JP7059784B2 - Air conditioner - Google Patents

Description

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

Conventionally, as one aspect of an air conditioner, a device in which components such as a steam compression type refrigeration cycle device and a blower are housed inside a housing has been developed. Such an air-conditioning device is arranged, for example, between the seat surface portion and the floor surface of the seat arranged in the vehicle, and the seat is used as an air-conditioning target space to improve its comfort.

As an invention relating 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 refrigerating cycle including a condenser and an evaporator and a centrifugal fan inside a main body case.

Japanese Unexamined Patent Publication No. 2017-187218

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 sufficiently flow air to the condenser and the evaporator. Therefore, there is a problem that the heat exchange performance of the condenser and the evaporator cannot be fully exhibited.

In view of the above points, it is an object of the present invention to improve the heat exchange performance of the heat exchanger of the refrigeration cycle device in the air conditioner in which the refrigeration cycle device, the blower and the like are housed in one housing.

In order to achieve the above object, the invention according to claim 1 comprises a refrigerating cycle apparatus (20) having a condenser (22) for condensing a high-pressure refrigerant and an evaporator (24) for evaporating a low-pressure refrigerant.
The first blower (30) that blows the heated air heated by the condenser, and
The second blower (31) that blows the cooling air cooled by the evaporator, and
A housing (10) for accommodating a refrigerating cycle device, a first blower and a second blower, is provided.
The first blower is located closer to the inlet side than the refrigerant flow outlet side of the condenser.
The condenser has a refrigerant inlet (226) into which the refrigerant flows and a refrigerant outlet (227) from which the refrigerant flows out, and is configured so that the refrigerant flows in one direction from the refrigerant inlet to the refrigerant outlet. And
The first blower is located closer to the refrigerant inlet than to the refrigerant outlet .

According to this, the heated air can be heat-exchanged in the relatively high temperature portion of the condenser. Therefore, in the condenser, the high-pressure refrigerant and the heated air can be efficiently exchanged with heat. Therefore, the heat exchange performance in the heat exchanger of the refrigeration cycle device can be improved.

The reference numerals in parentheses of each means described in this column and the scope of claims indicate the correspondence with the specific means described in the embodiments described later.

It is external perspective view of the air conditioner which concerns on 1st Embodiment. It is a perspective view which shows the state which the upper cover of the air conditioner which concerns on 1st Embodiment is removed. It is a perspective view which shows the state which the 1st blower and the 2nd blower of the air conditioner which concerns on 1st Embodiment are removed. 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 in 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 in 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 the arrangement relation of the 1st blower, the condenser and the like of the air conditioner which concerns on 1st Embodiment. It is explanatory drawing for demonstrating the arrangement relation of the 1st blower, the condenser and the like of the air conditioner which concerns on 2nd Embodiment. It is explanatory drawing for demonstrating the arrangement relation of the 1st blower, the condenser and the like of the air conditioner which concerns on 3rd Embodiment. It is explanatory drawing for demonstrating the arrangement relation of the 1st blower, the condenser and the like of the air conditioner which concerns on 4th Embodiment. It is explanatory drawing for demonstrating the arrangement relation of the 1st blower, the condenser and the like of the air conditioner which concerns on 5th Embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each of the following embodiments, the parts that are the same or equal to each other are designated by the same reference numerals in the drawings.

Further, the arrows indicating up / down, left / right, and front / back in each figure are orthogonal coordinate systems in three-dimensional space (for example, X-axis, Y-axis, Z-axis) in order to facilitate understanding of the positional relationship of each configuration in the embodiment. ) Is illustrated as a standard corresponding to). Therefore, the posture of the air conditioner according to the present invention is not limited to the state shown in each figure, and can be changed as appropriate.

(First Embodiment)
The air conditioner 1 according to the first embodiment is used as a seat air conditioner for enhancing the comfort of a occupant sitting on a seat by using a seat arranged in a vehicle interior of a vehicle as an air conditioning target space. The air conditioner 1 is arranged in a small space between the seat surface of the seat and the floor of the passenger compartment, and supplies air conditioning air (for example, cold air or hot air) through a duct arranged on the seat. By doing so, it is configured to enhance the comfort of the occupants sitting in the seats.

As shown in FIGS. 1 to 3, the air conditioner 1 according to the first embodiment includes a steam compression type 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 inside 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 occupant 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. 1 to 3. Note that FIG. 2 shows a state in which the upper cover 11 is removed from the state of FIG. 1, and FIG. 3 shows a state in which 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 arranged between the seat surface portion of the seat and the vehicle interior floor surface. As shown in FIG. 1, the housing 10 is composed of 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 an open upper portion. The upper cover 11 is formed with 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 on the right side of the upper cover 11. The hot air vent 12 is a vent for sucking the air outside the housing 10 (that is, the air inside the vehicle interior) into the housing 10 when the first blower 30 or the like, which will be described later, is operated. ..

As shown in FIGS. 1 to 6, the condenser 22 of the refrigerating cycle device 20 is arranged at a position below the hot air vent 12 inside the housing 10. Therefore, the air sucked from the hot air vent 12 heats by exchanging heat with the high-pressure refrigerant when passing through the condenser 22, and is supplied as hot air WA.

The cold air vent 13 is opened on the left side portion of the upper cover 11 and is arranged so as to be symmetrical with the hot air vent 12. Like the hot air vent 12, the cold air vent 13 is a vent for sucking the outside air of the housing 10 into the inside when the first blower 30 or the like is operated.

The evaporator 24 of the refrigeration cycle device 20 is arranged 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 as it passes through the evaporator 24 and is supplied as cold air CA.

A supply port 14 is opened in the central portion on the rear side of the upper cover 11. The supply port 14 is a vent for supplying the air-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-conditioned space.

Although not shown, the end of the duct is connected to the supply port 14. The duct is arranged along the side portion of the seat and is configured to guide the air-conditioned air to the space where the occupant sits on the seat. The space in the seat where the occupants are seated corresponds to the space subject to air conditioning.

Further, an exhaust port 16 is opened in the front central portion of the upper cover 11. The exhaust port 16 is an opening inside the housing 10 from which a part of the air whose temperature has been adjusted by the refrigeration cycle device 20 is exhausted. The air blown out from the exhaust port 16 is blown to the outside of the air-conditioned space.

The main body case 15 constitutes the main part of the housing 10, and is formed in a box shape with an open upper portion. As shown in FIGS. 2 to 6, constituent devices such as the refrigerating cycle device 20 and the first blower 30 are arranged inside the main body case 15.

