TW202409480A - Refrigeration cycle device - Google Patents

Abstract

Provided is a refrigeration cycle device capable of inhibiting enlargement of a housing, inhibiting an increase in pressure loss and enhancing the air volume at the same time. The refrigeration cycle device is provided with a housing in which a heat interchanger and an air blower machine are accommodated. The air blower machine is a double-suction centrifugal blower including an impeller and a scroll cashing. The impeller has a plurality of blades arranged in a circumferential direction around a rotation axis. The scroll cashing is formed with a first fan suction inlet, a second fan suction inlet and a delivery outlet and an impeller is arranged inside. The scroll cashing has a first side wall surface, a second side wall surface and a peripheral wall surface, where the first side wall surface and the second side wall surface are arranged vertically to the rotation axis and interposing the impeller, and the peripheral wall surface connects the first side wall surface and the second side wall surface. The first fan suction inlet is formed on the first side wall surface. The second fan suction inlet is formed on the second side wall surface. A unit suction inlet is formed on the surface of the housing opposite to the first side wall surface. A suction duct is formed inside the housing from the unit suction inlet passing around the outer side of the peripheral wall to the second fan suction inlet.

Description

Refrigeration circulation device

The present disclosure relates to a refrigeration cycle device.

As is known, there is a technique of housing a double-suction multi-blade blower (sirocco fan) in a casing of an indoor unit (for example, see Patent Document 1). [Prior technical literature] [Patent Document]

Patent document 1: Japanese Patent Publication No. Sho 60-014021

[Problem to be solved by the invention]

However, in the technology shown in Patent Document 1, when the airflow flowing in from the suction port of the indoor unit flows toward either of the two suction ports of the double-suction multi-blade blower, the direction of the airflow is in the casing. All will turn. Therefore, pressure loss is likely to increase. In addition, in order to suppress the increase in pressure, the casing is enlarged.

This disclosure was developed to solve the above-mentioned problems. An object is to provide a refrigeration cycle device that can suppress an increase in pressure loss while suppressing an increase in the size of the casing, and increase the air volume. [Technical means used to solve problems]

The refrigeration cycle device of the present disclosure is provided with a shell, and the shell system accommodates a heat exchanger and an air blower inside; in the refrigeration cycle device: the aforementioned air blower is a double-suction centrifugal air blower with an impeller and a scroll casing. The impeller It has a plurality of fan blades arranged along the circumferential direction with the rotation axis as the center. The scroll shell is formed with a first fan suction inlet, a second fan suction inlet and a delivery outlet, and the aforementioned impeller is arranged inside; The scroll casing has a first side wall surface and a second side wall surface, and a peripheral wall surface. The first side wall surface and the second side wall surface are arranged perpendicular to the aforementioned rotation axis and across the aforementioned impeller. The peripheral wall surface is connected to the aforementioned peripheral wall surface. The first side wall surface and the aforementioned second side wall surface; the aforementioned first fan suction port is formed on the aforementioned first side wall surface; the aforementioned second fan suction port is formed on the aforementioned second side wall surface; and the aforementioned first side wall surface is opposite to the aforementioned first side wall surface. A unit suction port is formed on the surface of the casing; and a suction air passage is formed in the casing system from the unit suction port around the outside of the peripheral wall surface to the second fan suction port. [Efficacy of the invention]

According to the refrigeration cycle device of the present disclosure, it is possible to suppress the enlargement of the casing, suppress the increase of pressure loss, and achieve the effect of increasing the air volume.

The embodiments of the refrigeration circulation device disclosed in the present invention are described with reference to the attached drawings. In each figure, the same component symbols are used for the same or equivalent parts, and repeated descriptions are appropriately simplified or omitted. For the convenience of explanation, the positional relationship of each structure will be shown based on the illustrated state. In addition, the present invention is not limited to the following embodiments, but can freely combine the embodiments, change any constituent elements of each embodiment, or omit any constituent elements of each embodiment within the scope of the present invention.

