JP2005241018A - Integral type air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an integral type air conditioner constituted by arranging a centrifugal indoor fan through a mouth ring on the downstream side of an indoor heat exchanger to reduce noise and to provide an air conditioner constituted by arranging an outdoor heat exchanger on the downstream side of an outdoor fan to reduce noise and suppress increase of fan motor input. <P>SOLUTION: In this integral type air conditioner constituted by arranging a unit storing a compressor, the outdoor heat exchanger, the indoor heat exchanger, the indoor fan, and the outdoor fan and the mouth ring between the indoor heat exchanger and the indoor fan, a circular arc plate 2 is provided at the outer periphery of the mouth ring to reduce noise. In the centrifugal type fan for feeding sucked air onto the downstream side in the axial direction due to a shape of a fan cover, outside diameter of a blade in contact with a hub is reduced for inside diameter of shroud suction port of the fan. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an integrated air conditioner.

  In general, the integrated air conditioner sucks air from the front of the unit and reaches the indoor fan suction port side via the indoor heat exchanger. A mouth ring provided in a casing is provided around the suction port side of the indoor fan. The air cooled by the indoor heat exchanger is blown out from the periphery of the indoor fan to the ventilation path, and blown into the room from the front of the unit.

  The integrated air conditioner described in Patent Document 1 is provided with an air inlet on the front of the front of the unit and air outlets on the left and right. And the air discharged from the indoor fan is blown out of the unit from the outlets installed on the left and right of the unit decorative frame. The casing is configured such that the amount of air blown from the left and right outlets is discharged in an equal amount on the left and right. Specifically, the blown air volume is equalized by providing convex noses on the lower left and upper right of the indoor fan.

  In addition, the structure of the centrifugal fan includes, as described in Patent Document 2, a hub, a plurality of blades erected on the hub, and a shroud that covers the outer periphery of the blade on the opposite hub side and forms a suction port. The outer diameter of the blade contacting the hub was larger than the inner diameter of the shroud.

JP 2001-221457 A

JP 2002-61597 A

  However, the integrated air conditioner described in Patent Document 1 has a problem that a fluid sound whose cause is not well understood is generated and the noise is increased in front of the unit.

  Also, if the outdoor fan is installed in a configuration that blows air sucked in from the periphery of the unit to the outdoor heat exchanger installed on the downstream side in the axial direction, fluid noise occurs and the unit noise increases. was there. For this reason, since the work amount by the blade increases, the power necessary for driving the fan increases. Therefore, there is a problem that the power consumption of the unit increases because the input power of the fan motor increases.

  A first object of the present invention is to reduce noise in an integrated air conditioner in which a centrifugal indoor fan is arranged via a mouth ring on the downstream side of an indoor heat exchanger.

  Moreover, the 2nd objective is providing the integrated air conditioner which reduced the noise and reduced the fan motor input in the air conditioner which has arrange | positioned the outdoor heat exchanger in the downstream of an outdoor fan.

  A third object is to provide an integrated air conditioner that improves the fan efficiency of an indoor fan.

  The first object is to provide an integrated air conditioner in which a compressor, an outdoor heat exchanger, an indoor heat exchanger, an indoor fan, and an outdoor fan are housed in a unit. A mouth ring provided around the suction port of the fan, and a plate-like member provided at a part or all of the outer periphery of the suction port of the indoor fan or the outdoor fan and having a portion higher than the raised height of the mouth ring. Is achieved.

  The second object is an integrated air conditioner in which a heat exchanger and a centrifugal fan in which a plurality of blades are arranged in a hub and a shroud is provided on the opposite side of the blades are housed in a unit. A partition plate that forms a discharge space together with a heat exchanger provided in the axial direction of the centrifugal fan, and a mouth ring that is provided in the partition plate and forms a suction port of the centrifugal fan; The fan is achieved by making the outer diameter of the blade in contact with the hub smaller than the inner diameter of the shroud suction port.

