JP2000039167A - Air-conditioning equipment and heat exchanger unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a refrigerant flow sound in dehumidification operation while suppressing the reduction of basic performance in cooling and heating operations in air-conditioning equipment with an indoor heat exchanger unit in a structure where two fin-tube-type heat exchangers are connected via a refrigerant constriction mechanism. SOLUTION: In air-conditioning equipment where a refrigerant passes through a refrigerant constriction mechanism 27 where the chanel resistance of a refrigerant is large and flows to a second heat exchanger 34 from a first heat exchanger 33 in dehumidification operation, a heat transfer pipe 26 immediately after an inlet 33a of the refrigerant of the first heat exchanger 33 in dehumidification operation and a heat transfer pipe 26 immediately before an outlet 33b of the refrigerant are arranged in a row at the upstream side of the air flow, the heat transfer pipe 26 immediately after an inlet 34a of the refrigerant of the second heat exchanger 34 and the heat transfer pipe 26 immediately before an outlet 34b of the refrigerant are arranged at the row of the upstream side of the air flow and at the row of the downstream side of the air flow, respectively, thus suppressing the reduction of basic performance on cooling and heating operations and reducing a refrigerant flow sound on dehumidification operation.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner capable of performing a dehumidifying operation in which room air is heated by the heat of condensation of a refrigeration cycle and a heat exchanger unit used therefor.

[0002]

2. Description of the Related Art A conventional air conditioner of this type is disclosed in Japanese Patent Application Laid-Open No. 9-42706. Less than,
The conventional air conditioner will be described with reference to the drawings.

FIG. 6 is a side sectional view of an indoor unit of the conventional air conditioner. In FIG. 6, the multi-stage bending indoor heat exchanger 1 incorporated in the indoor unit is thermally divided into a front lower part 2, a front upper part 3, and a rear part 4 and bent. The heat exchanger tubes 6 provided in the indoor heat exchanger 1 so as to penetrate the plurality of fins 5 are arranged in two rows in the direction of air flow, and the heat exchanger tubes 6 are connected at ends.
Further, the dehumidification control valve 7 has a fully opened state and a slightly opened state, and has a function of being opened slightly during the dehumidifying operation to perform a throttling action.

When the once-through fan type fan 10 rotates, the suction grills 11a, 1a on the front and upper surfaces are formed.
1b, the air flows in from the indoor heat exchanger 1 via the filter 8 and heat exchange with the refrigerant.
It is arranged so as to be blown into the room from the outlet 12. Reference numeral 9 denotes a rear casing, and a dew tray 9a for the rear portion 4 of the indoor heat exchanger 1 is integrally formed. 12a is an air outlet wind direction plate, and 17 is a dew tray for the lower front part 2 and the upper front part 3 of the indoor heat exchanger 1.

FIG. 7 shows the entire refrigeration cycle of a conventional air conditioner. In FIG. 7, a compressor 13 capable of controlling the rotation speed, a four-way valve 14 for switching the operation state, an outdoor heat exchanger 15, an electric expansion valve 16 capable of being fully opened without a throttling effect, and the indoor heat exchanger 1 described above. And a dehumidification control valve 7, which are connected to form a refrigeration cycle. FIG. 7 schematically shows a refrigerant path of the indoor heat exchanger 1.

[0006] Refrigerant paths during each operation of the conventional air conditioner thus configured will be described.

First, during the cooling operation, the four-way valve 14 is switched to the cooling side, the dehumidification control valve 7 is opened, and the electric expansion valve 16 is appropriately throttled, so that the compressor 13 and the four-way valve 14 , Outdoor heat exchanger 15, electric expansion valve 1
6. Upper front part 3 of indoor heat exchanger 1, indoor heat exchanger 1
A refrigerant path is formed in the order of the back part 4, the dehumidification control valve 7 in the fully opened state, the lower front part 2 of the indoor heat exchanger 1, the four-way valve 14, and the compressor 13, and the outdoor heat exchanger 15 is used as a condenser, indoor heat The entire exchanger 1 acts as an evaporator.

At this time, the flow direction of the air is indicated by a white arrow, but in the indoor heat exchanger 1, the heat transfer tube 6 immediately after the refrigerant inlet is located on the windward side of the front upper section 3 and the rear section 4
The refrigerant path is configured so as to flow out of the heat transfer pipe 6 on the leeward side to the dehumidification control valve 7, and after flowing through the dehumidification control valve 7, the refrigerant flows into the heat transfer pipe 6 on the windward side of the lower part 2 on the front side. It is configured to flow out of the heat transfer tube 6 on the leeward side of the portion 2.

As described above, by forming the refrigerant path so that the refrigerant flows in the same direction as the air flow as a whole, in the evaporator in which the refrigerant temperature sequentially decreases due to the pressure loss,
Since the temperature gradient of the refrigerant and the temperature gradient of the air always have a certain temperature difference with respect to the flow direction of the air, the cooling is efficiently performed, and since the two heat transfer tube paths are configured in parallel, the pressure of the refrigerant increases. Loss is reduced, and more efficient cooling operation is performed.

Next, during the heating operation, the four-way valve 14 is switched to the heating side, the dehumidification control valve 7 is opened, and the electric expansion valve 16 is appropriately throttled, so that the compressor 13, the four-way valve 14. lower front part 2 of indoor heat exchanger 1,
Dehumidification control valve 7, fully open, rear portion 4 of indoor heat exchanger 1, upper front portion 3 of indoor heat exchanger 1, electric expansion valve 1
6. A refrigerant path is formed in the order of the outdoor heat exchanger 15, the four-way valve 14, and the compressor 13, and the entire indoor heat exchanger 1 functions as a condenser and the outdoor heat exchanger 15 functions as an evaporator.

At this time, in the indoor heat exchanger 1, the heat transfer tube 6 immediately after the entrance of the refrigerant is taken as the leeward side of the front lower portion 2, and flows out of the heat transfer tube 6 on the windward side of the front lower portion 2 to the dehumidification control valve 7. Thus, after passing through the dehumidification control valve 7, the refrigerant path flows into the heat transfer pipe 6 on the leeward side of the rear part 4 and flows out of the heat transfer pipe 6 on the leeward side of the upper front part 3. ing.

As described above, by forming the refrigerant path so that the refrigerant flows in the direction opposite to the air flow as a whole,
In a condenser in which the refrigerant temperature gradually decreases from superheated gas to supercooled liquid, the temperature gradient of the refrigerant and the temperature gradient of the air always have a certain temperature difference with respect to the flow direction of the air, so that they are efficiently heated and more efficient Heating operation will be performed.

During the dehumidification operation, the four-way valve 14 is switched in the same direction as the cooling operation, the dehumidification control valve 7 is slightly opened, and the electric expansion valve 16 is fully opened, as shown by the one-dot chain line arrow. And the same refrigerant path as in the cooling operation described above. The difference from the cooling operation is that the electric expansion valve 1
6 is fully opened, and the dehumidification control valve 7 is narrowed to a slightly open state, so that the outdoor heat exchanger 15 and the upper front part 3 and the rear part 4 of the indoor heat exchanger 1 are used as condensers, and the indoor heat exchanger 1 is used.
Is that the lower part 2 on the front side functions as an evaporator.

When the indoor air is flown by the fan 10, the indoor air is cooled and dehumidified by the lower front portion 2 of the indoor heat exchanger 1 acting as an evaporator, and at the same time, the indoor heat exchanger 1 serving as a heater is provided. Are heated in the upper front portion 3 and the rear portion 4 of the airbag, and these airs are mixed and blown into the room.

At this time, the front upper section 3 and the rear section 4 functioning as a condenser and the front lower section 2 functioning as an evaporator are thermally separated, so that the front upper section 3 functioning as a condenser is provided. In addition, there is no loss due to heat leakage between the rear part 4 and the front lower part 2 functioning as an evaporator, and the dehumidifying ability does not decrease.

Further, the condensed water generated in the lower front part 2 functioning as the evaporator is not transmitted to the upper front part 3 and the rear part 4 functioning as the condenser and re-evaporated.

In this air conditioner, the heat exchange portion functioning as a condenser and the heat exchange portion functioning as an evaporator in the indoor heat exchanger are not arranged side by side in the air flow direction. The size of the heat exchanger in the direction of air flow does not increase, and the heat exchange part functioning as a condenser and the heat exchange part functioning as an evaporator in the indoor heat exchanger are arranged side by side in the air flow direction. The air conditioner can be made smaller (thinner) than those that are used.

[0018]

However, the conventional air conditioner has a configuration in which the refrigerant that has just passed through the heat transfer pipe 6 on the leeward side of the rear part 4 flows into the dehumidification control valve 7 during the dehumidification operation. Therefore, a gas-liquid two-phase refrigerant that has not been completely condensed tends to flow into the dehumidification control valve 7, and refrigerant flow noise is generated due to a difference in pressure loss between the liquid refrigerant and the gas refrigerant.
As a countermeasure, it was necessary to add a large amount of vibration damping material to the dehumidification control valve 7 for absorbing vibration.

In view of the above-mentioned problems, the present invention provides two heat exchangers connected via a refrigerant throttle mechanism so that the refrigerant flow and the air flow become parallel during the cooling operation and the refrigerant flow and the air flow during the heating operation. Compared to a conventional air conditioner with a fin tube type indoor heat exchanger configured so that the flow is countercurrent,
It is an object of the present invention to reduce a decrease in basic performance during a cooling operation and a heating operation, and to reduce a refrigerant flow noise during a dehumidifying operation with an inexpensive and simple configuration.

[0020]

In order to achieve this object, an air conditioner according to the present invention is characterized in that a heat transfer tube through which a refrigerant flows through a plurality of plate-like fins arranged in parallel at right angles and through which a refrigerant flows is formed in a direction in which air flows. The fin tube type indoor heat exchanger configured in a plurality of rows is thermally divided into a first heat exchanger and a second heat exchanger in a step direction substantially perpendicular to the air flow direction, The first heat exchanger and the second heat exchanger are connected via a refrigerant throttle mechanism having a state in which the flow path resistance of the refrigerant is large and a state in which the flow path resistance of the refrigerant is small, so that the cooling operation and the dehumidifying operation are performed. The refrigerant flows from the first heat exchanger to the second heat exchanger, configures a refrigeration cycle so that the refrigerant flows from the second heat exchanger to the first heat exchanger during the heating operation, and the refrigerant flows during the dehumidification operation. When the refrigerant throttle mechanism is in a state where the flow path resistance of the refrigerant is large, the first In an air conditioner capable of dehumidifying indoor air with the second heat exchanger while heating indoor air with the exchanger, the air conditioner immediately after the refrigerant inlet of the first heat exchanger during the dehumidifying operation The heat transfer tubes and the heat transfer tubes immediately before the outlet of the refrigerant are arranged in a row on the upstream side of the air flow, and the heat transfer tubes immediately after the inlet of the refrigerant of the second heat exchanger during the dehumidifying operation are arranged on the upstream side of the air flow. , And the heat transfer tubes immediately before the outlet of the refrigerant were arranged in a row on the downstream side of the flow of air.

The heat exchanger tubes of the present invention are provided with a plurality of heat transfer tubes which are inserted at right angles to the plate-like fins arranged in parallel and through which the refrigerant flows, in a plurality of rows in the direction of air flow.
The heat transfer tubes adjacent to the two refrigerant inlets and outlets are both inserted at right angles to a fin tube type first heat exchanger arranged in a row on the upstream side of the air flow, and a plurality of plate-like fins arranged in parallel. The heat transfer tubes through which the refrigerant flows are formed in a plurality of rows in the direction of air flow, and the heat transfer tubes near the one of the two refrigerant inlets and outlets are arranged on the upstream side of the air flow. A fin tube-shaped second heat exchanger arranged in a row in which the heat transfer tubes arranged and adjacent to the inlet and outlet of the other refrigerant are on the downstream side of the flow of air; and two inlets and outlets of two refrigerants of the first heat exchanger The flow path resistance of the refrigerant provided in the middle of the connecting pipe connecting the inlet / outlet of one of the refrigerants and the inlet / outlet of the refrigerant arranged in the upstream row of the air flow of the second heat exchanger is large. Cold with a state and a low flow path resistance of the refrigerant The first heat exchanger and the second heat exchanger are arranged such that the first heat exchanger and the second heat exchanger do not overlap in the direction of air flow. is there.

Thus, the two heat exchangers connected via the refrigerant throttle mechanism both have the refrigerant flow and the air flow parallel during the cooling operation, and have the counterflow between the refrigerant flow and the air flow during the heating operation. Compared with a conventional air conditioner having a fin tube type indoor heat exchanger configured as described above, a decrease in basic performance during cooling operation and heating operation is reduced, and refrigerant flow noise during dehumidification operation is reduced. It can be reduced with a simple configuration.

[0023]

According to the first aspect of the present invention, a plurality of heat transfer tubes, which are inserted at right angles into a large number of plate-like fins arranged in parallel and through which a refrigerant flows, are formed in a plurality of rows in the direction of air flow. The fin tube type indoor heat exchanger is thermally divided into a first heat exchanger and a second heat exchanger in a step direction substantially perpendicular to the flow direction of the air, and the first heat exchanger and the second heat exchanger are separated from each other. The first heat exchanger is connected to the heat exchanger via a refrigerant throttle mechanism having a state in which the flow path resistance of the refrigerant is large and a state in which the flow path resistance of the refrigerant is low, and performs the cooling operation and the dehumidification operation from the first heat exchanger. 2
The refrigeration cycle is configured such that the refrigerant flows to the heat exchanger, and the refrigerant flows from the second heat exchanger to the first heat exchanger during the heating operation. In the air conditioner, which is configured to be large and capable of dehumidifying indoor air with the second heat exchanger while heating indoor air with the first heat exchanger, the first heat during the dehumidifying operation is provided. The heat transfer tubes immediately after the refrigerant inlet of the exchanger and the heat transfer tubes immediately before the refrigerant outlet are arranged in the upstream row of the air flow, and the heat transfer tubes immediately after the refrigerant inlet of the second heat exchanger during the dehumidifying operation. The heat pipes are arranged in a row on the upstream side of the air flow, and the heat transfer tubes immediately before the outlet of the refrigerant are arranged in a row on the downstream side of the air flow.

Thus, during the cooling operation, the heat transfer tube immediately after the refrigerant inlet of the indoor heat exchanger is on the upstream side of the air flow, and the heat transfer tube immediately before the refrigerant outlet is on the downstream side of the air flow. As a whole, the refrigerant flow and the air flow become parallel flows, and the temperature gradient of the refrigerant and the temperature gradient of the air always have a certain temperature difference with respect to the flow direction of the air. The basic performance is almost the same as that of an air conditioner having an indoor heat exchanger in which the flow and the air flow are parallel flows.

In the heating operation, the heat transfer tube immediately after the refrigerant inlet of the indoor heat exchanger is on the downstream side of the flow of air.
Since the heat transfer tube immediately before the outlet of the refrigerant is on the upstream side of the air flow, the refrigerant flow and the air flow are countercurrent as a whole, and the temperature gradient of the refrigerant and the temperature gradient of the air are always constant in the air flow direction. With a certain temperature difference, air can be heated efficiently,
The basic performance is almost the same as that of the air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the conventional heating operation.

In the dehumidifying operation, since the heat transfer tubes immediately before the refrigerant outlet of the first heat exchanger are arranged in the upstream row of the air flow, the refrigerant immediately before flowing into the refrigerant throttle mechanism is the first heat exchanger. Heat exchange is performed with air before being heated by the heat exchanger, and a sufficient supercooled liquid can be obtained. Thereby, the refrigerant flowing into the refrigerant throttle mechanism becomes a liquid refrigerant,
Since the pressure is reduced by the stable flow, the refrigerant flow noise is reduced.

Further, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is reduced, sufficient heating, dehumidification and cooling of air can be performed, and a predetermined refrigeration cycle can be constituted with low power consumption. It becomes possible.

According to a second aspect of the present invention, in the air conditioner according to the first aspect of the present invention, the first heat exchanger is configured such that the refrigerant flows through the refrigerant inlet during the dehumidifying operation during the dehumidifying operation; The heat transfer tube path is configured such that after the refrigerant flows in the same direction as the air flow, the refrigerant flows in the direction facing the air flow and flows out of the refrigerant outlet during the dehumidifying operation.

Thus, during the cooling operation and the dehumidifying operation,
In the first heat exchanger, the refrigerant flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then passes through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in opposite directions. flow,
During the heating operation, the refrigerant flows through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows, and then flows through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are counter flows. Become.

Therefore, during the cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger and the second half
The heat exchanger serves as a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. In this portion, the temperature difference between the refrigerant and the air is always constant with respect to the air flow direction. Can be secured. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are in opposing flows. The refrigerant that has been heated in the first half of the refrigerant flow of the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and the adverse effect due to the refrigerant flow and the air flow being opposed flows is as follows. I don't know. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

Also, during the heating operation, the latter half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger and the first heat exchanger is connected to the heat transfer tube path where the refrigerant flow and the air flow are opposed. In this portion, a temperature difference between the temperature gradient of the refrigerant and the temperature gradient of the air can always be ensured with respect to the flow direction of the air, and the heat transfer tube path of the first heat exchanger (the refrigerant path) Since the latter half of the refrigerant flow becomes the counterflow, the sufficiently cooled refrigerant can flow out of the first heat exchanger. The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. A heat transfer tube path in which the refrigerant flow and the air flow sometimes flow in opposite directions
The refrigerant which has been cooled by the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow.
Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the heating operation.

In the dehumidifying operation, in the first heat exchanger, the refrigerant flows into the refrigerant throttle mechanism immediately after passing a plurality of heat transfer tubes arranged in the upstream row of the air flow continuously. It is easy to configure such a heat transfer tube path (refrigerant path), and in that case, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism is further improved. This allows
The refrigerant flowing into the refrigerant throttle mechanism is more likely to be a liquid refrigerant than the invention of the first aspect, and is depressurized by a more stable flow, so that the refrigerant flow noise is further reduced as compared with the invention of the first aspect.

Further, by sufficiently cooling the air, even if the compression ratio of the refrigeration cycle is made smaller than that of the first embodiment, it is possible to sufficiently heat, dehumidify and cool the air. A predetermined refrigeration cycle can be configured with less power consumption than the described invention.

According to a third aspect of the present invention, in the air conditioner of the first aspect of the present invention, the first heat exchanger has two rows of heat transfer tubes in a flow direction of the air, and two heat transfer tube paths. Are configured in parallel, during the dehumidifying operation, the refrigerant flows in from the inlet of the refrigerant during the dehumidifying operation and is divided into two heat transfer pipe paths. In each of the heat transfer pipe paths, first, the upstream side of the air flow After passing through a plurality of heat transfer tubes in a row in a row in succession, and then continuously passing through a plurality of heat transfer tubes in a row on the downstream side of the air flow, a row in the upstream row of the air flow is It is configured to continuously pass through the remaining heat transfer tubes, merge, and flow out of the refrigerant outlet during the dehumidifying operation.

Thus, during the cooling operation and the dehumidifying operation,
In the first heat exchanger, the refrigerant flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then passes through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in opposite directions. flow,
During the heating operation, the refrigerant flows through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows, and then flows through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are counter flows. Become.

During the cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger and the second heat exchanger
Heat transfer tube path (refrigerant path) where refrigerant flow and air flow are parallel flow
In this portion, a temperature difference between the temperature gradient of the refrigerant and the temperature gradient of the air can always be ensured with respect to the flow direction of the air. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are in opposing flows. The refrigerant that has been heated in the first half of the refrigerant flow of the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and the adverse effect due to the refrigerant flow and the air flow being opposed flows is as follows. I don't know. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

Further, since the two heat transfer tube paths are configured in parallel, the pressure loss during the cooling operation is reduced,
Performance degradation can be prevented.

During the heating operation, the second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger and the first heat exchanger is connected to the heat transfer pipe path (the refrigerant flow and the air flow are opposed). In this portion, a temperature difference between the temperature gradient of the refrigerant and the temperature gradient of the air can always be ensured with respect to the flow direction of the air, and the heat transfer tube path of the first heat exchanger (the refrigerant path) Since the latter half of the refrigerant flow becomes the counterflow, the sufficiently cooled refrigerant can flow out of the first heat exchanger. The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. A heat transfer tube path in which the refrigerant flow and the air flow sometimes flow in opposite directions
The refrigerant which has been cooled by the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow.
Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the heating operation.

In the dehumidifying operation, in the first heat exchanger, the refrigerant flows into the refrigerant throttle mechanism immediately after passing a plurality of heat transfer tubes arranged in the upstream row of the air flow continuously. Since such a heat transfer tube path (refrigerant path) is configured, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism is further improved. Thereby, the refrigerant flowing into the refrigerant throttle mechanism more easily becomes a liquid refrigerant than the invention described in claim 1,
Since the pressure is reduced by the more stable flow, the refrigerant flow noise is further reduced as compared with the first aspect.