Implementation 1. Refer to Figures 1 to 16 for explanation of Implementation 1 of the present disclosure. Figure 1 is a perspective top view of the interior of the housing of the indoor unit of the refrigeration cycle device. Figure 2 is a cross-sectional view of the indoor unit of the refrigeration cycle device. Figure 3 is a cross-sectional view obtained according to the section A-A shown in Figure 1. Figure 4 is a cross-sectional view of the air blower of the refrigeration cycle device. Figure 5 is a three-dimensional view of the impeller of the air blower of the refrigeration cycle device. Figure 6 is a perspective top view of the interior of the housing of different examples of the indoor unit of the refrigeration cycle device. Figure 7 is a cross-sectional view of the impeller of the air blower of the refrigeration cycle device. FIG8 is a cross-sectional view of a different example of an indoor unit of a refrigeration cycle device. FIG9 is a top view of an impeller of a blower of a refrigeration cycle device. FIG10 and FIG11 are top views of different examples of an impeller of a blower of a refrigeration cycle device. FIG12 to FIG15 are cross-sectional views of modified examples of an indoor unit of a refrigeration cycle device. FIG16 is a perspective top view of the inside of a casing of a different example of an indoor unit of a refrigeration cycle device.

The refrigeration cycle device of this embodiment is, for example, an air conditioning device. A refrigeration cycle device as an air conditioning device has an indoor unit and an outdoor unit. Each indoor unit and outdoor unit is equipped with a heat exchanger. The heat exchanger of the indoor unit and the heat exchanger of the outdoor unit are connected by refrigerant pipes arranged in a circular manner. The refrigeration cycle device circulates the refrigerant flowing in the refrigerant piping between the heat exchanger of the indoor unit and the heat exchanger of the outdoor unit, thereby causing heat to transfer between the heat exchanger of the indoor unit and the heat exchanger of the outdoor unit. move between them to function as a heat pump.

As shown in Fig. 1 to Fig. 3, the indoor unit of the refrigeration cycle device of this embodiment has a housing 10. The housing 10 has, for example, a rectangular shape. That is, in the illustrated configuration example, the housing 10 has a top surface 11, a bottom surface 12, and four side surfaces. The top surface 11 and the bottom surface 12 face each other. In addition, the left and right side surfaces and the front and rear side surfaces also face each other.

In the configuration example described here, the indoor unit is a ceiling-hung type. That is, the top surface 11 side of the housing 10 is fixed to the ceiling of the room. A unit suction port 13 is formed on the bottom surface 12 of the housing 10 . A unit blowout port 14 is formed on one side of the housing 10 . An air passage leading from the unit suction inlet 13 to the unit blowout outlet 14 is formed inside the casing 10 .

The housing 10 contains a heat exchanger 20, a blower 100, and an electrical component box 15. The heat exchanger 20 and the blower 100 are arranged in the air duct inside the housing 10. The blower 100 is arranged on the upstream side of the heat exchanger 20 in the air duct inside the housing 10. In other words, the blower 100 is arranged on the primary side of the heat exchanger 20. As shown in FIG. 3, the heat exchanger 20 is arranged in a V-shape, for example, on the upstream side of the unit blow-out port 14. The electrical component box 15 contains electrical components such as a control substrate and a power supply device.

The air blower 100 is a so-called double suction type centrifugal air blower. As shown in FIGS. 1 , 2 and 4 , the air blower 100 includes an impeller 200 , a scroll casing 110 , a motor 101 and a shaft 102 .

The impeller 200 is a centrifugal fan for generating airflow of the blower 100. The impeller 200 is disposed inside the vortex housing 110. The impeller 200 can rotate inside the vortex housing 110 around the shaft 102 forming a rotation axis.

As shown in FIG5 , the impeller 200 includes a main plate 201, two side plates 202, and a plurality of blades 210. The main plate 201 is a disc-shaped member. The shaft 102 is fixed to the center of the main plate 201. The plurality of blades 210 are arranged in a radial pattern on both surfaces of the main plate 201 along the circumferential direction of the main plate 201.

One end of each fan blade 210 is connected to the main plate part 201 , and the other end is connected to the side plate part 202 . That is, the plurality of fan blades 210 are respectively arranged between the main plate part 201 and the side plate part 202. The plurality of fan blades 210 are arranged along the circumferential direction with the rotation axis of the impeller 200 as the center. The plurality of fan blades 210 are arranged at certain intervals from each other in the circumferential direction of the main plate portion 201 .

The side plate 202 is a circular ring-shaped member. The side plate 202 is fixed to the end of the outer peripheral side opposite to the main plate 201 of the plurality of blades 210. The side plate 202 connects the plurality of blades 210 to maintain the positional relationship of the front ends of each blade 210 and reinforce the plurality of blades 210.

