making the angle formed by the wall section 161a and the surface of the flat plate section 125 on the heat exchanger 104 side equal to or less than 90°, it can be ensured that the air blown out into the heat exchanger chamber S102 from the scroll blowout opening 135a is reliably diffused to the outside of the scroll blowout opening 135a.

(2) Operation of Air Conditioner

Next, operation of the air conditioner 101 of the present embodiment will be described using FIG. 10 to FIG. 12.

When the motor 133 is started to actuate the centrifugal fan 103, air is sucked into the fan chamber S101 of the unit casing 102 via the unit suction opening 102g or the unit suction opening 102h, and the air that has been sucked into the fan chamber S101 is sucked into the scroll casings 132a and 132b through the scroll suction openings 134a and 134b and is blown out from the inner peripheral sides to the outer peripheral sides of the impellers 131a and 131b. The air that has been blown out to the outer peripheral sides of the impellers 131a and 131b and whose pressure has been boosted is blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b disposed so as to correspond to the communication openings 125a and 125b in the partition member 124. Then, the air that has been blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b is cooled or heated as a result of heat exchange being performed with refrigerant flowing inside the heat transfer tube of the heat exchanger 104 and is blown out into the room from the unit blowout opening 1021.

Here, in the air conditioner 101 of the present embodiment, the wall sections 161a and 161b that project from the heat exchanger 104 side of the flat plate section 125 are disposed outside the scroll outlet sections 137a and 137b, so that the negative pressure portions S103 whose pressure is lower than the pressure of the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b are formed in the outside vicinities of the scroll blowout openings 135a and 135b. Additionally, the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b (see arrow F in FIG. 12) flows so as to be pulled into the negative pressure portions S103, so that the air is more diffused to the outsides of the scroll blowout openings 135a and 135b in comparison to when wall sections are not disposed in the scroll outlet sections (see arrow f showing the flow of air when wall sections are not disposed in the scroll outlet sections). Specifically, the wall sections 161a and 161b are disposed outside the scroll outlet sections 137a and 137b in the rotational axis O direction, so that inside the heat exchanger chamber S102, the negative pressure portions S103 are formed in the outside vicinities of the scroll blowout openings 135a and 135b in the rotational axis O direction. For this reason, when the impellers 131a and 131b are disposed so as to rotate about the rotational axis O along the flat plate section 125 of the partition member 124 as in the air conditioner 101 of the present embodiment, there is a strong tendency for it to be difficult for the air blown out to the heat exchanger chamber S102 from the scroll outlet sections 137a and 137b opening in the direction intersecting the rotational axis O to be diffused in the direction along the rotational axis O, but because the negative pressure portions S103 are formed, the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b flows so as to be pulled into the negative pressure portions S103, so that it becomes easier for the air to be diffused to the outsides of the scroll blowout openings 135a and 135b in the rotational axis O direction. Thus, nonuniformity in the flow of air passing through the heat exchanger 104 can be controlled while controlling a reduction in blowing capability.

Moreover, the wall section 161a is disposed on the scroll casing 132b, which is the adjacent scroll casing, side of the outside of the scroll outlet section 137a and the wall section 161b is disposed on the scroll casing 132a, which is the adjacent scroll casing, side of the outside of the scroll outlet section 137b, so that inside the heat exchanger chamber S102, the negative pressure portions S103 are formed on the scroll casing 132b side of the scroll blowout opening 135a and on the scroll casing 132a side of the scroll blowout opening 135b. For this reason, when the impellers 131a and 131b are disposed so as to rotate about the rotational axis O along the flat plate section 125 of the partition member 124 and the impellers 131a and 131b and the scroll casings 132a and 132b are disposed plurally juxtaposed in the rotational axis O direction as in the air conditioner 101 of the present embodiment, a clearance is formed between the mutually adjacent scroll casing 132a and scroll casing 132b in the rotational axis O direction, and it becomes difficult for the air that has been blown out the heat exchanger chamber S102 from the scroll outlet sections 137a and 137b to pass through the portion corresponding to this clearance, but because the negative pressure portions S103 are formed, the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b flows so as to be pulled into the negative pressure portions S103, so that it becomes easier for the air to be diffused toward the scroll casing 132b side of the scroll blowout opening 135a and toward the scroll casing 132a side of the scroll blowout opening 135b. Thus, nonuniformity in the flow of air passing through the heat exchanger 104 can be controlled while controlling a reduction in blowing capability.