Further, by sufficiently cooling the air, even if the compression ratio of the refrigeration cycle is made smaller than that of the first embodiment, it is possible to sufficiently heat, dehumidify and cool the air. A predetermined refrigeration cycle can be configured with less power consumption than the described invention.

According to a fourth aspect of the present invention, in the air conditioner of the first aspect, the first heat exchanger has two rows of heat transfer tubes in a flow direction of the air and has two heat transfer tube paths. A main first heat exchanger configured in parallel with the main heat exchanger and a single row of heat transfer tubes in the air flow direction, the length of the step direction substantially perpendicular to the air flow direction being shorter than that of the main first heat exchanger; The auxiliary first heat exchanger, wherein during the dehumidifying operation, the refrigerant flows into the auxiliary first heat exchanger from the inlet of the refrigerant during the dehumidifying operation, and the plurality of heat transfer tubes of the auxiliary first heat exchanger Continuously flows through the auxiliary first heat exchanger, flows out into the two heat transfer tube paths, flows into the main first heat exchanger, and in each of the heat transfer tube paths, firstly, air A predetermined number of tubes continuously pass through the plurality of heat transfer tubes in the upstream row of After continuously passing through the plurality of heat transfer tubes in the side row, continuously passing through the remaining heat transfer tubes in the upstream row of the air flow, merging and flowing out of the refrigerant outlet during the dehumidifying operation. Wherein the auxiliary first heat exchanger is located on the upstream side of the air flow of the main first heat exchanger, and the refrigerant in the cooling operation and the dehumidifying operation of the main first heat exchanger. Is arranged so as not to be located on the upstream side of the air flow of the heat transfer tube immediately before the outlet of the heat transfer tube.

Thus, during the cooling operation and the dehumidifying operation,
In the first heat exchanger, the refrigerant flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then passes through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in opposite directions. flow,
During the heating operation, the refrigerant flows through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows, and then flows through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are counter flows. Become.

During the cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger and the second heat exchanger
Heat transfer tube path (refrigerant path) where refrigerant flow and air flow are parallel flow
In this portion, a temperature difference between the temperature gradient of the refrigerant and the temperature gradient of the air can always be ensured with respect to the flow direction of the air. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are in opposing flows. The refrigerant that has been heated in the first half of the refrigerant flow of the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and the adverse effect due to the refrigerant flow and the air flow being opposed flows is as follows. I don't know. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

In the cooling operation, the main first heat exchanger through which the refrigerant flows after the auxiliary first heat exchanger has two heat transfer tube paths arranged in parallel, so that the pressure loss during the cooling operation is reduced. The size can be reduced, and a decrease in performance can be prevented. Although the auxiliary first heat exchanger has one heat transfer tube path, the refrigerant flowing through the auxiliary first heat exchanger during the cooling operation has a low degree of dryness, so that the pressure loss does not increase so much.

During the heating operation, the second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger and the first heat exchanger is connected to the heat transfer tube path (the refrigerant flow and the air flow are opposed). In this portion, a temperature difference between the temperature gradient of the refrigerant and the temperature gradient of the air can always be ensured with respect to the flow direction of the air, and the heat transfer tube path of the first heat exchanger (the refrigerant path) Since the latter half of the refrigerant flow becomes the counterflow, the sufficiently cooled refrigerant can flow out of the first heat exchanger. The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. A heat transfer tube path in which the refrigerant flow and the air flow sometimes flow in opposite directions
The refrigerant which has been cooled by the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow.
Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the heating operation.

In the dehumidifying operation, in the first heat exchanger, immediately after the refrigerant continuously passes through a plurality of heat transfer tubes arranged in a row on the upstream side of the air flow of the main first heat exchanger. And a heat transfer tube path (refrigerant path) that flows into the refrigerant throttle mechanism, and the auxiliary first heat exchanger is a heat transfer tube immediately before the refrigerant outlet during the cooling operation and the dehumidifying operation of the main first heat exchanger. Is arranged so as not to be located on the upstream side of the airflow of the air, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism is further improved. Thereby, the refrigerant flowing into the refrigerant throttle mechanism is more likely to be a liquid refrigerant than the invention described in claim 1, and is further reduced in pressure by a stable flow.
The refrigerant flow noise is further reduced as compared with the first aspect.

Further, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is smaller than that of the first aspect, sufficient heating, dehumidification and cooling of air can be achieved. A predetermined refrigeration cycle can be configured with less power consumption than the described invention.

In the first heat exchanger, the refrigerant flows first during the cooling operation and finally flows during the heating operation because of the auxiliary first heat exchanger having one heat transfer tube path. The flow rate of the refrigerant flowing through the first heat exchanger is increased, the heat transfer coefficient in the pipe is increased, and the heat transfer performance is improved. Therefore, during the heating operation, the sufficiently cooled refrigerant can flow out of the first heat exchanger.

Further, since the first heat exchanger is constructed by connecting the main first heat exchanger and the auxiliary first heat exchanger in series, the heat transfer tubes of the main first heat exchanger having different refrigerant temperatures flowing in the tubes. There is no heat conduction through the plate fins between the heat transfer tubes of the auxiliary first heat exchanger and the heat transfer tubes of the auxiliary first heat exchanger, and the heat exchange performance is improved.

A part of the main first heat exchanger is located on the leeward side of the auxiliary first heat exchanger, but the part of the main first heat exchanger located on the leeward side of the auxiliary first heat exchanger is Also,
Since the plate-like fins are not continuous between the main first heat exchanger and the auxiliary first heat exchanger, the airflow hits the leeward edge of the plate-like fins of the main first heat exchanger, and the airflow is disturbed. Since heat is exchanged between the plate-shaped fins of the main first heat exchanger and the air flow, and because the auxiliary first heat exchanger has a single row of heat transfer tubes in the air flow direction. In addition, a decrease in the heat exchange performance of the first heat exchanger due to the fact that a part of the main first heat exchanger is located on the leeward side of the auxiliary first heat exchanger is small.

The invention described in claim 5 provides the invention according to claims 1 to 4
In the air conditioner according to any one of the above, in the dehumidifying operation of the first heat exchanger, the heat transfer tubes in the upstream row of the air flow and the heat transfer tubes in the downstream row of the air flow immediately before the outlet of the refrigerant. Are provided on the plate-like fin between the rows of the heat transfer tubes to eliminate heat conduction between the rows.

Thus, during the dehumidifying operation, the low-temperature supercooled liquid refrigerant in the heat transfer tube immediately before the outlet of the refrigerant of the first heat exchanger is replaced by the relatively high-temperature superheated gas or gas-liquid mixture in the heat transfer tube on the leeward side. Since it is sufficiently cooled by low-temperature air without being heated by the phase refrigerant, it becomes a low-temperature supercooled liquid refrigerant. Accordingly, the refrigerant flowing into the refrigerant throttle mechanism is more likely to be a liquid refrigerant than the inventions described in the first to fourth aspects, and the pressure is reduced by the stable flow, so that the refrigerant flow noise is generated in the first to fourth aspects. It becomes even smaller than.

Further, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is made smaller than that of the first to fourth aspects, sufficient heating, dehumidification and cooling of air can be performed. A predetermined refrigeration cycle can be configured with less power consumption than the inventions described in 1 to 4.

The invention according to claim 6 is the invention according to claims 1 to 5
In the air conditioner according to any one of the above, the indoor unit that houses the indoor heat exchanger includes a once-through type fan,
The indoor unit has suction grills on the front and upper surfaces thereof, and the first heat exchanger constituting the indoor heat exchanger,
A second heat which is located between the suction grill on the front surface and the fan and exchanges heat with air passing through the front side of the suction grill on the front side and the front side of the suction grill on the upper surface to constitute the indoor heat exchanger The exchanger is located between the suction grill on the upper surface and the fan, and is configured to exchange heat with air that has passed through the rear part of the suction grill on the upper surface.

As a result, the first heat exchanger can be made larger than the second heat exchanger, and the wind speed of the air flow passing through the first heat exchanger is faster than the wind speed of the air flow passing through the second heat exchanger.
During the dehumidifying operation, the heating performance of the first heat exchanger is good, and the refrigerant tends to be a supercooled liquid. In addition, since the wind speed of the airflow passing through the second heat exchanger is low, the dehumidifying efficiency of the air passing through the second heat exchanger is good.

The invention according to claim 7 is the invention according to claims 1 to 6
In the air conditioner according to any one of the above aspects, the heat transfer tubes in the upstream row of the air flow immediately before the outlet of the refrigerant during the dehumidifying operation of the first heat exchanger are relatively air-cooled in the first heat exchanger. It is arranged in a place where the flow of the air is fast.

Thus, during the dehumidifying operation, the cooling efficiency of the refrigerant passing through the heat transfer tube immediately before the outlet of the refrigerant of the first heat exchanger is improved, and the sufficiently cooled low-temperature supercooled liquid refrigerant is supplied to the refrigerant throttle mechanism. Can flow in. Thereby, the refrigerant flowing into the refrigerant throttle mechanism is more likely to be a liquid refrigerant than the inventions of the first to sixth aspects, and the pressure is reduced by a more stable flow, so that the refrigerant flow noise is the invention of the first to sixth aspects. It becomes even smaller than.

Further, by sufficiently subcooling, even if the compression ratio of the refrigeration cycle is made smaller than that of the first to sixth aspects, sufficient heating, dehumidification and cooling of air can be performed. A predetermined refrigeration cycle can be configured with less power consumption than the inventions described in 1 to 6.

According to an eighth aspect of the present invention, the heat transfer tubes through which the refrigerant flows at right angles to the plate-like fins arranged in parallel to each other and through which the refrigerant flows are formed in a plurality of rows in the flow direction of the air. A fin tube-shaped first heat transfer tube, which is arranged in a row on the upstream side of the air flow, wherein the heat transfer tubes adjacent to the entrance and exit are both provided;
Heat exchangers and heat transfer tubes through which the refrigerant flows at right angles to the plate-like fins arranged in a large number in parallel and in which the refrigerant flows are formed in a plurality of rows in the direction of air flow. The fin tube type second heat transfer tubes, which are arranged in a row on the upstream side of the flow of air, in which the heat transfer tubes near the entrance and exit are arranged in a row on the downstream side of the flow of air, and the other heat transfer tubes near the entrance and exit of the other refrigerant are arranged in the row, 2 heat exchangers, one of the two refrigerant inlets and outlets of the first heat exchanger, and one of the refrigerant inlets and outlets arranged in a row on the upstream side of the air flow of the second heat exchanger. And a refrigerant throttle mechanism provided in the middle of the connection pipe connecting the refrigerant and having a state in which the flow path resistance of the refrigerant is large and a state in which the flow path resistance of the refrigerant is small. The first heat exchanger and the second heat exchange So that they do not overlap in the direction of air flow. A heat exchanger unit disposed between the heat exchanger and the second heat exchanger.

Thus, the heat exchanger unit according to the present invention is used for the indoor heat exchanger of the air conditioner, and the refrigerant flows from the compressor to the four-way valve, the outdoor heat exchanger, When the refrigeration cycle is configured to flow in the order of the electric expansion valve in the throttled state, the first heat exchanger, the refrigerant throttle mechanism in the state in which the flow path resistance of the refrigerant is small, and the second heat exchanger, the first heat exchanger and the second heat exchanger The heat exchangers both function as evaporators, allowing cooling operation.

At this time, the heat transfer tube immediately after the inlet of the refrigerant of the first heat exchanger and the heat transfer tube immediately after the inlet of the refrigerant of the second heat exchanger are on the upstream side of the air flow, and the heat transfer tube of the second heat exchanger Since the heat transfer tube immediately before the outlet is on the downstream side of the air flow, the refrigerant flow and the air flow are parallel as a whole, and the temperature gradient of the refrigerant and the temperature gradient of the air are always in the air flow direction. The difference can be secured, and the basic performance is almost the same as that of the indoor heat exchanger in which the refrigerant flow and the air flow are parallel flows during the conventional cooling operation.

The refrigerant is supplied from the compressor to the four-way valve, the second
When the refrigeration cycle is configured to flow in the order of the heat exchanger, the refrigerant throttle mechanism in which the flow path resistance of the refrigerant is small, the first heat exchanger, the electric expansion valve in an appropriately throttled state, and the outdoor heat exchanger, Both the heat exchanger and the second heat exchanger function as condensers, thereby enabling a heating operation.

At this time, the heat transfer tube immediately after the refrigerant inlet of the second heat exchanger is on the downstream side of the flow of air, and the heat transfer tube immediately before the refrigerant outlet of the second heat exchanger and the refrigerant of the first heat exchanger are connected. Since the heat transfer tube immediately before the outlet is on the upstream side of the air flow, the refrigerant flow and the air flow are opposed to each other as a whole, and the temperature gradient of the refrigerant and the temperature gradient of the air are always in the air flow direction. The difference can be secured, and the basic performance is almost the same as that of the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the conventional heating operation.

Further, the refrigerant flows from the compressor to the four-way valve, the outdoor heat exchanger, the fully-open electric expansion valve, the first heat exchanger, the refrigerant throttle mechanism having a large refrigerant flow resistance, and the second heat exchanger. When the refrigeration cycle is configured to flow in the order of the exchanger, the first heat exchanger functions as a condenser and the second heat exchanger functions as an evaporator, thereby enabling a dehumidifying operation without lowering the room temperature.

At this time, since the heat transfer tubes immediately before the outlet of the refrigerant of the first heat exchanger are arranged in the row on the upstream side of the flow of the air, the refrigerant immediately before flowing into the refrigerant throttle mechanism is supplied to the first heat exchanger. And heat exchange with the air before being heated, and it is possible to obtain a sufficient supercooled liquid. As a result, the refrigerant flowing into the refrigerant throttle mechanism becomes a liquid refrigerant, and is decompressed by a stable flow, so that the refrigerant flow noise becomes extremely small as compared with the gas-liquid two-phase refrigerant.

Also, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is reduced, sufficient heating, dehumidification and cooling of air can be performed, and a predetermined refrigeration cycle can be configured with low power consumption. It becomes possible.

According to a ninth aspect of the present invention, in the heat exchanger unit according to the eighth aspect, the first heat exchanger comprises:
When the refrigerant flows from the inlet / outlet of the refrigerant on the anti-refrigerant throttle mechanism side to the inlet / outlet of the refrigerant on the refrigerant throttle mechanism side, the refrigerant flows in from the inlet / outlet of the refrigerant on the anti-refrigerant throttle mechanism side, and flows in the same direction as the air flow. After that, the refrigerant flows in a direction opposite to the air flow, and the heat transfer tube path is configured such that the refrigerant flows out of the refrigerant inlet / outlet on the refrigerant throttle mechanism side.

Thus, during the cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is
The heat exchanger serves as a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. In this portion, the temperature difference between the refrigerant and the air is always constant with respect to the air flow direction. Can be secured. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are in opposing flows. The refrigerant that has been heated in the first half of the refrigerant flow of the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and the adverse effect due to the refrigerant flow and the air flow being opposed flows is as follows. I don't know. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

During the heating operation, the second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger and the first heat exchanger is connected to the heat transfer tube path (opposite flow) between the refrigerant flow and the air flow. In this portion, a temperature difference between the temperature gradient of the refrigerant and the temperature gradient of the air can always be ensured with respect to the flow direction of the air, and the heat transfer tube path of the first heat exchanger (the refrigerant path) Since the latter half of the refrigerant flow becomes the counterflow, the sufficiently cooled refrigerant can flow out of the first heat exchanger. The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. A heat transfer tube path in which the refrigerant flow and the air flow sometimes flow in opposite directions
The refrigerant which has been cooled by the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow.
Therefore, the basic performance is almost the same as that of the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the conventional heating operation.

In the dehumidifying operation, in the first heat exchanger, the refrigerant flows into the refrigerant throttle mechanism immediately after passing a plurality of heat transfer tubes arranged in the upstream row of the air flow continuously. It becomes easy to configure such a heat transfer tube path (refrigerant path), and in this case, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism is further improved. This allows
The refrigerant flowing into the refrigerant throttle mechanism is more likely to be a liquid refrigerant than the invention described in claim 8, and the pressure is reduced by the stable flow, so that the refrigerant flow noise is further reduced as compared with the invention described in claim 8.

Further, by sufficiently subcooling, even if the compression ratio of the refrigeration cycle is made smaller than that of the invention described in claim 8, sufficient heating, dehumidification and cooling of air can be performed. A predetermined refrigeration cycle can be configured with less power consumption than the described invention.

According to a tenth aspect of the present invention, in the heat exchanger unit of the eighth aspect, the first heat exchanger has two rows of heat transfer tubes in the air flow direction. When the refrigerant flows from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism to the inlet / outlet of the refrigerant on the side of the refrigerant throttle mechanism, the refrigerant flows from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism. The heat is divided into two heat transfer pipe paths, and in each of the heat transfer pipe paths, first, a predetermined number of the heat transfer pipes are continuously passed through a plurality of heat transfer pipes on the upstream side of the air flow, and then the air flow After successively passing through the plurality of heat transfer tubes in the downstream row, continuously passing through the remaining heat transfer tubes in the row on the upstream side of the air flow, and merging, the refrigerant of the refrigerant throttle mechanism side It is configured to flow out of the doorway.

Thus, during the cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is
The heat exchanger serves as a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. In this portion, the temperature difference between the refrigerant and the air is always constant with respect to the air flow direction. Can be secured. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are in opposing flows. The refrigerant that has been heated in the first half of the refrigerant flow of the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and the adverse effect due to the refrigerant flow and the air flow being opposed flows is as follows. I don't know. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

Since the two heat transfer tube paths are configured in parallel, the pressure loss during the cooling operation is reduced,
Performance degradation can be prevented.

During the heating operation, the second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger and the first heat exchanger is connected to the heat transfer tube path (the refrigerant flow and the air flow are opposed). In this portion, a temperature difference between the temperature gradient of the refrigerant and the temperature gradient of the air can always be ensured with respect to the flow direction of the air, and the heat transfer tube path of the first heat exchanger (the refrigerant path) Since the latter half of the refrigerant flow becomes the counterflow, the sufficiently cooled refrigerant can flow out of the first heat exchanger. The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. A heat transfer tube path in which the refrigerant flow and the air flow sometimes flow in opposite directions
The refrigerant which has been cooled by the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow.
Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the heating operation.

During the dehumidifying operation, in the first heat exchanger, the refrigerant flows into the refrigerant throttle mechanism immediately after passing a plurality of heat transfer tubes arranged in the upstream row of the air flow continuously. Since such a heat transfer tube path (refrigerant path) is configured, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism is further improved. Thereby, the refrigerant flowing into the refrigerant throttle mechanism is more likely to be a liquid refrigerant than the invention described in claim 8,
Since the pressure is reduced by the stable flow, the refrigerant flow noise is further reduced as compared with the eighth aspect.

Further, by sufficiently cooling the air, even if the compression ratio of the refrigeration cycle is made smaller than that of the invention described in claim 8, sufficient heating, dehumidification and cooling of air can be performed. A predetermined refrigeration cycle can be configured with less power consumption than the described invention.

According to an eleventh aspect of the present invention, in the heat exchanger unit of the eighth aspect, the first heat exchanger has two rows of heat transfer tubes in the air flow direction. The paths are configured in parallel, and the heat transfer tubes adjacent to the refrigerant inlet / outlet on the refrigerant throttle mechanism side are located in a lower stage than the heat transfer tubes adjacent to the refrigerant inlet / outlet on the anti-refrigerant throttle mechanism side, and are configured in parallel. One of the two heat transfer tube paths is formed from the inlet / outlet of the refrigerant on the anti-refrigerant throttle mechanism side to the upper end of the heat exchanger,
Further, the row moves to the row near the upper end of the heat exchanger, which is on the downstream side of the air flow, and is formed toward the center of the heat exchanger toward the lower end of the heat exchanger, and further, the row on the upstream side of the air flow near the center of the heat exchanger. And the other of the two heat transfer tube paths formed in parallel to the lower end of the heat exchanger toward the refrigerant inlet and outlet of the refrigerant throttle mechanism side, and the other end of the heat exchanger lower end from the refrigerant inlet and outlet of the anti-refrigerant throttle mechanism side To the center of the heat exchanger toward the center of the heat exchanger, and then move to a row on the downstream side of the air flow near the center of the heat exchanger and form toward the lower end of the heat exchanger. Then, the process moves to a row on the upstream side of the heat exchanger, and is formed up to the refrigerant inlet / outlet on the refrigerant throttle mechanism side toward the upper end of the heat exchanger.

Thus, during the cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is
The heat exchanger serves as a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. In this portion, the temperature difference between the refrigerant and the air is always constant with respect to the air flow direction. Can be secured. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are in opposing flows. The refrigerant that has been heated in the first half of the refrigerant flow of the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and the adverse effect due to the refrigerant flow and the air flow being opposed flows is as follows. I don't know. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

In the first heat exchanger, since two heat transfer tube paths are formed in parallel, the pressure loss during the cooling operation is reduced, and a decrease in performance can be prevented.