The vortex casing 110 straightens the air blown out from the impeller 200. The vortex casing 110 has a first side wall surface 111, a second side wall surface 112, and a peripheral wall surface 113. The first side wall surface 111 and the second side wall surface 112 are respectively arranged to be perpendicular to the rotation axis of the impeller 200. The first side wall surface 111 and the second side wall surface 112 are provided on both sides of the impeller 200 in the rotation axis direction of the impeller 200. That is, the first side wall surface 111 and the second side wall surface 112 are arranged to sandwich the impeller 200.

The peripheral wall surface 113 is provided to surround the impeller 200 from the radial outer side of the impeller 200 . The peripheral wall surface 113 connects the first side wall surface 111 and the second side wall surface 112 . The first side wall surface 111 and the second side wall surface 112 are arranged to face each other via the peripheral wall surface 113 . The peripheral wall surface 113 is arranged parallel to the rotation axis of the impeller, for example. In addition, the peripheral wall surface 113 may also be inclined relative to the rotation axis of the impeller 200, and is not limited to a configuration parallel to the rotation axis.

The first side wall surface 111 is formed with a first fan suction port 121. The second side wall surface 112 is formed with a second fan suction port 122. The first fan suction port 121 and the second fan suction port 122 are respectively circular with the rotation axis of the impeller 200 as the center. In addition, the shapes of the suction ports are not limited to circular shapes, and may be other shapes such as elliptical shapes.

A first bell mouth 114 is formed on the outer peripheral portion of the first fan suction port 121 of the first side wall surface 111 . The first bell mouth 114 rectifies the gas sucked by the impeller 200 and causes it to flow into the first fan suction inlet 121 . Similarly, the second bell mouth 115 rectifies the gas sucked by the impeller 200 and makes it flow into the second fan suction inlet 122 . The opening diameters of the first bell mouth 114 and the second bell mouth 115 are formed in a manner that gradually decreases from the outside to the inside of the scroll shell 110 . Thereby, the air near the first fan suction port 121 and the second fan suction port 122 will flow smoothly along the first bell mouth 114 and the second bell mouth 115 and be sucked in from the first fan suction port 121 and the second fan suction port 121 . Port 122 efficiently flows into impeller 200.

A delivery port 130 is formed in the scroll casing 110 . The delivery port 130 is an opening for the airflow in the volute casing 110 generated by the impeller 200 to be delivered. The opening shape of the delivery port 130 is, for example, a rectangular shape. However, the opening shape of the outlet 130 is not limited to a rectangular shape. The opening surface of the delivery port 130 is arranged parallel to the rotation axis of the impeller 200 .

The peripheral wall surface 113 of the vortex housing 110 guides the airflow generated by the impeller 200 to the outlet 130 along the curved wall surface. When viewed from a direction parallel to the rotation axis of the impeller 200, the peripheral wall surface 113 is formed as a curved surface in a spiral shape. As for the spiral shape, for example, there are logarithmic spirals, Archimedean spirals, or spiral shapes based on asymptotic curves. Thereby, the air sent out from the impeller 200 will flow smoothly in the gap between the impeller 200 and the peripheral wall in the direction of the outlet 130. Therefore, in the vortex housing 110, the static pressure of the air toward the outlet 130 is effectively increased.

In the following description, the "rotating shaft of the impeller 200" may be referred to as the "rotating shaft of the blower 100". The blower 100 constructed in the above manner is a double-intake centrifugal blower that inhales air from both ends of the rotating shaft of the blower 100 and blows out air in a direction perpendicular to the rotating shaft of the blower 100.

The motor 101 of the blower 100 is arranged on the second side wall surface 112 side of the scroll casing 110 . The shaft 102 transmits the rotational driving force of the motor 101 to each impeller 200 of each air blower 100 . The motor 101 is fixed on the top surface 11 of the housing 10 .

The blower 100 is configured in a housing 10 such that the first side wall surface 111 of the vortex housing 110 is close to the bottom surface 12 of the housing, and the second side wall surface 112 of the vortex housing 110 is close to the top surface 11. That is, the bottom surface 12 faces the first side wall surface 111. As mentioned above, the bottom surface 12 of the housing 10 is formed with a unit suction port 13. In other words, the bottom surface 12 of the housing 10, which is a face portion of the housing 10 and faces the first side wall surface 111, is formed with a unit suction port 13. Furthermore, the unit suction port 13 faces the first side wall surface 111.