  The third object is to arrange a compressor, an outdoor heat exchanger, an indoor heat exchanger, a plurality of blades in a hub, and provide a shroud on the opposite side of the blade in the unit. In an integrated air conditioner that houses a centrifugal indoor fan that blows air from the exchanger to an outlet and an outdoor fan, the indoor fan has a blade outer diameter that contacts the hub rather than the inner diameter of the shroud suction port. This is achieved by increasing the size.

  As described above, according to the present invention, noise can be reduced in an integrated air conditioner in which a centrifugal indoor fan is arranged on the downstream side of an indoor heat exchanger via a mouth ring.

  Moreover, in the air conditioner having the outdoor heat exchanger arranged on the downstream side of the outdoor fan, it is possible to provide an integrated air conditioner with reduced noise and reduced fan motor input.

  Moreover, the integrated air conditioner which improved the fan efficiency of the indoor fan can be provided.

  In addition, about the effect | action which achieves the said effect, it becomes clear from the following description.

  An embodiment of the present invention will be described with reference to FIGS.

  The top view of the integrated air conditioner 100 which concerns on a present Example is shown in FIG. The integrated air conditioner 100 is provided with a partition plate 102 inside the housing 101 for partitioning into an indoor side and an outdoor side. On the indoor side, a heat exchanger 103 and a centrifugal indoor fan 10 that sucks indoor air and promotes heat exchange of the heat exchanger 103 are disposed, and the air discharged from the indoor fan 10 is integrated with air conditioning. Air passages 20 are provided to guide air to outlets 104 provided on the front left and right sides of machine 100. The front side of the air passage 20 is constituted by a suction side casing 21 between the heat exchanger 103 and the indoor fan 10, and the back side is constituted by a back side casing 19. The mouth ring 1 is arranged on the surface of the suction side casing 21 on the indoor heat exchanger 103 side. A centrifugal indoor fan 10 that sucks air from the axial direction and blows it out in the circumferential direction is disposed on the air passage 20 side of the mouth ring 1. The direction of the air discharged from the indoor fan 10 in the width direction of the integrated air conditioner 100 is changed by 90 degrees in order to blow out from the front into the room.

  As shown in the front sectional view of FIG. 4, protruding noses 22 and 23 are provided in the air passage 20 in order to distribute the air discharged by the indoor fan 10 to the left and right.

  Returning to FIG. 2, a suction ring 2 is mounted on the outer periphery of the mouth ring 1 with the configuration shown in FIG. 1.

  On the outdoor side, a centrifugal outdoor fan 30 that sucks outside air from the compressor 105, the heat exchanger 106, and the outside air intake 107 provided on the left and right side surfaces and the top surface of the casing and promotes heat exchange of the heat exchanger 106. Is provided. The indoor and outdoor fans are connected to a fan motor 108, and both fans rotate when the fan motor 108 rotates.

  The compressor 105, the indoor heat exchanger 103, and the outdoor heat exchanger 106 are connected by a refrigerant pipe 109 to constitute a series of refrigeration cycles.

  During the cooling operation of the integrated air conditioner 100, a drain water flow path (not shown) is configured so that drain water generated in the indoor heat exchanger 103 flows out to the bottom of the casing on the outdoor side.

  A splash ring 35 is installed on the outer periphery of the outdoor fan 30 as shown in FIG. The performance of the outdoor heat exchanger 106 is improved.

  Next, an example in which the suction ring 2 according to an embodiment of the present invention is applied to the indoor fan 10 will be described with reference to FIG. The mouth ring 1 is provided in a suction-side casing 21 on the suction port side of an air passage 20 that houses a centrifugal indoor fan 10. One end of the mouth ring 1 is attached to the suction side casing 21, and the other end is inserted into the suction port of the shroud 11 of the indoor fan 10. A suction ring 2 in which a plate is formed in an arc shape is mounted on the outer periphery of the mouth ring 1. The suction ring 2 does not have to cover the entire circumference of the mouth ring 1 and does not necessarily have a C shape (semi-circular plate-like rib) as in this embodiment. There may be no plate-like member (rib). In this embodiment, an arcuate suction ring 2 is installed on the upper semicircular portion of the mouth ring 1. The suction ring 2 may be attached to the suction-side casing 21 of the air passage 20 as a separate part from the mouth ring 1 or may be integrally molded with the mouth ring 1.