During the heating operation, the second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger and the first heat exchanger is connected to the heat transfer tube path (the refrigerant flow and the air flow are opposed). In this portion, a temperature difference between the temperature gradient of the refrigerant and the temperature gradient of the air can always be ensured with respect to the flow direction of the air, and the heat transfer tube path of the first heat exchanger (the refrigerant path) Since the latter half of the refrigerant flow becomes the counterflow, the sufficiently cooled refrigerant can flow out of the first heat exchanger. The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. A heat transfer tube path in which the refrigerant flow and the air flow sometimes flow in opposite directions
The refrigerant which has been cooled by the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow.
Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the heating operation.

During the dehumidifying operation, in the first heat exchanger, the refrigerant flows into the refrigerant throttle mechanism immediately after passing continuously through a plurality of heat transfer tubes arranged in the upstream row of the air flow. Since such a heat transfer tube path (refrigerant path) is configured, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism is further improved. Thereby, the refrigerant flowing into the refrigerant throttle mechanism is more likely to be a liquid refrigerant than the invention described in claim 8,
Since the pressure is reduced by the stable flow, the refrigerant flow noise is further reduced as compared with the eighth aspect.

Further, by sufficiently subcooling, even if the compression ratio of the refrigeration cycle is made smaller than that of the invention described in claim 8, sufficient heating, dehumidification and cooling of air can be performed. A predetermined refrigeration cycle can be configured with less power consumption than the described invention.

Further, in a wall-mounted type air conditioner having a suction grill on the front and upper surfaces of the main body and an outlet on the lower part of the front, and having a built-in once-through fan, between the suction grill on the front and the fan. The first heat exchanger is arranged to exchange heat between the air passing through the front side suction grille and the front side of the upper side suction grille and the refrigerant in the first heat exchanger. In the case where the second heat exchanger is disposed between the first heat exchanger and the air passing through the rear part of the suction grill on the upper surface and heat exchanges the refrigerant in the second heat exchanger, the refrigerant throttle of the first heat exchanger is provided. The heat transfer tube close to the inlet / outlet of the refrigerant on the mechanism side, that is, the heat transfer tube immediately before the outlet of the refrigerant during the dehumidifying operation of the first heat exchanger is the air at the portion of the first heat exchanger where the flow of air is relatively fast. Located upstream of the stream Therefore, the cooling efficiency of the refrigerant passing through the heat transfer tube immediately before the outlet of the refrigerant of the first heat exchanger during the dehumidifying operation is improved, and the sufficiently cooled low-temperature supercooled liquid refrigerant flows into the refrigerant throttle mechanism. be able to.

At this time, the direction of the air flow passing through the first heat exchanger is the same as that from the upstream row of the air flow of the first heat exchanger to the downstream row of the air flow. In addition to the row direction component of the first heat exchanger, there is a stepwise component of the first heat exchanger that goes from the upper portion to the lower portion of the first heat exchanger. It becomes a heat transfer tube path through which the refrigerant flows from the upper part to the lower part of the first heat exchanger. During the heating operation, it becomes a heat transfer pipe path through which the refrigerant flows from the lower part to the upper part of the first heat exchanger as a whole.

Therefore, in the first heat exchanger, the ratio of the heat transfer tube path in which the refrigerant flow and the air flow become parallel flow during the cooling operation and the refrigerant flow and the air flow become counter flow during the heating operation increases, and the first heat exchange The heat exchange performance of the vessel is improved.

According to a twelfth aspect of the present invention, in the heat exchanger unit according to the eighth aspect, the first heat exchanger has two rows of heat transfer tubes in a flow direction of air and has two heat transfer tube paths. Have a main first heat exchanger configured in parallel with the main heat exchanger and a row of heat transfer tubes in the air flow direction, and have a length in a step direction substantially perpendicular to the air flow direction than the main first heat exchanger. When the refrigerant flows from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism to the inlet / outlet of the refrigerant on the side of the refrigerant throttle mechanism, the refrigerant flows from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism. After flowing into the auxiliary first heat exchanger and continuously passing through a plurality of heat transfer tubes of the auxiliary first heat exchanger, the auxiliary first heat exchanger
It flows out of the heat exchanger, is diverted to the two heat transfer tube paths, flows into the main first heat exchanger, and in each of the heat transfer tube paths, first, a plurality of rows in the upstream side of the air flow. After passing through a predetermined number of heat transfer tubes continuously, and then successively passing through a plurality of heat transfer tubes in a row on the downstream side of the air flow, and then remaining in the row on the upstream side of the air flow. The auxiliary first heat exchanger is configured to continuously pass through the heat pipe, merge and flow out of the refrigerant inlet / outlet on the side of the refrigerant throttle mechanism, and the auxiliary first heat exchanger is configured to control the flow of air of the main first heat exchanger. On the upstream side,
In addition, it is arranged so as not to be located on the upstream side of the air flow of the heat transfer tube of the main first heat exchanger which is close to the inlet / outlet of the refrigerant on the side of the refrigerant throttle mechanism.

Thus, during cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger and the second
The heat exchanger serves as a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. In this portion, the temperature difference between the refrigerant and the air is always constant with respect to the air flow direction. Can be secured. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are in opposing flows. The refrigerant that has been heated in the first half of the refrigerant flow of the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and the adverse effect due to the refrigerant flow and the air flow being opposed flows is as follows. I don't know. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

In the cooling operation, the main first heat exchanger through which the refrigerant flows after the auxiliary first heat exchanger has two heat transfer tube paths arranged in parallel, so that the pressure loss during the cooling operation is reduced. The size can be reduced, and a decrease in performance can be prevented. Although the auxiliary first heat exchanger has one heat transfer tube path, the refrigerant flowing through the auxiliary first heat exchanger during the cooling operation has a low degree of dryness, so that the pressure loss does not increase so much.

During the heating operation, the second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger and the first heat exchanger is connected to the heat transfer tube path (the refrigerant flow and the air flow are opposed). In this portion, a temperature difference between the temperature gradient of the refrigerant and the temperature gradient of the air can always be ensured with respect to the flow direction of the air, and the heat transfer tube path of the first heat exchanger (the refrigerant path) Since the latter half of the refrigerant flow becomes the counterflow, the sufficiently cooled refrigerant can flow out of the first heat exchanger. The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. A heat transfer tube path in which the refrigerant flow and the air flow sometimes flow in opposite directions
The refrigerant which has been cooled by the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow.
Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the heating operation.

In the dehumidifying operation, in the first heat exchanger, immediately after the refrigerant continuously passes through a plurality of heat transfer tubes arranged in the upstream row of the air flow in the main first heat exchanger. And a heat transfer tube path (refrigerant path) that flows into the refrigerant throttle mechanism, and the auxiliary first heat exchanger is a heat transfer tube immediately before the refrigerant outlet during the cooling operation and the dehumidifying operation of the main first heat exchanger. Is arranged so as not to be located on the upstream side of the airflow of the air, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism is further improved. Accordingly, the refrigerant flowing into the refrigerant throttle mechanism is more likely to be a liquid refrigerant than the invention described in claim 8, and the pressure is reduced by a more stable flow.
Refrigerant flow noise is further reduced as compared with the eighth aspect.

Further, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is made smaller than that of the invention described in claim 8, sufficient heating, dehumidification and cooling of air can be performed. A predetermined refrigeration cycle can be configured with less power consumption than the described invention.

In the first heat exchanger, the refrigerant flows first during the cooling operation and finally flows during the heating operation because of the auxiliary first heat exchanger having one heat transfer tube path. The flow rate of the refrigerant flowing through the first heat exchanger is increased, the heat transfer coefficient in the pipe is increased, and the heat transfer performance is improved. Therefore, during the heating operation, the sufficiently cooled refrigerant can flow out of the first heat exchanger.

Further, since the first heat exchanger is constructed by connecting the main first heat exchanger and the auxiliary first heat exchanger in series, the heat transfer tubes of the main first heat exchanger having different refrigerant temperatures flowing in the tubes. There is no heat conduction through the plate fins between the heat transfer tubes of the auxiliary first heat exchanger and the heat transfer tubes of the auxiliary first heat exchanger, and the heat exchange performance is improved.

A part of the main first heat exchanger is located on the leeward side of the auxiliary first heat exchanger, but a part of the main first heat exchanger located on the leeward side of the auxiliary first heat exchanger is located. Also,
Since the plate-like fins are not continuous between the main first heat exchanger and the auxiliary first heat exchanger, the airflow hits the leeward edge of the plate-like fins of the main first heat exchanger, and the airflow is disturbed. Since heat is exchanged between the plate-shaped fins of the main first heat exchanger and the air flow, and because the auxiliary first heat exchanger has a single row of heat transfer tubes in the air flow direction. In addition, a decrease in the heat exchange performance of the first heat exchanger due to the fact that a part of the main first heat exchanger is located on the leeward side of the auxiliary first heat exchanger is small.

According to a thirteenth aspect of the present invention, in the heat exchanger unit of the eighth aspect, the first heat exchanger has two rows of heat transfer tubes in the direction of air flow and has two heat transfer tube paths. Have a main first heat exchanger configured in parallel with the main heat exchanger and a row of heat transfer tubes in the air flow direction, and have a length in a step direction substantially perpendicular to the air flow direction than the main first heat exchanger. The heat transfer tube of the main first heat exchanger, which comprises a short auxiliary first heat exchanger and is close to the inlet and outlet of the refrigerant on the side of the refrigerant throttle mechanism, has the auxiliary first heat exchanger which is close to the inlet and outlet of the refrigerant on the side opposite to the refrigerant throttle mechanism. A heat transfer tube path of the auxiliary first heat exchanger is located at a lower stage than a heat transfer tube of the heat exchanger, and a refrigerant inlet / outlet port on a side opposite to the refrigerant throttle mechanism disposed near a lower end of the auxiliary first heat exchanger. From the top to the heat exchanger upper end to the heat transfer tube near the upper end of the heat exchanger, the main first heat exchange One of the two heat transfer tube paths configured in parallel with each other is formed from a branch portion connected to a heat transfer tube near the heat exchanger upper end of the auxiliary first heat exchanger toward the heat exchanger upper end, and Move to the row on the downstream side of the air flow near the upper end of the heat exchanger, form to the center of the heat exchanger toward the lower end of the heat exchanger, and further form the row on the upstream side of the air flow near the center of the heat exchanger. The other of the two heat transfer tube paths which are formed toward the lower end of the transfer heat exchanger to the refrigerant inlet / outlet on the side of the refrigerant throttle mechanism and are arranged in parallel with the main first heat exchanger are the auxiliary first heat exchangers. From the diversion section connected to the heat transfer tubes near the upper end of the heat exchanger to the center of the heat exchanger toward the lower end of the heat exchanger, and then to the row near the center of the heat exchanger, which is on the downstream side of the air flow. Formed toward the lower end of the heat exchanger, and further near the lower end of the heat exchanger It is obtained by the configuration toward the upstream side to become transfer heat exchanger upper column of air flow forms to entrance of refrigerant in the refrigerant throttle mechanism side.

Thus, during the cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is connected to the second part.
The heat exchanger serves as a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. In this portion, the temperature difference between the refrigerant and the air is always constant with respect to the air flow direction. Can be secured. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are in opposing flows. The refrigerant that has been heated in the first half of the refrigerant flow of the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and the adverse effect due to the refrigerant flow and the air flow being opposed flows is as follows. I don't know. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

In the cooling operation, the main first heat exchanger, through which the refrigerant flows after the auxiliary first heat exchanger, has two heat transfer tube paths arranged in parallel, so that the pressure loss during the cooling operation is reduced. The size can be reduced, and a decrease in performance can be prevented. Although the auxiliary first heat exchanger has one heat transfer tube path, the refrigerant flowing through the auxiliary first heat exchanger during the cooling operation has a low degree of dryness, so that the pressure loss does not increase so much.

In the heating operation, the second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger and the first heat exchanger is connected to the heat transfer tube path (the refrigerant flow and the air flow are opposed). In this portion, a temperature difference between the temperature gradient of the refrigerant and the temperature gradient of the air can always be ensured with respect to the flow direction of the air, and the heat transfer tube path of the first heat exchanger (the refrigerant path) Since the latter half of the refrigerant flow becomes the counterflow, the sufficiently cooled refrigerant can flow out of the first heat exchanger. The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. A heat transfer tube path in which the refrigerant flow and the air flow sometimes flow in opposite directions
The refrigerant which has been cooled by the heat exchanger and is in a gas-liquid two-phase state flows, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow.
Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the heating operation.

In the dehumidifying operation, in the first heat exchanger, immediately after the refrigerant continuously passes through a plurality of heat transfer tubes arranged in the upstream row of the air flow of the main first heat exchanger. And a heat transfer tube path (refrigerant path) that flows into the refrigerant throttle mechanism, and the auxiliary first heat exchanger is a heat transfer tube immediately before the refrigerant outlet during the cooling operation and the dehumidifying operation of the main first heat exchanger. Is arranged so as not to be located on the upstream side of the airflow of the air, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism is further improved. Accordingly, the refrigerant flowing into the refrigerant throttle mechanism is more likely to be a liquid refrigerant than the invention described in claim 8, and the pressure is reduced by a more stable flow.
Refrigerant flow noise is further reduced as compared with the eighth aspect.

Further, by sufficiently subcooling, even if the compression ratio of the refrigeration cycle is smaller than that of the invention described in claim 8, sufficient heating, dehumidification and cooling of air can be performed. A predetermined refrigeration cycle can be configured with less power consumption than the described invention.

Further, in the first heat exchanger, the refrigerant flows first during the cooling operation and finally flows during the heating operation because of the auxiliary first heat exchanger having one heat transfer tube path. The flow rate of the refrigerant flowing through the first heat exchanger is increased, the heat transfer coefficient in the pipe is increased, and the heat transfer performance is improved. Therefore, during the heating operation, the sufficiently cooled refrigerant can flow out of the first heat exchanger.

Further, since the first heat exchanger is constructed by connecting the main first heat exchanger and the auxiliary first heat exchanger in series, the heat transfer tubes of the main first heat exchanger having different refrigerant temperatures flowing through the tubes are provided. There is no heat conduction through the plate fins between the heat transfer tubes of the auxiliary first heat exchanger and the heat transfer tubes of the auxiliary first heat exchanger, and the heat exchange performance is improved.

Note that a part of the main first heat exchanger is located on the leeward side of the auxiliary first heat exchanger, but a part of the main first heat exchanger which is located on the leeward side of the auxiliary first heat exchanger. Also,
Since the plate-like fins are not continuous between the main first heat exchanger and the auxiliary first heat exchanger, the airflow hits the leeward edge of the plate-like fins of the main first heat exchanger, and the airflow is disturbed. Since heat is exchanged between the plate-shaped fins of the main first heat exchanger and the air flow, and because the auxiliary first heat exchanger has a single row of heat transfer tubes in the air flow direction. In addition, a decrease in the heat exchange performance of the first heat exchanger due to the fact that a part of the main first heat exchanger is located on the leeward side of the auxiliary first heat exchanger is small.

Further, in a wall-mounted type air conditioner having a suction grill on the front and upper surfaces of the main body and a blowout port on the lower front, and having a built-in once-through fan, a space between the front suction grill and the fan. The first heat exchanger is arranged to exchange heat between the air passing through the front side suction grille and the front side of the upper side suction grille and the refrigerant in the first heat exchanger. In the case where the second heat exchanger is disposed between the first heat exchanger and the air passing through the rear part of the suction grill on the upper surface and heat exchanges the refrigerant in the second heat exchanger, the refrigerant throttle of the first heat exchanger is provided. The heat transfer tube close to the inlet / outlet of the refrigerant on the mechanism side, that is, the heat transfer tube immediately before the outlet of the refrigerant during the dehumidifying operation of the first heat exchanger is the air at the portion of the first heat exchanger where the flow of air is relatively fast. Located upstream of the stream Therefore, during the dehumidifying operation, the cooling efficiency of the refrigerant passing through the heat transfer pipe immediately before the outlet of the refrigerant of the first heat exchanger is improved, and the sufficiently cooled low-temperature supercooled liquid refrigerant flows into the refrigerant throttle mechanism. be able to.

At this time, the direction of the air flow passing through the main first heat exchanger of the first heat exchanger depends on the direction of the air flow from the upstream row of the main first heat exchanger. In addition to the row direction component of the main first heat exchanger going to the downstream row, there is a stepwise component of the main first heat exchanger going from the upper part to the lower part of the main first heat exchanger. When the cooling operation is performed, the refrigerant flows from the upper part to the lower part of the main first heat exchanger when viewed as a whole. When the heating operation is performed as a whole, the refrigerant flows from the lower part to the upper part of the main first heat exchanger. A heat transfer tube path through which the refrigerant flows.

Therefore, in the main first heat exchanger of the first heat exchanger, the ratio of the heat transfer tube path in which the refrigerant flow and the air flow become parallel flow during the cooling operation and the refrigerant flow and the air flow become counter flow during the heating operation is reduced. And the heat exchange performance of the first heat exchanger is improved.

At this time, the auxiliary first heat exchanger is disposed in an extra space between the suction grills on the front and upper surfaces and the main first heat exchanger, so that the air conditioner is enlarged. Without adding an auxiliary first heat exchanger,
The heat exchange performance of the heat exchanger can be improved.

According to a fourteenth aspect of the present invention, in the heat exchanger unit according to any one of the eighth to thirteenth aspects, there is provided a heat exchanger unit comprising: a first heat exchanger; Between the row of heat transfer tubes on the upstream side of the flow and the row of heat transfer tubes on the downstream side of the flow of air, cuts are provided on the plate-like fins to eliminate heat conduction between the rows of heat transfer tubes It is.

Thus, during the dehumidifying operation, the low-temperature supercooled liquid refrigerant in the heat transfer tube immediately before the outlet of the refrigerant of the first heat exchanger is replaced by the relatively high-temperature superheated gas or gas-liquid mixture in the leeward heat transfer tube. Since it is sufficiently cooled by low-temperature air without being heated by the phase refrigerant, it becomes a low-temperature supercooled liquid refrigerant. Accordingly, the refrigerant flowing into the refrigerant throttle mechanism is more likely to be a liquid refrigerant than the inventions described in claims 8 to 13, and the pressure is reduced by a more stable flow.
To 13 are smaller than those of the inventions described in (13) to (13).

Further, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is made smaller than that of the inventions described in claims 8 to 13, sufficient heating, dehumidification and cooling of air can be performed. A predetermined refrigeration cycle can be configured with less power consumption than the inventions described in 8 to 13.

According to a fifteenth aspect of the present invention, in the heat exchanger unit according to any one of the eighth to fourteenth aspects, the refrigerant throttle mechanism is constituted by a control valve having a fully open state and a slightly open state. Things.

Thus, the refrigerant throttle mechanism having a state in which the flow path resistance of the refrigerant is large and a state in which the flow path resistance of the refrigerant is small is provided.
It can be constituted by one control valve. In addition, since the flow path resistance can be arbitrarily set during the dehumidifying operation, the amount of dehumidified air and the blowing temperature can be finely controlled.

According to a sixteenth aspect of the present invention, in the heat exchanger unit according to any one of the eighth to fourteenth aspects, the refrigerant throttle mechanism is provided in a capillary tube and a bypass which bypasses the capillary tube. It is constituted by the two-way valve provided.

Thus, a refrigerant throttle mechanism having a state in which the flow path resistance of the refrigerant is large and a state in which the flow path resistance of the refrigerant is low is provided.
Inexpensive configuration is possible with a capillary tube and a two-way valve.

[0116]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of an air conditioner according to the present invention and a heat exchanger unit used for the same will be described below with reference to the drawings.

(Embodiment 1) FIG. 1 is a side sectional view of an indoor unit according to Embodiment 1 of the air conditioner according to the present invention.

In FIG. 1, a multi-stage bending indoor heat exchanger 21 incorporated in an indoor unit is thermally divided into a lower front portion 22, a front upper portion 23 and a rear portion 24 and bent. In the indoor heat exchanger 21, heat transfer tubes 26 provided to penetrate a plurality of plate-like fins 25 are formed in two rows in the direction of air flow, and each heat transfer tube 26 is connected at an end. I have.

The first heat exchanger 33 is constituted by the upper front part 23 and the rear part 24, and the lower front part 22 is formed by the second heat exchanger 33.
A first heat exchanger 33 and a second heat exchanger 3
4 are connected via a refrigerant throttle mechanism 27 having a state where the flow path resistance of the refrigerant is large and a state where the flow path resistance of the refrigerant is small. In this embodiment, as the refrigerant throttle mechanism 27, a dehumidification control valve 27 having a fully opened state and a slightly opened state, and being in a slightly opened state during the dehumidifying operation and having a function of performing a throttling operation is used.

When the once-through fan type fan 30 is rotated, the suction grills 31a, 3a on the front and upper surfaces are formed.
Air is introduced from 1b, is exchanged with the refrigerant in the indoor heat exchanger 21 through the filter 28, passes through the fan 30, and is blown out from the outlet 32 into the room.