As shown in FIGS. 1 and 2 , a suction air duct 300 is formed inside the casing 10 . The suction air duct 300 is an air duct that goes from the unit suction inlet 13 around the outside of the peripheral wall surface 113 of the scroll casing 110 to reach the second fan suction inlet 122 . The suction air duct 300 goes from the first side wall surface 111 side of the scroll casing 110 around the outside of the peripheral wall surface 113 to the second side wall surface 112 side. As shown in FIG. 1 , the suction air duct 300 is divided into a first air duct 301 , a second air duct 302 , a third air duct 303 and a fourth air duct 304 around the outer part of the peripheral wall 113 .

In the indoor unit of the air conditioning device belonging to the refrigeration cycle device configured in the above manner, when the impeller 200 of the blower 100 is rotated by the motor 101, a flow from the unit suction inlet 13 to the unit is generated in the air duct in the casing 10. Blow out the airflow from outlet 14. Part of the air sucked into the casing 10 from the unit suction port 13 flows into the scroll casing 110 from the first fan suction port 121 of the blower 100 .

The remaining part of the air sucked into the housing 10 from the unit suction port 13 flows toward the second side wall surface 112 through the suction duct 300. More specifically, the air that does not flow into the first fan suction port 121 first flows toward the peripheral wall surface 113 along the first side wall surface 111. Then, the air is divided into the first duct 301, the second duct 302, the third duct 303 and the fourth duct 304 and bypasses the outer side of the peripheral wall surface 113. The air that passes through the first duct 301, the second duct 302, the third duct 303 and the fourth duct 304 respectively converges in the space between the second side wall surface 112 and the top surface 11 of the housing 10. Furthermore, the merged air flows into the spiral casing 110 from the first fan inlet 121 of the blower 100 .

According to the indoor unit of the air conditioning device belonging to the refrigeration cycle device constructed in the above manner, a part of the air sucked into the housing 10 from the unit suction port 13 can flow directly into the spiral housing 110 from the first fan suction port 121 of the blower 100. In addition, the air that does not flow into the first fan suction port 121 can flow directly into the spiral housing 110 from the second fan suction port 122 through the suction duct 300. Therefore, even if the first fan suction port 121 of the blower 100 is arranged close to the unit suction port 13, the increase in pressure loss can be suppressed. According to this, the enlargement of the housing 10 can be suppressed, and the increase in pressure loss can be suppressed, and the air volume can be increased.

In the duct cross-sectional area of the portion of the outer side of the peripheral wall surface 113 of the suction duct 300, the duct cross-sectional area on the opposite side of the outlet 130 of the rotating shaft of the blower 100 is larger than the duct cross-sectional area on the side of the outlet 130 of the rotating shaft of the blower 100. The side of the outlet 130 of the rotating shaft of the blower 100 in the portion of the suction duct 300 around the outer side of the peripheral wall surface 113 refers to: the first duct 301 and the fourth duct 304 of the example shown in FIG. 1. Furthermore, the side of the outlet 130 of the rotating shaft of the blower 100 in the portion of the suction duct 300 around the outer side of the peripheral wall surface 113 refers to: the second duct 302 and the third duct 303 of the example shown in FIG. 1. Furthermore, the total cross-sectional area of the second air duct 302 and the third air duct 303 is greater than the total cross-sectional area of the first air duct 301 and the fourth air duct 304 .

In addition, the portion that bypasses the suction air duct 300 on the outside of the peripheral wall surface 113 is not limited to the configuration example shown in FIG. 1 in which it is divided into four air ducts. For other examples, as shown in FIG. 6 , the first air duct 301 and the second air duct 302 can also be connected. Furthermore, as shown in FIG. 6 , only the first air duct 301 , the second air duct 302 and the third air duct 303 may be formed.

As mentioned above, the plurality of blades 210 are disposed on both sides of the main board portion 201. That is, as shown in FIG7 , the plurality of blades 210 have a plurality of first blades 211 and a plurality of second blades 212. The plurality of first blades 211 are disposed on the surface of the first side wall surface 111 side of the main board portion 201. The plurality of second blades 212 are disposed on the surface of the second side wall surface 112 side of the main board portion 201. In the present embodiment, as shown in FIG8 , the length A of the first blade 211 in the direction parallel to the rotation axis of the blower 100 can be made greater than the length B of the second blade 212 in the direction parallel to the rotation axis of the blower 100. Thereby, the suction volume sucked in from the first fan suction port 121 is increased, and the pressure loss can be reduced and the air supply efficiency can be improved.