The installation position of the suction ring 2 is preferably at least the outer shape MD ₂ of the mouth ring 1 (outside the outer shape MD ₂ ). At least suction from the nose 22 to the nose 21 in the rotational direction of the indoor fan 10 in the range of the nose 22 formed into a convex shape above the air passage 20 and the nose 23 formed into a convex shape below the air passage 20. The ring 2 needs to be erected.

  Further, the height SH of the suction ring 2 is preferably equal to or higher than the height MH from the surface of the suction side casing 21 of the mouth ring 1. It is not necessary to make everything higher than the raised height of the mouth ring 1, and it is sufficient to make the place that is most effective for noise reduction.

  In the integrated air conditioner having the above structure, the operation of the indoor fan 10 will be described.

  The suction ring 2 is not provided on the suction port side of the conventional indoor fan. For this reason, noise of unknown cause was generated. At present, the mechanism of noise generation has not been clarified in detail, but a leading theory has been obtained through experiments on air flow visualization. This will be described below.

  As shown in FIG. 2, the axial center of the indoor fan 10 is deviated from the lateral center of the integrated air conditioner. This is shifted so that the axial center of the indoor fan is away from the space in which the compressor 105 is stored because the compressor 105 is stored. In order to make the blowout air volume of the blowout opening 104 provided on the front left and right of the main body the same, the shapes and heights of the noses 22 and 23 are determined as shown in FIG. Since the height of the nose is different between the right and left of the air passage 20, the passage cross-sectional area of the air blown from the indoor fan 10 is different on the right and left, and when the same amount of air flows to the left and right of the casing, The flow rate on the small side increases and the static pressure decreases. For this reason, the velocity of the airflow discharged from the indoor fan 10 is supposed to be different between the left and right sides of the casing. If there is a difference in the airflow speed between the left and right sides of the bath 20, the air that has passed through the mouth ring 1 is sucked into the air passage 20 where the airflow speed is high and the pressure is low, and is sucked into the central portion of the indoor fan 10 inlet. The air flow was disturbed at the fan suction port. It is thought that fluid noise is generated due to the turbulence of the air flow, and the noise increases in front of the unit. Further details will be described with reference to FIGS.

As shown in FIG. 1, when the centrifugal indoor fan 10 is rotationally driven, indoor air passes through the indoor heat exchanger 103 and is sucked into the mouth ring 1. At this time, along with the mainstream from the axial direction, the air sucked from the outer peripheral direction of the mouth diameter MD ₁ of the mouth ring 1 extends along the surface of the wall surface 21 of the air passage 20 and further rises in the fan axial direction. The air is sucked into the indoor fan 10 along the surface.

As shown in the front view of the integrated air conditioner in FIG. 4, the air discharged in the centrifugal direction by the rotation of the indoor fan 10 is distributed to the left and right of the air passage 20. The air passage 20 is provided with sudden noses 21 and 23 for efficiently distributing the air discharged from the circumferential direction of the centrifugal indoor fan 10 to the left and right. Example for _A 1 _{<A 2} cross-sectional area _{A 1} of the nose 23 side with respect to the cross-sectional area _{A 2} of the nose 22 of the air passage 20 are the shown. Assume that the flow velocity on the nose 23 side is v ₁ , the flow velocity on the nose 22 side is v _2, and the air volume Q discharged from the indoor fan 10 to the left and right air passages 20 is the same. At this time, the relationship between the flow velocity v, the air volume Q, and the cross-sectional area A is v = Q / A, so v ₁ > v ₂ If the flow velocity distribution of air is different between the right and left of the air passage 20, the static pressure on the nose 23 side having a high flow velocity is lower than that on the nose 22 side. Since air easily flows toward the lower pressure side, the air flowing along the mouth ring wall surface is drawn into the nose 23 side.