Reference numeral 29 denotes a rear casing, and a dew tray 29a for the rear portion 24 of the indoor heat exchanger 21 is integrally formed. 32a is an air outlet wind direction plate, 39 is a front lower part 22 and a front upper part 2 of the indoor heat exchanger 21.
3 is a dew saucer.

The air conditioner of the first embodiment has a fin tube in which a plurality of heat transfer tubes 26 which are inserted at right angles to a plurality of plate-like fins 25 arranged in parallel and through which a refrigerant flows are formed in two rows in the direction of air flow. The indoor heat exchanger 21 is thermally divided into a first heat exchanger 33 and a second heat exchanger 34 in a step direction substantially perpendicular to the direction of air flow, and the first heat exchanger 33 and the second heat exchanger The heat exchanger 34 is connected to the refrigerant throttle mechanism 27 having a state in which the flow path resistance of the refrigerant is large and a state in which the flow path resistance of the refrigerant is low (the state is fully opened and slightly opened, and becomes slightly opened during the dehumidifying operation to perform the throttle action. The refrigerant flows from the first heat exchanger 33 to the second heat exchanger 34 during the cooling operation and the dehumidifying operation, and from the second heat exchanger 34 during the heating operation. The refrigeration cycle is configured so that the refrigerant flows to the first heat exchanger 33. And, the refrigerant throttle mechanism 27 during the dehumidifying operation
In the state where the flow path resistance of the refrigerant is large, the first heat exchanger 33
In the air conditioner in which the indoor air can be dehumidified by the second heat exchanger 34 while the indoor air is heated by the heat transfer, the transfer immediately after the refrigerant inlet 33a of the first heat exchanger 33 during the dehumidifying operation is performed. The heat pipe 26 and the heat transfer pipe 26 immediately before the refrigerant outlet 33b are arranged in a row on the upstream side of the air flow, and the heat transfer pipe 26 immediately after the refrigerant inlet 34a of the second heat exchanger 34 during the dehumidifying operation is connected to the air flow. The heat transfer tubes 26 in the upstream row and immediately before the refrigerant outlet 34b are arranged in the downstream row of the air flow.

In the first heat exchanger 33, during the dehumidifying operation, the refrigerant flows through the inlet 33a of the refrigerant during the dehumidifying operation, flows in the same direction as the air flow, and then flows in the direction opposite to the air flow. The refrigerant flows into the outlet 33b of the refrigerant during the dehumidifying operation.
The heat transfer tube path is configured to flow out of the heat transfer tube.

More specifically, the first heat exchanger 33 includes:
It has two rows of heat transfer tubes 26 in the direction of air flow, two heat transfer tube paths are configured in parallel, and during the dehumidifying operation, the refrigerant is
At the time of the dehumidifying operation, the refrigerant flows in through the inlet 33a and is divided into two heat transfer pipe paths. In each heat transfer pipe path, first, a predetermined number (2,2) of a plurality of heat transfer pipes 26 in the upstream row of the air flow is provided. 3) after passing continuously, and then four consecutively through the plurality of heat transfer tubes 26 in the downstream row of the air flow, and then passing the remaining heat transfer tubes 26 in the upstream row of the air flow. (Two or three) continuously, and merged to flow out of the refrigerant outlet 33b during the dehumidifying operation.

In addition, during the dehumidifying operation of the first heat exchanger 33, the space between the heat transfer tubes 26 in the upstream row of the air flow and the heat transfer tubes 26 in the downstream row of the air flow immediately after the inlet 33a of the refrigerant. In the dehumidifying operation of the first heat exchanger 33, the heat transfer tubes are provided between the heat transfer tubes 26 in the upstream row of the air flow and the heat transfer tubes 26 in the downstream row of the air flow immediately before the outlet 33b of the refrigerant. Cuts 25 a for eliminating heat conduction between 26 rows are provided in the plate-like fin 25.

In the heat exchanger unit of the first embodiment, the heat transfer tubes 26 which are inserted at right angles to the plate-like fins 25 arranged in parallel and through which the refrigerant flows are formed in two rows in the direction of air flow. A first heat exchanger 33 in the form of a fin tube in which the heat transfer tubes 26 adjacent to the two refrigerant inlets / outlets 33a, 33b are both arranged in a row on the upstream side of the air flow; The heat transfer tubes 26 which are inserted at right angles to the fins 25 and through which the refrigerant flows are formed in a plurality of rows in the air flow direction, and the heat transfer tubes 26 which are close to one of the two refrigerant inlets / outlets 34a and 34b. Are arranged in a row on the upstream side of the air flow, and the heat transfer tubes 26 adjacent to the other refrigerant inlet / outlet 34b are arranged in a row on the downstream side of the air flow.
4 and the two refrigerant inlets / outlets 33a of the first heat exchanger 33,
A refrigerant flow path provided in the middle of a connection pipe connecting one of the refrigerant inlets / outlets 33b among the refrigerants 33b and the refrigerant inlet / outlets 34a arranged in a row on the upstream side of the air flow of the second heat exchanger 34. The refrigerant throttle mechanism 27 has a state in which the resistance is large and a state in which the flow path resistance of the refrigerant is small. The first heat exchanger 33 and the second heat exchanger 34 are arranged in the first heat exchanger 34 so that they do not overlap in the direction of air flow. The heat exchanger 33 and the second heat exchanger 34 are arranged.

When the refrigerant flows from the inlet / outlet 33a of the refrigerant on the side of the refrigerant restricting mechanism 27 to the inlet / outlet 33b of the refrigerant on the side of the refrigerant restricting mechanism 27, the first heat exchanger 33
After flowing in from the refrigerant inlet / outlet 33a on the side of the anti-refrigerant throttle mechanism 27 and flowing in the same direction as the air flow, the refrigerant flows in the direction opposite to the air flow and the refrigerant inlet / outlet 33b on the refrigerant throttle mechanism 27 side. The heat transfer tube path is configured to flow out of the heat transfer tube.

More specifically, the first heat exchanger 33 includes:
It has two rows of heat transfer tubes 26 in the direction of air flow, two heat transfer tube paths are configured in parallel, and the refrigerant flows from the inlet / outlet 33a of the refrigerant on the anti-refrigerant throttle mechanism 27 side to the inlet / outlet 33b of the refrigerant on the refrigerant throttle mechanism 27 side. Flows, the refrigerant flows in from the refrigerant inlet / outlet 33a on the side of the anti-refrigerant throttle mechanism 27 and is divided into two heat transfer tube paths. In each of the heat transfer tube paths,
First, a plurality of heat transfer tubes 2 in a row on the upstream side of the air flow.
6 continuously through a predetermined number of tubes, and then continuously through a plurality of heat transfer tubes 26 in a row on the downstream side of the air flow.
It is configured to continuously pass through the remaining heat transfer tubes 26 in the row on the upstream side of the air flow, to merge, and to flow out of the refrigerant inlet / outlet 33b on the refrigerant throttle mechanism 27 side.

The heat transfer tubes 26 in the row on the upstream side of the air flow adjacent to the refrigerant inlet / outlet 33a of the first heat exchanger 33 on the side opposite to the refrigerant throttling mechanism 27, and the heat transfer tubes 26 in the row on the downstream side of the air flow. Between the rows with the heat transfer tubes 26, and the heat transfer tubes 26 in the row on the upstream side of the air flow near the refrigerant inlet / outlet 33b on the refrigerant throttle mechanism 27 side of the first heat exchanger 33 and the downstream side of the air flow. A cut 25 a for eliminating heat conduction between the rows of the heat transfer tubes 26 is provided in the plate-like fin 25 between the rows of the heat transfer tubes 26.

FIG. 2 shows the entire refrigeration cycle of the air conditioner of this embodiment. In FIG. 2, a compressor 35 capable of controlling the rotation speed, a four-way valve 3 for switching the operation state
6. The outdoor heat exchanger 37, the electric expansion valve 38 capable of being fully opened without a throttling effect, and the indoor heat exchanger 21 and the dehumidification control valve 27 described above, which are connected to form a refrigeration cycle. I have.

First, during the cooling operation, the four-way valve 36 is switched to the cooling side, the dehumidification control valve 27 is opened, and the electric expansion valve 38 is appropriately squeezed. , Outdoor heat exchanger 37, electric expansion valve 3
8, the first heat exchanger 33 of the indoor heat exchanger 21 (the upper part 23 on the front side of the indoor heat exchanger 21 and the rear part 24 of the indoor heat exchanger 21), the dehumidification control valve 27 in the fully open state, and the indoor heat exchanger 2
The first heat exchanger 34 (the lower front part 22 of the indoor heat exchanger 21), the four-way valve 36, and the compressor 35 constitute a refrigerant path in this order, and the outdoor heat exchanger 37 is a condenser and the indoor heat exchanger 21 The whole acts as an evaporator.

When the fan 30 is rotated, the indoor air is drawn into the suction grills 31a, 31a on the front and upper surfaces.
b, and passes through the indoor heat exchanger 21 after being removed by the filter 28. Then, the air is cooled by the indoor heat exchanger 21, passes through the fan 30, and is blown into the room from the outlet 32.

At this time, the indoor heat exchanger 21 during the cooling operation is
The refrigerant inlet 33a is the refrigerant inlet / outlet 33a of the first heat exchanger 33 on the side opposite to the refrigerant throttle mechanism 27, and the heat transfer tube 26 immediately behind the refrigerant inlet 33a is on the upstream side of the flow of air. The refrigerant outlet 34b of the indoor heat exchanger 21 during the cooling operation is connected to the refrigerant inlet / outlet 34 of the second heat exchanger 34 on the side opposite to the refrigerant throttle mechanism 27.
b, and the heat transfer tube 26 immediately before that is downstream of the flow of air. The refrigerant inlet 34a of the second heat exchanger 34 during the cooling operation is connected to the refrigerant throttle mechanism 27 of the second heat exchanger 34.
Side refrigerant inlet / outlet 34a, and the heat transfer tube 26
Is upstream of the air flow.

Further, in the indoor heat exchanger 21, the first heat exchanger 33 is connected to the refrigerant inlet 33a of the first heat exchanger 33.
The refrigerant flowing into the heat exchanger flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in opposite directions. The refrigerant flows out of the first heat exchanger 33 from the refrigerant outlet 33b. afterwards,
The refrigerant that has flowed into the second heat exchanger 34 from the refrigerant inlet 34a of the second heat exchanger 34 via the dehumidification control valve 27 in the fully opened state is a heat transfer tube path (refrigerant) in which the refrigerant flow and the air flow are parallel. And flows out of the second heat exchanger 34 from the refrigerant outlet 34b.

Therefore, during the cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger 33 and the second heat exchanger 34 form a heat transfer tube in which the refrigerant flow and the air flow are parallel. In the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow become parallel flows as a whole, and the refrigerant flow and the air flow become parallel flows, in the evaporator where the refrigerant temperature sequentially decreases due to pressure loss The air can be cooled efficiently with a constant temperature difference between the refrigerant temperature gradient and the air temperature gradient with respect to the air flow direction. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger 33 is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are opposed to each other. The refrigerant which has been heated in the first half of the refrigerant flow of the first heat exchanger 33 and has been in a gas-liquid two-phase state flows, has almost no change in the temperature of the refrigerant, and has an adverse effect due to the refrigerant flow and the air flow being opposed to each other. There is no end.
Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

Further, since the two heat transfer tube paths are formed in parallel, the pressure loss during the cooling operation is reduced,
Performance degradation can be prevented.

Next, during the heating operation, the four-way valve 36 is switched to the heating side, the dehumidification control valve 27 is opened, and the electric expansion valve 38 is appropriately squeezed. 36, the second heat exchanger 34 of the indoor heat exchanger 21 (the lower part 22 on the front surface of the indoor heat exchanger 21), the dehumidification control valve 27 in the fully opened state, the first heat exchanger 33 of the indoor heat exchanger 21 (the indoor heat exchanger 33) A refrigerant path is formed in the order of the rear part 24 of the exchanger 21, the upper front part 23 of the indoor heat exchanger 21), the electric expansion valve 38, the outdoor heat exchanger 37, the four-way valve 36, and the compressor 35 in this order. 37 serves as an evaporator, and the entire indoor heat exchanger 21 serves as a condenser.

When the fan 30 is rotated, the indoor air is drawn into the suction grills 31a and 31a on the front and upper surfaces.
b, and passes through the indoor heat exchanger 21 after being removed by the filter 28. Then, the air is heated by the indoor heat exchanger 21, passes through the fan 30, and is blown into the room through the outlet 32.

At this time, the indoor heat exchanger 21 during the heating operation is
The refrigerant inlet 34b is the refrigerant inlet / outlet 34b of the second heat exchanger 34 on the side opposite to the refrigerant throttle mechanism 27, and the heat transfer tube 26 immediately behind the refrigerant inlet 34b is downstream of the flow of air. The refrigerant outlet 33a of the indoor heat exchanger 21 during the heating operation is connected to the refrigerant inlet / outlet 33 of the first heat exchanger 33 on the side opposite to the refrigerant throttle mechanism 27.
a, and the heat transfer tube 26 immediately before that is upstream of the flow of air. The outlet 34a of the refrigerant of the second heat exchanger 34 during the heating operation is the inlet / outlet 34a of the refrigerant on the refrigerant throttle mechanism 27 side of the second heat exchanger 34. It is on the upstream side.

Further, in the indoor heat exchanger 21, the second heat exchanger 34 is connected to the refrigerant inlet 34b of the second heat exchanger 34.
The refrigerant that has flowed in flows through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are countercurrent, and flows out of the second heat exchanger 34 from the refrigerant outlet 34a. Thereafter, the refrigerant flowing into the first heat exchanger 33 from the refrigerant inlet 33b of the first heat exchanger 33 via the dehumidification control valve 27 in the fully opened state is a heat transfer tube path in which the refrigerant flow and the air flow are parallel. After flowing through the (refrigerant path), the refrigerant flow and the air flow flow through a heat transfer tube path (refrigerant path) in which the refrigerant flows in opposite directions, and flow out of the first heat exchanger 33 from the refrigerant outlet 33a.

Therefore, during the heating operation, the second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger 34 and the first heat exchanger 33 is formed by the heat transfer tube in which the refrigerant flow and the air flow are opposed to each other. In the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are opposed to each other, and the refrigerant flow and the air flow are opposed to each other, the refrigerant temperature sequentially decreases from the superheated gas to the supercooled liquid. In such a condenser, air can be efficiently heated with a constant temperature difference between the refrigerant temperature gradient and the air temperature gradient in the air flow direction. Also, the first
Since the latter half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the heat exchanger 33 is a counterflow, the sufficiently cooled refrigerant is transferred to the first flow path.
It can be discharged from the heat exchanger 33. The first
The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the heat exchanger 33 is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. Heat exchanger 3 having a heat transfer tube path in which air flows in opposite directions
The refrigerant cooled in 4 flows into a gas-liquid two-phase state, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the heating operation.

Further, during the heating operation of the indoor heat exchanger 21, between the rows of the heat transfer tubes 26 in the upstream row of the air flow and the heat transfer pipes 26 in the downstream row of the air flow immediately before the refrigerant outlet 33a. Cut 2 for eliminating heat conduction between 26 rows of heat transfer tubes
Since the 5 a is provided on the plate-like fin 25, during the heating operation, the inside of the heat transfer tube 26 immediately before the refrigerant outlet 33 a during the heating operation of the indoor heat exchanger 21 (immediately before the refrigerant outlet 33 a of the first heat exchanger 33). Is cooled sufficiently by the low-temperature air without being heated by the relatively high-temperature superheat or the gas-liquid two-phase refrigerant in the heat transfer tube 26 on the leeward side of the low-temperature supercooled liquid refrigerant. It becomes a liquid refrigerant. Thereby, the refrigerant cooled more sufficiently than the one in which such a cut 25 a is not provided in the plate-like fin 25 can flow out of the first heat exchanger 33.

Next, during the dehumidification operation, the four-way valve 36 is switched to the same side as the cooling operation, the dehumidification control valve 27 is slightly opened, and the electric expansion valve 16 is fully opened. The compressor 35, the four-way valve 36, the outdoor heat exchanger 37, the electric expansion valve 38 in the fully open state, the first heat exchanger 33 of the indoor heat exchanger 21 (the upper front portion 23 of the indoor heat exchanger 21, the indoor heat exchanger 23, The rear part 24 of the exchanger 21), the dehumidification control valve 27 in the slightly opened state, the second heat exchanger 34 of the indoor heat exchanger 21 (the lower part 22 on the front side of the indoor heat exchanger 21), the four-way valve 36, the compressor 35 And the first heat exchanger 33 of the indoor heat exchanger 21 together with the outdoor heat exchanger 15.
(The upper front part 23 and the rear part 24) are used as a condenser,
The second heat exchanger 34 of the indoor heat exchanger 21 (front lower part 2
2) acts as an evaporator.

When the fan 30 is rotated, the indoor air is drawn into the suction grills 31a, 31a on the front and upper surfaces.
b, and passes through the indoor heat exchanger 21 after being removed by the filter 28. At this time, the front upper part 23 or the rear part 2 of the indoor heat exchanger 21 functioning as a condenser
4 (first heat exchanger 33), the air is heated, and the lower front part 2 of the indoor heat exchanger 21 functioning as an evaporator
2 (second heat exchanger 34) is cooled (dehumidified)
Is done. Thereafter, the air passes through the fan 30 and is mixed, and is blown into the room from the blowout port 32.

At this time, the upper front part 23 and the rear part 24 (first heat exchanger 33) of the indoor heat exchanger 21 functioning as a condenser, and the indoor heat exchanger 2 functioning as an evaporator
1 is thermally separated from the front lower part 22 (second heat exchanger 34), and the front upper part 23 and rear part 24 (first heat exchanger 33) functioning as a condenser, and the evaporator Lower part 22 (second heat exchanger 3)
4) There is no loss due to heat leakage, and the dehumidifying ability does not decrease.

Further, the front upper portion 23 and the rear portion 24
In order to make the (first heat exchanger 33) function as a condenser and make the front lower part 22 (second heat exchanger 34) function as an evaporator, the front lower part 22 (second heat exchanger) that functions as an evaporator The condensed water generated in 34) is not transmitted to the front upper section 23 and the rear section 24 (first heat exchanger 33) functioning as a condenser and re-evaporated.

This air conditioner has a heat exchange part (front upper part 23 and rear part 24) functioning as a condenser and a heat exchange part (front lower part 22) serving as an evaporator in the indoor heat exchanger 21. ) Are not arranged side by side in the air flow direction, so that the size of the indoor heat exchanger 21 in the air flow direction does not increase, and the heat exchange portion functioning as a condenser in the indoor heat exchanger. The air conditioner is smaller (thinner) than the heat exchanger that functions as an evaporator and is arranged side by side in the air flow direction.
can do.

In this embodiment, the refrigerant inlet 33a of the indoor heat exchanger 21 during the dehumidifying operation is the refrigerant inlet / outlet 33a of the first heat exchanger 33 on the side opposite to the refrigerant restricting mechanism 27, and the heat transfer tube immediately after that. Reference numeral 26 denotes an upstream side of the air flow. Further, the refrigerant outlet 34b of the indoor heat exchanger 21 during the dehumidifying operation is the refrigerant inlet / outlet 34b of the second heat exchanger 34 on the side opposite to the refrigerant throttle mechanism 27, and the heat transfer tube 26 immediately before the outlet 34b. Downstream. Further, the refrigerant inlet 34a of the second heat exchanger 34 during the dehumidifying operation is the refrigerant inlet / outlet 34a of the second heat exchanger 34 on the side of the refrigerant throttle mechanism 27, and the heat transfer tube 26 immediately after the refrigerant inlet / outlet 34a serves as a flow passage for the air. It is on the upstream side.

In the indoor heat exchanger 21, the first heat exchanger 33 is connected to the refrigerant inlet 33a of the first heat exchanger 33.
The refrigerant flowing into the heat exchanger flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in opposite directions. The refrigerant flows out of the first heat exchanger 33 from the refrigerant outlet 33b. afterwards,
The refrigerant that has flowed into the second heat exchanger 34 from the refrigerant inlet 34a of the second heat exchanger 34 via the dehumidification control valve 27 in the slightly open state is a heat transfer tube path in which the refrigerant flow and the air flow are parallel. (Refrigerant path) and flows out of the second heat exchanger 34 from the refrigerant outlet 34b.

In the dehumidifying operation, since the heat transfer tubes 26 immediately before the refrigerant outlet 33b of the first heat exchanger 33 are arranged in a row on the upstream side of the air flow, the refrigerant throttle mechanism (the dehumidifying control valve 2) is used.
The refrigerant immediately before flowing into 7) exchanges heat with the air before being heated by the first heat exchanger 33, so that a sufficient supercooled liquid can be obtained. As a result, the refrigerant flowing into the refrigerant throttle mechanism (the dehumidification control valve 27) becomes a liquid refrigerant and is depressurized by stable flow, so that the refrigerant flow noise is reduced. Further, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is reduced, sufficient heating, dehumidification and cooling of air can be performed, and a predetermined refrigeration cycle can be configured with low power consumption. .