As shown in FIG. 9 , each of the plurality of blades 210 of the impeller 200 of the air blower 100 has a turbine blade 221 and a multi-blade blade 222 . The turbine airfoil 221 is provided on the inner circumferential side of the multi-blade airfoil 222 in the radial direction centered on the rotation axis of the impeller 200 . On the contrary, the multi-blade airfoil 222 is provided on the outer circumferential side than the turbine airfoil 221 in the radial direction centered on the rotation axis of the impeller 200 . The turbine airfoil 221 is formed so that the exit angle is 90 degrees or less and faces the fan blades. The multi-wing wing 222 forms a forward fan blade with an exit angle greater than 90 degrees. Here, the exit angle is the angle between the tangent line between the center line of the fan blade 210 and the outer diameter circle of the impeller 200 at the intersection point of the outer diameter circle of the impeller 200 and the center line of the fan blade 210 . The boundary between the turbine airfoil 221 and the multi-blade airfoil 222 is shown as a dotted line in FIG. 9 .

Each of the plurality of fan blades 210 is formed such that the height from the plate surface of the main plate portion 201 becomes lower toward the inner circumferential side from the inner circumferential end 204 . Furthermore, the turbine blade portion 221 includes the inner peripheral end portion 204 . In addition, the position of the inner peripheral end 204 is shown as a one-dot chain line in FIG. 9 .

As shown in FIG1 , when the blower 100 is viewed from a direction parallel to the rotation axis of the blower 100, the turbine blade 221 is exposed from the suction port of the blower 100. By designing in this way, the pressure recovery performance of the blower 100 can be improved by utilizing the turbine blade 221, and the input can be reduced.

In addition, the impeller 200 of the blower 100 is not limited to the one having both the turbine wing portion 221 and the multi-blade wing portion 222 as shown in FIG. 9 . The impeller 200 may also have only the turbine wing 221 as shown in FIG. 10 . In addition, the impeller 200 may also have only the multi-wing wing portion 222 as shown in FIG. 11 .

In addition, different structures may be adopted on the first side wall surface 111 side and the second side wall surface 112 side of the main panel portion 201 . That is, the first fan blade 211 and the second fan blade 212 may have different structures. For example, one of the first blade 211 and the second blade 212 may be configured as shown in FIG. 9 , and the other may be configured as shown in FIG. 10 . In addition, for example, one of the first fan blade 211 and the second fan blade 212 may be configured as shown in FIG. 9 , and the other may be configured as shown in FIG. 11 . Alternatively, for example, one of the first blade 211 and the second blade 212 may be configured as shown in FIG. 10 , and the other may be configured as shown in FIG. 11 .

Next, referring to FIG. 12 to FIG. 15 , the modified examples of the vortex shell 110 of the blower 100 of the present embodiment are described. In the first modified example shown in FIG. 12 , the portion of the circumferential wall surface 113 of the vortex shell 110 facing the main plate portion 201 of the impeller 200 is the most protruding toward the outer periphery, and the closer to the first side wall surface 111 and the second side wall surface 112, the less it protrudes toward the outer periphery. Furthermore, when viewing a cross section passing through the rotation axis of the blower 100, the portion of the circumferential wall surface 113 away from the first side wall surface 111 and the second side wall surface 112 is smoothly curved in a protruding manner toward the outer periphery. According to this first modification, the pressure loss of the airflow passing through the outer side of the peripheral wall surface 113 of the suction duct 300 can be reduced, and the air supply efficiency can be improved.

In the second modification shown in FIG. 13 , the outer peripheral edge portion of the second bell mouth 115 of the scroll casing 110 is chamfered. Therefore, when viewing the cross section passing through the rotation axis of the air blower 100, the outer peripheral edge of the second bell mouth 115 presents a smooth arc shape. Furthermore, in the structure shown in FIG. 13 , the outer peripheral edge portion of the first bell mouth 114 of the scroll casing 110 is similarly chamfered. Therefore, when viewing the cross section passing through the rotation axis of the air blower 100, the outer peripheral edge portion of the first bell mouth 114 exhibits a smooth arc shape. According to this second modification, the pressure loss of the air flow passing through the suction air duct 300 can be reduced, and the air supply efficiency can be improved.