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

Next, the configuration of the refrigeration cycle device 20 in the air conditioner 1 will be described with reference to the drawings. As described above, the refrigeration cycle device 20 is housed inside the housing 10 and constitutes a steam compression type refrigeration cycle.

The refrigeration cycle device 20 includes a compressor 21, a condenser 22, a decompression unit 23, an evaporator 24, and an accumulator 25. The refrigerating cycle device 20 functions to cool or heat the air blown to the vicinity of the seat, which is the air-conditioned space, by circulating the refrigerant by operating the compressor 21.

Here, the refrigeration cycle device 20 employs an HFC-based refrigerant (specifically, R134a) as the refrigerant, and uses a steam compression type 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, as the refrigerant, an HFO-based refrigerant (for example, R1234yf), a natural refrigerant (for example, R744), or the like may be adopted. Further, the refrigerant contains refrigerating machine oil for lubricating the compressor 21, and a part of the refrigerating machine oil circulates in a cycle together with the refrigerant.

The compressor 21 sucks in the refrigerant, compresses it, and discharges it in the refrigerating cycle device 20. The compressor 21 is configured as an electric compressor in which a fixed capacity type compression mechanism having a fixed discharge capacity is driven by an electric motor, and is inside the main body case 15 as shown in FIGS. 2, 3 and the like. It is located on the rear side. As the compression mechanism of the compressor 21, various compression mechanisms such as a scroll type compression mechanism and a vane type compression mechanism can be adopted.

The operation (that is, the rotation speed) of the electric motor constituting the compressor 21 is controlled by the control signal output from the control unit 60 shown in FIG. 7. Then, the control unit 60 controls the rotation speed of the electric motor, so that the refrigerant discharge capacity of the compressor 21 is changed.

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

As shown in FIGS. 2 to 4, the condenser 22 is arranged on the right side of the main body case 15 and is located below the hot air vent 12. The heat exchange portion 22A of the condenser 22 is formed to be 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 exchange portion 22A of the condenser 22.

That is, the condenser 22 heats the air into warm air WA by exchanging heat between the high-temperature and high-pressure discharged refrigerant discharged from the compressor 21 and the air sucked from the hot air vent 12. Can be done. That is, the condenser 22 operates as a heat exchanger for heating and functions as a radiator.

The heat exchange portion 22A of the condenser 22 is formed in a flat plate shape having a plurality of tubes and fins extending in a longitudinal direction. As shown in FIGS. 2 to 6, the condenser 22 is arranged so that the longitudinal direction of the heat exchange unit 22A is along the front-rear direction of the air conditioner 1.

Further, as shown in FIGS. 5 and 6, the condenser 22 is arranged so that the heat exchange unit 22A is located above the bottom surface 15A of the housing 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 exchange unit 22A flows, and functions as a part of the hot air side ventilation passage 17.

A decompression unit 23 is connected to the outlet side of the condenser 22. The decompression unit 23 is composed of a so-called fixed throttle, and decompresses the refrigerant flowing out of the condenser 22. As shown in FIG. 4, the decompression unit 23 is arranged 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. If the refrigerant flowing out of the condenser 22 can be depressurized, various configurations can be adopted as the depressurizing unit. For example, the capillary tube may be adopted as the pressure reducing unit 23, or an expansion valve whose throttle opening degree can be controlled by the control signal of the control unit 60 may be used for the pressure reducing unit 23.

The inlet side of the evaporator 24 is connected to the outlet side of the decompression unit 23. The evaporator 24 has a heat exchange section 24A formed in a flat plate shape by laminating a plurality of tubes and fins, and absorbs heat from the air passing through the heat exchange section 24A, and a low-pressure refrigerant flowing through each tube. To 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 arranged inside the housing 10 at a distance in the left-right direction with respect to the condenser 22.

The heat exchange portion 24A of the evaporator 24 is formed to be larger than the opening area of the cold air vent 13. Therefore, the air sucked from the cold air vent 13 passes through the heat exchange portion 24A of the evaporator 24.

That is, the evaporator 24 can cool the air into 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.

The heat exchange portion 24A of the evaporator 24 is formed in a flat plate shape having a plurality of tubes and fins extending in a longitudinal direction. As shown in FIGS. 2 to 6, the evaporator 24 is arranged so that the longitudinal direction of the heat exchange unit 24A is along the front-rear direction of the air conditioner 1.

As shown in FIGS. 5 and 6, the evaporator 24 is arranged so that the heat exchange unit 24A is located above the bottom surface 15A of the housing 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 exchange unit 24A flows, and functions as a part of the cold air side ventilation passage 18.

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

A suction pipe of the compressor 21 is connected to the gas phase refrigerant outlet in 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 arranged inside the housing 10. The first blower 30 is a blower having an impeller having a plurality of blades and an electric motor for rotating 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 first blower 30 can blow air to the seat, which is the space to be air-conditioned, through the supply port 14 by rotating the impeller. That is, the first blower 30 of the present embodiment is a so-called suction type 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 arranged 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-conditioned 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 type 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 arranged below the first blower 30 and the second blower 31. The fan support portion 55 is arranged between the condenser 22 and the evaporator 24, and has a first mounting opening 56 and a second mounting opening 57. As shown in FIGS. 3 to 6, the fan support portion 55 is arranged so as to be located at a predetermined height from the housing bottom surface 15A in the housing 10, and is located between the condenser 22 and the evaporator 24. The space is divided into upper and lower parts.

The first mounting opening 56 is an opening to which the first blower 30 is mounted, and is arranged on the rear side of the fan support portion 55. On the other hand, the second mounting opening 57 is an opening to which the second blower 31 is mounted, and is arranged on the front side of the fan support portion 55 so as to be adjacent to the first mounting opening 56.

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

Then, 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.

Note that 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. And FIG. 6 shows the VI-VI cross section 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 has 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. It has 40 and. The hot air switching unit 35 is a mechanism for switching the blowing destination of the hot air WA heated by the condenser 22. The cold air switching unit 40 is a mechanism for switching the 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 arranged 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 arranged between the condensers 22 and the evaporators 24 arranged on the left and right sides inside 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 closer to the condenser 22), and the cold air switching unit 40 is the condenser 22 and the evaporator. It is located on the left side between the 24 (ie, the side closer to the evaporator 24).