During the dehumidifying operation, the first heat exchanger 33
In the heat transfer tube path (refrigerant), the refrigerant flows into the refrigerant throttle mechanism (dehumidification control valve 27) immediately after passing a plurality of heat transfer tubes 26 arranged in a row on the upstream side of the air flow. Since the path is configured, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism (the dehumidification control valve 27) is further improved. Thus, the refrigerant flowing into the refrigerant throttle mechanism easily becomes a liquid refrigerant, and is depressurized by a more stable flow, so that the refrigerant flow noise is further reduced. In addition, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is reduced, sufficient heating, dehumidification and cooling of air can be performed, and a predetermined refrigeration cycle can be configured with less power consumption. Becomes

In the present embodiment, the heat transfer tubes 26 in the upstream row of the air flow and the heat transfer tubes 26 in the downstream row of the air flow immediately before the refrigerant outlet 33b during the dehumidifying operation of the first heat exchanger 33. A gap 25a for eliminating heat conduction between the 26 rows of heat transfer tubes is provided in the plate-like fin 25 between
During the dehumidifying operation, the refrigerant outlet 33b of the first heat exchanger 33
The low-temperature supercooled liquid refrigerant in the heat transfer tube 26 immediately before is sufficiently cooled by the low-temperature air without being heated by the relatively high-temperature superheat or the gas-liquid two-phase refrigerant in the heat transfer tube 26 on the leeward side. Therefore, it becomes a low-temperature supercooled liquid refrigerant. As a result, the refrigerant flowing into the refrigerant throttle mechanism (dehumidification control valve 27) is more likely to be a liquid refrigerant than the one in which such a cut 25a is not provided in the plate-like fin 25, and the pressure is reduced by a more stable flow. The refrigerant flow noise is even smaller than that without 25a. In addition, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is smaller than that having no cut 25a, sufficient heating, dehumidification and cooling of air can be performed, and the air can be cooled more than that without the cut 25a. A predetermined refrigeration cycle can be configured with low power consumption.

Further, in this embodiment, since the refrigerant throttle mechanism is constituted by the dehumidification control valve 27 having the fully open state and the slightly open state, the state in which the flow resistance of the refrigerant is large and the flow resistance of the refrigerant are small. The refrigerant throttle mechanism having the state can be constituted by one dehumidification control valve 27. In addition, since the flow path resistance can be arbitrarily set during the dehumidifying operation, the amount of dehumidified air and the blowing temperature can be finely controlled.

(Embodiment 2) FIG. 3 is a sectional side view of an indoor unit according to Embodiment 2 of the air conditioner of the present invention.

In FIG. 3, a multi-stage bending indoor heat exchanger 41 incorporated in an indoor unit is thermally divided into a lower front portion 42, a front upper portion 43, and a rear portion 44 and bent. In the indoor heat exchanger 41, the heat transfer tubes 26 provided so as to penetrate the plurality of plate-like fins 45 are arranged in two rows in the direction of air flow, and the heat transfer tubes 26 are connected at ends. I have.

Further, the front lower part 42 and the front upper part 4
3 together with the first heat exchanger 53,
The first heat exchanger 53 and the second heat exchanger 5
4 are connected via a refrigerant throttle mechanism 27 having a state where the flow path resistance of the refrigerant is large and a state where the flow path resistance of the refrigerant is small. In this embodiment, as the refrigerant throttle mechanism 27, a dehumidification control valve 27 having a fully opened state and a slightly opened state, and being in a slightly opened state during the dehumidifying operation and having a function of performing a throttling operation is used.

When the once-through fan type fan 30 rotates, the suction grills 31a, 3a on the front and upper surfaces are formed.
Air is introduced from 1b, is exchanged with the refrigerant in the indoor heat exchanger 41 via the filter 28, and then passes through the fan 30 and is blown into the room through the outlet 32.

Reference numeral 29 denotes a rear casing, in which a dew tray 29a for the rear portion 44 (second heat exchanger 54) of the indoor heat exchanger 41 is integrally formed. 32a is an air outlet wind direction plate, 39 is a lower front part 4 of the indoor heat exchanger 41.
2 is a dew tray for the front upper portion 43 (first heat exchanger 53).

The air conditioner of the second embodiment has a fin tube in which a plurality of heat transfer tubes 26, which are inserted at right angles through a plurality of plate-like fins 45 arranged in parallel and through which a refrigerant flows, are arranged in two rows in the direction of air flow. The indoor heat exchanger 41 is thermally divided into a first heat exchanger 53 and a second heat exchanger 54 in a step direction substantially perpendicular to the flow direction of air, and the first heat exchanger 53 and the second heat exchanger The heat exchanger 54 is connected to the refrigerant throttle mechanism 27 having a state in which the flow path resistance of the refrigerant is large and a state in which the flow path resistance of the refrigerant is low. The refrigerant flows from the first heat exchanger 53 to the second heat exchanger 54 during the cooling operation and the dehumidifying operation, and flows from the second heat exchanger 54 during the heating operation. The refrigeration cycle is configured so that the refrigerant flows to the first heat exchanger 53. And, the refrigerant throttle mechanism 27 during the dehumidifying operation
In a state where the flow path resistance of the refrigerant is large, and the first heat exchanger 53
In the air conditioner in which the indoor air can be dehumidified by the second heat exchanger 54 while the indoor air is heated by the air conditioner, the transfer immediately after the refrigerant inlet 53a of the first heat exchanger 53 during the dehumidifying operation is performed. The heat pipe 26 and the heat transfer pipe 26 immediately before the refrigerant outlet 53b are arranged in a row on the upstream side of the air flow, and the heat transfer pipe 26 immediately after the refrigerant inlet 54a of the second heat exchanger 54 during the dehumidifying operation is connected to the air flow. The heat transfer tubes 26 in the upstream row and immediately before the refrigerant outlet 54b are arranged in the downstream row of the air flow.

In the first heat exchanger 53, during the dehumidifying operation, the refrigerant flows from the inlet 53a of the refrigerant during the dehumidifying operation, flows in the same direction as the air flow, and then flows in the direction opposite to the air flow. Refrigerant outlet 53b at the time of dehumidifying operation
The heat transfer tube path is configured to flow out of the heat transfer tube.

More specifically, the first heat exchanger 53 includes:
It has two rows of heat transfer tubes 26 in the direction of air flow, two heat transfer tube paths are configured in parallel, and during the dehumidifying operation, the refrigerant is
At the time of the dehumidifying operation, the refrigerant flows in through the inlet 53a and is divided into two heat transfer tube paths. In each heat transfer tube path, first, a predetermined number (3, 4) continuously, and then five successively through the plurality of heat transfer tubes 26 in the downstream row of the air flow, and then the remaining heat transfer tubes 26 in the upstream row of the air flow. (Two or three) continuously, and are merged and flow out from the outlet 53b of the refrigerant in the dehumidifying operation.

In addition, during the dehumidifying operation of the first heat exchanger 53, the space between the heat transfer tubes 26 in the upstream row of the air flow and the heat transfer tubes 26 in the downstream row of the air flow immediately after the inlet 53a of the refrigerant. In the dehumidifying operation of the first heat exchanger 53, the heat transfer pipes are provided between the heat transfer pipes 26 in the upstream row of the air flow immediately before the refrigerant outlet 53b and the heat transfer pipes 26 in the downstream row of the air flow. Cuts 45a for eliminating heat conduction between the 26 rows are provided in the plate-like fin 45.

The indoor unit accommodating the indoor heat exchanger 41 has a built-in flow-through fan 30, and has suction grills 31a, 31b on the front and upper surfaces of the indoor unit main body. The first heat exchanger 53 constituting
A second heat exchanger, which is located between the front suction grill 31a and the fan 30, exchanges heat with the air passing through the front suction grill 31a and the front side of the upper suction grill 31b, thereby forming the indoor heat exchanger 41. The heat exchanger 54 is located between the suction grill 31b on the upper surface and the fan 30,
The heat exchange is performed with the air that has passed through the back side of the suction grill 31b on the upper surface.

In the dehumidifying operation of the first heat exchanger 53, the heat transfer tubes 26 in the upstream row of the air flow immediately before the refrigerant outlet 53b have a relatively high air flow in the first heat exchanger 53. It is located at the place.

In the heat exchanger unit of the second embodiment, the heat transfer tubes 26 which are inserted at right angles into the plate-like fins 45 arranged in parallel and through which the refrigerant flows are formed in two rows in the air flow direction. A fin tube-shaped first heat exchanger 53 in which the heat transfer tubes 26 adjacent to the two refrigerant inlets / outlets 53a, 53b are both arranged in a row on the upstream side of the air flow; The heat transfer tubes 26 that are inserted at right angles to the fins 45 and through which the refrigerant flows inside are arranged in a plurality of rows in the direction of air flow, and the heat transfer tubes 26 that are close to the one of the two refrigerant outlets 54a and 54b. Are arranged in a row on the upstream side of the air flow, and the heat transfer tubes 26 adjacent to the other refrigerant inlet / outlet 54b are arranged in a row on the downstream side of the air flow.
4 and two refrigerant inlets / outlets 53a of the first heat exchanger 53,
A refrigerant flow path provided in the middle of a connection pipe connecting one of the refrigerant inlets / outlets 53b of the refrigerants 53b and the refrigerant inlets / outlets 54a arranged in a row on the upstream side of the air flow of the second heat exchanger 54. The refrigerant throttle mechanism 27 has a state in which the resistance is high and a state in which the flow path resistance of the refrigerant is low. The first heat exchanger 53 and the second heat exchanger 54 are arranged so that they do not overlap in the direction of air flow. The first heat exchanger 53 and the second heat exchanger 54 are arranged.

When the refrigerant flows from the refrigerant inlet / outlet 53a on the anti-refrigerant throttling mechanism 27 side to the refrigerant inlet / outlet 53b on the refrigerant throttling mechanism 27 side, the first heat exchanger 53
After flowing in from the refrigerant inlet / outlet 53a on the side of the anti-refrigerant throttle mechanism 27 and flowing in the same direction as the air flow, the refrigerant flows in the direction opposite to the air flow and the refrigerant inlet / outlet 53b on the refrigerant throttle mechanism 27 side. A heat transfer tube path is configured to flow out of the tube.

More specifically, the first heat exchanger 53 includes:
It has two rows of heat transfer tubes 26 in the direction of air flow, and two heat transfer tube paths are configured in parallel. Flows, the refrigerant flows in from the refrigerant inlet / outlet 53a on the side of the anti-refrigerant throttle mechanism 27 and is divided into two heat transfer tube paths. In each heat transfer tube path,
First, a plurality of heat transfer tubes 2 in a row on the upstream side of the air flow.
6 continuously passes through a predetermined number (3, 4), and then passes through a plurality of heat transfer tubes 26 in a row on the downstream side of the air flow in succession, and then upstream of the air flow. (2, 3) continuously pass through the remaining heat transfer pipes 26, merge, and flow out of the refrigerant inlet / outlet 53b on the refrigerant throttle mechanism 27 side.

The first heat exchanger 53 has two rows of heat transfer tubes 26 in the direction of air flow, two heat transfer tube paths are configured in parallel, and the refrigerant inlet / outlet port 5 on the refrigerant throttle mechanism 27 side.
3b is located at a lower stage than the heat transfer tube 26 adjacent to the inlet / outlet 53a of the refrigerant on the side of the anti-refrigerant throttle mechanism 27, and one of the two heat transfer tube paths configured in parallel has the anti-refrigerant It is formed from the refrigerant inlet / outlet 53a on the throttle mechanism 27 side toward the upper end of the heat exchanger, and further moves to a row downstream of the air flow near the upper end of the heat exchanger and near the center of the heat exchanger toward the lower end of the heat exchanger. To the row on the upstream side of the air flow near the center of the heat exchanger, and toward the lower end of the heat exchanger, the refrigerant inlet / outlet 53b on the refrigerant throttle mechanism 27 side.
The other of the two heat transfer tube paths formed in parallel with each other is formed from the refrigerant inlet / outlet 53a on the side of the anti-refrigerant throttle mechanism 27 toward the heat exchanger lower end and near the center of the heat exchanger, and further heat exchange. In the vicinity of the center of the heat exchanger, it moves to the row on the downstream side of the air flow and is formed toward the lower end of the heat exchanger. The structure is formed up to the refrigerant inlet / outlet 53b on the refrigerant throttle mechanism 27 side.

The heat transfer tubes 26 in the row on the upstream side of the air flow adjacent to the refrigerant inlet / outlet 53a on the side opposite to the refrigerant throttle mechanism 27 of the first heat exchanger 53 and the heat transfer tubes 26 in the row on the downstream side of the air flow. Between the rows with the heat transfer tubes 26, and the rows of the heat transfer tubes 26 on the upstream side of the flow of air adjacent to the refrigerant inlet / outlet 53b on the refrigerant throttle mechanism 27 side of the first heat exchanger 53 and the downstream side of the flow of air. A cut 45a for eliminating heat conduction between the rows of the heat transfer tubes 26 is provided in the plate-like fin 45 between the rows of the heat transfer tubes 26.

The entire refrigeration cycle of the air conditioner of the second embodiment is the same as that of the entire refrigeration cycle of the air conditioner of the first embodiment shown in FIG.
A heat exchanger 53 is provided, and instead of the second heat exchanger 34, a second
This is equivalent to the one provided with the heat exchanger 54.

First, at the time of the cooling operation, the four-way valve 36 is switched to the cooling side, the dehumidification control valve 27 is opened, and the electric expansion valve 38 is appropriately throttled, so that the compressor 35, the four-way valve 36, the outdoor heat exchanger 37 The expansion valve 38, the first heat exchanger 53 of the indoor heat exchanger 41 (the upper part 4 of the front surface of the indoor heat exchanger 41)
3, the lower front part 42 of the indoor heat exchanger 41), the dehumidification control valve 27 in the fully open state, and the second heat exchanger 5 of the indoor heat exchanger 41.
4 (the rear part 44 of the indoor heat exchanger 41), the four-way valve 36,
A refrigerant path is formed in the order of the compressor 35 and the outdoor heat exchanger 37
To act as a condenser and the entire indoor heat exchanger 41 as an evaporator.

When the fan 30 is rotated, the indoor air is drawn into the suction grills 31a and 31a on the front and upper surfaces.
b, and after passing through the indoor heat exchanger 41 after being removed by the filter 28. Then, the air is cooled by the indoor heat exchanger 41, passes through the fan 30, and is blown into the room from the blowout port 32.

At this time, the indoor heat exchanger 41 during the cooling operation
Is the refrigerant inlet / outlet 53a of the first heat exchanger 53 on the side opposite to the refrigerant throttle mechanism 27, and the heat transfer tube 26 immediately after the inlet 53a is on the upstream side of the flow of air. The refrigerant outlet 54b of the indoor heat exchanger 41 during the cooling operation is connected to the refrigerant inlet / outlet 54 of the second heat exchanger 54 on the side opposite to the refrigerant throttle mechanism 27.
b, and the heat transfer tube 26 immediately before that is downstream of the flow of air. The refrigerant inlet 54a of the second heat exchanger 54 during the cooling operation is connected to the refrigerant throttle mechanism 27 of the second heat exchanger 54.
Side of the refrigerant inlet / outlet 54a, and the heat transfer tube 26
Is upstream of the air flow.

At this time, in the indoor heat exchanger 41, the refrigerant is supplied to the refrigerant inlet 5 of the first heat exchanger 53 during the cooling operation.
3a (the refrigerant inlet / outlet 53a on the side of the anti-refrigerant throttle mechanism 27) flows into the first heat exchanger 53 and is divided into two heat transfer tube paths. In each heat transfer tube path, first, the upstream side of the air flow A predetermined number (3, 4) of the plurality of heat transfer tubes 26 are continuously passed through a plurality of rows, and then a plurality of the heat transfer tubes 26 are continuously passed through a plurality of rows of the downstream rows of the air flow. After that, the remaining heat transfer tubes 26 in the row on the upstream side of the air flow continuously pass (two or three tubes) and merge to form a refrigerant outlet 53b of the first heat exchanger 53 during the cooling operation. (Refrigerant throttle mechanism 2
The refrigerant flows out of the first heat exchanger 53 from the inlet / outlet 53b) of the refrigerant on the seventh side. That is, the refrigerant that has flowed into the first heat exchanger 53 flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then flows through the heat transfer tube path in which the refrigerant flow and the air flow flow in opposite directions. (Refrigerant path) and flows out of the first heat exchanger 53. After that, the refrigerant flowed into the second heat exchanger 54 from the refrigerant inlet 54a of the second heat exchanger 54 (the refrigerant inlet / outlet 54a on the refrigerant throttle mechanism 27 side) during the cooling operation via the dehumidification control valve 27 in the fully opened state. The refrigerant is divided into two heat transfer pipe paths, and in each heat transfer pipe path, first, two consecutive heat transfer pipes 26 in a row on the upstream side of the air flow continuously pass through the heat transfer pipes. Two of the heat transfer tubes 26 in a row on the downstream side of the flow continuously pass through the two heat transfer tubes 26 and merge, and the refrigerant outlet 54b of the second heat exchanger 54 during the cooling operation (on the side of the anti-refrigerant throttle mechanism 27 side). The second heat exchanger 54 is connected to the refrigerant port 54b).
Spills out. That is, the refrigerant that has flowed into the second heat exchanger 54 flows through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and flows out of the second heat exchanger 54.

Therefore, during the cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger 53 and the second heat exchanger 54 form a heat transfer tube in which the refrigerant flow and the air flow are parallel. In the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow become parallel flows as a whole, and the refrigerant flow and the air flow become parallel flows, in the evaporator where the refrigerant temperature sequentially decreases due to pressure loss In addition, the air can be efficiently cooled with a constant temperature difference between the refrigerant temperature gradient and the air temperature gradient with respect to the air flow direction. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger 53 is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are opposed to each other. (1) The refrigerant which is heated in the first half of the refrigerant flow of the heat exchanger 53 and is in a gas-liquid two-phase state flows, and there is almost no change in the temperature of the refrigerant, and the refrigerant flow and the air flow are countercurrent to each other. There is no end.
Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

Further, since the two heat transfer tube paths are formed in parallel, the pressure loss during the cooling operation is reduced,
Performance degradation can be prevented.

Next, during the heating operation, the four-way valve 36 is switched to the heating side, the dehumidification control valve 27 is opened, and the electric expansion valve 38 is appropriately throttled, so that the compressor 35, the four-way valve 36, and the indoor heat exchanger 41 are controlled. The second heat exchanger 54 (the rear portion 44 of the indoor heat exchanger 41), the dehumidification control valve 27 in the fully opened state, the first heat exchanger 53 of the indoor heat exchanger 41 (the lower front portion 42 of the indoor heat exchanger 41, Upper part 4 at the front of indoor heat exchanger 41
3), electric expansion valve 38, outdoor heat exchanger 37, four-way valve 3
6, a refrigerant path is formed in the order of the compressor 35, the outdoor heat exchanger 37 acts as an evaporator, and the entire indoor heat exchanger 41 acts as a condenser.

When the fan 30 is rotated, the indoor air is drawn into the suction grills 31a and 31a on the front and upper surfaces.
b, and after passing through the indoor heat exchanger 41 after being removed by the filter 28. Then, the air is heated by the indoor heat exchanger 41, passes through the fan 30, and is blown into the room through the blowout port 32.

At this time, the indoor heat exchanger 41 during the heating operation
The refrigerant inlet 54b is the refrigerant inlet / outlet 54b of the second heat exchanger 54 on the side opposite to the refrigerant throttle mechanism 27, and the heat transfer tube 26 immediately behind the refrigerant inlet 54b is on the downstream side of the flow of air. Further, the refrigerant outlet 53a of the indoor heat exchanger 41 during the heating operation is connected to the refrigerant inlet / outlet 53 of the first heat exchanger 53 on the side opposite to the refrigerant throttle mechanism 27.
a, and the heat transfer tube 26 immediately before that is upstream of the flow of air. The outlet 54a of the refrigerant of the second heat exchanger 54 during the heating operation is the inlet / outlet 54a of the refrigerant on the side of the refrigerant throttle mechanism 27 of the second heat exchanger 54, and the heat transfer tube 26 immediately before the outlet 54a It is on the upstream side.

