JP2019196846A - Air conditioner - Google Patents

Abstract

To provide an air conditioner having a refrigeration cycle device and a fan stored in one casing, for improving the heat exchange performance of a heat exchanger of the refrigeration cycle device.SOLUTION: The air conditioner includes a refrigeration cycle device 20 having a condenser 22 for condensing high pressure refrigerant and a vaporizer 24 for vaporizing low pressure refrigerant, a first fan 30 for blowing heated air heated in the condenser 22, a second fan 31 for blowing cooled air cooled in the vaporizer 24, and a casing 10 storing the refrigeration cycle device 20, the first fan 30, and the second fan 31, the first fan 30 being arranged closer to the inlet side than the refrigerant flow outlet side of the condenser 22.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an air conditioner in which components such as a refrigeration cycle are housed in a housing.

  2. Description of the Related Art Conventionally, as an aspect of an air conditioner, one in which constituent devices such as a vapor compression refrigeration cycle apparatus and a blower are accommodated in a housing has been developed. Such an air conditioner is disposed, for example, between a seat surface portion and a floor surface of a seat disposed in a vehicle, and the seat is used as an air-conditioning target space to improve the comfort.

  As an invention related to such an air conditioner, for example, the invention described in Patent Document 1 is known. The air conditioner described in Patent Document 1 houses a refrigeration cycle including a condenser and an evaporator, and one centrifugal fan inside a main body case.

JP 2017-187218 A

  However, in the air conditioner described in Patent Document 1, since all the constituent devices are arranged in one housing, it is not possible to allow sufficient air to flow to the condenser and the evaporator. Therefore, there exists a problem that the heat exchange performance of a condenser and an evaporator cannot fully be exhibited.

  In view of the above points, an object of the present invention is to improve heat exchange performance in a heat exchanger of a refrigeration cycle apparatus in an air conditioner in which a refrigeration cycle apparatus, a blower, and the like are accommodated in a single housing.

In order to achieve the above object, in the invention according to claim 1, a refrigeration cycle apparatus (20) having a condenser (22) for condensing high-pressure refrigerant and an evaporator (24) for evaporating low-pressure refrigerant;
A first blower (30) for blowing heated air heated by a condenser;
A second blower (31) for blowing cooling air cooled by an evaporator;
A refrigeration cycle device, a housing (10) for housing the first blower and the second blower,
The first blower is disposed closer to the inlet side than the refrigerant flow outlet side of the condenser.

  According to this, heating air can be heat-exchanged in the part which becomes high temperature among condensers. For this reason, in a condenser, high-pressure refrigerant and heated air can be efficiently heat-exchanged. Therefore, the heat exchange performance in the heat exchanger of the refrigeration cycle apparatus can be improved.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

1 is an external perspective view of an air conditioner according to a first embodiment. It is a perspective view which shows the state which removed the upper cover of the air conditioner which concerns on 1st Embodiment. It is a perspective view which shows the state which removed the 1st air blower of the air conditioner which concerns on 1st Embodiment, and the 2nd air blower. It is a top view which shows the internal structure of the air conditioner which concerns on 1st Embodiment. It is sectional drawing which shows the VV cross section in FIG. It is sectional drawing which shows the VI-VI cross section in FIG. It is a block diagram which shows the control system of the air conditioner which concerns on 1st Embodiment. It is a top view which shows the internal structure at the time of the heating mode of the air conditioner which concerns on 1st Embodiment. It is explanatory drawing which shows the flow of the air to the supply port side in the heating mode which concerns on 1st Embodiment. It is explanatory drawing which shows the flow of the air to the exhaust-port side in the heating mode which concerns on 1st Embodiment. It is a top view which shows the internal structure at the time of the air mix mode of the air conditioner which concerns on 1st Embodiment. It is explanatory drawing which shows the flow of the air to the supply port side in the air mix mode which concerns on 1st Embodiment. It is explanatory drawing which shows the flow of the air to the exhaust-port side in the air mix mode which concerns on 1st Embodiment. It is a top view which shows the condenser which concerns on 1st Embodiment. It is explanatory drawing for demonstrating arrangement | positioning relationships, such as a 1st air blower and a condenser of the air conditioner which concerns on 1st Embodiment. It is explanatory drawing for demonstrating arrangement | positioning relationships, such as a 1st air blower and a condenser of the air conditioner which concerns on 2nd Embodiment. It is explanatory drawing for demonstrating arrangement | positioning relationships, such as a 1st air blower and a condenser of the air conditioner which concerns on 3rd Embodiment. It is explanatory drawing for demonstrating arrangement | positioning relationships, such as a 1st air blower and a condenser of the air conditioner which concerns on 4th Embodiment. It is explanatory drawing for demonstrating arrangement | positioning relationships, such as a 1st air blower and a condenser of the air conditioner which concerns on 5th Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

  In addition, the arrows indicating up, down, left, and right in each figure indicate a three-dimensional orthogonal coordinate system (for example, X axis, Y axis, Z axis) in order to facilitate understanding of the positional relationship of each component in the embodiment. ) Is exemplified as a standard corresponding to the above. Accordingly, the attitude and the like of the air conditioner according to the present invention are not limited to the states shown in the drawings, and can be changed as appropriate.

(First embodiment)
The air conditioner 1 according to the first embodiment is used in a seat air conditioner for improving the comfort of a passenger sitting on a seat, with a seat arranged in the vehicle interior of the vehicle as an air-conditioning target space. The air conditioner 1 is disposed in a small space between the seat surface portion of the seat and the passenger compartment floor, and supplies conditioned air (for example, cold air or hot air) through a duct disposed on the seat. Thus, it is configured to enhance the comfort of the passenger sitting on the seat.

  As shown in FIGS. 1 to 3, the air conditioner 1 according to the first embodiment includes a vapor compression refrigeration cycle device 20, a first blower 30, a second blower 31, and a hot air switching unit 35. The cold air switching unit 40 is housed in the housing 10.

  Therefore, the air conditioner 1 adjusts the temperature of the air blown by the operation of the first blower 30 and the second blower 31 by the refrigeration cycle device 20 and supplies the air to the passenger sitting on the seat through a duct or the like arranged on the seat. can do.

  First, a specific configuration of the housing 10 will be described with reference to FIGS. 2 shows a state where the upper cover 11 is removed from the state of FIG. 1, and FIG. 3 shows a state where the first blower 30 and the second blower 31 are removed from the state of FIG.

  In the air conditioner 1, the housing 10 is formed in a rectangular parallelepiped shape that can be disposed between the seat surface portion of the seat and the passenger compartment floor surface. As shown in FIG. 1, the housing 10 includes an upper cover 11 and a main body case 15.

  The upper cover 11 constitutes the upper surface of the housing 10 and is attached so as to close the opening of the main body case 15 having a box shape with the top opened. The upper cover 11 has a hot air vent 12, a cold air vent 13, a supply port 14, and an exhaust port 16.

  The hot air vent 12 is opened in the right side portion of the upper cover 11. The hot air vent 12 is a vent for sucking air outside the casing 10 (that is, air in the passenger compartment) into the casing 10 in accordance with the operation of the first blower 30 and the like described later. .

  As shown in FIGS. 1 to 6, the condenser 22 of the refrigeration cycle apparatus 20 is disposed in the housing 10 at a position below the hot air vent 12. Accordingly, the air sucked from the hot air vent 12 is heated by exchanging heat with the high-pressure refrigerant when passing through the condenser 22 and supplied as hot air WA.

  The cold air vent 13 is opened on the left side of the upper cover 11 and is arranged so as to be symmetric with the hot air vent 12. The cold air vent 13 is a vent for sucking air outside the housing 10 into the interior in accordance with the operation of the first blower 30 and the like, like the hot air vent 12.

  An evaporator 24 of the refrigeration cycle apparatus 20 is disposed at a position below the cold air vent 13 inside the housing 10. Therefore, the air sucked from the cold air vent 13 is cooled when passing through the evaporator 24 and supplied as cold air CA.

  A supply port 14 is opened at the rear center portion of the upper cover 11. The supply port 14 is a vent for supplying conditioned air (for example, hot air WA, cold air CA, mixed air MA) whose temperature has been adjusted by the refrigeration cycle device 20 in the air conditioner 1 to the air-conditioning target space.

  Although illustration is omitted, an end portion of a duct is connected to the supply port 14. The duct is disposed along the side of the seat and the like, and is configured to guide the conditioned air to a space where a passenger is seated in the seat. The space on the seat where the passenger is seated corresponds to the air-conditioning target space.

  Further, an exhaust port 16 is opened at the front center portion of the upper cover 11. The exhaust port 16 is an opening through which a part of the air whose temperature has been adjusted by the refrigeration cycle apparatus 20 is exhausted inside the housing 10. The air blown out from the exhaust port 16 is blown to the outside of the air conditioning target space.

  The main body case 15 constitutes a main part of the housing 10 and is formed in a box shape with the upper part opened. As shown in FIGS. 2 to 6, components such as the refrigeration cycle apparatus 20 and the first blower 30 are arranged inside the main body case 15.

  As shown in FIGS. 5, 6, etc., a hot air side ventilation path 17 and a cold air side ventilation path 18 are formed inside the main body case 15. The warm air side ventilation path 17 is a ventilation path through which the warm air WA heated by the condenser 22 circulates, and the cold air side ventilation path 18 is a ventilation path through which the cold air CA cooled by the evaporator 24 circulates. is there. Each of the hot air side air passage 17 and the cold air side air passage 18 is configured by the housing bottom surface 15A of the main body case 15 and the constituent devices.

  Next, the configuration of the refrigeration cycle apparatus 20 in the air conditioner 1 will be described with reference to the drawings. As described above, the refrigeration cycle apparatus 20 is accommodated in the housing 10 and constitutes a vapor compression refrigeration cycle.

  The refrigeration cycle apparatus 20 includes a compressor 21, a condenser 22, a decompression unit 23, an evaporator 24, and an accumulator 25. The refrigeration cycle apparatus 20 functions to cool or heat the air blown around the seat, which is the air-conditioning target space, by circulating the refrigerant by the operation of the compressor 21.