In the third modification shown in FIG. 14 , the outer peripheral portion of the second bell mouth 115 of the scroll casing 110 is smoothly continuous with the peripheral wall surface 113 . Furthermore, in the structural example shown in FIG. 14 , the outer peripheral portion of the first bell mouth 114 of the scroll casing 110 is also smoothly continuous with the peripheral wall surface 113 . According to this third modification, the pressure loss of the air flow passing through the suction air duct 300 can be reduced, and the air supply efficiency can be improved.

In the fourth variant shown in FIG. 15 , no bell mouth is provided on the second side wall surface 112 of the vortex shell 110. With such a structure, the distance between the second side wall surface 112 of the vortex shell 110 and the top surface 11 of the housing 10 is expanded, and the space where the air flows of the first air duct 301, the second air duct 302, the third air duct 303 and the fourth air duct 304 passing through the suction air duct 300 converge with each other can be widened. Therefore, the suction volume of the second fan suction port 122 can be increased, and the air supply efficiency can be improved. In addition, as shown in FIG. 15 , the outer peripheral portion of the second fan suction port 122 in the second side wall surface 112 can be chamfered. In this case, when viewing a cross section passing through the rotation axis of the blower 100, the outer peripheral portion of the second fan suction port 122 presents a smooth arc shape. Thus, the separation of the airflow when being sucked by the second fan suction port 122 can be alleviated.

In addition, in the configuration example shown in FIG. 1 , the heat exchanger 20 is arranged at a position that is not opposite to the outlet 130 of the blower 100. According to such an arrangement, the unit depth direction of the housing 10 of the indoor unit can be shortened. However, the arrangement of the heat exchanger 20 is not limited to the example shown in FIG. 1 . For another example, as shown in FIG. 16 , the heat exchanger 20 can be arranged at a position that is opposite to the outlet 130 of the blower 100. According to such an arrangement, the unit width direction of the housing 10 of the indoor unit can be shortened.

Furthermore, in the structural example shown in FIG. 1 , the unit air outlet 14 of the casing 10 and the outlet 130 of the blower 100 are arranged so as not to face each other. In other words, in the projection plane parallel to the unit blowout port 14, the unit blowout port 14 and the delivery port 130 are arranged so as not to overlap. Noise generated during operation of the air blower 100 is mainly emitted from the outlet 130 toward the outside of the air blower 100 . According to such a configuration, the noise emitted from the outlet 130 when the air blower 100 is operating does not directly leak from the unit air outlet 14 to the outside of the casing 10, so that noise can be reduced. [Industrial availability]

The present disclosure can be applied to a refrigeration cycle device having a casing housing a blower and a heat exchanger.

10: Housing 11: Top surface 12: Bottom surface 13: Unit suction port 14: Unit blow-out port 15: Electrical parts box 20: Heat exchanger 100: Blower 101: Motor 102: Shaft 110: Vortex housing 111: First side wall surface 112: Second side wall surface 113: Peripheral wall surface 114: First bell mouth 115: Second bell mouth 121: First fan suction port 122: Second fan suction port 130: Blow-out port 200: Impeller 201: Main plate 202: Side plate 204: Inner peripheral end portion 210: Blade 211: First blade 212: Second blade 221: Turbine wing 222: Multi-wing wing 300: Intake air duct 301: First air duct 302: Second air duct 303: Third air duct 304: Fourth air duct