As shown in FIGS. 5 and 6, the frame member 45 is arranged below the fan support portion 55 between the condenser 22 and the evaporator 24, and extends in the front-rear direction. The frame member 45 is formed in an arc shape that bulges downward with respect to a cross section perpendicular to the front-rear direction.

A section 45A is formed at the lower end of the frame member 45 that bulges 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 partitioned to the left and right by the partition 45A.

The space below the frame member 45 and on the right side of the compartment 45A communicates with the space below the condenser 22 and forms a part of the hot air side ventilation passage 17. Similarly, the space below the frame member 45 and on the left side of the compartment 45A communicates with the space below the evaporator 24 and forms a part of the cold air side ventilation passage 18.

Further, in the central portion in the front-rear direction of the frame member 45, a partition rib for partitioning the space between the fan support portion 55 and the frame member 45 in the front-rear direction is formed. 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 the air supplied from the supply port 14 flows in. 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 the air blown from the exhaust port 16 flows in.

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

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

Therefore, 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 toward the right side of the housing 10 in which the condenser 22 is arranged. 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 divided through the hot air supply opening 36 and the hot air exhaust opening 37. It faces the portion located on the 45A side. The portion located on the condenser 22 side is located above the portion located on the partition portion 45A side in the vertical direction of the air conditioner 1.

As a result, the opening areas of the hot air supply opening 36 and the hot air exhaust opening 37 form the hot air supply opening 36 and the like so as to cross the hot air side ventilation passage 17 in the left-right direction (that is, horizontally). It will be larger than the opening area when

Further, as shown in FIGS. 4 to 6, the condenser 22 is arranged so that the longitudinal direction of the heat exchange portion 22A is along the front-rear direction. In the hot air switching unit 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 has both the amount of air flowing into the hot air supply opening 36 and the amount of air flowing into the hot air exhaust opening 37 with respect to the air passing through the heat exchange unit 22A of the condenser 22. It can be secured sufficiently.

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

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

The cold air exhaust opening 42 is formed in front of the left side of the frame member 45, and communicates the exhaust space 57A with the cold air side ventilation passage 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 swells downward toward the central portion 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. It is open to the part.

Therefore, 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 toward the left side of the housing 10 in which the evaporator 24 is arranged. 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 portion 45A side via the cold air supply opening 41 and the cold air exhaust opening 42. Facing the part to be treated. The portion located on the evaporator 24 side is located above the portion located on the partition portion 45A side in the vertical direction of the air conditioner 1.

As a result, 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 passage 18 in the left-right direction (that is, horizontally). It will be larger than the area.

Then, as shown in FIGS. 4 to 6, the evaporator 24 is arranged so that the longitudinal direction of the heat exchange portion 24A is along the front-rear 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 is sufficient for both the amount of air flowing into the cold air supply opening 41 and the amount of air flowing into the cold air exhaust opening 42 with respect to the air passing through the heat exchange unit 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 slide 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 attached along the arc of the frame member 45 between the position where the hot air supply opening 36 is closed and the position where the cold air supply opening 41 is closed. There is.

Therefore, the air conditioner 1 moves the supply slide door 46, so that 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 are used. 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 adjusting 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 attached along the arc of the frame member 45 between the position where the hot air exhaust opening 37 is closed and the position where the cold air exhaust opening 42 is closed. There is.

Therefore, the air conditioner 1 moves the exhaust slide door 47, so that 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 pass through the air volume. The air volume of the cold air CA flowing into the exhaust space 57A can be adjusted. That is, the exhaust slide door 47 can adjust the ratio of the hot air WA and the cold air CA in the air blown from the exhaust port 16, and functions as an exhaust side air volume adjusting unit.

As shown in FIG. 4 and the like, the drive motor 50 is arranged inside the housing 10. The drive motor 50 is composed of a so-called servomotor, and functions as a drive source for sliding 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 forward from the drive motor 50 and has two gear portions 48A. Further, the supply shaft 48 is arranged so as to cross above the supply slide door 46 in the front-rear direction.

The 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 tooth portions 46A of the supply slide door 46 are each formed so as to mesh with the teeth in the gear portion 48A of the supply shaft 48.

Therefore, 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 and move 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, the 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 arranged at the front end of the supply shaft 48 and meshes with a driven gear portion 49B arranged at the rear end of the exhaust shaft 49. It is configured as follows. Therefore, the power generated by the drive motor 50 is transmitted to the exhaust shaft 49 as the supply shaft 48 rotates.

Two tooth portions 47A 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 each formed so as to mesh with the gear portion 49A of the exhaust shaft 49.

Therefore, the power generated by the drive motor 50 is transmitted via 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 and move 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, whereby the supply slide door The slide movement of the 46 can be linked with the slide movement of the exhaust slide door 47.

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 hot air WA in the air flowing into the supply space 56A increases. The air conditioner 1 can supply the mixed air MA having a lower temperature than the heating mode and a higher temperature than the cooling mode to the space to be air-conditioned, and can realize an air mix mode rather than heating.

Further, when the exhaust slide door 47 moves so that the opening area in the hot air exhaust opening 37 increases, the supply slide door 46 moves so as to increase the opening area in the cold air supply opening 41.

In this case, the air volume ratio of the hot 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 having a lower temperature than the heating mode and a higher temperature than the cooling mode to the air-conditioned space, and can realize the air mix mode from the cooling mode.

According to the air conditioner 1 according to the first embodiment configured in this way, air conditioning is performed by using the hot air WA heated by the condenser 22 of the refrigerating cycle device 20 and the cold air CA cooled by the evaporator 24. Air-conditioned air can be supplied to the seat, which is the target space.

Then, according to the air conditioner 1, the cooling mode for supplying the cold air CA to the air conditioning target space and the air conditioning target space by controlling the operation of the hot air switching unit 35 and the cold air switching unit 40. It is possible to realize a heating mode for supplying hot air WA and an air mix mode for supplying mixed air MA whose temperature is adjusted by mixing cold air CA and hot air WA to the air-conditioned space.

Next, the 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 composed of a so-called tank-and-tube type 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 and arranged in parallel in the left-right direction so that their longitudinal directions coincide with each other in the front-rear direction. The shape of the cross section of the tube 221 perpendicular to the longitudinal direction is a flat oval shape (that is, a flat shape). The tube 221 is arranged so that the flow direction of the air flowing outside the tube 221 coincides with the major axis direction in the flat shape.

Further, a wave-shaped fin 224 as a heat transfer member is bonded 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.