  Here, the refrigeration cycle apparatus 20 employs an HFC-based refrigerant (specifically, R134a) as a refrigerant, and uses a vapor compression subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. It is composed. Of course, an HFO refrigerant (for example, R1234yf), a natural refrigerant (for example, R744), or the like may be employed as the refrigerant. Furthermore, the refrigerant is mixed with refrigerating machine oil for lubricating the compressor 21, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

  In the refrigeration cycle apparatus 20, the compressor 21 sucks in refrigerant, compresses it, and discharges it. The compressor 21 is configured as an electric compressor that drives a fixed displacement type compression mechanism with a fixed discharge capacity by an electric motor. As shown in FIGS. 2 and 3, the compressor 21 is disposed inside the main body case 15. It is arranged on the rear side. In addition, as a compression mechanism of the compressor 21, various compression mechanisms, such as a scroll type compression mechanism and a vane type compression mechanism, are employable.

  The operation (that is, the rotation speed) of the electric motor constituting the compressor 21 is controlled by a control signal output from the control unit 60 shown in FIG. And the refrigerant | coolant discharge capability of the compressor 21 is changed because the said control part 60 controls the rotation speed of an electric motor.

  The inlet side of the condenser 22 is connected to a discharge pipe from which the high-pressure refrigerant compressed by the compressor 21 is discharged. The condenser 22 has a heat exchanging part 22A configured by laminating a plurality of tubes and fins in a flat plate shape, and exchanges heat between the air passing through the heat exchanging part 22A and the high-pressure refrigerant flowing through each tube. Let The detailed configuration of the condenser 22 will be described later.

  As shown in FIGS. 2 to 4, the condenser 22 is disposed on the right side of the main body case 15 and is located below the hot air vent 12. The heat exchanging part 22 </ b> A of the condenser 22 is formed larger than the opening area of the hot air vent 12. Therefore, the air sucked from the hot air vent 12 passes through the heat exchanging portion 22 </ b> A of the condenser 22.

  That is, the condenser 22 heat-exchanges the high-temperature and high-pressure discharged refrigerant discharged from the compressor 21 and the air sucked from the hot air vent 12 to heat the air to the hot air WA. Can do. That is, the condenser 22 operates as a heat exchanger for heating and functions as a radiator.

  And 22 A of heat exchange parts of the condenser 22 are formed in the flat form which makes a longitudinal direction the direction where a some tube and fin extend. As shown in FIGS. 2 to 6, the condenser 22 is arranged such that the longitudinal direction of the heat exchange unit 22 </ b> A is along the front-rear direction of the air conditioner 1.

  Further, as shown in FIGS. 5 and 6, the condenser 22 is arranged such that the heat exchanging portion 22 </ b> A is positioned above the casing bottom surface 15 </ b> A by a predetermined distance. The space formed below the condenser 22 is a space through which the hot air WA that has passed through the heat exchanging portion 22 </ b> A circulates, and functions as a part of the warm air side ventilation path 17.

  A decompression unit 23 is connected to the outlet side of the condenser 22. The decompression unit 23 is configured by a so-called fixed throttle, and decompresses the refrigerant that has flowed out of the condenser 22. As shown in FIG. 4, the decompression unit 23 is disposed on the front side inside the main body case 15.

  In the air conditioner 1, a fixed throttle is used as the decompression unit 23, but the present invention is not limited to this mode. As long as the refrigerant flowing out of the condenser 22 can be depressurized, various configurations can be employed as the depressurization unit. For example, a capillary tube may be employed as the decompression unit 23, or an expansion valve capable of controlling the throttle opening degree by a control signal from the control unit 60 may be used for the decompression unit 23.

  The inlet side of the evaporator 24 is connected to the outlet side of the decompression unit 23. The evaporator 24 includes a heat exchanging portion 24A configured by laminating a plurality of tubes and fins and configured in a flat plate shape. The evaporator 24 absorbs heat from the air passing through the heat exchanging portion 24A and flows through each tube. Evaporate.

  As shown in FIGS. 2 to 4, the evaporator 24 is arranged on the left side of the main body case 15 and is located below the cold air vent 13. Therefore, in the air conditioner 1, the evaporator 24 is disposed in the housing 10 with a space in the left-right direction with respect to the condenser 22.

  And the heat exchange part 24A of the evaporator 24 is formed larger than the opening area of the vent hole 13 for cold air. Accordingly, the air sucked from the cold air vent 13 passes through the heat exchanging portion 24 </ b> A of the evaporator 24.

  That is, the evaporator 24 can cool the air into the cold air CA by exchanging heat between the air sucked from the cold air vent 13 and the low-pressure refrigerant decompressed by the decompression unit 23. That is, the evaporator 24 operates as a cooling heat exchanger and functions as a heat absorber.

  And the heat exchange part 24A of the evaporator 24 is formed in the flat form which makes the direction where a some tube and fin extend the longitudinal direction. As shown in FIGS. 2 to 6, the evaporator 24 is arranged such that the longitudinal direction of the heat exchange unit 24 </ b> A is along the front-rear direction of the air conditioner 1.

  As shown in FIGS. 5 and 6, the evaporator 24 is disposed such that the heat exchanging portion 24 </ b> A is positioned above the housing bottom surface 15 </ b> A by a predetermined distance. The space formed below the evaporator 24 is a space through which the cold air CA that has passed through the heat exchanging section 24 </ b> A flows, and functions as a part of the cold air side ventilation path 18.

  An accumulator 25 is connected to the outlet side of the evaporator 24 and is disposed on the left side rear side of the main body case 15. The accumulator 25 separates the gas-liquid refrigerant flowing out of the evaporator 24 and stores excess liquid-phase refrigerant in the refrigeration cycle.

  A suction pipe of the compressor 21 is connected to the gas phase refrigerant outlet of the accumulator 25. Therefore, the gas phase refrigerant separated by the accumulator 25 is sucked into the compressor 21 via the suction pipe.

  As shown in FIG. 2, a first blower 30 and a second blower 31 are disposed inside the housing 10. The first blower 30 is a blower configured to include an impeller having a plurality of blades and an electric motor that rotates the impeller.

  The first blower 30 is located on the rear side between the condenser 22 and the evaporator 24, and is located below the supply port 14. Therefore, the 1st air blower 30 can blow with respect to the sheet | seat which is air-conditioning object space via the supply port 14 by rotating an impeller. That is, the first blower 30 of the present embodiment is a so-called suction blower that generates an air flow from the condenser 20 toward the first blower 30 by the rotation of the impeller.

  The second blower 31 is a blower having an impeller and an electric motor, like the first blower 30. As shown in FIG. 2, the second blower 31 is disposed between the condenser 22 and the evaporator 24 so as to be adjacent to the front side of the first blower 30.

  The second blower 31 is located below the exhaust port 16. Therefore, the second blower 31 can blow air to the outside of the air conditioning target space through the exhaust port 16 by rotating the impeller. That is, the second blower 31 of the present embodiment is a so-called suction blower that generates an air flow from the evaporator 24 toward the second blower 31 by the rotation of the impeller.

  As shown in FIG. 3 and the like, a fan support portion 55 is disposed below the first blower 30 and the second blower 31. The fan support portion 55 is disposed between the condenser 22 and the evaporator 24, and has a first attachment opening 56 and a second attachment opening 57. As shown in FIGS. 3 to 6, the fan support portion 55 is disposed so as to be located at a predetermined height from the housing bottom surface 15 </ b> A of the housing 10, and between the condenser 22 and the evaporator 24. The space is divided up and down.

  The first attachment opening 56 is an opening to which the first blower 30 is attached, and is disposed on the rear side of the fan support portion 55. On the other hand, the second attachment opening 57 is an opening to which the second blower 31 is attached and is disposed adjacent to the first attachment opening 56 on the front side of the fan support portion 55.

  Therefore, the first blower 30 can suck the air below the fan support portion 55 through the first mounting opening 56 and supply the air to the supply port 14. The second blower can suck the air below the fan support portion 55 through the second mounting opening 57 and blow it to the exhaust port 16.

  The configuration of the hot air switching unit 35 and the cold air switching unit 40 in the air conditioner 1 will be described with reference to the drawings.

  FIG. 5 shows a VV cross section in FIG. 4 and shows an example of the flow of air (that is, cold air CA) by the first blower 30. FIG. 6 shows a cross section taken along the line VI-VI in FIG. 4, and shows an example of the flow of air (that is, warm air WA) by the second blower 31.

  As shown in FIG. 3, the air conditioner 1 includes a hot air switching unit 35 and a cold air switching unit below the first blower 30 and the second blower 31 between the condenser 22 and the evaporator 24. 40. The warm air switching unit 35 is a mechanism for switching the air blow destination of the warm air WA heated by the condenser 22. The cold air switching unit 40 is a mechanism for switching the air blowing destination of the cold air CA cooled by the evaporator 24.

  The hot air switching unit 35 and the cold air switching unit 40 include a frame member 45 disposed below the fan support unit 55, a supply slide door 46, an exhaust slide door 47, a drive motor 50, and the like. ing.

  That is, the hot air switching unit 35 and the cold air switching unit 40 are disposed between the condenser 22 and the evaporator 24 disposed on the left and right sides in the housing 10. The hot air switching unit 35 is located on the right side between the condenser 22 and the evaporator 24 (that is, the side close to the condenser 22), and the cold air switching unit 40 includes the condenser 22 and the evaporator. 24 on the left side (ie, the side close to the evaporator 24).

  As shown in FIGS. 5 and 6, the frame member 45 is disposed below the fan support portion 55 between the condenser 22 and the evaporator 24, and extends along the front-rear direction. The said frame member 45 is formed in the circular arc shape which expanded below regarding the cross section perpendicular | vertical to the front-back direction.

A partition portion 45A is formed at the lower end portion of the frame member 45 swelled in an arc shape. The partition portion 45A is formed in a wall shape that closes between the lower end portion of the frame member 45 and the inner surface of the housing bottom surface 15A, and extends in the front-rear direction. That is, the space below the frame member 45 is divided into left and right by the partition portion 45A.