Fig. 1 is a perspective top view of the inside of the casing of the indoor unit included in the refrigeration cycle apparatus according to Embodiment 1. Fig. 2 is a cross-sectional view of the indoor unit included in the refrigeration cycle apparatus according to Embodiment 1. FIG. 3 is a cross-sectional view taken along the cross-section A-A shown in FIG. 1 of the first embodiment. Fig. 4 is a cross-sectional view of an air blower included in the refrigeration cycle apparatus according to Embodiment 1. FIG. 5 is a perspective view of the impeller of the blower included in the refrigeration cycle apparatus according to Embodiment 1. FIG. 6 is a perspective top view of the inside of the casing of a different example of the indoor unit included in the refrigeration cycle apparatus according to the first embodiment. Fig. 7 is a cross-sectional view of the impeller of the blower included in the refrigeration cycle apparatus according to Embodiment 1. 8 is a cross-sectional view of a different example of the indoor unit included in the refrigeration cycle apparatus according to Embodiment 1. FIG. 9 is a top view of the impeller of the blower included in the refrigeration cycle apparatus according to Embodiment 1. FIG. FIG. 10 is a plan view of a different example of the impeller of the blower included in the refrigeration cycle apparatus according to Embodiment 1. FIG. FIG. 11 is a plan view of a different example of an impeller of a blower included in the refrigeration cycle apparatus according to Embodiment 1. FIG. Fig. 12 is a cross-sectional view of a modified example of the indoor unit included in the refrigeration cycle apparatus according to Embodiment 1. Fig. 13 is a cross-sectional view of a modified example of the indoor unit included in the refrigeration cycle apparatus according to Embodiment 1. Fig. 14 is a cross-sectional view of a modified example of the indoor unit included in the refrigeration cycle apparatus according to Embodiment 1. Fig. 15 is a cross-sectional view of a modified example of the indoor unit included in the refrigeration cycle apparatus according to Embodiment 1. 16 is a perspective top view of the inside of the casing of a different example of the indoor unit included in the refrigeration cycle apparatus according to Embodiment 1.

10: Shell

14: Unit blowing outlet

15: Electrical parts box

20: Heat exchanger

100: Blower

101: Motor

110: Vortex shell

122:Second fan suction inlet

130: Send to exit

200: Impeller

221:Turbine wing

301: First air duct

302:Second air channel

303: The third air duct

304:Fourth Wind Channel

Claims (8)

A refrigeration circulation device is provided with a shell, and the shell is housed in an internal heat exchanger and a blower; in the refrigeration circulation device: The blower is a double-suction centrifugal blower, and has: An impeller having a plurality of blades arranged along a circumferential direction with a rotation axis as the center; and A vortex shell is formed with a first fan suction port, a second fan suction port and a delivery port, and the impeller is arranged inside; The vortex shell has: A first side wall surface and a second side wall surface, which are arranged perpendicular to the rotation axis and separated by the impeller; and A peripheral wall surface is connected to the first side wall surface and the second side wall surface; The first fan suction port is formed on the first side wall surface; The second fan suction port is formed on the second side wall surface; The surface of the housing facing the first side wall surface is formed with a unit suction port; An air intake duct is formed in the housing from the unit suction port around the outer side of the peripheral wall surface to reach the second fan suction port; The peripheral wall surface on the opposite side of the delivery port relative to the rotating shaft is connected to the inner wall surface of the housing; Among the air duct cross-sectional area of the portion of the suction duct that bypasses the outer side of the peripheral wall surface, the air duct cross-sectional area on the opposite side of the delivery port relative to the rotating shaft is greater than the air duct cross-sectional area on the delivery port side relative to the rotating shaft. A refrigeration circulation device as described in claim 1, wherein, when viewing a cross section passing through the aforementioned rotating shaft, a portion of the aforementioned peripheral wall surface away from the aforementioned first side wall surface and the aforementioned second side wall surface is smoothly curved in a manner of protruding toward the outer peripheral side. A refrigeration circulation device as described in claim 1 or 2, wherein the blower has a bell mouth, and the bell mouth is arranged on the periphery of the second fan suction port of the second side wall surface; The periphery of the bell mouth is smoothly continuous with the peripheral wall surface. A refrigeration circulation device as described in claim 1 or 2, wherein the outer peripheral edge of the aforementioned second fan suction port of the aforementioned second side wall surface is chamfered. The refrigeration cycle device according to claim 1 or 2, wherein the impeller system includes a main plate part and a plurality of fan blades; The aforementioned plurality of fan blades have: A plurality of first fan blades provided on the first side wall side of the main plate portion; A plurality of second fan blades provided on the second side wall surface side of the main plate portion; The length of the first fan blade in the direction parallel to the rotation axis is greater than the length of the second fan blade in the direction parallel to the rotation axis. A refrigeration circulation device as described in claim 1 or 2, wherein the surface of the shell facing the second side wall is fixed to the ceiling in the room. A refrigeration circulation device as described in claim 1 or 2, wherein, when the blower is viewed from a direction parallel to the rotation axis, the fan blade is exposed from one or both of the first fan suction port and the second fan suction port. A refrigeration circulation device as described in claim 1 or 2, wherein the plurality of blades of the impeller each have a turbine wing portion forming a backward blade with an outlet angle of less than 90 degrees.