The heat exchange unit 22A described above is composed of a laminated body in which a plurality of tubes 221 and a plurality of fins 224 are alternately laminated. Inserts 225 extending substantially parallel to the longitudinal direction of the tube to reinforce the heat exchange portion 22A are provided at both ends of the heat exchange portion 22A in the tube stacking direction.

The header tanks 222 and 223 communicate with a plurality of tubes 221 to collect or distribute the refrigerant to the plurality of tubes 221. Header tanks 222 and 223 are provided at both ends in the longitudinal direction of the tube (front and rear ends in the present embodiment) one by one. The header tanks 222 and 223 extend in a direction orthogonal to the longitudinal direction of the tube (in the present embodiment, the left-right direction).

Here, of the pair of header tanks 222 and 223, the one arranged on the rear side and distributing the refrigerant to the tube 221 is referred to as an inlet tank 222. Further, of the pair of header tanks 222 and 223, the one arranged on the front side and collecting 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 inflow port for flowing the high-pressure refrigerant discharged from the compressor 21 into the inlet tank 222. The refrigerant inlet 226 is arranged on one end side (in this embodiment, the right end side) in the tube stacking direction in the inlet tank 222.

The outlet tank 223 is provided with a refrigerant outlet 227 as an outlet for discharging the refrigerant to the inlet side of the decompression unit 23. The refrigerant outlet 227 is arranged on the other end side (in this embodiment, the left end side) of the outlet tank 223 in the tube stacking direction.

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

Therefore, 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 the condenser 22.

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 seen from the upper side of the air conditioner 1. Hereinafter, the plan view seen from the upper side of the air conditioner 1 is referred to as an upper plan view.

It should be noted that the arrangement including the sizes of the condenser 22 and the first blower 30 shown in FIG. 15 is for convenience of explanation and does not indicate the actual arrangement. Further, in FIG. 15, solid arrows schematically show the flow of the refrigerant, and white arrows schematically show the flow of air.

As shown in FIGS. 2 and 15, the first blower 30 is arranged 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 first blower 30 is arranged so as to blow heated air at a portion of the heat exchange portion 22A of the condenser 22 on the upstream side of the refrigerant flow.

In the present embodiment, as shown in FIG. 15, when viewed from the left-right direction of the air conditioner 1 in an upward plan view, the first blower 30 and the heat exchange portion 22A of the condenser 22 are on the upstream side of the refrigerant flow. The site is overlapped with each other. 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 portion of the heat exchange portion 22A of the condenser 22 on the upstream side of the refrigerant flow are arranged so as to overlap each other. ..

Specifically, when viewed from the left-right direction of the air conditioner 1 in an upward plan view, the first blower 30 and the portion of the heat exchange portion 22A of the condenser 22 on the most upstream side of the refrigerant flow are superimposed and arranged. ing. Further, in the upper plan view, when viewed from the left-right direction of the air conditioner 1, the entire first blower 30 and the portion of the heat exchange portion 22A of the condenser 22 on the upstream side of the refrigerant flow are superimposed and arranged. ..

Further, as shown in FIGS. 2 and 15, the second blower 31 is arranged closer to the inlet side than the refrigerant flow outlet side of the evaporator 24. In other words, the second blower 31 is arranged so as to blow the cooled air cooled at the portion of the heat exchange portion 24A of the evaporator 24 on the upstream side of the refrigerant flow.

In the present embodiment, as shown in FIG. 15, when viewed from the left-right direction of the air conditioner 1 in an upward plan view, the second blower 31 and the heat exchange portion 24A of the evaporator 24 on the upstream side of the refrigerant flow. The parts are overlapped and arranged. 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 portion of the heat exchange portion 24A of the evaporator 24 on the upstream side of the refrigerant flow are arranged so as to overlap each other. ..

Specifically, when viewed from the left-right direction of the air conditioner 1 in an upward plan view, the second blower 31 and the portion of the heat exchange portion 24A of the evaporator 24 on the most upstream side of the refrigerant flow are arranged in an overlapping manner. ing. Further, in the upper plan view, when viewed from the left-right direction of the air conditioner 1, the entire second blower 31 and the portion of the heat exchange portion 24A of the evaporator 24 on the upstream side of the refrigerant flow are superimposed and arranged. ..

Next, the 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 constituent devices of the air conditioner 1.

The control unit 60 includes a well-known microcomputer including a CPU, ROM, RAM, and the like, and peripheral circuits thereof. Then, the control unit 60 performs various arithmetic processes based on the control program stored in the ROM, and controls the operation of each component device.

A compressor 21, a first blower 30, a second blower 31, and a drive motor 50 are connected to the output side of the control unit 60. Therefore, the control unit 60 adjusts the refrigerant discharge performance (for example, refrigerant pressure) by the compressor 21, the ventilation performance of the first blower 30 (for example, the air flow amount), and the ventilation performance of the second blower 31 according to the situation. 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 a cooling mode, a heating mode, and an 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 is composed of a plurality of types of sensors used for controlling the air conditioning operation of the air conditioning device 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 arranged, for example, in the refrigerant pipe connected to the evaporator 24. Therefore, the control unit 60 can determine the magnitude of the load of the air conditioner 1 during the air conditioning operation according to the magnitude of the low pressure side refrigerant pressure of the cycle detected by the pressure sensor 62, and responds accordingly. Control can be done.

Further, the air conditioning sensor 61 is a suction temperature sensor that detects the temperature of the air sucked by the hot air vent 12, the cold air vent 13, and the temperature of the air that has passed through the condenser 22 (that is, the warm air WA). It includes a hot air temperature sensor that detects the temperature of air (that is, cold air CA) that has passed through the evaporator 24, and a cold air temperature sensor that detects the temperature of the air (that is, cold air CA).

The air conditioning sensor 61 detects, for example, a temperature sensor (that is, an evaporator temperature sensor) that detects the refrigerant temperature on the low pressure side of the cycle, a high pressure sensor that detects the refrigerant pressure on the high pressure side of the cycle, and the temperature of the high pressure refrigerant. It may include a temperature sensor to be used. Then, 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 a cooling mode in which cold air CA is supplied to a seat which is an 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, and the hot air switching unit 35 And the cold air switching unit 40 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 56A and supplies it to the seat which is the air-conditioned space through 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 open. 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 portion 24A of the evaporator 24.

At this time, the air is endothermic 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 passage 18 and flows into the supply space 56A through the cold air supply opening 41. Then, the cold air CA is sucked from the supply space 56A by the first blower 30, and is supplied to the air-conditioned space from the supply port 14.