  A space below the frame member 45 and on the right side of the partition portion 45 </ b> A communicates with a space below the condenser 22 and constitutes a part of the warm air side ventilation path 17. Similarly, a space below the frame member 45 and on the left side of the partition portion 45 </ b> A communicates with a space below the evaporator 24 and constitutes a part of the cold air side ventilation path 18.

  A partition rib that partitions the space between the fan support portion 55 and the frame member 45 in the front-rear direction is formed at the center in the front-rear direction of the frame member 45. The space on the rear side of the partition rib communicates with the first mounting opening 56 and functions as a supply space 56A into which air supplied from the supply port 14 flows. The space on the front side of the partition rib communicates with the second mounting opening 57 and functions as an exhaust space 57A into which air blown from the exhaust port 16 flows.

  The hot air supply opening 36 and the hot air exhaust opening 37 constituting the hot air switching part 35 are arranged on the right side of the partition part 45A in the frame member 45 so as to be adjacent to each other in the front-rear direction. The hot air supply opening 36 is formed at the rear right side of the frame member 45, and communicates the supply space 56 </ b> A with the hot air side ventilation path 17. The hot air exhaust opening 37 is formed on the right front side of the frame member 45, and communicates the exhaust space 57 </ b> A and the hot air side ventilation path 17.

  As shown in FIGS. 5 and 6, the frame member 45 is formed in an arc shape that bulges downward toward the center in the left-right direction, and the hot air supply opening 36 and the hot air exhaust opening 37 are The right side of the frame member 45 is opened.

  Accordingly, the opening edges of the hot air supply opening 36 and the hot air exhaust opening 37 are formed so as to draw a downward arc as the distance from the right side of the housing 10 in which the condenser 22 is disposed. That is, of the opening edges of the hot air supply opening 36 and the hot air exhaust opening 37, the portion located on the condenser 22 side is separated from the partition portion through the hot air supply opening 36 and the hot air exhaust opening 37. It faces the part located on the 45A side. And the site | part located in the condenser 22 side is located above the site | part located in the partition part 45A side regarding the up-down direction of the air conditioner 1. FIG.

  Accordingly, the hot air supply opening 36 and the hot air exhaust opening 37 are formed so that the hot air supply opening 36 and the like are crossed in the left-right direction (that is, horizontally). In this case, the opening area becomes larger.

  Moreover, as shown in FIGS. 4-6, the condenser 22 is arrange | positioned so that the longitudinal direction of 22 A of heat exchange parts may follow a front-back direction. In the hot air switching section 35, the hot air supply opening 36 and the hot air exhaust opening 37 are arranged side by side in the front-rear direction.

  As a result, the air conditioner 1 relates to the air that has passed through the heat exchanging portion 22A of the condenser 22 for both the air volume flowing into the hot air supply opening 36 and the air volume flowing into the hot air exhaust opening 37. It can be secured sufficiently.

  The cold air supply opening 41 and the cold air exhaust opening 42 constituting the cold air switching unit 40 are arranged on the left side of the partition 45A in the frame member 45 so as to be adjacent to each other in the front-rear direction.

  The cold air supply opening 41 is formed at the left rear side of the frame member 45, and communicates the supply space 56 </ b> A with the cold air side ventilation path 18. As shown in FIG. 5, the cold air supply opening 41 is adjacent to the hot air supply opening 36 in the left-right direction in the frame member 45.

  The cold air exhaust opening 42 is formed on the left front side of the frame member 45, and communicates the exhaust space 57 </ b> A and the cold air side ventilation path 18. As shown in FIG. 6, the cold air exhaust opening 42 is adjacent to the hot air exhaust opening 37 in the left-right direction in the frame member 45.

  As described above, the frame member 45 is formed in an arc shape that bulges downward toward the center in the left-right direction, and the cold air supply opening 41 and the cold air exhaust opening 42 are on the left side of the frame member 45. Opened in the part.

  Accordingly, the opening edges of the cold air supply opening 41 and the cold air exhaust opening 42 are formed so as to draw a downward arc as the distance from the left side of the housing 10 in which the evaporator 24 is disposed. That is, of the opening edges of the cold air supply opening 41 and the cold air exhaust opening 42, the portion located on the evaporator 24 side is located on the partition 45A side via the cold air supply opening 41 and the cold air exhaust opening 42. It faces the part to do. And the site | part located in the evaporator 24 side is located above the site | part located in the partition part 45A side regarding the up-down direction of the air conditioner 1. FIG.

  Thereby, the opening area of the cold air supply opening 41 and the cold air exhaust opening 42 is an opening when the cold air supply opening 41 or the like is formed so as to cross the cold air side ventilation path 18 in the left-right direction (ie, horizontal). It becomes larger than the area.

  And as shown in FIGS. 4-6, the evaporator 24 is arrange | positioned so that the longitudinal direction of 24 A of heat exchange parts may follow a front-back direction. In the cold air switching unit 40, the cold air supply opening 41 and the cold air exhaust opening 42 are arranged side by side in the front-rear direction.

  As a result, the air conditioner 1 has sufficient airflow flowing into the cold air supply opening 41 and airflow flowing into the cold air exhaust opening 42 with respect to the air that has passed through the heat exchanging portion 24A of the evaporator 24. Can be secured.

  A supply slide door 46 is movably attached to the rear side of the frame member 45. The supply sliding door 46 is formed in a plate shape larger than the opening areas of the hot air supply opening 36 and the cold air supply opening 41, and is curved along the arc of the frame member 45.

  The supply slide door 46 is slidably mounted along the arc of the frame member 45 between a position where the hot air supply opening 36 is closed and a position where the cold air supply opening 41 is closed. Yes.

  Therefore, the air conditioner 1 moves the supply slide door 46 to move the air volume of the hot air WA flowing into the supply space 56A through the hot air supply opening 36 and the cold air supply opening 41. The air volume of the cold air CA flowing into the supply space 56A can be adjusted. That is, the supply slide door 46 can adjust the ratio of the hot air WA and the cold air CA in the air supplied from the supply port 14 and functions as a supply-side air volume adjustment unit.

  On the other hand, an exhaust slide door 47 is movably attached to the front side of the frame member 45. The exhaust slide door 47 is formed in a plate shape larger than the opening areas of the hot air exhaust opening 37 and the cold air exhaust opening 42, and is curved along the arc of the frame member 45.

  The exhaust slide door 47 is slidably mounted along the arc of the frame member 45 between a position where the hot air exhaust opening 37 is closed and a position where the cold air exhaust opening 42 is closed. Yes.

  Therefore, the air conditioner 1 moves the exhaust slide door 47 to move the air volume of the hot air WA flowing into the exhaust space 57A through the hot air exhaust opening 37 and the cold air exhaust opening 42. The air volume of the cold air CA flowing into the exhaust space 57A can be adjusted. In other words, the exhaust slide door 47 can adjust the ratio of the warm air WA and the cool air CA in the air blown from the exhaust port 16 and functions as an exhaust air volume adjustment unit.

  As shown in FIG. 4 and the like, a drive motor 50 is disposed inside the housing 10. The drive motor 50 is constituted by a so-called servo motor, and functions as a drive source for slidingly moving the supply slide door 46 and the exhaust slide door 47. The operation of the drive motor 50 is performed based on a control signal from the control unit 60.

  A supply shaft 48 is connected to the drive shaft of the drive motor 50. The supply shaft 48 extends from the drive motor 50 toward the front side, and has two gear portions 48A. The supply shaft 48 is disposed so as to cross the upper side of the supply slide door 46 in the front-rear direction.

  Then, two tooth portions 46A are arranged on the upper surface of the supply slide door 46 so as to extend in the left-right direction. The teeth 46A of the supply sliding door 46 are formed so as to mesh with the teeth in the gear 48A of the supply shaft 48, respectively.

  Accordingly, the power generated by the drive motor 50 is transmitted to the supply slide door 46 via the gear portion 48A and the tooth portion 46A. That is, the air conditioner 1 can slide the supply slide door 46 to an arbitrary position in the left-right direction by controlling the operation of the drive motor 50 by the control unit 60.

  On the other hand, an exhaust shaft 49 is rotatably supported on the front side of the supply shaft 48. The exhaust shaft 49 extends toward the front side so as to be parallel to the supply shaft 48 and has two gear portions 49A.

  As shown in FIG. 4, a transmission gear portion 48B is disposed at the front end portion of the supply shaft 48 and meshes with a driven gear portion 49B disposed at the rear end portion of the exhaust shaft 49. It is configured as follows. Accordingly, the power generated by the drive motor 50 is transmitted to the exhaust shaft 49 as the supply shaft 48 rotates.

  Then, two tooth portions 47 </ b> A are arranged on the upper surface of the exhaust slide door 47 so as to extend in the left-right direction. The tooth portions 47A of the exhaust slide door 47 are formed so as to mesh with the gear portions 49A of the exhaust shaft 49, respectively.

  Accordingly, the power generated by the drive motor 50 is transmitted through the supply shaft 48 to rotate the exhaust shaft 49. As a result, the exhaust slide door 47 slides between the hot air exhaust opening 37 and the cold air exhaust opening 42. That is, the air conditioner 1 can slide the exhaust slide door 47 to an arbitrary position in the left-right direction by controlling the operation of the drive motor 50 by the control unit 60.

  Further, according to the air conditioner 1, the power of the drive motor 50 is transmitted to the supply slide door 46 and the exhaust slide door 47 via the supply shaft 48 and the exhaust shaft 49, thereby supplying the supply slide door. The slide movement 46 and the slide movement of the exhaust slide door 47 can be linked.

  As shown in FIGS. 8 to 13, when the exhaust slide door 47 moves so that the opening area in the cold air exhaust opening 42 increases, the supply slide door 46 has an opening area in the hot air supply opening 36. Move to increase.