Further, the wall section 161a is disposed on the motor 133 side of the outside of the scroll outlet section 137a and the wall section 161b is disposed on the motor 133 side of the outside of the scroll outlet section 137b, so that inside the heat exchanger chamber S102, the negative pressure portions S103 are formed on the motor 133 side of the scroll blowout opening 135a and on the motor 133 side of the scroll blowout opening 135b. For this reason, when the motor 133 that drives the impellers 131a and 131b to rotate is disposed on the rotational axis O direction sides of the scroll casings 132a and 132b as in the air conditioner 101 of the present embodiment, the air that has been blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b ends up mainly passing through the portions of the heat exchanger 104 facing the scroll casings 132a and 132b with the flat plate section 124 interposed therebetween and it becomes difficult for the air to pass through the portion of the heat exchanger 104 facing the motor 133 with the flat plate section 124 interposed therebetween, but because the negative pressure portions S103 are formed, the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b flows so as to be pulled into the negative pressure portions S103, so that it becomes easier for the air to be diffused toward the motor 133 side of the scroll blowout openings 135a and 135b. Thus, nonuniformity in the flow of air passing through the heat exchanger 104 can be controlled while controlling a reduction in blowing capability.

Further, in the air conditioner 101 of the present embodiment, by making the distance c equal to or less than 0.5 times the rotor width W of the impellers 131a and 131b, the negative pressure portions S103 can be reliably formed in the outside vicinities of the scroll blowout openings 135a and 135b.

Further, in the air conditioner 101 of the present embodiment, by making the distance a greater than 0—that is, by allowing the end portions of the scroll outlet sections 137a and 137b on the heat exchanger 104 side to project toward the heat exchanger chamber S102—the negative pressure portions S103 comprising spaces interposed between the wall sections 161a and 161b and the end portions of the scroll outlet sections 137a and 137b on the heat exchanger 104 side can be formed in the outside vicinities of the scroll blowout openings 135a and 135b where the effect of causing the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b to be diffused outside the scroll blowout openings 135a and 135b is large. Moreover, by making the distance a equal to or less than 0.3 times the rotor diameter D of the impellers 131a and 131b, a distance that is sufficient for the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b to diffuse outside the scroll blowout openings 135a and 135b can be ensured between the scroll blowout openings 135a and 135b and the heat exchanger 104.

Further, in the air conditioner 101 of the present embodiment, by making the distance b equal to or greater than the distance a—that is, by allowing the end portions of the wall sections 161a and 161b to project further toward the heat exchanger 104 than the end portions of the scroll outlet sections 137a and 137b on the heat exchanger 104 side—the difference in pressure between the pressure of the negative pressure portions S103 comprising spaces interposed between the wall sections 161a and 161b and the end portions of the scroll outlet sections 137a and 137b on the heat exchanger 104 side and the pressure of the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 1135a and 135b can be made greater, so that the effect of causing the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b to be diffused to the outsides of the scroll blowout openings 135a and 135b can be raised. Moreover, by making the distance b equal to or less than 0.5 times the rotor diameter D of the impellers 131a and 131b, it can be ensured that the flow of air to be diffused by the negative pressure portions S103 to the outsides of the scroll blowout openings 135a and 135b is, as much as possible, not restricted by the wall sections 161a and 161b, so that the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b can be further diffused outside the wall sections 161a and 161b.

Further, in the air conditioner 101 of the present embodiment, by making the angle θ greater than 30°, the negative pressure portions S103 can be reliably formed in the outside vicinities of the scroll blowout openings 135a and 135b. Moreover, by making the angle θ equal to or less than 90°, it can be ensured that the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b is reliably diffused outside of the scroll blowout openings 135a and 135b.

In this manner, in the air conditioner 101 of the present embodiment, whereas the heat exchanger 104 faces substantially the entire flat plate section 125 of the partition member 124, the communication openings 125a and 125b in the flat plate section 125—that is, the scroll blowout openings 135a and 135b in the scroll casings 132a and 132b—are only disposed partially in the flat plate section 125 of the partition member 124, but by disposing the wall sections 161a and 161b, the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b can be diffused outside the scroll blowout openings 135a and 135b—and particularly outside in the rotational axis O direction—and allowed to pass through the heat exchanger 104 without having to increase the size of the scroll blowout openings 135a and 135b, and nonuniformity in the flow of air passing through the heat exchanger 104 can be controlled.

Moreover, because the wall sections 161a and 161b are disposed on the heat exchanger chamber S102 side of the flat plate section 125 of the partition member 124, problems do not arise where the wall sections 161a and 161b hinder the scroll suction openings 134a and 134b such that dynamic pressure recovery in the scroll outlet sections 137a and 137b becomes difficult, and the wall sections 161a and 161b are effective as means to control nonuniformity in the flow of air passing through the heat exchanger 104 when there is no extra space inside the fan chamber S101 or when the unit casing 102 must be made compact.