In this cooling mode, since the hot air supply opening 36 is closed by the supply slide door 46, the air on the hot air side ventilation passage 17 side is supplied by the operation of the first blower 30 to supply the space 56A. Will not be sucked into. That is, in this case, the first blower 30 does not generate an air flow of a hot air vent 12 → a condenser 22 → a hot air side ventilation passage 17 → a 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 amount of heat absorbed by the refrigerant in the evaporator 24 of the refrigeration cycle device 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 amount of heat absorbed by the refrigerant in the evaporator 24 by adjusting the amount of air blown by 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 57A below the second blower 31 and blows air to the outside of the air-conditioned space through the exhaust port 16.

As shown in FIG. 6, in the cooling mode, the hot air exhaust opening 37 is open and the cold air exhaust opening 42 is closed. Therefore, the second blower 31 sucks air from the hot air vent 12 and passes it through the heat exchange portion 22A 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 warm air WA. The warm air WA that has passed through the condenser 22 flows through the hot air side ventilation passage 17 and flows into the exhaust space 57A through the hot air exhaust opening 37. Then, the warm air WA is sucked from the exhaust space 57A by the second blower 31, and is blown to the outside of the air-conditioned space from the exhaust port 16.

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 passage 18 side is sucked into the exhaust space 57A by the operation of the second blower 31. Will not be. That is, in this case, the second blower 31 does not generate an air flow of cold air vent 13 → evaporator 24 → cold air side ventilation passage 18 → 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 device 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 amount of heat released from the refrigerant in the condenser 22 by adjusting the amount of air blown by the second blower 31 in the cooling mode.

As described above, the air conditioner 1 supplies the cold air CA cooled by the evaporator 24 to the air-conditioned space from the supply port 14 by the first blower 30, and also supplies the hot air WA heated by the condenser 22. , The second blower 31 can blow air from the exhaust port 16. That is, the air conditioner 1 can realize a cooling mode in which cold air CA is supplied to a seat which is an air conditioning target space.

Then, according to the air conditioner 1, the amount of heat absorbed by the refrigerant in the evaporator 24 can be adjusted by adjusting the amount of air blown by the first blower 30 in the cooling mode, and the amount of air blown by the second blower 31 can be adjusted. By adjusting, the amount of heat released from the refrigerant in the condenser 22 can be adjusted.

As a result, the air conditioner 1 can appropriately adjust the amount of heat released from the refrigerant in the condenser 22 and the amount of heat absorbed by the refrigerant in the evaporator 24 in the cooling mode, making it easy to balance the refrigerating cycle device 20 and making it stable. Can be operated.

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

The second blower 31 in this case is an exhaust blower for blowing air to the outside of the air-conditioned space, and at the same time, functions as a hot air blower for blowing hot air WA. That is, 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. 8 to 10. In the heating mode, the control unit 60 closes the cold air supply opening 41 at the supply slide door 46 and closes the hot air exhaust opening 37 at the exhaust slide door 47, and the hot air switching unit 35 and the hot air exhaust opening 37 are closed. The cold 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 56A and supplies it to the seat which is the air-conditioned space through 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 open. Therefore, as shown in FIG. 9, the first blower 30 sucks air from the hot air vent 12 and passes it through the heat exchange portion 22A 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 warm air WA. The warm air WA that has passed through the condenser 22 flows through the hot air side ventilation passage 17 and flows into the supply space 56A through the hot air supply opening 36. Then, the warm air WA is sucked from the supply space 56A by the first blower 30, and is supplied to the air-conditioned space from the supply port 14.

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 passage 18 side is sucked into the supply space 56A by the operation of the first blower 30. There is no such thing. That is, in this case, the first blower 30 does not generate an air flow of cold air vent 13 → evaporator 24 → cold air side ventilation passage 18 → 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 amount of heat released from the refrigerant in the condenser 22 of the refrigeration cycle device 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 amount of heat released from the refrigerant in the condenser 22 by adjusting the amount of air blown by 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 57A and blows air to the outside of the air-conditioned space through the exhaust port 16. As shown in FIG. 10, in the heating mode, the cold air exhaust opening 42 is open and the hot air exhaust opening 37 is closed. Therefore, the second blower 31 sucks air from the cold air vent 13 and passes it through the heat exchange unit 24A of the evaporator 24.

In this case, the air is endothermic 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 passage 18 and flows into the exhaust space 57A through 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 to the outside of the air-conditioned space from the exhaust port 16.

In this heating mode, since the hot air exhaust opening 37 is closed by the exhaust slide door 47, the air on the hot air side ventilation passage 17 side is exhausted by the operation of the second blower 31. Will not be sucked into. That is, in this case, the second blower 31 does not generate an air flow of a hot air vent 12 → a condenser 22 → a hot air side ventilation passage 17 → a 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 amount of heat absorbed by the refrigerant in the evaporator 24 of the refrigeration cycle device 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 amount of heat absorbed by the refrigerant in the evaporator 24 by adjusting the amount of air blown by the second blower 31 in the heating mode.

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

Then, according to the air conditioner 1, the amount of heat released from the refrigerant in the condenser 22 can be adjusted by adjusting the amount of air blown by the first blower 30 in the heating mode, and the amount of air blown by the second blower 31 can be adjusted. By adjusting, the amount of heat absorbed by the refrigerant in the evaporator 24 can be adjusted.

As a result, the air conditioner 1 can appropriately adjust the amount of heat released from the refrigerant in the condenser 22 and the amount of heat absorbed by the refrigerant in the evaporator 24 in the heating mode, making it easy to balance the refrigerating cycle device 20 and making it stable. Can be operated.

The first blower 30 in the heating mode is a supply blower for supplying air-conditioned air to the air-conditioned space, and at the same time, functions as a hot air blower for blowing 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.

The second blower 31 in this case is an exhaust blower for blowing air to the outside of the air-conditioned space, and at the same time, functions as a cold air blower for blowing 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.

Subsequently, the operation of the air conditioner 1 in the air mix mode will be described with reference to FIGS. 11 to 13. The air mix mode is an operation mode in which a mixed air MA in which hot air WA and cold air CA are mixed is supplied to the air-conditioned space.

In the air mix mode, the control unit 60 controls the position of the supply slide door 46 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 slide door 47 to secure the opening area of the hot air exhaust opening 37 and the opening area of the cold air exhaust opening 42.