  In this case, the air volume ratio of the cold air CA in the air flowing into the exhaust space 57A increases, and the air volume ratio of the warm air WA in the air flowing into the supply space 56A increases. The air conditioner 1 can supply the mixed air MA, which is lower in temperature than the heating mode and higher in temperature than the cooling mode, to the air conditioning target space, and can realize an air mix mode from heating.

  When the exhaust slide door 47 moves so that the opening area of the hot air exhaust opening 37 increases, the supply slide door 46 moves so that the opening area of the cold air supply opening 41 increases.

  In this case, the air volume ratio of the warm air WA in the air flowing into the exhaust space 57A increases, and the air volume ratio of the cold air CA in the air flowing into the supply space 56A increases. The air conditioner 1 can supply the mixed air MA, which is lower in temperature than the heating mode and higher in temperature than the cooling mode, to the air conditioning target space, and can realize an air mix mode from cooling.

  According to the air conditioner 1 according to the first embodiment configured as described above, air conditioning is performed using the warm air WA heated by the condenser 22 of the refrigeration cycle apparatus 20 or the cold air CA cooled by the evaporator 24. Air-conditioned air can be supplied to the sheet that is the target space.

  And according to the said air conditioner 1, the cooling mode which supplies the cool air CA with respect to air-conditioning object space by controlling the action | operation of the switch part 35 for hot air and the switch part 40 for cold air, It is possible to realize a heating mode for supplying warm air WA, and an air mix mode for supplying mixed air MA, the temperature of which is adjusted by mixing cold air CA and warm air WA, to the air-conditioning target space.

  Next, a detailed configuration of the condenser 22 in the air conditioner 1 according to the first embodiment will be described with reference to the drawings. As shown in FIG. 14, the condenser 22 is a so-called tank-and-tube heat exchanger. Therefore, the condenser 22 includes a plurality of tubes 221 through which the refrigerant flows and a pair of header tanks 222 and 223.

  A plurality of tubes 221 are stacked in parallel in the left-right direction so that the longitudinal direction thereof coincides with the front-rear direction. The shape of the cross section perpendicular to the longitudinal direction of the tube 221 is a flat oval shape (that is, a flat shape). The tube 221 is disposed so that the flow direction of the air flowing outside the tube 221 matches the major axis direction in the flat shape.

  A wave-shaped fin 224 as a heat transfer member is joined to the outer surface of the tube 221. The fins 224 increase the heat exchange area (that is, the heat transfer area) with the air flowing around the tube 221 and promote the heat exchange between the refrigerant and the air.

  Hereinafter, the longitudinal direction of the tube 221 is referred to as a tube longitudinal direction, and the stacking direction of the tubes 221 is referred to as a tube stacking direction.

  22 A of heat exchange parts mentioned above are comprised by the laminated body on which the several tube 221 and the several fin 224 were laminated | stacked alternately. Inserts 225 that extend substantially in parallel with the tube longitudinal direction and reinforce the heat exchange part 22A are provided at both ends of the heat exchange part 22A in the tube stacking direction.

  The header tanks 222 and 223 communicate with the plurality of tubes 221, and collect or distribute refrigerant to the plurality of tubes 221. One header tank 222, 223 is provided at each of both end portions in the longitudinal direction of the tube (in this embodiment, front and rear end portions). The header tanks 222 and 223 extend in a direction orthogonal to the tube longitudinal direction (in the present embodiment, the left-right direction).

  Here, of the pair of header tanks 222 and 223, the one disposed on the rear side and that distributes the refrigerant to the tube 221 is referred to as an inlet tank 222. Further, among the pair of header tanks 222 and 223, the one that is disposed on the front side and collects the refrigerant flowing out from the tube 221 is referred to as an outlet tank 223.

  The inlet tank 222 is provided with a refrigerant inlet 226 as an inlet for allowing the high-pressure refrigerant discharged from the compressor 21 to flow into the inlet tank 222. The refrigerant inlet 226 is disposed on one end side of the inlet tank 222 in the tube stacking direction (right end side in this embodiment).

  The outlet tank 223 is provided with a refrigerant outlet 227 as an outlet through which the refrigerant flows out to the inlet side of the decompression unit 23. The refrigerant outlet 227 is disposed on the other end side in the tube stacking direction of the outlet tank 223 (in the present embodiment, on the left end side).

  The condenser 22 is formed in a rectangular shape having a long tube longitudinal direction. The flow direction of the refrigerant flowing through each tube 221 of the condenser 22 is the same. The refrigerant inlet 226 is disposed on one end side of the tube 221 in the tube longitudinal direction. The refrigerant outlet 227 is disposed on the other end side of the tube 221 in the tube longitudinal direction.

  For this reason, in the condenser 22, the refrigerant flows linearly in one direction from the refrigerant inlet 226 toward the refrigerant outlet 227. That is, the condenser 22 is configured so that the refrigerant does not make a U-turn inside thereof.

  Next, the arrangement relationship between the condenser 22 and the first blower 30 in the air conditioner 1 according to the first embodiment will be described with reference to the drawings. FIG. 15 shows a plan view as viewed from above the air conditioner 1. Hereinafter, the plan view viewed from the upper side of the air conditioner 1 is referred to as an upper plan view.

  In addition, arrangement | positioning etc. which contain the magnitude | size of the condenser 22 shown in FIG. 15, the 1st air blower 30, etc. are for convenience of description, and do not show actual arrangement. In FIG. 15, the solid line arrow schematically shows the refrigerant flow, and the white arrow schematically shows the air flow.

  As shown in FIGS. 2 and 15, the first blower 30 is disposed closer to the refrigerant inlet 226 than the refrigerant outlet 227 of the condenser 22. That is, the first blower 30 is arranged closer to the inlet side than the refrigerant flow outlet side of the condenser 22. In other words, the 1st air blower 30 is arrange | positioned so that the heating air heated in the site | part of a refrigerant | coolant flow upstream among 22 A of heat exchange parts of the condenser 22 may be ventilated.

  In the present embodiment, as shown in FIG. 15, when viewed from the left-right direction of the air conditioner 1 in the upper plan view, the first blower 30 and the heat exchange part 22 </ b> A of the condenser 22 on the upstream side of the refrigerant flow. The site is polymerized. That is, in the upper plan view, when viewed from the left-right direction of the air conditioner 1, the first blower 30 and the heat exchange part 22 </ b> A of the condenser 22 are arranged so as to overlap with the upstream portion of the refrigerant flow. .

  Specifically, in the upper plan view, when viewed from the left-right direction of the air conditioner 1, the first blower 30 and the portion of the heat exchange part 22A of the condenser 22 on the most upstream side of the refrigerant flow are superposed. ing. Moreover, when viewed from the left-right direction of the air conditioner 1 in the upper plan view, the entire first blower 30 and the upstream portion of the refrigerant flow in the heat exchanging portion 22A of the condenser 22 are arranged in a superposed manner. .

  Further, as shown in FIGS. 2 and 15, the second blower 31 is disposed closer to the inlet side than the refrigerant flow outlet side of the evaporator 24. In other words, the 2nd air blower 31 is arrange | positioned so that the cooling air cooled in the site | part of the refrigerant | coolant flow upstream among 24 A of heat exchange parts of the evaporator 24 may be ventilated.

  In the present embodiment, as shown in FIG. 15, when viewed from the left-right direction of the air conditioner 1 in the upper plan view, the second blower 31 and the heat exchange part 24 </ b> A of the evaporator 24 on the upstream side of the refrigerant flow. The site is polymerized. That is, in the upper plan view, when viewed from the left-right direction of the air conditioner 1, the second blower 31 and the heat exchange part 24 </ b> A of the evaporator 24 are arranged so as to overlap with the upstream portion of the refrigerant flow. .

  Specifically, when viewed from the left-right direction of the air conditioner 1 in the upper plan view, the second blower 31 and the portion on the most upstream side of the refrigerant flow in the heat exchanging portion 24A of the evaporator 24 are superposed. ing. In addition, when viewed from the left and right directions of the air conditioner 1 in an upper plan view, the entire second blower 31 and the upstream portion of the refrigerant flow in the heat exchanging portion 24A of the evaporator 24 are superposed. .

  Next, a control system of the air conditioner 1 according to the first embodiment will be described with reference to the drawings. As shown in FIG. 7, the air conditioner 1 has a control unit 60 for controlling the operation of the components of the air conditioner 1.

  The control unit 60 includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. And the control part 60 performs various arithmetic processing based on the control program memorize | stored in the ROM, and controls the action | operation of each component apparatus.

  The compressor 21, the first blower 30, the second blower 31, and the drive motor 50 are connected to the output side of the control unit 60. Therefore, the said control part 60 adjusts the refrigerant | coolant discharge performance (for example, refrigerant | coolant pressure) by the compressor 21, the ventilation performance (for example, ventilation volume) of the 1st blower 30, and the ventilation performance of the 2nd blower 31 according to a condition. can do.

  Further, the control unit 60 can adjust the air volume balance of the cold air CA and the hot air WA in the hot air switching unit 35 and the cold air switching unit 40 by controlling the operation of the drive motor 50. That is, the control unit 60 can change the operation mode in the air conditioner 1 to any one of the cooling mode, the heating mode, and the air mix mode.

  A plurality of types of air conditioning sensors 61 are connected to the input side of the control unit 60. The air conditioning sensor includes a plurality of types of sensors used for controlling the air conditioning operation of the air conditioner 1, and includes a pressure sensor 62.

  The pressure sensor 62 is a detection unit for detecting the refrigerant pressure on the low-pressure side of the cycle, and is disposed, for example, in the refrigerant pipe connected to the evaporator 24. Therefore, the control unit 60 can determine the magnitude of the load during the air-conditioning operation of the air conditioner 1 according to the magnitude of the low-pressure refrigerant pressure of the cycle detected by the pressure sensor 62, and accordingly Control can be performed.

  Further, the air conditioning sensor 61 is a suction temperature sensor for detecting the temperature of air sucked through the hot air vent 12 and the cold air vent 13, and the temperature of the air that has passed through the condenser 22 (that is, hot air WA). And a cold air temperature sensor for detecting the temperature of the air that has passed through the evaporator 24 (ie, the cold air CA).