(3) Modification 1

In the air conditioner 101 of the present embodiment also, similar to modification 1 of the air conditioner 1 of the first embodiment, serrations may be disposed in the end portions of the wall sections 161a and 161b on the heat exchanger 104 side (see FIG. 13). Thus, variations in the pressure of the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b at the end portions of the wall sections 161a and 161b on the heat exchanger 104 side can be controlled, and the occurrence of noise resulting from pressure variations at the end portions of the wall sections 161a and 161b on the heat exchanger 104 side can be controlled.

Further, in the air conditioner 101 of the present embodiment also, similar to modification 2 of the air conditioner 1 of the first embodiment, plural dimples (see FIG. 14) or plural through holes 173 (see FIG. 15) may be disposed in the inner surfaces of the wall sections 161a and 161b. Thus, the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b can be matched to the surfaces of the wall sections 161a and 161b on the sides of the scroll outlet sections 137a and 137b, and the effect of causing the air blown out into the heat exchanger chamber S102 from the scroll blowout openings 135a and 135b to be diffused to the outsides of the scroll blowout openings 135a and 135b can be raised.

Moreover, in the air conditioner 101 of the present embodiment also, similar to modification 3 of the air conditioner 1 of the first embodiment, serrations 171 and plural dimples 172 or the through holes 173 may be simultaneously disposed in the wall sections 161a and 161b (see FIG. 16, which shows an example where the serrations 171 and the dimples 172 are disposed). Thus, the effect of disposing serrations and the effect of disposing plural dimples or through holes can be simultaneously obtained.

(2) Modification 2

Further, in the air conditioner 101 of the second embodiment (including modification 1) also, similar to modification 4 of the air conditioner 1 of the first embodiment, the scroll outlet sections 137a and 137b of the scroll casings 132a and 132b may be formed so as to extend toward the communication openings 125a and 125b while slanting toward the motor 133 but without their size L in the rotational axis O direction being enlarged (see FIG. 17). Thus, it becomes easier for the air that has been blown out into the heat exchanger chamber S102 to pass through the portion of the heat exchanger 104 facing the motor 133 with the flat plate section 125 interposed therebetween, and nonuniformity in the flow of air passing through the heat exchanger 104 can be controlled. Moreover, because it is ensured that the size L of the scroll outlet sections 137a and 137b in the rotational axis O direction is not enlarged, it also becomes difficult for drawbacks such as dynamic pressure recovery in the scroll outlet sections 137a and 137b becoming difficult to occur, and a reduction in blowing performance can be controlled.

Other Embodiments

Embodiments of the present invention have been described on the basis of the drawings, but the specific configuration thereof is not limited to these embodiments and may be altered in a range that does not depart from the gist of the invention.

For example, in the first embodiment, an example was described where the present invention was applied to a ceiling-hung type air conditioner, and in the second embodiment, an example was described where the present invention was applied to a duct type air conditioner, but the present invention is not limited thereto and may also be applied to a ceiling-embedded type air conditioner that is disposed with a unit casing partitioned by a partition member into a fan chamber and a heat exchanger chamber, with a centrifugal fan including an impeller and a scroll casing housing the impeller being disposed inside the fan chamber and a heat exchanger being disposed inside the heat exchanger chamber facing a scroll blowout opening in the scroll casing.

INDUSTRIAL APPLICABILITY

By utilizing the present invention, nonuniformity in the flow of air passing through a heat exchanger can be controlled while controlling a reduction in blowing capability in an air conditioner disposed with a unit casing partitioned by a partition member into a fan chamber and a heat exchanger chamber, with a centrifugal fan that includes an impeller and a scroll casing housing the impeller being disposed inside the fan chamber and a heat exchanger being disposed inside the heat exchanger chamber so as to face a scroll blowout opening in the scroll casing.

Number	Date	Country	Kind
2004-282115	Sep 2004	JP	national
2005-139411	May 2005	JP	national

Number	Name	Date	Kind
2250978	Weiland et al.	Jul 1941	A
2322357	Hagen	Jun 1943	A
2387348	Place	Oct 1945	A
3374831	Sieverding	Mar 1968	A
3524328	Schuster	Aug 1970	A
4189281	Katagiri et al.	Feb 1980	A
4840221	Dumas et al.	Jun 1989	A

Number	Date	Country
03-18415	Feb 1991	JP
05-099444	Apr 1993	JP
2002-106945	Apr 2002	JP

Air conditioner

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