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 56A and supplies it to the seat which is the air-conditioned space through the supply port 14. ..

In the air mix mode, the 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, passes through the heat exchange portion 22A of the condenser 22, and at the same time sucks air from the cold air vent 13. It is passed through the heat exchange section 24A of the evaporator 24.

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 to become warm air WA. The warm air WA that has passed through the condenser 22 flows through the hot air side ventilation passage 17 and flows into the supply space 56A through the hot air supply opening 36.

On the other hand, the air passing through the evaporator 24 is endothermic 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 passage 18, and flows into the supply space 56A through the cold air supply opening 41.

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

As described above, since 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, the temperature flowing into the supply space 56A The air volume ratios of the air WA and the cold air CA can be adjusted, and the mixed air MA can be made available from the supply port 14.

That is, the air conditioner 1 appropriately adjusts the temperature of the air conditioning 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 be done.

Then, when the second blower 31 is operated in the air mix mode, the second blower 31 sucks air from the exhaust space 57A and the air-conditioned space through the exhaust port 16 as in the cooling mode described above. Blow to the outside of.

As shown in FIG. 13, in the air mix mode, the opening area is secured for both the hot air exhaust opening 37 and the cold air exhaust opening 42. Therefore, the second blower 31 sucks air from the hot air vent 12 and passes through the heat exchange portion 22A of the condenser 22, and at the same time sucks air from the cold air vent 13 and heat exchange portion of the evaporator 24. Pass 24A.

Then, the warm air WA that has passed through the condenser 22 flows through the hot air side ventilation passage 17 and flows into the exhaust space 57A from the hot air exhaust opening 37. Similarly, the cold air CA that has passed through the evaporator 24 flows through the cold air side ventilation passage 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 by the second blower 31 and blown from the exhaust port 16 to the outside of the air-conditioned space as the mixed air MA.

As described above, the exhaust slide 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 ratios of the air WA and the cold air CA can be adjusted, and the mixed air MA can be made ready to be blown from the exhaust port 16.

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

In the refrigerating cycle device 20, the refrigerant circulates by the operation of the compressor 21, and the refrigerant contains refrigerating machine oil. Therefore, when the compressor 21 is controlled to periodically repeat operation and stop when the load is low, it is assumed that the refrigerating machine oil returning to the compressor 21 with the circulation of the refrigerant will be insufficient. To.

In this respect, the air conditioner 1 performs the air mix mode as shown in FIGS. 11 to 13 when the air conditioner load is low. By operating the air conditioner 1 in the air mix mode, the minimum rotation speed of the electric motor of the compressor 21 can be maintained above a predetermined standard.

That is, when the air conditioning load is low, the air conditioner 1 can maintain the circulation amount of the refrigerant in the refrigeration cycle device 20 at or above a predetermined standard by setting the air mix mode, and the load is low. Even in the case of, the amount of return of refrigerating machine oil to the compressor 21 (that is, oil return) can be secured.

Further, in this case, the air-conditioning device 1 sets the air-conditioning target space to air-conditioning while keeping the minimum rotation speed of the electric motor at or above a predetermined standard by setting the air-mix mode. That is, the air conditioner 1 does not periodically repeat the operation and stop of the electric motor of the compressor 21, and can reduce the vibration caused by the ON-OFF control of the compressor 21.

As described above, as shown in FIGS. 1 to 3, the air conditioner 1 according to the first embodiment includes a steam compression type refrigeration cycle device 20, a first blower 30, a second blower 31, and a temperature. The wind switching unit 35 and the cold air switching unit 40 are housed inside the housing 10.

As shown in FIGS. 4 to 6, in the air-conditioning apparatus 1, the hot air switching unit 35 blows the hot air WA heated by the condenser 22 to the outside of the air-conditioned space, and the cold air switching unit 40. Therefore, the cold air CA cooled by the evaporator 24 can be supplied to the air-conditioned space. That is, the air-conditioning device 1 can realize a cooling mode for cooling the air-conditioned space by compactly accommodating the constituent devices such as the refrigerating cycle device 20 inside the housing 10.

Further, as shown in FIGS. 8 to 10, the air conditioner 1 supplies the hot air WA heated by the condenser 22 to the air-conditioned space by the hot air switching unit 35, and also supplies the cold air switching unit 40. Therefore, the cold air cooled by the evaporator 24 can be blown to the outside of the air-conditioned space. That is, the air-conditioning device 1 can realize a heating mode for heating the air-conditioned space by compactly accommodating the constituent devices of the refrigerating cycle device 20 inside the housing 10.

Then, according to the air conditioner 1, the ventilation capacity of the first blower 30 and the second blower 31 can be individually adjusted, so that the amount of heat released from the refrigerant in the condenser 22 of the refrigeration cycle device 20 and the evaporator 24 The amount of heat absorbed by the refrigerant can be appropriately adjusted. As a result, the air conditioner 1 can easily balance the refrigeration cycle device 20 and operate it stably.

As shown in FIGS. 4 to 13, inside the housing 10 of the air conditioner 1, the first blower 30 and the second blower 31 are heat exchangers (that is, condensers 22 or evaporation) with respect to the flow of blown air. It is located on the downstream side of the vessel 24). Therefore, according to the air conditioner 1, the degree of freedom in designing the arrangement of the first blower 30 and the second blower 31 inside the housing 10 can be increased, and the size of the air conditioner 1 can be increased (that is, the housing). 10) can be suppressed.

Then, in the air conditioner 1 according to the first embodiment, as shown in FIGS. 6 and 9, the hot air switching unit 35 is the first on the downstream side of the condenser 22 with respect to the flow of the hot air WA. It is arranged on the upstream side of the blower 30 and the second blower 31. Further, as shown in FIGS. 5 and 10, the cold air switching unit 40 is arranged on the downstream side of the evaporator 24 and on the upstream side of the first blower 30 and the second blower 31 with respect to the flow of the cold air CA. ing.

As a result, the air conditioner 1 has components such as a condenser 22, an evaporator 24, a first blower 30, a second blower 31, a hot air switching unit 35, and a cold air switching unit 40 inside the housing 10. On the other hand, it can be housed compactly.

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

As a result, according to the air conditioner 1, the switching of the hot air WA flow by the hot air switching unit 35 and the switching of the cold air CA flow by the cold air switching unit 40 are surely realized, and each component device is used. It can be compactly housed inside the housing 10.