  The air conditioning sensor 61 is, for example, a temperature sensor (that is, an evaporator temperature sensor) that detects a refrigerant temperature on the low pressure side of the cycle, a high pressure sensor that detects a refrigerant pressure on the high pressure side of the cycle, and a temperature of the high pressure refrigerant. A temperature sensor may be included. An operation panel for instructing the operation of the air conditioner 1 may be connected to the input side of the control unit 60.

  As described above, the air conditioner 1 according to the first embodiment can execute the cooling mode in which the cold air CA is supplied to the sheet that is the air-conditioning target space. Here, the operation of the air conditioner 1 in the cooling mode will be described with reference to FIGS. 4 to 6.

  In this cooling mode, the control unit 60 closes the hot air supply opening 36 with the supply slide door 46 and closes the cold air exhaust opening 42 with the exhaust slide door 47 so as to close the hot air switching unit 35. And the switching part 40 for cold air is controlled. That is, as shown in FIGS. 4 to 6, in the hot air switching unit 35, the hot air exhaust opening 37 is fully opened, and in the cold air switching unit 40, the cold air supply opening 41 is fully opened.

  As shown in FIG. 5, when the first blower 30 is operated in this state, the first blower 30 sucks air from the supply space 56 </ b> A and supplies the air to the sheet that is the air-conditioning target space via the supply port 14. .

  As described above, in the cooling mode, the hot air supply opening 36 is closed and the cold air supply opening 41 is opened. Therefore, as shown in FIG. 5, the first blower 30 sucks air from the cold air vent 13 and passes it through the heat exchange section 24 </ b> A of the evaporator 24.

  At this time, the air is absorbed by the low-pressure refrigerant flowing inside the evaporator 24 and becomes cold air CA. The cold air CA that has passed through the evaporator 24 flows through the cold air side ventilation path 18 and flows into the supply space 56A from the cold air supply opening 41. The cold air CA is sucked from the supply space 56A by the first blower 30 and supplied from the supply port 14 to the air-conditioning target space.

  In this cooling mode, since the hot air supply opening 36 is closed by the supply slide door 46, the air on the warm air side ventilation path 17 side is supplied to the supply space 56 </ b> A by the operation of the first blower 30. Never be sucked into. That is, in this case, the first blower 30 does not cause the air flow of the hot air vent 12 → the condenser 22 → the hot air side ventilation path 17 → the hot air supply opening 36.

  Therefore, in the cooling mode of the air conditioner 1, the cold air CA is generated by cooling the air blown by the first blower 30 by heat exchange with the low-pressure refrigerant in the evaporator 24. That is, the heat absorption amount of the refrigerant in the evaporator 24 of the refrigeration cycle apparatus 20 is greatly affected by the amount of air blown by the first blower 30. In other words, the air conditioner 1 can adjust the heat absorption amount of the refrigerant in the evaporator 24 by adjusting the air flow rate of the first blower 30 in the cooling mode.

  Further, when the second blower 31 is operated in the cooling mode, the second blower 31 sucks air from the exhaust space 57 </ b> A below and blows it out of the air-conditioning target space through the exhaust port 16.

  As shown in FIG. 6, in the cooling mode, the hot air exhaust opening 37 is opened, and the cold air exhaust opening 42 is closed. Accordingly, the second blower 31 sucks air from the hot air vent 12 and passes it through the heat exchanging portion 22 </ b> A of the condenser 22.

  At this time, the air is heated by heat exchange with the high-pressure refrigerant flowing through the condenser 22 and becomes hot air WA. The warm air WA that has passed through the condenser 22 flows through the warm air side ventilation passage 17 and flows into the exhaust space 57A from the warm air exhaust opening 37. The warm air WA is sucked from the exhaust space 57A by the second blower 31 and is blown from the exhaust port 16 to the outside of the air-conditioning target space.

  In this cooling mode, since the cold air exhaust opening 42 is closed by the exhaust slide door 47, the air on the cold air side ventilation path 18 side is sucked into the exhaust space 57A by the operation of the second blower 31. It will never be. That is, in this case, the second blower 31 does not cause an air flow of the cold air vent 13 → the evaporator 24 → the cold air side ventilation path 18 → the cold air exhaust opening 42.

  Therefore, in the cooling mode of the air conditioner 1, the warm air WA is generated by heating the air blown by the second blower 31 with the heat of the high-pressure refrigerant in the condenser 22. That is, the amount of heat released from the refrigerant in the condenser 22 of the refrigeration cycle apparatus 20 is greatly affected by the amount of air blown by the second blower 31. In other words, the air conditioner 1 can adjust the heat release amount of the refrigerant in the condenser 22 by adjusting the air flow rate of the second blower 31 in the cooling mode.

  Thus, the air conditioner 1 supplies the cold air CA cooled by the evaporator 24 from the supply port 14 to the air-conditioning target space by the first blower 30 and also the hot air WA heated by the condenser 22. The second blower 31 can blow air from the exhaust port 16. In other words, the air conditioner 1 can realize a cooling mode in which the cold air CA is supplied to the sheet that is the air conditioning target space.

  And according to the said air conditioner 1, in the air_conditioning | cooling mode, the heat absorption amount of the refrigerant | coolant in the evaporator 24 can be adjusted by adjusting the air flow rate of the 1st air blower 30, and the air flow rate of the 2nd air blower 31 can be adjusted. By adjusting, the heat dissipation amount of the refrigerant in the condenser 22 can be adjusted.

  Thereby, the air conditioner 1 can appropriately adjust the heat release amount of the refrigerant in the condenser 22 and the heat absorption amount of the refrigerant in the evaporator 24 in the cooling mode, and can easily balance the refrigeration cycle apparatus 20 in a stable manner. Can be activated.

  The first blower 30 in the cooling mode functions as a supply blower for supplying conditioned air to the air-conditioning target space, and at the same time, functions as a cold air blower for blowing the cold air CA. In other words, the first blower 30 sucks air through the evaporator 24 as at least one of the condenser 22 and the evaporator 24.

  And the 2nd air blower 31 in this case is functioning as an air blower for exhaust_gas | exhaustion for ventilating the exterior of air-conditioning object space, and an air blower for warm air WA at the same time. In other words, the second blower 31 sucks air through the condenser 22 as at least the other of the condenser 22 and the evaporator 24.

  Next, the operation of the air conditioner 1 in the heating mode will be described with reference to FIGS. In the heating mode, the control unit 60 closes the cold air supply opening 41 with the supply slide door 46 and closes the hot air exhaust opening 37 with the exhaust slide door 47 to switch the hot air switching unit 35 and The cool air switching unit 40 is controlled. That is, as shown in FIGS. 8 to 10, in the hot air switching unit 35, the hot air supply opening 36 is fully opened, and in the cold air switching unit 40, the cold air exhaust opening 42 is fully opened.

  As shown in FIG. 9, when the first blower 30 is operated in this state, the first blower 30 sucks air from the supply space 56 </ b> A and supplies the air to the seat that is the air-conditioning target space via the supply port 14. .

  As described above, in the heating mode, the cold air supply opening 41 is closed and the hot air supply opening 36 is opened. Therefore, as shown in FIG. 9, the first blower 30 sucks air from the hot air vent 12 and passes the heat exchange part 22 </ b> A of the condenser 22.

  At this time, the air is heated by the heat of the high-pressure refrigerant flowing inside the condenser 22 and becomes hot air WA. The warm air WA that has passed through the condenser 22 flows through the warm air side ventilation path 17 and flows into the supply space 56 </ b> A from the warm air supply opening 36. Then, the warm air WA is sucked from the supply space 56 </ b> A by the first blower 30 and supplied from the supply port 14 to the air-conditioning target space.

  In the heating mode, since the cold air supply opening 41 is closed by the supply slide door 46, the air on the cold air side ventilation path 18 side is sucked into the supply space 56A by the operation of the first blower 30. There is nothing. That is, in this case, the first air blower 30 does not cause an air flow of the cold air vent 13 → the evaporator 24 → the cold air side ventilation path 18 → the cold air supply opening 41.

  Therefore, in the heating mode of the air conditioner 1, the warm air WA is generated by heating the air blown by the first blower 30 with the heat of the high-pressure refrigerant in the condenser 22. That is, the heat release amount of the refrigerant in the condenser 22 of the refrigeration cycle apparatus 20 is greatly affected by the amount of air blown by the first blower 30. In other words, the air conditioner 1 can adjust the heat radiation amount of the refrigerant in the condenser 22 by adjusting the air volume of the first blower 30 in the heating mode.

  Further, when the second blower 31 is operated in the heating mode, the second blower 31 sucks air from the exhaust space 57 </ b> A and blows it outside the air-conditioning target space through the exhaust port 16. As shown in FIG. 10, in the heating mode, the cold air exhaust opening 42 is opened, and the hot air exhaust opening 37 is closed. Accordingly, the second blower 31 sucks air from the cold air vent 13 and passes it through the heat exchanging portion 24 </ b> A of the evaporator 24.

  In this case, the air is absorbed by the low-pressure refrigerant flowing through the evaporator 24 and becomes cold air CA. The cold air CA that has passed through the evaporator 24 flows through the cold air side ventilation path 18 and flows into the exhaust space 57A from the cold air exhaust opening 42. Then, the cold air CA is sucked from the exhaust space 57A by the second blower 31 and is blown from the exhaust port 16 to the outside of the air conditioning target space.

  In this heating mode, since the warm air exhaust opening 37 is closed by the exhaust slide door 47, the air on the warm air side ventilation path 17 side is exhausted by the operation of the second blower 31. Never be sucked into. That is, in this case, the second air blower 31 does not cause the air flow of the hot air vent 12 → the condenser 22 → the hot air side ventilation path 17 → the hot air exhaust opening 37.