At this time, in the indoor heat exchanger 41, the refrigerant flows into the refrigerant inlet 5 of the second heat exchanger 54 during the heating operation.
4b (the refrigerant inlet / outlet 54b on the side of the anti-refrigerant throttle mechanism 27) flows into the second heat exchanger 54 and is divided into two heat transfer tube paths. In each heat transfer tube path, first, the downstream side of the air flow Two successively pass through the plurality of heat transfer tubes 26 in the row, and then successively pass through the plurality of heat transfer tubes 26 in the row on the upstream side of the air flow, and merge. During the heating operation, the second heat exchanger 5 is connected to the refrigerant outlet 54a of the second heat exchanger 54 (the refrigerant inlet / outlet 54a on the refrigerant throttle mechanism 27 side).
4 Outflow. That is, the refrigerant that has flowed into the second heat exchanger 54 flows out of the second heat exchanger 54 through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in opposite directions. Thereafter, the refrigerant flowed into the first heat exchanger 53 from the refrigerant inlet 53b (the refrigerant inlet / outlet 53b of the refrigerant throttle mechanism 27 side) of the first heat exchanger 53 during the heating operation via the fully opened dehumidification control valve 27. First, the refrigerant continuously (two or three) continuously passes through the plurality of heat transfer tubes 26 in the row on the upstream side of the air flow, and then passes through the plurality of heat transfer tubes in the row on the downstream side of the air flow. After passing five heat pipes 26 continuously, the remaining heat transfer pipes 26 in the row on the upstream side of the air flow (3, 4) are continuously passed and merged, and the first heat transfer pipes during the heating operation are combined. The refrigerant outlet 53a of the heat exchanger 53 (the refrigerant inlet / outlet 5 on the side opposite to the refrigerant throttle mechanism 27).
3a) flows out of the first heat exchanger 53. That is,
The refrigerant flowing into the first heat exchanger 53 flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then flows into a heat transfer tube path (refrigerant) in which the refrigerant flow and the air flow flow in opposite directions. And flows out of the first heat exchanger 53.

Therefore, during the heating operation, the second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger 54 and the first heat exchanger 53 is formed by the heat transfer tube in which the refrigerant flow and the air flow are opposed to each other. In the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are opposed to each other, and the refrigerant flow and the air flow are opposed to each other, the refrigerant temperature sequentially decreases from the superheated gas to the supercooled liquid. In such a condenser, air can be efficiently heated with a constant temperature difference between the refrigerant temperature gradient and the air temperature gradient in the air flow direction. Also, the first
Since the latter half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the heat exchanger 53 is a counterflow, the sufficiently cooled refrigerant is transferred to the first flow path.
It can be discharged from the heat exchanger 53. The first
The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the heat exchanger 53 becomes a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. Heat exchanger 5 having a heat transfer tube path in which air flows in opposite directions
The refrigerant cooled in 4 flows into a gas-liquid two-phase state, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the heating operation.

Further, during the heating operation of the indoor heat exchanger 41, the space between the heat transfer pipes 26 in the upstream row of the air flow and the heat transfer pipes 26 in the downstream row of the air flow immediately before the refrigerant outlet 53a. Cut 4 to eliminate heat conduction between 26 rows of heat transfer tubes
Since 5 a is provided on the plate-like fin 45, during the heating operation, the heat transfer tube 26 immediately before the refrigerant outlet 53 a during the heating operation of the indoor heat exchanger 41 (immediately before the refrigerant outlet 53 a of the first heat exchanger 53). Is cooled sufficiently by the low-temperature air without being heated by the relatively high-temperature superheat or the gas-liquid two-phase refrigerant in the heat transfer tube 26 on the leeward side of the low-temperature supercooled liquid refrigerant. It becomes a liquid refrigerant. Thereby, the refrigerant that is more sufficiently cooled than that in which the cut 45 a is not provided in the plate-like fin 45 can flow out of the first heat exchanger 53.

Next, at the time of the dehumidifying operation, the four-way valve 36 is switched to the same side as the cooling operation, the dehumidifying control valve 27 is slightly opened, and the electric expansion valve 16 is fully opened.
5, the four-way valve 36, the outdoor heat exchanger 37, the fully-open electric expansion valve 38, the first heat exchanger 53 of the indoor heat exchanger 41 (the upper front portion 43 of the indoor heat exchanger 41, The refrigerant path in the order of the lower front part 42), the dehumidification control valve 27 in the slightly opened state, the second heat exchanger 54 of the indoor heat exchanger 41 (the rear part 44 of the indoor heat exchanger 41), the four-way valve 36, and the compressor 35. And the indoor heat exchanger 4 together with the outdoor heat exchanger 15
The first heat exchanger 53 (the upper front part 43 and the lower front part 42) functions as a condenser, and the second heat exchanger 54 (the rear part 44) of the indoor heat exchanger 41 functions as an evaporator. .

When the fan 30 is rotated, the indoor air is drawn into the suction grills 31a, 31a on the front and upper surfaces.
b, and after passing through the indoor heat exchanger 41 after being removed by the filter 28. At this time, the air that has passed through the front upper section 43 or the front lower section 42 (first heat exchanger 53) of the indoor heat exchanger 41 functioning as a condenser is heated, and the air of the indoor heat exchanger 41 functioning as an evaporator is heated. The air that has passed through the rear portion 44 (second heat exchanger 54) is cooled (dehumidified). Thereafter, the air passes through the fan 30 and is mixed, and is blown into the room from the blowout port 32.

At this time, the upper front portion 43 and the lower front portion 42 (first heat exchanger 53) of the indoor heat exchanger 41 functioning as a condenser, and the rear portion 44 of the indoor heat exchanger 41 functioning as an evaporator. (Second heat exchanger 54) is thermally separated from upper front part 43 and front lower part 42 (first heat exchanger 53) that function as condensers.
The back part 44 (second heat exchanger 5) functioning as an evaporator
4) There is no loss due to heat leakage, and the dehumidifying ability does not decrease.

The upper front portion 43 and the lower front portion 42 (first heat exchanger 53) function as a condenser, and the rear portion 44 (second heat exchanger 54) functions as an evaporator. The condensed water generated in the back part 44 (second heat exchanger 54) functioning as a propeller is transmitted to the front upper part 43 and the front lower part 42 (first heat exchanger 53) functioning as a condenser and re-evaporated. There is no end.

This air conditioner has a heat exchange portion (front upper portion 43 and front lower portion 42) functioning as a condenser and a heat exchange portion (rear portion 44) functioning as an evaporator in the indoor heat exchanger 41. ) Are not arranged side by side in the air flow direction, so that the size of the indoor heat exchanger 41 in the air flow direction does not increase, and the heat exchange portion functioning as a condenser in the indoor heat exchanger. The air conditioner is smaller (thinner) than the heat exchanger that functions as an evaporator and is arranged side by side in the direction of air flow.
can do.

In the present embodiment, the refrigerant inlet 53a of the indoor heat exchanger 41 during the dehumidifying operation is the refrigerant inlet / outlet 53a of the first heat exchanger 53 on the side opposite to the refrigerant throttle mechanism 27, and the heat transfer tube immediately after that. Reference numeral 26 denotes an upstream side of the air flow. Further, the refrigerant outlet 54b of the indoor heat exchanger 41 during the dehumidifying operation is the refrigerant inlet / outlet 54b of the second heat exchanger 44 on the side opposite to the refrigerant throttle mechanism 27. Downstream. Further, the refrigerant inlet 54a of the second heat exchanger 54 during the dehumidifying operation is the refrigerant inlet / outlet 54a of the second heat exchanger 54 on the side of the refrigerant throttle mechanism 27, and the heat transfer tube 26 immediately behind the refrigerant inlet / outlet 54a serves as an air flow passage. It is on the upstream side.

At this time, in the indoor heat exchanger 41, the refrigerant is supplied to the refrigerant inlet 5 of the first heat exchanger 53 during the cooling operation.
3a (the refrigerant inlet / outlet 53a on the side of the anti-refrigerant throttle mechanism 27) flows into the first heat exchanger 53 and is divided into two heat transfer tube paths. In each heat transfer tube path, first, the upstream side of the air flow A predetermined number (3, 4) of the plurality of heat transfer tubes 26 are continuously passed through a plurality of rows, and then a plurality of the heat transfer tubes 26 are continuously passed through a plurality of rows of the downstream rows of the air flow. After that, the remaining heat transfer tubes 26 in the row on the upstream side of the air flow continuously pass (two or three tubes) and merge to form a refrigerant outlet 53b of the first heat exchanger 53 during the cooling operation. (Refrigerant throttle mechanism 2
The refrigerant flows out of the first heat exchanger 53 from the inlet / outlet 53b) of the refrigerant on the seventh side. That is, the refrigerant that has flowed into the first heat exchanger 53 flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then flows through the heat transfer tube path in which the refrigerant flow and the air flow flow in opposite directions. (Refrigerant path) and flows out of the first heat exchanger 53. Thereafter, the refrigerant flows into the second heat exchanger 54 from the refrigerant inlet 54a (the refrigerant inlet / outlet 54a of the refrigerant throttle mechanism 27) of the second heat exchanger 54 during the cooling operation via the slightly opened dehumidification control valve 27. The cooled refrigerant is divided into two heat transfer tube paths. In each of the heat transfer tube paths, first, two consecutive heat transfer tubes 26 in a row on the upstream side of the air flow continuously pass through the heat transfer tube paths. After passing through two heat transfer tubes 26 in a row on the downstream side of the flow of heat, the two heat transfer tubes 26 merge and merge, and the refrigerant outlet 54b of the second heat exchanger 54 during cooling operation (the side opposite to the refrigerant throttle mechanism 27) From the inlet / outlet 54b) of the refrigerant to the second heat exchanger 54
Spills out. That is, the refrigerant that has flowed into the second heat exchanger 54 flows through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and flows out of the second heat exchanger 54.

In the dehumidifying operation, since the heat transfer tubes 26 immediately before the refrigerant outlet 53b of the first heat exchanger 53 are arranged in a row on the upstream side of the air flow, the refrigerant throttle mechanism (the dehumidifying control valve 2) is used.
The refrigerant immediately before flowing into 7) exchanges heat with the air before being heated in the first heat exchanger 53, so that a sufficient supercooled liquid can be obtained. As a result, the refrigerant flowing into the refrigerant throttle mechanism (the dehumidification control valve 27) becomes a liquid refrigerant and is depressurized by stable flow, so that the refrigerant flow noise is reduced. Further, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is reduced, sufficient heating, dehumidification and cooling of air can be performed, and a predetermined refrigeration cycle can be configured with low power consumption. .

During the dehumidifying operation, the first heat exchanger 53
In the heat transfer tube path (refrigerant), the refrigerant flows into the refrigerant throttle mechanism (dehumidification control valve 27) immediately after passing a plurality of heat transfer tubes 26 arranged in a row on the upstream side of the air flow. Since the path is configured, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism (the dehumidification control valve 27) is further improved. Thus, the refrigerant flowing into the refrigerant throttle mechanism easily becomes a liquid refrigerant, and is depressurized by a more stable flow, so that the refrigerant flow noise is further reduced. In addition, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is reduced, sufficient heating, dehumidification and cooling of air can be performed, and a predetermined refrigeration cycle can be configured with less power consumption. Becomes

In this embodiment, the heat transfer tubes 26 in the upstream row of the air flow and the heat transfer tubes 26 in the downstream row of the air flow immediately before the refrigerant outlet 53b during the dehumidifying operation of the first heat exchanger 53 are provided. A gap 45a for eliminating heat conduction between the 26 rows of the heat transfer tubes is provided in the plate-like fin 45 between the rows.
During the dehumidifying operation, the refrigerant outlet 53b of the first heat exchanger 53
The low-temperature supercooled liquid refrigerant in the heat transfer tube 26 immediately before is sufficiently cooled by the low-temperature air without being heated by the relatively high-temperature superheat or the gas-liquid two-phase refrigerant in the heat transfer tube 26 on the leeward side. Therefore, it becomes a low-temperature supercooled liquid refrigerant. As a result, the refrigerant flowing into the refrigerant throttle mechanism (dehumidification control valve 27) is more likely to be a liquid refrigerant than the one in which such a cut 45a is not provided in the plate-like fin 45, and the pressure is reduced by a more stable flow. The refrigerant flow noise is even smaller than that without 45a. In addition, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is smaller than that having no cut 45a, sufficient heating, dehumidification and cooling of air can be performed, and the air can be cooled more than that without the cut 45a. A predetermined refrigeration cycle can be configured with low power consumption.

In the present embodiment, the upper front part 43 and the lower front part 42 of the indoor heat exchanger 41 are used as the first heat exchanger 53, function as a condenser during the dehumidifying operation, and the rear part 44 of the indoor heat exchanger 41 is used. Is used as a second heat exchanger 54 and functions as an evaporator during the dehumidifying operation. Therefore, the first heat exchanger 53 can be made larger than the second heat exchanger 54, and the wind speed of the airflow passing through the first heat exchanger 53 is Since the speed of the air flow passing through the second heat exchanger 54 is higher than the wind speed, the heating performance in the first heat exchanger 53 is good during the dehumidifying operation, and the refrigerant is liable to become a supercooled liquid. In addition, since the velocity of the airflow passing through the second heat exchanger 54 is low, the dehumidifying efficiency of the air passing through the second heat exchanger 54 is good.

In this embodiment, the first heat exchanger 5
3 has two rows of heat transfer tubes 26 in the air flow direction, two heat transfer tube paths are configured in parallel, and a refrigerant throttle mechanism 27 is provided.
Transfer tube 26 adjacent to the inlet / outlet 53b of the refrigerant on the side is located at a lower stage than the heat transfer tube 26 adjacent to the inlet / outlet 53a of the refrigerant on the side of the anti-refrigerant throttle mechanism 27, and the two heat transfer tube paths configured in parallel One is formed from the inlet / outlet 53a of the refrigerant on the side of the anti-refrigerant throttle mechanism 27 toward the upper end of the heat exchanger, and further moves to a row on the downstream side of the air flow near the upper end of the heat exchanger toward the lower end of the heat exchanger. Formed near the center of the heat exchanger,
Further, the flow shifts to a row on the upstream side of the air flow near the center of the heat exchanger, and is formed toward the lower end of the heat exchanger to the refrigerant inlet / outlet 53b on the side of the refrigerant throttle mechanism 27, and is configured in a parallel path.
The other of the two heat transfer tube paths is formed from the refrigerant inlet / outlet 53a on the side of the anti-refrigerant throttle mechanism 27 toward the heat exchanger lower end to near the center of the heat exchanger, and further near the heat exchanger center to the downstream side of the air flow. To a row that is formed toward the lower end of the heat exchanger, and further to a row that is on the upstream side of the flow of air near the lower end of the heat exchanger, and reaches the upper end of the heat exchanger to the refrigerant inlet / outlet 53b on the refrigerant throttle mechanism 27 side. It is configured to be formed.

The suction grills 31a and 31b are provided on the front and upper surfaces of the main body, and the outlet 32 is provided at the lower part of the front surface. The first heat exchanger 53 is disposed between the first heat exchanger 53 and the fan 30 to heat air passing through the front grille 31a and the front grille 31b on the upper side and the refrigerant in the first heat exchanger 53. Replace the suction grill 31b and fan 3 on the top.
The second heat exchanger 54 is arranged between the first heat exchanger 0 and the refrigerant in the second heat exchanger 54 to exchange heat with the air that has passed through the upper front portion of the suction grille 31b on the far side.

For this reason, the heat transfer tubes 26 in the vicinity of the refrigerant inlet / outlet 53b of the first heat exchanger 53 on the side of the refrigerant throttle mechanism 27,
That is, the heat transfer tube 26 immediately before the refrigerant outlet 53b during the dehumidifying operation of the first heat exchanger 53 is located on the upstream side of the air flow in the first heat exchanger 53 where the air flow is relatively fast. Therefore, during the dehumidifying operation, the cooling efficiency of the refrigerant passing through the heat transfer tube 26 immediately before the refrigerant outlet 53b of the first heat exchanger 53 is improved, and the sufficiently cooled low-temperature supercooled liquid refrigerant is cooled by the refrigerant throttle mechanism. 27.

At this time, the direction of the air flow passing through the first heat exchanger 53 is changed from the row on the upstream side of the air flow of the first heat exchanger 53 to the row on the downstream side of the air flow. There is a stepwise component of the first heat exchanger 53 going from the upper part to the lower part of the first heat exchanger 53 in addition to the row direction component of the first heat exchanger 53 going. Viewed from a perspective, a heat transfer tube path through which the refrigerant flows from the upper portion to the lower portion of the first heat exchanger 53 is provided. Become a route. Therefore, in the first heat exchanger 53, the ratio of the heat transfer tube path in which the refrigerant flow and the air flow become parallel flow during the cooling operation and the refrigerant flow and the air flow become counter flow during the heating operation increases, and the first heat exchanger 53 The heat exchange performance is improved.

Further, in this embodiment, the refrigerant throttle mechanism is constituted by the dehumidification control valve 27 having the fully opened state and the slightly opened state. The refrigerant throttle mechanism having the state can be constituted by one dehumidification control valve 27. In addition, since the flow path resistance can be arbitrarily set during the dehumidifying operation, the amount of dehumidified air and the blowing temperature can be finely controlled.

(Embodiment 3) FIG. 4 is a side sectional view of an indoor unit according to Embodiment 3 of the air conditioner according to the present invention.

[0200] In Fig. 4, an indoor heat exchanger 61 incorporated in an indoor unit includes a main first heat exchanger 62 which is bent in a dogleg shape and disposed on the front surface, and a front surface of the main first heat exchanger 62. It is thermally divided into an auxiliary first heat exchanger 63 disposed on the upper side and a rear heat exchanger 64 disposed on the rear side and serving as a second heat exchanger 74. The main first heat exchanger 62 and the auxiliary first heat exchanger 63 constitute a first heat exchanger 73.

The indoor heat exchanger 61 is provided with a heat transfer tube 26 provided to penetrate a plurality of plate-like fins 65.
The auxiliary first heat exchanger 63 has one row in the air flow direction, and the main first heat exchanger 62 and the second heat exchanger 74 have two rows in the air flow direction. Connected at the ends.

The first heat exchanger 73 and the second heat exchanger 7
4 are connected via a refrigerant throttle mechanism 27 having a state where the flow path resistance of the refrigerant is large and a state where the flow path resistance of the refrigerant is small. In this embodiment, as the refrigerant throttle mechanism 27, a dehumidification control valve 27 having a fully opened state and a slightly opened state, and being in a slightly opened state during the dehumidifying operation and having a function of performing a throttling operation is used.

The rotation of the once-through fan type fan 30 causes the suction grills 31a, 3a on the front and top surfaces.
Air is introduced from 1b, is exchanged with the refrigerant in the indoor heat exchanger 61 via the filter 28, and then passes through the fan 30 and is blown into the room from the outlet 32.

Reference numeral 29 denotes a rear casing, which is a rear heat exchanger 64 of the indoor heat exchanger 61 (second heat exchanger 74).
Are integrally formed. 32a
Is an outlet wind direction plate, and 39 is a main first heat exchanger 62 and an auxiliary first heat exchanger 63 of the indoor heat exchanger 61 (first heat exchanger 7).
It is a dew saucer for 3).

In the air conditioner of the third embodiment, the heat transfer tubes 26, which are inserted at right angles through the plate-like fins 65 arranged in parallel and through which the refrigerant flows, are arranged in two rows (partly three rows) in the air flow direction.
The fin tube type indoor heat exchanger 61 constructed as described above is thermally transferred to the first heat exchanger 7 in a step direction substantially perpendicular to the air flow direction.
3 and a second heat exchanger 74, and the first heat exchanger 73 and the second heat exchanger 74 are refrigerant throttles having a state in which the flow path resistance of the refrigerant is large and a state in which the flow path resistance of the refrigerant is small. Mechanism 27 (dehumidification control valve 2 having a fully opened state and a slightly opened state, which is slightly opened during the dehumidifying operation and has a function of performing a throttling operation.
7) during cooling operation and dehumidifying operation.
The refrigeration cycle is configured such that the refrigerant flows from the heat exchanger 73 to the second heat exchanger 74, and the refrigerant flows from the second heat exchanger 74 to the first heat exchanger 73 during the heating operation, and the refrigerant throttle mechanism during the dehumidifying operation. In the air conditioner in which the indoor air is dehumidified by the second heat exchanger 74 while the indoor air is heated by the first heat exchanger 73 while the flow path resistance of the refrigerant is set to be large, The heat transfer tubes 26 immediately before the refrigerant inlet 73a and the heat transfer tubes 26 immediately before the refrigerant outlet 73b of the first heat exchanger 73 in the dehumidifying operation are arranged in a row on the upstream side of the air flow, and the second heat The heat transfer tubes 26 immediately after the refrigerant inlet 74a of the exchanger 74 are arranged in a row on the upstream side of the air flow, and the heat transfer tubes 26 immediately before the refrigerant outlet 74b are arranged in a row on the downstream side of the air flow.

In the first heat exchanger 73, during the dehumidifying operation, the refrigerant flows through the refrigerant inlet 73a during the dehumidifying operation, flows in the same direction as the air flow, and then faces the air flow. 73b of refrigerant at the time of the dehumidifying operation
The heat transfer tube path is configured to flow out of the heat transfer tube.