As shown in FIGS. 4 to 6 and the like, the condenser 22 is arranged so that the longitudinal direction of the heat exchange portion 22A is in 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 have a hot air side ventilation. On the road 17, they are arranged side by side in the front-rear direction.

As a result, according to the air conditioner 1, regarding the flow of the hot air WA that has passed through the heat exchange portion 22A of the condenser 22, the ventilation resistance when passing through the hot air supply opening 36 and the hot air exhaust opening 37 is increased. While reducing the amount, it is possible to secure the air volume of the warm air WA that can pass through each.

The evaporator 24 is arranged so that the longitudinal direction of the heat exchange portion 24A is in the front-rear direction. Further, the cold air switching unit 40 has 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 in the front-rear direction in the cold air side ventilation passage 18. They are arranged side by side.

As a result, according to the air conditioner 1, regarding the flow of cold air CA that has passed through the heat exchange unit 24A of the evaporator 24, while reducing the ventilation resistance when passing through the cold air supply opening 41 and the cold air exhaust opening 42. , It is possible to secure the air volume of the cold air CA that can pass through each.

Further, the air conditioner 1 according to the first embodiment has a supply slide door 46 and an exhaust slide door 47 that are slidably attached 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-conditioned space. Then, 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-conditioned 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. Thereby, the mixed air MA in which the hot air WA and the cold air CA are mixed can be supplied to the air-conditioned space from the supply port 14.

Further, the air-conditioning device 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 air-conditioning device 1 can move the sliding door 47 to the outside of the air-conditioned space. Therefore, 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 standard by setting the air mix mode for supplying the mixed air MA described above.

As a result, in the refrigerating cycle device 20 of the air conditioning device 1, even when the air conditioning load is low, the refrigerant exceeding a predetermined standard circulates, so that 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 set to the air mix mode as shown in FIGS. 11 to 13 so that the refrigerant discharge capacity corresponds to the air conditioning load. Can continue to operate. That is, since the air conditioner 1 does not periodically repeat the operation and stop of the compressor 21, it is possible to suppress the generation of vibration caused by this.

In the air conditioner 1, the supply slide door 46 and the exhaust slide door 47 are configured to transmit the power of the drive motor 50 by the supply shaft 48 and the exhaust shaft 49 to move. That is, the movement of the exhaust slide door 47 is linked to 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 interlocks with this to increase 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 is linked to 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 warm air WA in MA can be increased.

Further, 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 this to increase the opening area of the cold air supply opening 41. Move to increase.

As a result, according to the air conditioner 1, in the air mix mode, the mixing supplied from the supply port 14 is linked to 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.

Further, in the air conditioner 1 according to the first embodiment, the first blower 30 is arranged closer to the inlet side than the refrigerant flow outlet side of the condenser 22. According to this, the heated air can be heat-exchanged in the portion of the condenser 22 where the temperature becomes relatively high. Therefore, in the condenser 22, the high-pressure refrigerant and the heated air can be efficiently exchanged with heat. Therefore, the heat exchange performance in the condenser 22 which is the heat exchanger of the refrigeration cycle device 20 can be improved.

More specifically, by arranging 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 is generated in the relatively hot portion of the condenser 22. Be heated. As a result, the blowing temperature of the warm air WA supplied from the supply port 14 can be efficiently increased.

Further, according to the air conditioner 1, the air flows concentrated in a part of the heat exchange unit 22A of the condenser 22, so that the effective heat exchange area of the condenser 22 becomes small. As a result, the high-pressure pressure of the refrigerating cycle device 20 rises, so that the blowing temperature of the hot air WA supplied from the supply port 14 can be raised.

On the other hand, by arranging 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 in the portion of the condenser 22 where the temperature difference from the air is relatively large. Is heated. Therefore, since the heat exchange efficiency in the condenser 22 is improved, the high pressure of the refrigerating cycle device 20 can be reduced. This makes it possible to improve the coefficient of performance (COP) of the refrigeration cycle device 20.

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

As shown in FIG. 16, the second blower 31 is arranged closer to the central portion than both the refrigerant flow outlet side and the inlet side of the evaporator 24. That is, the second blower 31 is arranged at a portion where the distance from the refrigerant flow outlet side of the evaporator 24 and the distance from the refrigerant flow inlet side are equal. In other words, the second blower 31 is arranged so as to blow the cooled air cooled in the central portion of the refrigerant flow in the heat exchange portion 24A of the evaporator 24.

In the present embodiment, as shown in FIG. 16, when viewed from the left-right direction of the air conditioner 1 in an upward plan view, the second blower 31 and the central portion of the heat exchange portion 24A of the evaporator 24 with the refrigerant flow center. Are arranged in a layered manner. That is, in an upward plan view, the second blower 31 and the central portion of the refrigerant in the heat exchange portion 24A of the evaporator 24 are arranged so as to overlap each other when viewed from the left-right direction of the air conditioner 1.

The configuration and operation of the other air conditioner 1 are the same as those in the first embodiment. Therefore, the same effect as that of the first embodiment can be obtained in the air conditioner 1 of the present embodiment.

Further, in the present embodiment, the second blower 31 is arranged closer to the central portion than both the refrigerant flow outlet side and the inlet side of the evaporator 24. According to this, since air flows over the entire surface of the heat exchange portion 24 of the evaporator 24, the effective heat exchange area of the evaporator 24 becomes large. As a result, the heat exchange efficiency in the evaporator 24 is improved, so that the coefficient of performance (COP) of the refrigeration cycle apparatus 20 can be improved.

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

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.

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

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 arranged so as not to polymerize with either the condenser 22 or the evaporator 24 when viewed from the front-rear direction of the air conditioner 1. Further, the first blower 30 is arranged 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 arranged on the left side and the rear side with respect to the condenser 22 in the upper plan view. That is, the first blower 30 is arranged 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 arranged 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 with respect to the evaporator 24 and on the refrigerant flow inlet side of the evaporator 24 in the upper plan view.

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

The configuration and operation of the other air conditioner 1 are the same as those in the first embodiment. Therefore, the same effect as that of the first embodiment can be obtained in the air conditioner 1 of the present embodiment.

(Fourth Embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIG. In the fourth embodiment, the arrangement of the first blower 30 and the second blower 31 is different from that of the first embodiment.

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. Therefore, in the upper plan view, the first blower 30 and the second blower 31 are not arranged between the condenser 22 and the evaporator 24.