  Therefore, in the heating mode of the air conditioner 1, the cold air CA is generated by absorbing the air blown by the second blower 31 with the low-pressure refrigerant in the evaporator 24. That is, the heat absorption amount of the refrigerant in the evaporator 24 of the refrigeration cycle apparatus 20 is greatly affected by the amount of air blown by the second blower 31. In other words, the air conditioner 1 can adjust the heat absorption amount of the refrigerant in the evaporator 24 by adjusting the amount of air blown by the second blower 31 in the heating mode.

  Thus, the air conditioner 1 supplies the warm air WA heated by the condenser 22 from the supply port 14 to the air-conditioning target space by the first blower 30 and also cool air CA cooled by the evaporator 24. The second blower 31 can blow air from the exhaust port 16. That is, the air conditioner 1 can realize a heating mode in which the hot air WA is supplied to the seat that is the air-conditioning target space.

  And according to the said air conditioning apparatus 1, in the heating mode, by adjusting the air flow rate of the 1st air blower 30, the thermal radiation amount of the refrigerant | coolant in the condenser 22 can be adjusted, and the air flow rate of the 2nd air blower 31 is adjusted. By adjusting, the heat absorption amount of the refrigerant in the evaporator 24 can be adjusted.

  Thereby, the said air conditioner 1 can adjust appropriately the heat dissipation amount of the refrigerant | coolant in the condenser 22 and the heat absorption amount of the refrigerant | coolant in the evaporator 24 in the heating mode, it is easy to balance the refrigerating-cycle apparatus 20, and is stable. Can be activated.

  The first blower 30 in the heating mode functions as a supply blower for supplying conditioned air to the air-conditioning target space, and at the same time, functions as a hot air blower for blowing the hot air WA. That is, the first blower 30 sucks air through the condenser 22 as at least one of the condenser 22 and the evaporator 24.

  And the 2nd air blower 31 in this case is functioning as an air blower for exhaust_gas | exhaustion for ventilating the exterior of air-conditioning object space, and simultaneously as an air blower for cold air CA. That is, the second blower 31 sucks air through the evaporator 24 as at least the other of the condenser 22 and the evaporator 24.

  Next, the operation of the air conditioner 1 in the air mix mode will be described with reference to FIGS. The air mix mode is an operation mode in which the mixed air MA obtained by mixing the hot air WA and the cold air CA is supplied to the air conditioning target space.

  In the air mix mode, the control unit 60 controls the position of the supply sliding door 46 so as to secure the opening area of the hot air supply opening 36 and the opening area of the cold air supply opening 41. At the same time, the control unit 60 controls the position of the exhaust sliding door 47 so that the opening area of the hot air exhaust opening 37 and the opening area of the cold air exhaust opening 42 are secured.

  As shown in FIG. 12, when the first blower 30 is operated in this state, the first blower 30 sucks air from the supply space 56 </ b> A and supplies the air to the seat that is the air-conditioning target space via the supply port 14. .

  In the air mix mode, an opening area is secured for both the hot air supply opening 36 and the cold air supply opening 41. Therefore, as shown in FIG. 12, the first blower 30 sucks air from the hot air vent 12 and passes the heat exchange part 22A of the condenser 22, and simultaneously sucks air from the cold air vent 13. The heat exchanger 24A of the evaporator 24 is passed through.

  As described above, the air passing through the condenser 22 is heated by the heat of the high-pressure refrigerant flowing inside the condenser 22 and becomes hot air WA. The warm air WA that has passed through the condenser 22 flows through the warm air side ventilation path 17 and flows into the supply space 56 </ b> A from the warm air supply opening 36.

  On the other hand, the air passing through the evaporator 24 is absorbed by the low-pressure refrigerant flowing through the evaporator 24 and becomes cold air CA. The cold air CA flows out from the evaporator 24 to the cold air side ventilation path 18 and flows into the supply space 56 </ b> A from the cold air supply opening 41.

  That is, in the air mix mode, the hot air WA and the cold air CA flow into and mix with the supply space 56A. Then, the air inside the supply space 56A is sucked in by the first blower 30 and supplied from the supply port 14 to the air-conditioning target space as the mixed air MA.

  As described above, the supply slide door 46 has a function of adjusting the opening area of the hot air supply opening 36 and the opening area of the cold air supply opening 41, so that the temperature flowing into the supply space 56A is adjusted. The air volume ratio of the wind WA and the cold air CA can be adjusted, and the mixed air MA can be supplied from the supply port 14.

  That is, the air conditioner 1 appropriately adjusts the temperature of the conditioned air (that is, the mixed air MA) supplied to the air-conditioning target space by adjusting the position of the supply slide door 46 in the air mix mode. Can do.

  Then, when the second blower 31 is operated in the air mix mode, the second blower 31 sucks air from the exhaust space 57 </ b> A as in the above-described cooling mode and the like, and the air-conditioning target space via the exhaust port 16. To the outside.

  As shown in FIG. 13, in the air mix mode, an opening area is secured for both the hot air exhaust opening 37 and the cold air exhaust opening 42. Accordingly, the second blower 31 sucks air from the hot air vent 12 and passes it through the heat exchanging portion 22A of the condenser 22, and simultaneously sucks air from the cool air vent 13 and heat exchanging portion of the evaporator 24. Pass 24A.

  Then, the warm air WA that has passed through the condenser 22 flows through the warm air side ventilation passage 17 and flows into the exhaust space 57A from the warm air exhaust opening 37. Similarly, the cold air CA that has passed through the evaporator 24 flows through the cold air side ventilation path 18 and flows into the exhaust space 57A from the cold air exhaust opening 42.

  Therefore, in the air mix mode, the hot air WA and the cold air CA flow into the exhaust space 57A and are mixed. Then, the air inside the exhaust space 57A is sucked in by the second blower 31 and is blown out from the exhaust port 16 to the outside of the air conditioning target space as the mixed air MA.

  As described above, the exhaust sliding door 47 has a function of adjusting the opening area of the hot air exhaust opening 37 and the opening area of the cold air exhaust opening 42, so that the temperature flowing into the exhaust space 57A. The air volume ratio of the wind WA and the cold air CA can be adjusted, and the mixed air MA can be blown from the exhaust port 16.

  Here, in the air conditioner 1, the control unit 60 is configured to control the operation of the compressor 21 according to the level of the air conditioning load detected by the pressure sensor 62 of the air conditioning sensor 61 or the like. In the conventional air conditioner, when such an air conditioning load is low, the operation and the operation stop of the electric motor constituting the compressor 21 are controlled to be repeated periodically.

  In the refrigeration cycle apparatus 20, the refrigerant circulates by the operation of the compressor 21, and the refrigerant contains refrigeration oil. For this reason, when the control is performed such that the operation and stoppage of the compressor 21 are periodically repeated at low load, it is assumed that the refrigerating machine oil returning to the compressor 21 due to the circulation of the refrigerant becomes insufficient. The

  In this regard, the air conditioner 1 performs an air mix mode as shown in FIGS. 11 to 13 when the air conditioning load is low. By operating the air conditioner 1 in the air mix mode, the minimum number of rotations of the electric motor of the compressor 21 can be maintained above a predetermined reference.

  That is, when the air conditioning load is low, the air conditioner 1 can maintain the circulating amount of the refrigerant in the refrigeration cycle device 20 at a predetermined reference or more by setting the air mix mode, and the low load Even in this case, it is possible to ensure the return amount of the refrigerating machine oil to the compressor 21 (that is, the oil return).

  Moreover, in this case, the air conditioner 1 air-conditions the air-conditioning target space while maintaining the minimum rotation speed of the electric motor at or above a predetermined reference by setting the air mix mode. That is, the air conditioner 1 can reduce the vibration caused by the ON-OFF control of the compressor 21 without periodically repeating the operation and stoppage of the electric motor of the compressor 21.

  As described above, the air-conditioning apparatus 1 according to the first embodiment includes the vapor compression refrigeration cycle apparatus 20, the first blower 30, the second blower 31, and the temperature as shown in FIGS. The wind switching unit 35 and the cold wind switching unit 40 are configured to be housed in the housing 10.

  As shown in FIGS. 4 to 6, in the air conditioner 1, the hot air switching unit 35 blows the hot air WA heated by the condenser 22 to the outside of the air conditioning target space, and the cold air switching unit 40. Thus, the cold air CA cooled by the evaporator 24 can be supplied to the air-conditioning target space. That is, the air conditioner 1 can realize a cooling mode for cooling the air-conditioning target space with a configuration in which components such as the refrigeration cycle apparatus 20 are accommodated in the housing 10 in a compact manner.

  In addition, as shown in FIGS. 8 to 10, the air conditioner 1 supplies the hot air WA heated by the condenser 22 to the air-conditioning target space by the hot air switching unit 35 and the cold air switching unit 40. Thus, the cold air cooled by the evaporator 24 can be blown to the outside of the air conditioning target space. That is, the air conditioner 1 can realize a heating mode for heating the air-conditioning target space with the configuration in which the components of the refrigeration cycle apparatus 20 are accommodated in the housing 10 in a compact manner.

  And according to the said air conditioner 1, since the ventilation capability of the 1st air blower 30 and the 2nd air blower 31 can be adjusted separately, the heat dissipation of the refrigerant | coolant in the condenser 22 of the refrigeration cycle apparatus 20, and the evaporator 24 The amount of heat absorbed by the refrigerant can be adjusted appropriately. As a result, the air conditioner 1 can easily balance the refrigeration cycle apparatus 20 and can be stably operated.

  As shown in FIGS. 4 to 13, the first blower 30 and the second blower 31 are heat exchangers (i.e., the condenser 22 or the evaporation) with respect to the flow of the blown air inside the housing 10 in the air conditioner 1. Disposed downstream of the container 24). For this reason, according to the air conditioner 1, the degree of freedom in design can be increased with respect to the arrangement of the first blower 30 and the second blower 31 inside the casing 10, and the size of the air conditioner 1 (that is, the casing) can be increased. 10) can be suppressed.

  And in the air conditioner 1 which concerns on 1st Embodiment, as shown to FIG. 6, FIG. 9, etc., the switching part 35 for warm air is 1st in the downstream rather than the condenser 22 regarding the flow of warm air WA. Arranged upstream of the blower 30 and the second blower 31. Further, as shown in FIGS. 5, 10, and the like, the cool air switching unit 40 is disposed downstream of the evaporator 24 and upstream of the first blower 30 and the second blower 31 with respect to the flow of the cool air CA. ing.