  This will be described with reference to FIG. FIG. 5 is a perspective view of the suction port surrounded by the mouth ring 1 from the indoor heat exchanger side, and shows the air flow on the surface of the mouth ring 1. The drawing on the left side of the drawing is a diagram in which the suction ring 2 is not provided, and the diagram on the right is a diagram in which the suction ring 2 according to the present embodiment is provided. As shown in the left figure, when the suction ring 2 is not provided, the air 200 on the side of the nose 23 is opposed to the rotation of the indoor fan 10 when the air 200 on the nose 23 side is sucked into the air passage 20 with a low pressure control. It is thought that a flow is formed. As described above, when an airflow opposite to the airflow that is about to be sucked into the center of the indoor fan 10 is generated at the fan intake port, the airflow is disturbed, and as a result, fluid noise is generated, resulting in an increase in noise. It is thought that it became.

  The operation when the suction ring 2 is installed for the air flow described above will be described with reference to the right side of FIG.

When the suction ring 2 is mounted on the outer periphery of the mouth ring 1, when the air sucked from the room is sucked into the mouth ring 1 along the wall surface of the suction side casing 21, it collides with the suction ring 2, and the air velocity is one end. In the lowered state, the air is guided to the suction port of the indoor fan 10 through the mouth ring 1. As shown in the present embodiment, the suction ring 2 is installed in a semicircular shape above the mouth ring 1 (in an arc shape from the nose 22 to the nose 23 of the air passage 20 where the flow velocity increases). The airflow velocity of the air that has passed through the suction ring 2 at the suction port is reduced. Since the indoor fan 10 rotates counterclockwise, the indoor fan 10 according to the present embodiment rotates counterclockwise in FIG. 4, and the centrifuge covered with the suction ring 2 due to the positional relationship between the noses 22 and 23 of the air passage 20. Most of the air sucked on the upper side of the fan 10 flows into the air passage 20 on the nose 23 side. Therefore, by suppressing the speed of the air flow sucked along the surface from the circumferential direction by the suction ring 2, the air volume on the nose 23 side is suppressed, and a relationship of v ₁ ≈v ₂ is established, and the static pressure is substantially equal on the left and right in the casing. Become. As shown in the right diagram of FIG. 5, the air flowing along the mouth ring wall surface flows to the center of the indoor fan 10, and the wind direction is unified in one direction, so that the airflow is not disturbed.

  As described above, the fluid noise generated by the turbulence of the airflow is reduced, so that the indoor noise is reduced. Since the above-mentioned theory is a hypothesis and it is unclear whether or not noise reduction can be actually performed, data comparing indoor noise with and without the suction ring 2 is shown in FIG. When compared with the same air volume, the noise is about 1 dB lower when the suction ring 2 is present. Therefore, the noise reduction effect on the indoor side can be obtained by attaching the suction ring 2 to the mouth ring 1 for the indoor fan 10 of the integrated air conditioner 100.

  If the structure of the suction ring described above is the structure of the air passage 20 and the indoor fan 10 shown in FIG. 4, it is installed in a bowl shape within the nose range at least from the nose 22 in the counterclockwise direction (the wind provided with the nose). If it is installed on the back surface of the road), the air flow noise at the indoor fan suction port is suppressed and the air flow noise is reduced, so that the noise reduction effect on the indoor side can be obtained.

  In addition, although the present Example demonstrated the integrated air conditioner which provided the two indoor side blower outlets, even if it is one, when the flow velocity of air is high, it is the same as the above from the fan peripheral direction of the mouth ring. Of the air flow sucked into the fan along the surface, the air flows in the direction opposite to the fan rotation direction, and noise may be generated. Moreover, it is anticipated that an air passage having a high flow velocity will also occur when there are three or more air outlets (when air outlets are provided in the lower part of the front in addition to the front left and right), and this also causes noise generation. Even in such a case, the suction ring according to the present embodiment is effective.

  Next, a modification of the suction ring 2 will be described with reference to FIG.