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

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

Further, the second blower 31 is arranged closer to the central portion than both the refrigerant flow outlet side and the inlet side of the evaporator 24. In other words, the second blower 31 is arranged so as to blow the cooled air cooled in the central portion of the refrigerant flow in the heat exchange portion 24A of the evaporator 24. In the present embodiment, when viewed from the left-right direction of the air conditioner 1 in an upward plan view, the second blower 31 and the central portion of the refrigerant flow in the heat exchange portion 24A of the evaporator 24 are arranged in an overlapping manner.

The configuration and operation of the other air conditioner 1 are the same as those in the first embodiment. Therefore, the same effect as that of the first embodiment can be obtained in the air conditioner 1 of the present embodiment.

Further, in the present embodiment, the second blower 31 is arranged closer to the central portion than both the refrigerant flow outlet side and the inlet side of the evaporator 24. According to this, since air flows over the entire surface of the heat exchange portion 24 of the evaporator 24, the effective heat exchange area of the evaporator 24 becomes large. As a result, the heat exchange efficiency in the evaporator 24 is improved, so that 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. In the fifth embodiment, the arrangement of the first blower 30 and the second blower 31 is different from that of the first embodiment.

As shown in FIG. 19, in the air conditioner 1 of the present embodiment, the first blower 30 is arranged on the lower side of the condenser 22. When viewed from the vertical direction of the air conditioner 1, the first blower 30 and the portion of the heat exchange portion 22A of the condenser 22 on the upstream side of the refrigerant flow are superimposed and arranged. That is, when viewed from the vertical direction of the air conditioner 1, the first blower 30 and the portion of the heat exchange portion 22A of the condenser 22 on the upstream side of the refrigerant flow are arranged so as to overlap each other.

Specifically, when viewed from the vertical direction of the air conditioner 1, the first blower 30 and the portion of the heat exchange portion 22A of the condenser 22 on the most upstream side of the refrigerant flow are superposed. Further, when viewed from the vertical direction of the air conditioner 1, the entire first blower 30 and the portion of the heat exchange portion 22A of the condenser 22 on the upstream side of the refrigerant flow are superimposed and arranged.

Further, in the air conditioner 1 of the present embodiment, the second blower 30 is arranged on the lower side of the evaporator 24. The second blower 31 is arranged closer to the central portion than both the refrigerant flow outlet side and the inlet side of the evaporator 24. In other words, the second blower 31 is arranged so as to blow the cooled air cooled in the central portion of the refrigerant flow in the heat exchange portion 24A of the evaporator 24. 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 portion 24A of the evaporator 24 are superimposed and arranged.

The configuration and operation of the other air conditioner 1 are the same as those in the first embodiment. Therefore, the same effect as that of the first embodiment can be obtained in the air conditioner 1 of the present embodiment.

Further, in the present embodiment, the second blower 31 is arranged closer to the central portion than both the refrigerant flow outlet side and the inlet side of the evaporator 24. According to this, since air flows over the entire surface of the heat exchange portion 24 of the evaporator 24, the effective heat exchange area of the evaporator 24 becomes large. As a result, the heat exchange efficiency in the evaporator 24 is improved, so that 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 that does not deviate from the gist of the present invention. In addition, the means disclosed in each of the above embodiments may be appropriately combined to the extent feasible.

(1) In the above-described embodiment, the air conditioner 1 is applied to a seat air conditioner having a seat as an air conditioning target space, but the present invention is not limited to this embodiment. As the constituent equipment in the air conditioner 1 described above, if the refrigeration cycle device 20, the first blower 30, the second blower 31, and the like are housed inside the housing 10, they may be configured to be used for other purposes. It is possible.

(2) Further, in the above-described embodiment, the housing 10 of the air conditioner 1 is configured in a rectangular parallelepiped shape that can be arranged between the seat surface portion of the seat and the floor surface of the passenger compartment, but the present invention is limited to this embodiment. It's not something. The external shape and the like of the housing 10 can be appropriately changed depending on the situation.

(3) In the above-described embodiment, the ventilation capacity of the first blower 30 and the second blower 31 is adjusted by changing the rotation speed of each electric motor according to the control signal from the control unit 60. It is not limited to the embodiment. It is also possible to adjust the blowing capacity by adopting blowers having different performances as the first blower 30 and the second blower 31.

(4) Further, in the above-described embodiment, the refrigerating cycle device 20 has a configuration having an accumulator 25, but is not limited to this embodiment. The refrigeration cycle device 20 may constitute a refrigeration cycle including 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 adopted as the first blower 30 and the second blower 31 has been described, but the configurations of the first blower 30 and the second blower 31 are not limited to this. For example, as the first blower 30, a so-called push-in type blower that generates an air flow from the first blower 30 toward the condenser 20 by the rotation of the impeller may be adopted. Similarly, as the second blower 31, a so-called push-in type blower that generates an air flow from the second blower 31 toward the evaporator 240 by the rotation of the impeller may be adopted.

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

10 Housing 20 Refrigeration cycle device 22 Condensator 24 Evaporator 30 1st blower 31 2nd blower

Claims (4)

A refrigeration cycle device (20) having a condenser (22) for condensing the high-pressure refrigerant and an evaporator (24) for evaporating the low-pressure refrigerant.
The first blower (30) that blows the heated air heated by the condenser, and
The second blower (31) that blows the cooling air cooled by the evaporator and the like.
The refrigerating cycle device, the first blower, and the housing (10) for accommodating the second blower are provided.
The first blower is arranged closer to the inlet side than the refrigerant flow outlet side of the condenser.
The condenser has a refrigerant inlet (226) into which the refrigerant flows in and a refrigerant outlet (227) from which the refrigerant flows out, and the refrigerant is unidirectionally directed from the refrigerant inlet toward the refrigerant outlet. It is configured to flow and
The first blower is an air conditioner arranged closer to the refrigerant inlet than the refrigerant outlet . The condenser has a plurality of tubes (221) through which the refrigerant flows, and the tubes are formed in a rectangular shape having a long longitudinal direction.
The flow directions of the refrigerant flowing through each of the tubes are the same.
The refrigerant inlet is arranged on one end side in the longitudinal direction of the tube.
The air conditioner according to claim 1 , wherein the refrigerant outlet is arranged on the other end side in the longitudinal direction of the tube. The first blower blows the heated air to the air-conditioned space, and the first blower blows the heated air to the air-conditioned space.
The air conditioner according to claim 1 or 2 , 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-conditioned space.
The air conditioner according to claim 1 or 2 , wherein the second blower blows the cooling air to the air conditioning target space.

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