  Thus, the air conditioner 1 includes components such as the condenser 22, the evaporator 24, the first blower 30, the second blower 31, the hot air switching unit 35, and the cold air switching unit 40 inside the housing 10. On the other hand, it can be accommodated compactly.

  As shown in FIGS. 2 to 6 and the like, in the air conditioner 1, the condenser 22 and the evaporator 24 are arranged in the housing 10 at intervals in the left-right direction. The hot air switching unit 35 is disposed on the right side of the condenser 22 between the condenser 22 and the evaporator 24, and the cold air switching unit 40 is disposed between the condenser 22 and the evaporator 24. It is arranged on the left side of the evaporator 24 side.

  As a result, according to the air conditioner 1, the hot air switching unit 35 reliably switches the hot air WA flow and the cold air switching unit 40 switches the cold air CA flow. The housing 10 can be accommodated in a compact manner.

  As shown in FIGS. 4 to 6 and the like, the condenser 22 is arranged such that the longitudinal direction of the heat exchange part 22A is the front-rear direction. The hot air switching unit 35 has a hot air supply opening 36 and a hot air exhaust opening 37, and the hot air supply opening 36 and the hot air exhaust opening 37 are connected to the hot air side ventilation. In the path 17, they are arranged side by side in the front-rear direction.

  Thereby, according to the said air conditioner 1, the ventilation resistance at the time of passing the warm air supply opening 36 and the warm air exhaust opening 37 regarding the flow of the warm air WA that has passed through the heat exchanging portion 22A of the condenser 22 is reduced. While reducing, the air volume of the warm air WA which can pass each can be ensured.

  And the evaporator 24 is arrange | positioned so that the longitudinal direction of the heat exchange part 24A may turn into the front-back direction. The cold air switching unit 40 includes a cold air supply opening 41 and a cold air exhaust opening 42, and the cold air supply opening 41 and the cold air exhaust opening 42 are arranged in the front-rear direction in the cold air side ventilation path 18. Are arranged side by side.

  Thereby, according to the said air conditioner 1, regarding the flow of the cold wind CA which passed the heat exchange part 24A of the evaporator 24, reducing the ventilation resistance at the time of passing the cold wind supply opening 41 and the cold wind exhaust opening 42. The air volume of the cool air CA that can pass through each of them can be secured.

  In addition, the air conditioner 1 according to the first embodiment includes a supply slide door 46 and an exhaust slide door 47 that are slidably mounted by the power of the drive motor 50. The supply slide door 46 adjusts the air volume ratio of the hot air WA and the cold air CA with respect to the air supplied from the supply port 14 to the air-conditioning target space. The exhaust slide door 47 adjusts the air volume ratio of the hot air WA and the cold air CA with respect to the air blown from the exhaust port 16 to the outside of the air-conditioning target space.

  Then, as shown in FIGS. 11 to 13, the air conditioner 1 moves the supply slide door 46 to a position where the opening area in the hot air supply opening 36 and the opening area in the cold air supply opening 41 are secured. Thus, the mixed air MA obtained by mixing the warm air WA and the cold air CA can be supplied from the supply port 14 to the air-conditioning target space.

  In addition, the air conditioner 1 moves the exhaust slide door 47 to a position where the opening area of the hot air exhaust opening 37 and the opening area of the cold air exhaust opening 42 are secured, so that the outside of the air conditioning target space is moved. Thus, the mixed air MA can be blown from the exhaust port 16.

  When the air conditioning load is low, the air conditioner 1 can maintain the minimum rotation speed of the compressor 21 at or above a predetermined reference by setting the above-described air mix mode for supplying the mixed air MA.

  Thereby, in the refrigeration cycle apparatus 20 of the air conditioner 1, even when the air conditioning load is low, refrigerant exceeding a predetermined reference circulates, and therefore, oil return to the compressor 21 can be ensured.

  Further, according to the air conditioner 1, when the air conditioning load is low, the compressor 21 is configured so that the refrigerant discharge capacity according to the air conditioning load is obtained by setting the air mix mode as shown in FIGS. The operation can be continued. That is, since the air conditioner 1 does not repeat the operation and the operation stop of the compressor 21 periodically, it is possible to suppress the occurrence of vibration caused by the operation.

  In the air conditioner 1, the supply slide door 46 and the exhaust slide door 47 are configured to move by transmitting the power of the drive motor 50 through the supply shaft 48 and the exhaust shaft 49. That is, the movement of the exhaust slide door 47 is interlocked with the movement of the supply slide door 46 via the exhaust shaft 49.

  Therefore, when the exhaust slide door 47 moves so as to increase the opening area of the cold air exhaust opening 42, the supply slide door 46 is interlocked with the opening area of the hot air supply opening 36. Move to increase

  As a result, according to the air conditioner 1, in the air mix mode, the mixed air supplied from the supply port 14 in conjunction with increasing the air volume ratio of the cold air CA in the mixed air MA blown from the exhaust port 16. The air volume ratio of the warm air WA in the MA can be increased.

  When the exhaust slide door 47 moves so as to increase the opening area of the hot air exhaust opening 37, the supply slide door 46 interlocks with the opening area of the cold air supply opening 41. Move to increase.

  Thereby, according to the said air conditioner 1, in the air mix mode, the mixing supplied from the supply port 14 in conjunction with increasing the air volume ratio of the warm air WA in the mixed air MA blown from the exhaust port 16. The air volume ratio of the cold air CA in the wind MA can be increased.

  In the air conditioner 1 according to the first embodiment, the first blower 30 is disposed closer to the inlet side than the refrigerant flow outlet side of the condenser 22. According to this, heating air can be heat-exchanged in the part which becomes high temperature among the condensers 22. For this reason, in the condenser 22, it is possible to efficiently exchange heat between the high-pressure refrigerant and the heated air. Therefore, the heat exchange performance in the condenser 22 which is a heat exchanger of the refrigeration cycle apparatus 20 can be improved.

  More specifically, by disposing the first blower 30 closer to the inlet side than the refrigerant flow outlet side of the condenser 22, in the heating mode, the heated air flows in a portion of the condenser 22 where the temperature is relatively high. Heated. Thereby, the blowing temperature of the warm air WA supplied from the supply port 14 can be raised efficiently.

  Furthermore, according to the air conditioner 1, air flows in a concentrated manner in a part of the heat exchanging portion 22 </ b> A of the condenser 22, so that the effective heat exchange area of the condenser 22 is reduced. Thereby, since the high pressure of the refrigeration cycle apparatus 20 is increased, the temperature at which the hot air WA is supplied from the supply port 14 can be increased.

  On the other hand, by disposing the first blower 30 closer to the inlet side than the refrigerant flow outlet side of the condenser 22, in the cooling mode, the heated air is heated in a portion of the condenser 22 where the temperature difference from the air is relatively large. Is heated. For this reason, since the heat exchange efficiency in the condenser 22 is improved, the high pressure of the refrigeration cycle apparatus 20 can be reduced. Thereby, the coefficient of performance (COP) of the refrigeration cycle apparatus 20 can be improved.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. The second embodiment is different from the first embodiment in the arrangement of the second blower 31.

  As shown in FIG. 16, the second blower 31 is disposed closer to the center than both the refrigerant flow outlet side and the inlet side of the evaporator 24. That is, the 2nd air blower 31 is arrange | positioned in the site | part from which the distance from the refrigerant | coolant flow outlet side of the evaporator 24 and the distance from the refrigerant | coolant flow inlet side become equivalent. In other words, the 2nd air blower 31 is arrange | positioned so that the cooling air cooled in the refrigerant | coolant flow center part among the heat exchange parts 24A of the evaporator 24 may be ventilated.

  In the present embodiment, as shown in FIG. 16, when viewed from the left and right directions of the air conditioner 1 in the upper plan view, the second blower 31 and the refrigerant flow center portion in the heat exchange portion 24 </ b> A of the evaporator 24. Are arranged in a polymerized manner. That is, when viewed from the left and right directions of the air conditioner 1 in the upper plan view, the second blower 31 and the refrigerant central portion of the heat exchanging portion 24A of the evaporator 24 are arranged so as to overlap each other.

  Other configurations and operations of the air conditioner 1 are the same as those in the first embodiment. Therefore, also in the air conditioner 1 of this embodiment, the effect similar to 1st Embodiment can be acquired.

  Furthermore, in this embodiment, the 2nd air blower 31 is arrange | positioned near the center part rather than both the refrigerant | coolant flow outlet side and inlet side of the evaporator 24. FIG. According to this, since air flows over the entire surface of the heat exchange section 24 of the evaporator 24, the effective heat exchange area of the evaporator 24 is increased. Thereby, since the heat exchange efficiency in the evaporator 24 improves, the coefficient of performance (COP) of the refrigeration cycle apparatus 20 can be improved.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. The third embodiment is different from the first embodiment in the arrangement of the first blower 30 and the second blower 31.

  As shown in FIG. 17, in the air conditioner 1 of the present embodiment, the distance between the condenser 22 and the evaporator 24 is shorter than the diameter of the first blower 30 in the upper plan view. Similarly, in the upper plan view, the distance between the condenser 22 and the evaporator 24 is shorter than the diameter of the second blower 31.

  For this reason, the first blower 30 and the second blower 31 are not disposed between the condenser 22 and the evaporator 24 in the upper plan view. Further, when viewed from the left and right directions of the air conditioner 1 in the upper plan view, the first blower 30 and the condenser 22 are arranged so as not to overlap. Similarly, the second blower 31 and the evaporator 24 are arranged so as not to overlap when viewed from the left-right direction of the air conditioner 1 in an upper plan view.