  The effect of reducing the indoor noise by the suction ring 2 is the same as that of the mouth ring 3 as shown in FIG. The mouth ring 3 of FIG. 5 is obtained by integrally injection-molding an arc-shaped rib 4 on the surface of the mouth ring wall surface so as to block the flow of airflow. In the case of the indoor fan 10 that rotates counterclockwise as shown in FIG. 4, the rib 4 only needs to be installed in a bowl shape within the range of the nose 23 from at least the nose 22 in the counterclockwise direction. The rib 4 of the present embodiment has a C-shape that covers the fan suction port in the same manner as the suction ring 2. The rib 4 suppresses the speed of the air flowing into the fan suction port, and can adjust the left and right airflow speeds inside the air passage 20. As a result, the airflow at the fan suction port is similar to the action of the suction ring 2. Disturbance can be suppressed, and the effect of reducing room noise can be obtained.

  In each of the above embodiments, the arc-shaped rib-shaped suction ring 2 is used. However, in order to reduce the flow velocity of the surface flow 200 shown in the left diagram of FIG. 5, a straight plate-shaped rib is provided upstream of this flow. However, noise can be reduced more than the right figure of FIG.

  Next, an embodiment of the outdoor fan 30 will be described with reference to FIG.

  The integrated air conditioner 100 shown in FIG. 8 is obtained by applying the suction ring 2 to the mouth ring 5 of the outdoor fan 30. The outdoor side sucks air from the outside air intake 107 by driving the outdoor fan 30, passes through the mouth ring 5 fixed to the fan cover 110, is sucked into the outdoor fan 30, and the air discharged from the outdoor fan is discharged to the outdoor heat exchanger 106. It is sprayed on and discharged outside the room. In the present embodiment, an example in which an L-shaped heat exchanger is applied is shown. However, since the cross-sectional area of the air passing is different between the right and left outlets of the outdoor fan 30 as described above, the flow velocity of air discharged from the fans is different. Is different. As described above, since the air at the fan suction port is drawn to the low pressure side where the airflow speed is high, the airflow is disturbed in contrast to the airflow sucked into the center of the fan, and fluid sound is generated. This fluid noise is added to the outdoor noise leaking outside the room.

  When the suction ring 2 shown in FIG. 1 is attached to the outer periphery of the mouth ring 5, the airflow speed passing through the suction ring 2 is reduced and discharged from the left and right of the outdoor fan 30, and the difference in airflow speed is suppressed. By controlling the static pressure distribution in the space of the exchanger 106, the air flowing along the wall surface of the mouth ring 5 flows to the center of the outdoor fan 30, the wind direction is unified in one direction, and the turbulence of the air flow is eliminated. As a result, it is possible to eliminate the generation of fluid noise caused by the turbulence of the air flow, and the outdoor noise is reduced because the fluid noise at the fan inlet is not added to the noise leaking outside.

  Moreover, when not using the suction ring 2 for the outdoor fans 30, you may install the mouth ring which provided the rib 4 like the mouth ring 3 shown in FIG.

  The application method of the suction ring 2 shown in FIG. 1 or the mouth ring 3 shown in FIG. 7 is the following three methods. (1) Applies only to indoor fans. (2) Applicable to indoor and outdoor fans. (3) Applies to outdoor fans only.

  Next, the indoor and outdoor fan shapes will be described with reference to FIGS.

In FIG. 9, the indoor fan 10 has a hub 13 having a boss 12 that transmits the rotational force of the fan motor 108 at the center of rotation, a plurality of blades 14 arranged at a predetermined interval on the hub 13, and the opposite of the hub 13. The shroud 11 is connected to each blade 14 on the side. The outer diameter D ₂ of the blade 14 is set to D ₂ SL ≧ D ₂ with respect to the maximum outer diameter D ₂ SL of the shroud 11, and as shown in the figure, the discharge is performed from the shroud 11 side to the hub 13 side, and the flow velocity distribution is appropriate. An inflection point 14a is provided in the middle for conversion. The outer diameter may be gradually reduced from the shroud 11 side toward the hub 13 side without providing the inflection point 14a. However, the blade outer diameter D ₂ H on the hub 13 side is D ₂ H> D ₁ S with respect to the suction port inner diameter D ₁ S of the shroud 11 and D ₂ H> DH with respect to the hub outer diameter DH. is there.