More specifically, the first heat exchanger 73 includes:
A main first heat exchanger 62 having two rows of heat transfer tubes 26 in the air flow direction and two heat transfer tube paths arranged in parallel, and a main first heat exchanger 62 having one row of heat transfer tubes 26 in the air flow direction. An auxiliary first heat exchanger 63 having a shorter length in a step direction substantially perpendicular to the direction of air flow than the heat exchanger 62. In the dehumidifying operation, the refrigerant flows from the inlet 73a of the refrigerant in the dehumidifying operation to the auxiliary first heat exchanger 63. After flowing into the first heat exchanger 63 and continuously passing through a plurality of (four) heat transfer tubes 26 of the auxiliary first heat exchanger 63, the auxiliary first
It flows out of the heat exchanger 63, is divided into two heat transfer tube paths, and flows into the main first heat exchanger 62. In each heat transfer tube path, first, a plurality of transfer lines in an upstream row of the air flow. A predetermined number (two or three) of the heat pipes 26 are continuously passed through the heat pipes 26, and then a plurality of the heat transfer pipes 26 in the row on the downstream side of the air flow (4, 4).
5) After passing continuously, the remaining three heat transfer tubes in the row on the upstream side of the air flow pass continuously (3 tubes), merge, and flow out of the refrigerant outlet 73b during the dehumidifying operation. The auxiliary first heat exchanger 63 is configured so that the main first heat exchanger 62
Is arranged so as not to be located on the upstream side of the air flow of the first heat exchanger 62 and on the upstream side of the air flow of the heat transfer tube 26 immediately before the refrigerant outlet 73b during the cooling operation and the dehumidifying operation of the main first heat exchanger 62. I have.

Further, during the dehumidifying operation of the first heat exchanger 73 (main first heat exchanger 62), the heat transfer tubes 26 in the upstream row of the air flow and the downstream row of the air flow immediately before the outlet 73b of the refrigerant. A cut 65 a for eliminating heat conduction between the rows of the heat transfer tubes 26 is provided in the plate-like fin 65 between the rows of the heat transfer tubes 26.

In addition, during the dehumidifying operation of the first heat exchanger 73, the space between the heat transfer tubes 26 in the upstream row of the air flow and the heat transfer tubes 26 in the downstream row of the air flow immediately after the inlet 73a of the refrigerant. Heat conduction between the 26 rows of heat transfer tubes (between the main first heat exchanger 62 and the auxiliary first heat exchanger 63) between the main first heat exchanger 62 and the auxiliary first heat exchanger 63). The plate fins 65 are provided with cuts 65b for eliminating the fins, and the plate fins 65 are provided for the main first heat exchanger 62 and the auxiliary first heat exchanger 63.
Divided.

[0210] The indoor unit accommodating the indoor heat exchanger 61 incorporates the once-through fan 30, and has suction grills 31a and 31b on the front and upper surfaces of the indoor unit main body. The first heat exchanger 73 constituting
A second heat exchanger, which is located between the front suction grill 31a and the fan 30, exchanges heat with air passing through the front suction grill 31a and the front side of the upper suction grill 31b and constitutes the indoor heat exchanger 61. The heat exchanger 74 is located between the suction grill 31b on the upper surface and the fan 30,
The heat exchange is performed with the air that has passed through the back side of the suction grill 31b on the upper surface.

Further, during the dehumidifying operation of the first heat exchanger 73, the heat transfer tubes 26 in the upstream row of the air flow immediately before the outlet 73b of the refrigerant have a relatively high air flow in the first heat exchanger 73. It is located at the place.

In the heat exchanger unit according to the third embodiment, the heat transfer tubes 26 which are inserted at right angles through the plate-like fins 65 arranged in parallel and through which the refrigerant flows are arranged in two rows (partly) in the air flow direction. 3), and two refrigerant inlets / outlets 73a,
The heat transfer tubes 26 adjacent to 73b are inserted through the fin tube-shaped first heat exchangers 73 arranged in a row on the upstream side of the air flow, and the plate-like fins 65 arranged in parallel at right angles. The heat transfer tubes 26 through which the refrigerant flows are formed in a plurality of rows in the air flow direction, and the two refrigerant inlets / outlets 74.
a, 74b, the heat transfer tubes 26 adjacent to the inlet / outlet 74a of the refrigerant are arranged in a row on the upstream side of the air flow, and the heat transfer tubes 26 adjacent to the inlet / outlet 74b of the other refrigerant are connected to the downstream side of the air flow. And a second heat exchanger 74 of a fin tube type arranged in a row, and one of the two refrigerant outlets 73a, 73b of the first heat exchanger 73.
A state in which the flow path resistance of the refrigerant provided in the middle of the connection pipe connecting the refrigerant to the inlet / outlet 74a of the refrigerant arranged in the row on the upstream side of the air flow of the second heat exchanger 74 is large. The first heat exchanger 73 and the second heat exchanger 74 are configured so as not to overlap in the direction of air flow so that the first heat exchanger 73 and the second heat exchanger 74 do not overlap in the direction of air flow.
A heat exchanger 74 is provided.

When the refrigerant flows from the refrigerant inlet / outlet 73a on the anti-refrigerant throttle mechanism 27 side to the refrigerant inlet / outlet 73b on the refrigerant throttle mechanism 27 side, the first heat exchanger 73
After flowing in from the refrigerant inlet / outlet 73a on the side of the anti-refrigerant throttle mechanism 27 and flowing in the same direction as the air flow, the refrigerant flows in the direction opposite to the air flow and the refrigerant inlet / outlet 73b on the refrigerant throttle mechanism 27 side. The heat transfer tube path is configured to flow out of the heat transfer tube.

More specifically, the first heat exchanger 73 includes:
A main first heat exchanger 62 having two rows of heat transfer tubes 26 in the air flow direction and two heat transfer tube paths arranged in parallel, and a main first heat exchanger 62 having one row of heat transfer tubes 26 in the air flow direction. An auxiliary first heat exchanger 63 having a shorter length in a step direction substantially perpendicular to the air flow direction than the heat exchanger 62;
When the refrigerant flows from the inlet / outlet 73a of the refrigerant on the 7th side to the inlet / outlet 73b of the refrigerant on the refrigerant throttle mechanism 27 side, the refrigerant flows into the auxiliary first heat exchanger 63 from the inlet / outlet 73a of the refrigerant on the anti-refrigerant throttle mechanism 27 side. Then, after successively passing through a plurality of (four) heat transfer tubes 26 of the auxiliary first heat exchanger 63, the auxiliary first heat exchanger 63
After flowing out of the heat exchanger 63, it is divided into two heat transfer tube paths and flows into the main first heat exchanger 62. In each of the heat transfer tube paths, first, a plurality of rows in an upstream row of the air flow are provided. A predetermined number (2,3) of the heat transfer tubes are continuously passed through the heat transfer tubes, and then a plurality of the heat transfer tubes in the row on the downstream side of the air flow are passed through the heat transfer tubes (4, 4).
5) After passing continuously, the remaining three heat transfer tubes in the row on the upstream side of the air flow continuously pass (three), and merge and flow out of the refrigerant inlet / outlet 73b of the refrigerant throttle mechanism 27 side. The auxiliary first heat exchanger 63 is configured such that the main first heat exchanger 63 is located on the upstream side of the air flow of the main first heat exchanger 62 and close to the refrigerant inlet / outlet 73 b on the refrigerant throttle mechanism 27 side. The heat exchanger 62 is arranged so as not to be located on the upstream side of the flow of air in the heat transfer tube 26 of the heat exchanger 62.

The first heat exchanger 73 has a main first heat exchanger 62 having two rows of heat transfer tubes 26 in the air flow direction and two heat transfer tube paths arranged in parallel with each other. Auxiliary first heat exchanger 63 having one row of heat transfer tubes 26 in the direction and having a shorter step length substantially perpendicular to the air flow direction than main first heat exchanger 62, Transfer tube 26 of the main first heat exchanger 62 near the inlet / outlet 73b of the refrigerant
Is located at a lower stage than the heat transfer tube 26 of the auxiliary first heat exchanger 63 near the refrigerant inlet / outlet 73a on the side of the anti-refrigerant throttle mechanism 27, and the heat transfer tube path of the auxiliary first heat exchanger 63 is 1
Anti-refrigerant throttle mechanism 2 arranged near the lower end of heat exchanger 63
The heat transfer tube 26 near the heat exchanger upper end is formed from the refrigerant inlet / outlet 73a on the seventh side toward the heat exchanger upper end.
One of the two heat transfer tube paths configured in parallel with the heat exchanger 62 is connected from the branch portion 26a connected to the heat transfer tube 26 near the upper end of the heat exchanger of the auxiliary first heat exchanger 63 to the upper end of the heat exchanger. To the row near the upper end of the heat exchanger to the downstream side of the air flow, and then to the lower end of the heat exchanger to the vicinity of the center of the heat exchanger. The other of the two heat transfer tube paths which are formed in parallel to the main first heat exchanger 62 are formed by moving to the row on the upstream side and extending toward the lower end of the heat exchanger to the inlet / outlet 73b of the refrigerant on the refrigerant throttle mechanism 27 side. The auxiliary first heat exchanger 63 is formed from the branch part 26a connected to the heat transfer tube 26 near the upper end of the heat exchanger to the lower end of the heat exchanger to the center of the heat exchanger, and further to the air near the center of the heat exchanger. To the row downstream of the heat flow to the bottom of the heat exchanger Selfish formed, further the heat exchanger bottom end vicinity in toward the upstream side to become transfer heat exchanger upper column of air flow the refrigerant throttle mechanism 27 side of the refrigerant entrance 73b
It is configured to be formed up to.

Further, the heat transfer tubes 26 in the row on the upstream side of the flow of air near the refrigerant inlet / outlet 73b on the side of the refrigerant throttle mechanism 27 of the first heat exchanger 73 (main first heat exchanger 62) are connected to the air. A cut 65 a for eliminating heat conduction between the rows of the heat transfer tubes 26 is provided in the plate-like fin 65 between the rows on the downstream side of the flow and the rows of the heat transfer tubes 26.

The heat transfer tubes 26 in the row on the upstream side of the flow of air near the refrigerant inlet / outlet 73a of the first heat exchanger 73 (main first heat exchanger 62) on the side opposite to the refrigerant throttle mechanism 27 are connected. Between the rows of the heat transfer tubes 26 (between the main first heat exchanger 62 and the auxiliary first heat exchanger 63) between the rows of the heat transfer tubes 26 on the downstream side of the flow of heat (the main first heat exchanger). A cut 65b for eliminating heat conduction between the first heat exchanger 62 and the auxiliary first heat exchanger 63 is provided on the plate-like fin 65, and the plate-like fin 65 is used for the main first heat exchanger 62 and the auxiliary first heat exchanger 63. It is divided into two parts for the exchanger 63.

The entire refrigeration cycle of the air conditioner of the third embodiment is the same as that of the entire refrigeration cycle of the air conditioner of the first embodiment shown in FIG.
A heat exchanger 73 is provided, and a second heat exchanger 34 is provided instead of the second heat exchanger 34.
This is equivalent to the one provided with the heat exchanger 74.

First, during the cooling operation, the four-way valve 36 is switched to the cooling side, the dehumidification control valve 27 is opened, and the electric expansion valve 38 is appropriately throttled, so that the compressor 35, the four-way valve 36, the outdoor heat exchanger 37 Expansion valve 38, first heat exchanger 73 of indoor heat exchanger 61 (auxiliary first heat exchanger 63, main first heat exchanger 62), fully open dehumidification control valve 27, indoor heat exchanger 6
1 second heat exchanger 74 (back heat exchanger 64), four-way valve 3
6, a refrigerant path is formed in the order of the compressor 35, the outdoor heat exchanger 37 acts as a condenser, and the entire indoor heat exchanger 61 acts as an evaporator.

When the fan 30 is rotated, the indoor air is drawn into the suction grills 31a, 31a on the front and upper surfaces.
b, and passes through the indoor heat exchanger 61 after being removed by the filter 28. Then, the air is cooled by the indoor heat exchanger 61, passes through the fan 30, and is blown into the room from the outlet 32.

At this time, the indoor heat exchanger 61 during the cooling operation
Is the refrigerant inlet / outlet 73a of the first heat exchanger 73 on the side opposite to the refrigerant throttle mechanism 27, and the heat transfer tube 26 immediately after the inlet 73a is on the upstream side of the flow of air. The refrigerant outlet 74b of the indoor heat exchanger 61 during the cooling operation is connected to the refrigerant inlet / outlet 74 of the second heat exchanger 74 on the side opposite to the refrigerant throttle mechanism 27.
b, and the heat transfer tube 26 immediately before that is downstream of the flow of air. The refrigerant inlet 74a of the second heat exchanger 74 during the cooling operation is connected to the refrigerant throttle mechanism 27 of the second heat exchanger 74.
Side refrigerant inlet / outlet 74a, and the heat transfer tube 26
Is upstream of the air flow.

At this time, in the indoor heat exchanger 61, the refrigerant flows into the refrigerant inlet 7 of the first heat exchanger 73 during the cooling operation.
The two heat exchangers 62 and 6 constituting the first heat exchanger 73 from 3a (the refrigerant inlet / outlet 73a on the anti-refrigerant throttle mechanism 27 side).
3, the air flows into the auxiliary first heat exchanger 63 located on the upstream side of the air flow, and continuously passes through a plurality of (four) heat transfer tubes 26 of the auxiliary first heat exchanger 63. Later assist 1
It flows out of the heat exchanger 63, is divided into two heat transfer pipe paths at the branch part 26a, flows into the main first heat exchanger 62, and
In each heat transfer tube path of the heat exchanger 62, first,
A predetermined number (two or three) of the plurality of heat transfer tubes continuously pass through the plurality of rows of the heat transfer tubes 26 on the upstream side of the air flow, and then the plurality of heat transfer tubes 26 of the row on the downstream side of the air flow pass through the plurality of heat transfer tubes 26. After passing continuously (4, 5), the remaining heat transfer tubes 26 in the row on the upstream side of the air flow (3) continuously pass and merge to form the first heat during cooling operation. The refrigerant flows out of the first heat exchanger 73 (outside the main first heat exchanger 62) from the refrigerant outlet 73b of the exchanger 73 (the refrigerant inlet / outlet 73b on the refrigerant throttle mechanism 27 side). That is, the refrigerant that has flowed into the first heat exchanger 73 flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then flows through the heat transfer tube path in which the refrigerant flow and the air flow flow in opposite directions. (Refrigerant path) and flows out of the first heat exchanger 73. afterwards,
The refrigerant flowing into the second heat exchanger 74 from the refrigerant inlet 74a of the second heat exchanger 74 (the refrigerant inlet / outlet 74a on the refrigerant throttle mechanism 27 side) during the cooling operation via the dehumidification control valve 27 in the fully open state is The flow is divided into two heat transfer pipe paths, and in each heat transfer pipe path, first, three successive heat transfer pipes 26 in a row on the upstream side of the air flow are successively passed. After passing three heat transfer tubes 26 in a row on the downstream side in a row, the three heat transfer tubes 26 merge and merge, and the refrigerant outlet 74b of the second heat exchanger 74 during the cooling operation (the refrigerant outlet 74b of the anti-refrigerant throttle mechanism 27 side). It flows out of the second heat exchanger 74 through the entrance 74b).
That is, the refrigerant that has flowed into the second heat exchanger 74 flows out of the second heat exchanger 74 through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel.

Therefore, during the cooling operation, the first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger 73 and the second heat exchanger 74 form a heat transfer tube in which the refrigerant flow and the air flow are parallel. In the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow become parallel flows as a whole, and the refrigerant flow and the air flow become parallel flows, in the evaporator where the refrigerant temperature sequentially decreases due to pressure loss The air can be cooled efficiently with a constant temperature difference between the refrigerant temperature gradient and the air temperature gradient with respect to the air flow direction. The second half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the first heat exchanger 73 is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are opposed to each other. (1) The refrigerant that has been heated in the first half of the refrigerant flow of the heat exchanger 73 and is in a gas-liquid two-phase state flows, and there is almost no change in the temperature of the refrigerant. There is no end.
Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in a parallel flow during the cooling operation.

In the cooling operation, the main first heat exchanger 62 through which the refrigerant flows after the auxiliary first heat exchanger 63 has two heat transfer tube paths arranged in parallel. Loss is reduced, and performance degradation can be prevented. Although the auxiliary first heat exchanger 63 has one heat transfer tube path, the pressure loss of the refrigerant flowing through the auxiliary first heat exchanger 63 during the cooling operation is not so large because the dryness is low.

Next, during the heating operation, the four-way valve 36 is switched to the heating side, the dehumidification control valve 27 is opened, and the electric expansion valve 38 is appropriately throttled, so that the compressor 35, the four-way valve 36, and the indoor heat exchanger 61 are controlled. The second heat exchanger 74 (the rear heat exchanger 6)
4), the dehumidification control valve 27 in the fully open state, the first heat exchanger 73 of the indoor heat exchanger 61 (main first heat exchanger 62, auxiliary first heat exchanger 63), the electric expansion valve 38, the outdoor heat exchanger A refrigerant path is formed in the order of 37, the four-way valve 36, and the compressor 35, and the outdoor heat exchanger 37 functions as an evaporator, and the entire indoor heat exchanger 61 functions as a condenser.

When the fan 30 is rotated, the indoor air is drawn into the suction grills 31a, 31a on the front and upper surfaces.
b, and passes through the indoor heat exchanger 61 after being removed by the filter 28. Then, the air is heated by the indoor heat exchanger 61, passes through the fan 30, and is blown into the room through the blowout port 32.

At this time, the indoor heat exchanger 61 during the heating operation
The refrigerant inlet 74b is the refrigerant inlet / outlet 74b of the second heat exchanger 74 on the side opposite to the refrigerant throttle mechanism 27, and the heat transfer tube 26 immediately behind the refrigerant inlet 74b is downstream of the flow of air. Further, the refrigerant outlet 73a of the indoor heat exchanger 61 during the heating operation is connected to the refrigerant inlet / outlet 73 of the first heat exchanger 73 on the side opposite to the refrigerant throttle mechanism 27.
a, and the heat transfer tube 26 immediately before that is upstream of the flow of air. The outlet 74a of the refrigerant of the second heat exchanger 74 during the heating operation is the inlet / outlet 74a of the refrigerant on the side of the refrigerant throttle mechanism 27 of the second heat exchanger 74, and the heat transfer tube 26 immediately before the outlet 74a serves as a flow passage for the air. It is on the upstream side.

At this time, in the indoor heat exchanger 61, the refrigerant flows into the refrigerant inlet 7 of the second heat exchanger 74 during the heating operation.
4b (refrigerant inlet / outlet 74b on the side of the anti-refrigerant throttle mechanism 27) flows into the second heat exchanger 74 and is divided into two heat transfer tube paths. Three consecutively pass through the plurality of heat transfer tubes 26 in the row on the side, and then successively pass through three heat transfer tubes 26 in the row on the upstream side of the air flow, and merge. Then, the refrigerant flows out of the second heat exchanger 74 from the refrigerant outlet 74a of the second heat exchanger 74 during the heating operation (the refrigerant inlet / outlet 74a on the side of the refrigerant throttle mechanism 27). That is, the refrigerant that has flowed into the second heat exchanger 74 flows through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are opposed to each other, and flows out of the second heat exchanger 74. Thereafter, through the dehumidification control valve 27 in the fully open state, the first heat exchanger 73 is configured from the refrigerant inlet 73b of the first heat exchanger 73 (the refrigerant inlet / outlet 73b on the refrigerant throttle mechanism 27 side) during the heating operation 2 Of the two heat exchangers 62 and 63, the heat flows into the main first heat exchanger 62 located downstream of the air flow, is divided into two heat transfer tube paths, and in each heat transfer tube path, (3) continuously pass through the plurality of heat transfer tubes 26 in the row on the upstream side of the air flow, and then pass the plurality of heat transfer tubes 26 in the row on the downstream side of the air flow (4, 5).
After passing continuously, the remaining heat transfer tubes 26 in the row on the upstream side of the air flow continuously pass (two or three),
It flows out of the main first heat exchanger 62 and merges at the branching section 26a, flows into the auxiliary first heat exchanger 63 located on the upstream side of the air flow, and has a plurality of auxiliary first heat exchangers 63. After successively passing through the (four) heat transfer tubes 26, the first heat exchanger 73 passes through the refrigerant outlet 73a of the first heat exchanger 73 during heating operation (the refrigerant inlet / outlet 73a on the anti-refrigerant throttle mechanism 27 side). Outflow to outside 73 (outside auxiliary first heat exchanger 63). That is, the refrigerant that has flowed into the first heat exchanger 73 flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then flows through the heat transfer tube path in which the refrigerant flow and the air flow flow in opposite directions. (Refrigerant path) and flows out of the first heat exchanger 73.