  Further, in the upper plan view, the first blower 30 is arranged so as not to overlap with either the condenser 22 or the evaporator 24 when viewed from the front-rear direction of the air conditioner 1. Similarly, the second blower 31 is disposed so as not to overlap with either the condenser 22 or the evaporator 24 when viewed from the front-rear direction of the air conditioner 1. The first blower 30 is disposed so as to overlap the second blower 31 when viewed from the front-rear direction of the air conditioner 1.

  Specifically, the first blower 30 is disposed on the left side and the rear side with respect to the condenser 22 in an upper plan view. That is, the first blower 30 is disposed on the evaporator 24 side with respect to the condenser 22 and on the refrigerant flow outlet side of the condenser 22 in the upper plan view.

  Further, the second blower 31 is disposed on the right side and the front side with respect to the evaporator 24 in the upper plan view. That is, the second blower 31 is arranged on the condenser 22 side and the refrigerant flow inlet side of the evaporator 24 with respect to the evaporator 24 in the upper plan view.

  In the present embodiment, the air conditioner 1 has a wall portion 70 that guides the warm air WA heated by the condenser 22 to the first blower 30 and guides the cool air CA cooled by the evaporator 24 to the second blower 31. is doing. The partition wall 70 is disposed so as to connect an end portion on the refrigerant flow outlet side of the condenser 22 and an end portion on the refrigerant flow outlet side of the evaporator 24 in an upper plan view.

  Other configurations and operations of the air conditioner 1 are the same as those in the first embodiment. Therefore, also in the air conditioner 1 of this embodiment, the effect similar to 1st Embodiment can be acquired.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIG. The fourth embodiment differs from the first embodiment in the arrangement of the first blower 30 and the second blower 31.

  As shown in FIG. 18, in the air conditioner 1 of the present embodiment, the distance between the condenser 22 and the evaporator 24 is shorter than the diameter of the first blower 30 in the upper plan view. Similarly, in the upper plan view, the distance between the condenser 22 and the evaporator 24 is shorter than the diameter of the second blower 31. For this reason, the first blower 30 and the second blower 31 are not disposed between the condenser 22 and the evaporator 24 in the upper plan view.

  Specifically, the first blower 30 is disposed on the right side of the condenser 22 in an upper plan view. That is, the first blower 30 is disposed on the opposite side of the evaporator 24 with respect to the condenser 22 in the upper plan view.

  Further, the second blower 31 is disposed on the left side of the evaporator 24 in the upper plan view. That is, in the upper plan view, the second blower 31 is disposed on the opposite side of the condenser 22 with respect to the evaporator 24.

  Furthermore, the 2nd air blower 31 is arrange | positioned near the center part rather than both the refrigerant | coolant flow outlet side and inlet side of the evaporator 24. FIG. In other words, the 2nd air blower 31 is arrange | positioned so that the cooling air cooled in the refrigerant | coolant flow center part among the heat exchange parts 24A of the evaporator 24 may be ventilated. In the present embodiment, when viewed from the left-right direction of the air conditioner 1 in the upper plan view, the second blower 31 and the central portion of the refrigerant flow in the heat exchanging portion 24A of the evaporator 24 are superposed.

  Other configurations and operations of the air conditioner 1 are the same as those in the first embodiment. Therefore, also in the air conditioner 1 of this embodiment, the effect similar to 1st Embodiment can be acquired.

  Furthermore, in this embodiment, the 2nd air blower 31 is arrange | positioned near the center part rather than both the refrigerant | coolant flow outlet side and inlet side of the evaporator 24. FIG. According to this, since air flows over the entire surface of the heat exchange section 24 of the evaporator 24, the effective heat exchange area of the evaporator 24 is increased. Thereby, since the heat exchange efficiency in the evaporator 24 improves, the coefficient of performance (COP) of the refrigeration cycle apparatus 20 can be improved.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described with reference to FIG. The fifth embodiment is different from the first embodiment in the arrangement of the first blower 30 and the second blower 31.

  As shown in FIG. 19, in the air conditioner 1 of the present embodiment, the first blower 30 is disposed on the lower side of the condenser 22. And when it sees from the up-down direction of the air conditioner 1, the 1st air blower 30 and the site | part of the refrigerant | coolant flow upstream among the heat exchange parts 22A of the condenser 22 are superposed | positioned. That is, when it sees from the up-down direction of the air conditioner 1, it arrange | positions so that the 1st air blower 30 and the site | part of the refrigerant | coolant flow upstream among the heat exchange parts 22A of the condenser 22 may overlap.

  Specifically, when viewed from the vertical direction of the air conditioner 1, the first blower 30 and the portion of the heat exchange part 22 </ b> A of the condenser 22 on the most upstream side of the refrigerant flow are superposed. Further, when viewed from the up-down direction of the air conditioner 1, the entire first blower 30 and the upstream portion of the refrigerant flow in the heat exchanging portion 22 </ b> A of the condenser 22 are arranged in a superposed manner.

  Moreover, in the air conditioner 1 of this embodiment, the 2nd air blower 30 is arrange | positioned under the evaporator 24. FIG. And the 2nd air blower 31 is arrange | positioned near the center part rather than both the refrigerant | coolant flow outlet side and inlet side of the evaporator 24. FIG. In other words, the 2nd air blower 31 is arrange | positioned so that the cooling air cooled in the refrigerant | coolant flow center part among the heat exchange parts 24A of the evaporator 24 may be ventilated. Specifically, when viewed from the vertical direction of the air conditioner 1, the second blower 31 and the central portion of the refrigerant flow in the heat exchange unit 24 </ b> A of the evaporator 24 are arranged in a superposed manner.

  Other configurations and operations of the air conditioner 1 are the same as those in the first embodiment. Therefore, also in the air conditioner 1 of this embodiment, the effect similar to 1st Embodiment can be acquired.

  Furthermore, in this embodiment, the 2nd air blower 31 is arrange | positioned near the center part rather than both the refrigerant | coolant flow outlet side and inlet side of the evaporator 24. FIG. According to this, since air flows over the entire surface of the heat exchange section 24 of the evaporator 24, the effective heat exchange area of the evaporator 24 is increased. Thereby, since the heat exchange efficiency in the evaporator 24 improves, the coefficient of performance (COP) of the refrigeration cycle apparatus 20 can be improved.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows, for example, within a range not departing from the gist of the present invention. Further, the means disclosed in each of the above embodiments may be appropriately combined within a practicable range.

  (1) In the embodiment described above, the air conditioner 1 is applied to a seat air conditioner that uses a seat as an air-conditioning target space. However, the present invention is not limited to this mode. If the refrigeration cycle apparatus 20, the first blower 30, the second blower 31, and the like are housed in the housing 10 as the constituent devices in the air conditioner 1 described above, they may be configured to be used for other purposes. Is possible.

  (2) Further, in the above-described embodiment, the casing 10 of the air conditioner 1 is configured in a rectangular parallelepiped shape that can be disposed between the seat surface portion of the seat and the passenger compartment floor surface. It is not something. About the external appearance shape etc. of the housing | casing 10, it is possible to change suitably according to a condition.

  (3) In the above-described embodiment, the air blowing capacity of the first blower 30 and the second blower 31 is adjusted by changing the number of rotations of each electric motor by a control signal from the control unit 60. It is not limited to the embodiment. By adopting a fan having different performance as the first fan 30 and the second fan 31, it is possible to adjust the blowing capacity.

  (4) In the above-described embodiment, the refrigeration cycle apparatus 20 is configured to include the accumulator 25, but is not limited to this mode. The refrigeration cycle apparatus 20 only needs to constitute a refrigeration cycle having at least a compressor 21, a condenser 22, a decompression unit 23, and an evaporator 24.

  (5) In the above-described embodiment, an example in which a suction-type blower is employed as the first blower 30 and the second blower 31 has been described. However, the configurations of the first blower 30 and the second blower 31 are not limited thereto. For example, as the first blower 30, a so-called push-type blower that generates an air flow from the first blower 30 toward the condenser 20 by the rotation of the impeller may be employed. Similarly, as the second blower 31, a so-called push-type blower that generates an air flow from the second blower 31 to the evaporator 240 by the rotation of the impeller may be employed.

  (6) In the above-described embodiment, the air conditioner 1 is configured to be capable of performing both the heating operation and the cooling operation, but is not limited to this aspect. For example, the air conditioner 1 may be configured as a heating device dedicated to heating operation, or may be configured as a cooling device dedicated to cooling operation.

DESCRIPTION OF SYMBOLS 10 Housing | casing 20 Refrigeration cycle apparatus 22 Condenser 24 Evaporator 30 1st air blower 31 2nd air blower

Claims (5)

A refrigeration cycle apparatus (20) having a condenser (22) for condensing high-pressure refrigerant and an evaporator (24) for evaporating low-pressure refrigerant;
A first blower (30) for blowing heated air heated by the condenser;
A second blower (31) for blowing cooling air cooled by the evaporator;
A housing (10) for housing the refrigeration cycle apparatus, the first blower and the second blower,
The said 1st air blower is an air conditioner arrange | positioned near the inlet side rather than the refrigerant | coolant flow outlet side of the said condenser. The condenser has a refrigerant inlet (226) through which a refrigerant flows and a refrigerant outlet (227) through which the refrigerant flows out, and the refrigerant flows in one direction from the refrigerant inlet to the refrigerant outlet. Configured to flow,
The air conditioner according to claim 1, wherein the first blower is disposed closer to the refrigerant inlet than the refrigerant outlet. The condenser has a plurality of tubes (221) through which refrigerant flows, and is formed in a rectangular shape with a long longitudinal direction of the tubes.
The flow direction of the refrigerant flowing through each tube is the same,
The refrigerant inlet is disposed on one end side in the longitudinal direction of the tube,
The air conditioner according to claim 2, wherein the refrigerant outlet is disposed on the other end side in the longitudinal direction of the tube. The first blower blows the heated air to an air-conditioning target space,
The air conditioner according to any one of claims 1 to 3, wherein the second blower blows the cooling air to the outside of the air conditioning target space. The first blower blows the heated air to the outside of the air-conditioning target space,
The air conditioner according to any one of claims 1 to 3, wherein the second blower blows the cooling air to the air conditioning target space.

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