In FIG. 10, the outdoor fan 30 includes a hub 33 having a boss 32 that transmits the rotational force from the fan motor 108 at the center of rotation, a plurality of blades 34 arranged at a predetermined interval on the hub 33, and the hub 33. The shroud 31 is connected to each blade 34 on the opposite side. The outer diameter D ₂ of the blade 34 is D ₂ SL ≧ D ₂ with respect to the maximum outer diameter D ₂ SL of the shroud 31, and as shown in the figure, the discharge is performed from the shroud 31 side to the hub 33 side and the flow velocity distribution is appropriate. An inflection point 34a is provided in the middle for conversion. The outer diameter may be gradually reduced from the shroud 31 side toward the hub 33 side without providing the inflection point 34a. However, the blade outer diameter D ₂ H on the hub 33 side is D ₂ H> D ₁ S with respect to the suction port inner diameter D ₁ S of the shroud 31, and D ₂ H = DH with respect to the hub outer diameter DH. To do.

The outdoor fan 30 is equipped with a splash ring 35 that scoops up drain water stored at the bottom of the outdoor casing and sprays it on the outdoor heat exchanger 106. In this embodiment, the splash ring 35 is attached to the outer periphery of the shroud 31. An example is shown. The splash ring 35 is annularly installed on the outer periphery of the shroud 31 outer diameter D ₂ SL.

  A general centrifugal fan has the same structure as the indoor fan 10. In this embodiment, a fan having a different blade shape is used although it is a centrifugal fan indoors and outdoors.

  The outdoor fan 30 is provided with a heat exchanger on the air discharge side, whereas the indoor fan 10 is provided with a heat exchanger on the suction side. That is, the suction space and the discharge space are partitioned by a fan cover (partition plate) 110, and this discharge space is surrounded by the fan cover 110 and the outdoor heat exchanger 106 (not shown, but the top and bottom plates are vertically moved by the top plate and the floor plate). It separates the inside and outside of the unit). And although it is the centrifugal outdoor fan 30, the outdoor heat exchanger 106 exists also in this fan axial direction. For this reason, the air discharged in the radial direction of the fan is forced to flow in the axial direction. In addition, the mouth ring 5 is provided in the fan cover 110 which is a partition plate, and the outdoor fan 30 is disposed so that the mouth ring 5 serves as a suction port. This point will be described in detail.

  The outdoor fan 30 sucks air from the outside air intake port 107 through the mouth ring 5. The air sucked into the fan flows through the wall surface of the blade 34 by the rotation of the fan and is discharged in the centrifugal direction. The air discharged from the centrifugal fan 30 is blown axially in order to blow to the outdoor heat exchanger 106. The blowing in the axial direction determines the wind direction according to the shape of the fan cover 110. For this reason, the direction of the air discharged from the vicinity of the shroud 31 is forcibly changed in the axial direction.

Here, in the case of the centrifugal fan structure as shown in FIG. 9, the blade outer diameter D ₂ H on the hub side is larger than the hub outer diameter, so if this is applied as the outdoor fan 30, the outdoor fan 30 blows out. When the air flows in the axial direction, the hub side blade surface generates work that disturbs the axial flow. Therefore, an increase in outdoor noise accompanying the generation of fluid noise due to turbulent flow and a fan accompanying increased blade work The input of the motor 108 is increased.

For this reason, the outdoor fan 30 is an outdoor fan 30 as shown in FIG. That is, in the outdoor fan 30, since the hub-side blade outer diameter D ₂ H and the hub outer diameter DH are equal, the blade area hindering the axial flow is reduced, and the axial air flow is reduced. The disturbing factor can be reduced, and at the same time, the amount of work on the blade surface of the hub can be reduced, so that it is possible to reduce noise due to fluid noise and motor input.

  The relationship between the height b2 of the discharge port of the blade 34 and the distance b3 from the shroud 31 to the inflection point 34a is preferably 0.28 <b3 / b2 <0.58.

  When the outdoor fan structure is changed from the indoor fan 10 type to the outdoor fan 30 structure and b3 / b2 = 0.29, and the same air volume is used, the noise is reduced by about 3 dB and the motor input is reduced by about 30%. did it.

Since the indoor fan 10 discharges air in the centrifugal direction and discharges it into the room as it is, if the area of the blade 14 becomes small like the outdoor fan 30, the amount of air discharged decreases. As a result of comparing the performance of the indoor fan 10 fan and the fan in which the structure of the indoor fan 10 is changed to the structure of the outdoor fan 30, the fan speed of the outdoor fan structure increases by 7.3% to obtain the same air volume. Noise has increased by 2.5dB. The relationship between the rotational speed n of the centrifugal fan and the noise SL is SL = 60log (n1 / n2), so that the noise increases as the rotational speed increases. Therefore, in the indoor fan 10, it is desirable that the relationship between the shroud suction port inner diameter D ₁ S and the hub side blade outer diameter D ₂ H is D ₁ S <D ₂ H.

  As described above, according to the present embodiment, an integrated air conditioner with reduced indoor noise can be provided. Moreover, the integrated air conditioner which reduced outdoor noise and motor input can be provided.

The figure which shows the structure of a suction ring. The top view of the integrated air conditioner. Integrated air conditioner sectional drawing. Front sectional drawing of an integrated air conditioner. The figure which shows the wind direction around a mouse ring. The graph which shows the noise reduction effect of a suction ring. The figure which shows the structure of a mouse ring. The top view of the integrated air conditioner. Sectional drawing which showed the structure of the indoor side centrifugal fan. Sectional drawing which showed the structure of the outdoor centrifugal fan. The figure which shows the structure of an outdoor centrifugal fan.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Mouse ring, 2 ... Suction ring, 4 ... Rib, 10 ... Indoor fan, 11 ... Shroud, 13 ... Hub, 14 ... Blade, 20 ... Air path, 30 ... Outdoor fan, 35 ... Splash ring, 100 ... Integrated Air conditioner, 103 ... indoor heat exchanger, 105 ... compressor, 106 ... outdoor heat exchanger.

Claims (6)

  In an integrated air conditioner in which a compressor, an outdoor heat exchanger, an indoor heat exchanger, an indoor fan, and an outdoor fan are housed in a unit, provided around the inlet of the indoor fan or outdoor fan An integrated air conditioner provided with a mouth ring and a plate-like member provided on a part or all of the outer periphery of the suction port of the indoor fan or the outdoor fan and having a portion higher than the raised height of the mouth ring.   2. The integrated air conditioner according to claim 1, wherein the plate-like member is an arc-like plate-like member provided on the outer periphery of the mouth ring.   2. The integrated air conditioner according to claim 1, wherein the plate-like member is a rib erected on a mouth ring.   In an integrated air conditioner, in which a heat exchanger and a centrifugal fan in which a plurality of blades are arranged on a hub and a shroud is provided on the opposite side of the blades are housed in a unit, the axial direction of the centrifugal fan A partition plate that forms a discharge space together with the heat exchanger provided in the above, and a mouth ring that is provided in the partition plate and forms a suction port of the centrifugal fan. The centrifugal fan is connected to the shroud suction port. An integrated air conditioner in which the outer diameter of the blade contacting the hub is smaller than the inner diameter.   5. The integrated air conditioner according to claim 4, wherein the heat exchanger is an outdoor heat exchanger, and the centrifugal fan is an outdoor fan. In the unit, a compressor, an outdoor heat exchanger, an indoor heat exchanger, and a plurality of blades are arranged on the hub, and a shroud is provided on the opposite side of the blade to blow air from the indoor heat exchanger. An integrated air conditioner that houses a centrifugal indoor fan that blows air to an outlet and an outdoor fan, wherein the indoor fan has a blade outer diameter that is larger in contact with the hub than the inner diameter of the shroud suction port. .

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