Therefore, during the heating operation, the latter half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the second heat exchanger 74 and the first heat exchanger 73 is formed by the heat transfer tube in which the refrigerant flow and the air flow are opposed. In the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are opposed to each other, and the refrigerant flow and the air flow are opposed to each other, the refrigerant temperature sequentially decreases from the superheated gas to the supercooled liquid. In such a condenser, air can be efficiently heated with a constant temperature difference between the refrigerant temperature gradient and the air temperature gradient in the air flow direction. Also, the first
Since the latter half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the heat exchanger 73 is a counterflow, the sufficiently cooled refrigerant is transferred to the first flow path.
It can be discharged from the heat exchanger 73. The first
The first half of the refrigerant flow in the heat transfer tube path (refrigerant path) of the heat exchanger 73 is a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow are parallel flows. Heat exchanger 7 having a heat transfer tube path in which air flows in opposite directions
The refrigerant cooled in 4 flows into a gas-liquid two-phase state, there is almost no change in the temperature of the refrigerant, and there is almost no adverse effect due to the parallel flow of the refrigerant flow and the air flow. Therefore, the basic performance is almost the same as that of the conventional air conditioner having the indoor heat exchanger in which the refrigerant flow and the air flow are in the opposite flow during the heating operation.

Further, during the heating operation of the indoor heat exchanger 61, the space between the heat transfer tubes 26 in the upstream row of the air flow and the heat transfer tubes 26 in the downstream row of the air flow immediately before the outlet 73a of the refrigerant (mainly) (Between the first heat exchanger 62 and the auxiliary first heat exchanger 63)
A gap 6 for eliminating heat conduction between the 26 rows of heat transfer tubes (between the main first heat exchanger 62 and the auxiliary first heat exchanger 63).
5b is provided on the plate-like fin 65, and the plate-like fin 65 is divided into two for the main first heat exchanger 62 and for the auxiliary first heat exchanger 63. Transfer tube 26 immediately before refrigerant outlet 73a during heating operation of
The low-temperature supercooled liquid refrigerant in the (heat transfer tube 26 of the auxiliary first heat exchanger 63) is heated to a relatively high temperature in the heat transfer tube 26 (heat transfer tube 26 of the main first heat exchanger 62) on the leeward side. Alternatively, since it is sufficiently cooled by low-temperature air without being heated by the gas-liquid two-phase refrigerant, it becomes a low-temperature supercooled liquid refrigerant. Thereby, the refrigerant that is more sufficiently cooled than that in which the cut 65 b is not provided in the plate-like fin 65 can flow out of the first heat exchanger 73.

In the first heat exchanger 73, the refrigerant flows last during the heating operation in the auxiliary first heat exchanger 63 having one heat transfer tube path. The flow velocity of the flowing refrigerant is increased, and the heat transfer coefficient in the pipe is increased, so that the heat transfer performance is improved. Therefore, the sufficiently cooled refrigerant can flow out of the first heat exchanger 73 during the heating operation.

Next, at the time of the dehumidifying operation, the four-way valve 36 is switched to the same side as the cooling operation, the dehumidifying control valve 27 is slightly opened, and the electric expansion valve 16 is fully opened.
5, a four-way valve 36, an outdoor heat exchanger 37, a fully opened electric expansion valve 38, a first heat exchanger 73 of an indoor heat exchanger 61 (an auxiliary first heat exchanger 63, a main first heat exchanger 62), Dehumidification control valve 27 in the slightly opened state, second heat exchanger 74 of indoor heat exchanger 61
(Back heat exchanger 64), a four-way valve 36, and a compressor 35 constitute a refrigerant path in this order, and together with the outdoor heat exchanger 15, the first heat exchanger 73 of the indoor heat exchanger 61 (the auxiliary first heat exchanger 63,
The main first heat exchanger 62) is a condenser, and the indoor heat exchanger 61
The second heat exchanger 74 (the backside heat exchanger 64) functions as an evaporator.

Then, when the fan 30 is rotated, the indoor air is drawn into the suction grills 31a, 31a on the front and upper surfaces.
b, and passes through the indoor heat exchanger 61 after being removed by the filter 28. At this time, the first heat exchanger 7 of the indoor heat exchanger 61 disposed on the front side functioning as a condenser
3 is heated, and the second heat exchanger 74 of the indoor heat exchanger 61 disposed on the rear side, which functions as an evaporator, is heated.
Is cooled (dehumidified). Thereafter, the air passes through the fan 30 and is mixed with the air, and
From the room.

At this time, the first heat exchanger 73 of the indoor heat exchanger 61 functioning as a condenser and the second heat exchanger 74 of the indoor heat exchanger 61 functioning as an evaporator are thermally separated. The first heat exchanger 73 functioning as a condenser
And the second heat exchanger 74 functioning as an evaporator, there is no loss due to heat leakage, and the dehumidifying ability does not decrease.

The indoor heat exchanger 6 arranged on the front side
The first heat exchanger 73 functions as a condenser, and the second heat exchanger 74 of the indoor heat exchanger 61 disposed on the rear side functions as an evaporator.
The condensed water generated in the heat exchanger 74 is not transmitted to the first heat exchanger 73 functioning as a condenser and re-evaporated.

In this air conditioner, the first heat exchanger 73 functioning as a condenser and the second heat exchanger 74 functioning as an evaporator in the indoor heat exchanger 61 are arranged in the direction of air flow. Therefore, the size of the indoor heat exchanger 61 in the direction of air flow does not increase, and the heat exchange portion functioning as a condenser and the heat exchange portion functioning as an evaporator in the indoor heat exchanger 61 are not provided. The air conditioner can be made smaller (thinner) than those arranged side by side in the air flow direction.

In the present embodiment, the refrigerant inlet 73a of the indoor heat exchanger 61 during the dehumidifying operation is the refrigerant inlet / outlet 73a of the first heat exchanger 73 on the side opposite to the refrigerant restricting mechanism 27, and the heat transfer tube immediately after that. Reference numeral 26 denotes an upstream side of the air flow. The refrigerant outlet 74b of the indoor heat exchanger 61 during the dehumidifying operation is the refrigerant inlet / outlet 74b of the second heat exchanger 74 on the side opposite to the refrigerant throttle mechanism 27. Downstream. Further, the refrigerant inlet 74a of the second heat exchanger 74 during the dehumidifying operation is the refrigerant inlet / outlet 74a of the second heat exchanger 74 on the side of the refrigerant throttle mechanism 27, and the heat transfer tube 26 immediately behind the inlet / outlet 74a of the refrigerant. It is on the upstream side.

During the dehumidifying operation, the indoor heat exchanger 61
The refrigerant enters the refrigerant inlet 73a of the first heat exchanger 73 during the dehumidifying operation (the refrigerant inlet / outlet 73a on the side opposite to the refrigerant throttle mechanism 27).
From the two heat exchangers 62 constituting the first heat exchanger 73,
Among the auxiliary heat exchangers 63, the air flows into the auxiliary first heat exchanger 63 located on the upstream side of the air flow, and continuously passes through a plurality of (four) heat transfer tubes 26 of the auxiliary first heat exchanger 63. Subsequent first
It flows out of the heat exchanger 63, is divided into two heat transfer pipe paths at the branch part 26a, flows into the main first heat exchanger 62, and
In each heat transfer tube path of the heat exchanger 62, first,
A predetermined number (two or three) of the plurality of heat transfer tubes continuously pass through the plurality of rows of the heat transfer tubes 26 on the upstream side of the air flow, and then the plurality of heat transfer tubes 26 of the row on the downstream side of the air flow pass through the plurality of heat transfer tubes 26. After passing continuously (4, 5 tubes), the remaining heat transfer tubes 26 in the row on the upstream side of the air flow (3 tubes) are continuously passed and merged to form the first heat in the dehumidifying operation. The refrigerant flows out of the first heat exchanger 73 (outside the main first heat exchanger 62) from the refrigerant outlet 73b of the exchanger 73 (the refrigerant inlet / outlet 73b on the refrigerant throttle mechanism 27 side). That is, the refrigerant that has flowed into the first heat exchanger 73 flows through a heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel, and then flows through the heat transfer tube path in which the refrigerant flow and the air flow flow in opposite directions. (Refrigerant path) and flows out of the first heat exchanger 73. afterwards,
The refrigerant that has flowed into the second heat exchanger 74 from the refrigerant inlet 74a (the refrigerant inlet / outlet 74a of the refrigerant throttle mechanism 27 side) of the second heat exchanger 74 during the dehumidification operation via the slightly opened dehumidification control valve 27. Is divided into two heat transfer pipe paths, and in each heat transfer pipe path, first, three successive heat transfer pipes 26 in a row on the upstream side of the air flow continuously pass, and then the air flow After passing three consecutive heat transfer tubes 26 in a row on the downstream side of the pipe, they merge, and the refrigerant outlet 74b of the second heat exchanger 74 during the dehumidifying operation (the refrigerant outlet of the anti-refrigerant throttle mechanism 27 side) Flows out of the second heat exchanger 74 through the entrance 74b).
That is, the refrigerant that has flowed into the second heat exchanger 74 flows out of the second heat exchanger 74 through the heat transfer tube path (refrigerant path) in which the refrigerant flow and the air flow flow in parallel.

In the dehumidifying operation, since the heat transfer tubes 26 immediately before the refrigerant outlet 73b of the first heat exchanger 73 are arranged in a row on the upstream side of the air flow, the refrigerant throttle mechanism (the dehumidifying control valve 2) is used.
The refrigerant immediately before flowing into 7) exchanges heat with the air before being heated by the first heat exchanger 73, so that a sufficient supercooled liquid can be obtained. As a result, the refrigerant flowing into the refrigerant throttle mechanism (the dehumidification control valve 27) becomes a liquid refrigerant and is depressurized by stable flow, so that the refrigerant flow noise is reduced. Further, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is reduced, sufficient heating, dehumidification and cooling of air can be performed, and a predetermined refrigeration cycle can be configured with low power consumption. .

At the time of the dehumidifying operation, the first heat exchanger 73
In the heat transfer tube path (refrigerant), the refrigerant flows into the refrigerant throttle mechanism (dehumidification control valve 27) immediately after passing a plurality of heat transfer tubes 26 arranged in a row on the upstream side of the air flow. Since the path is configured, the performance of cooling and liquefying the refrigerant flowing into the refrigerant throttle mechanism (the dehumidification control valve 27) is further improved. Thus, the refrigerant flowing into the refrigerant throttle mechanism easily becomes a liquid refrigerant, and is depressurized by a more stable flow, so that the refrigerant flow noise is further reduced. In addition, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is reduced, sufficient heating, dehumidification and cooling of air can be performed, and a predetermined refrigeration cycle can be configured with less power consumption. Becomes

In this embodiment, the heat transfer tubes 26 in the upstream row of the air flow and the heat transfer tubes 26 in the downstream row of the air flow immediately before the refrigerant outlet 73b during the dehumidifying operation of the first heat exchanger 73 are used. A gap 65a for eliminating heat conduction between the 26 rows of heat transfer tubes is provided in the plate-like fin 65 between the rows of the first heat exchanger 73 and the heat transfer pipe immediately before the refrigerant outlet 73b of the first heat exchanger 73 during the dehumidifying operation. The low-temperature supercooled liquid refrigerant in the heat transfer tube 26 is sufficiently cooled by the low-temperature air without being heated by the relatively high-temperature superheat or the gas-liquid two-phase refrigerant in the heat transfer tube 26 on the leeward side thereof. It becomes a supercooled liquid refrigerant. This allows
The refrigerant flowing into the refrigerant throttle mechanism (the dehumidification control valve 27) is more likely to be a liquid refrigerant than the one in which such a cut 65a is not provided in the plate-like fin 65, and is further reduced in pressure by a stable flow, so that there is no cut 65a. The refrigerant flow noise is smaller than that of the refrigerant. In addition, by sufficiently cooling, even if the compression ratio of the refrigeration cycle is smaller than that having no cut 65a, sufficient heating, dehumidification and cooling of air can be performed, and the air can be cooled more than that without the cut 65a. A predetermined refrigeration cycle can be configured with low power consumption.

In this embodiment, the heat exchangers on the front side of the indoor heat exchanger 61 (the main first heat exchanger 62 and the auxiliary first heat exchanger 6
3) is used as the first heat exchanger 73 and functions as a condenser during the dehumidifying operation, and the rear heat exchanger 64 of the indoor heat exchanger 61 is used as the second heat exchanger 74 and functions as the evaporator during the dehumidifying operation. The first heat exchanger 73 can be made larger than the second heat exchanger 74, and the wind speed of the airflow passing through the first heat exchanger 73 is faster than the wind speed of the airflow passing through the second heat exchanger 74. Occasionally, the heating performance of the first heat exchanger 73 is good, and the refrigerant tends to be a supercooled liquid. In addition, since the wind speed of the airflow passing through the second heat exchanger 74 is low, the dehumidifying efficiency of the air passing through the second heat exchanger 74 is good.

In this embodiment, the first heat exchanger 7
Reference numeral 3 denotes a main first heat exchanger 62 having two rows of heat transfer tubes 26 in the air flow direction and having two heat transfer tube paths arranged in parallel.
And an auxiliary first heat exchanger 63 having one row of heat transfer tubes 26 in the direction of air flow and having a shorter step length than the main first heat exchanger 62 in a direction substantially perpendicular to the direction of air flow, The heat transfer tube 26 of the main first heat exchanger 62 near the refrigerant inlet / outlet 73b on the refrigerant throttle mechanism 27 side is a heat transfer tube of the auxiliary first heat exchanger 63 near the refrigerant inlet / outlet 73a on the anti-refrigerant throttle mechanism 27 side. 26, the heat transfer tube path of the auxiliary first heat exchanger 63 is supplied with heat from the refrigerant inlet / outlet 73a of the anti-refrigerant throttle mechanism 27 disposed near the lower end of the auxiliary first heat exchanger 63. Heat transfer tubes 26 near the top of the heat exchanger toward the top of the exchanger
One of the two heat transfer tube paths formed in parallel with the main first heat exchanger 62 is connected to the heat transfer tube 26 near the upper end of the heat exchanger of the auxiliary first heat exchanger 63. 26
a from the upper part of the heat exchanger to the upper end of the heat exchanger, and then to a row on the downstream side of the air flow near the upper end of the heat exchanger, and to the lower end of the heat exchanger to the vicinity of the center of the heat exchanger. In the vicinity of the center, the flow shifts to a row on the upstream side of the air flow, and is formed toward the lower end of the heat exchanger to the refrigerant inlet / outlet 73b on the refrigerant throttle mechanism 27 side. The other of the two heat transfer tube paths is formed from the branch portion 26a connected to the heat transfer tube 26 near the upper end of the heat exchanger of the auxiliary first heat exchanger 63 to the heat exchanger lower end and near the center of the heat exchanger. Moved to the row on the downstream side of the air flow near the center of the heat exchanger and formed toward the lower end of the heat exchanger,
Further, the structure moves to a row on the upstream side of the air flow near the lower end of the heat exchanger, and is formed up to the refrigerant inlet / outlet 73b on the refrigerant throttle mechanism 27 side toward the upper end of the heat exchanger.

The air inlet grills 31a and 31b are provided on the front and upper surfaces of the main body, and the outlet 32 is provided on the lower front surface. The first heat exchanger 73 is disposed between the first heat exchanger 73 and the fan 30 to heat air passing through the front grille 31a and the front grille 31b on the upper side and the refrigerant in the first heat exchanger 73. Replace the suction grill 31b and fan 3 on the top.
The second heat exchanger 74 is disposed between the first heat exchanger 74 and the air in the second heat exchanger 74 and the air that has passed through the upper part of the suction grill 31b at the back side is exchanged.

For this reason, the heat transfer tubes 26 in the vicinity of the refrigerant inlet / outlet 73b of the first heat exchanger 73 on the side of the refrigerant throttle mechanism 27,
That is, the heat transfer tube 26 immediately before the refrigerant outlet 73 b during the dehumidifying operation of the first heat exchanger 73 is located on the upstream side of the air flow at a location where the air flow is relatively fast in the first heat exchanger 73. Therefore, during the dehumidifying operation, the cooling efficiency of the refrigerant passing through the heat transfer tube 26 immediately before the refrigerant outlet 73b of the first heat exchanger 73 is improved, and the sufficiently cooled low-temperature supercooled liquid refrigerant is cooled. 27.

At this time, the direction of the airflow passing through the main first heat exchanger 62 of the first heat exchanger 73 is changed from the row of the main first heat exchanger 62 which is on the upstream side of the air flow. In addition to the row direction component of the main first heat exchanger 62 heading toward the row on the downstream side of the flow, the stepwise component of the main first heat exchanger 62 heading from the top to the bottom of the main first heat exchanger 62 is However, at the time of the dehumidifying operation and the cooling operation, as a whole, the main first heat exchanger 62 becomes a heat transfer tube path through which the refrigerant flows from the upper part to the lower part,
At the time of the heating operation, as a whole, the main first heat exchanger 62
Is a heat transfer tube path through which the refrigerant flows from the lower part to the upper part. Therefore, in the main first heat exchanger 62 of the first heat exchanger 73, the ratio of the heat transfer tube path in which the refrigerant flow and the air flow become parallel flow during the cooling operation and the refrigerant flow and the air flow become counter flow during the heating operation increases. However, the heat exchange performance of the first heat exchanger 73 is improved.

At this time, the auxiliary first heat exchanger 63
Is disposed in a surplus space between the suction grills 31a, 31b on the front and top surfaces and the main first heat exchanger 62, so that the auxiliary first heat exchanger can be used without increasing the size of the air conditioner.
By adding the heat exchanger 63, the heat exchange performance of the first heat exchanger 73 can be improved.

Further, since the first heat exchanger 73 is configured by connecting the main first heat exchanger 62 and the auxiliary first heat exchanger 63 in series, the main first heat exchanger 73 having different temperatures of the refrigerant flowing through the tubes. 62 and the heat transfer tube 26 of the auxiliary first heat exchanger 63
The heat conduction transmitted through the plate-like fins 65 disappears,
Heat exchange performance is improved.

Although a part of the main first heat exchanger 62 is located on the leeward side of the auxiliary first heat exchanger 63, the main first heat exchanger 62 is located on the leeward side of the auxiliary first heat exchanger 63. Also in the located portion, since the plate-like fins 65 are not continuous between the main first heat exchanger 62 and the auxiliary first heat exchanger 63, the windward side of the plate-like fins 65 of the main first heat exchanger 62. Since the air flow hits the edge, the air flow is disturbed, and heat exchange is performed between the plate-like fin 65 of the main first heat exchanger 62 and the air flow, and the auxiliary first heat exchanger 63 Since it has one row of heat transfer tubes 26 in the flow direction, the heat of the first heat exchanger 62 due to the part of the main first heat exchanger 62 being located on the leeward side of the auxiliary first heat exchanger 63 The drop in exchange performance is small.

Further, in this embodiment, the refrigerant throttle mechanism is constituted by the dehumidification control valve 27 having the fully open state and the slightly open state. The refrigerant throttle mechanism having a state can be constituted by one dehumidification control valve 27. In addition, since the flow path resistance can be arbitrarily set during the dehumidifying operation, the amount of dehumidified air and the blowing temperature can be finely controlled.

(Embodiment 4) FIG. 5 is a sectional side view of an indoor unit according to Embodiment 4 of the air conditioner of the present invention.

In the air conditioner of the fourth embodiment, as shown in FIG. 5, a first heat exchanger 73 and a second heat exchanger 74 are provided in a capillary tube 27a and a bypass path bypassing the capillary tube 27a. It is connected via a refrigerant throttle mechanism constituted by a two-way valve 27b.

The air conditioner of the fourth embodiment differs from the air conditioner of the third embodiment shown in FIG. 4 in that the refrigerant throttle mechanism 27 has a fully open state and a slightly open state. Instead of using the dehumidification control valve 27 having a function of performing an operation, the dehumidification control valve 27 is constituted by a capillary tube 27a and a two-way valve 27b provided in a bypass path bypassing the capillary tube 27a and opened during cooling operation and heating operation and closed during dehumidification operation. This uses a refrigerant throttle mechanism.

The other configuration is the same as that of the air conditioner of the third embodiment. The same components as those of the air conditioner of the third embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted.

First, during the cooling operation, the four-way valve 36 is switched to the cooling side, the two-way valve 27b is opened, and the electric expansion valve 38 is appropriately throttled, so that the compressor 35, the four-way valve 36, the outdoor heat exchanger 37, Expansion valve 38, first heat exchanger 61
Heat exchanger 73 (auxiliary first heat exchanger 63, main first heat exchanger 62), open two-way valve 27b, second heat exchanger 74 of indoor heat exchanger 61 (backside heat exchanger 64), A refrigerant path is formed in the order of the four-way valve 36 and the compressor 35, and the outdoor heat exchanger 37 acts as a condenser and the entire indoor heat exchanger 61 acts as an evaporator.

Next, during the heating operation, the four-way valve 36 is switched to the heating side, the two-way valve 27b is opened, and the electric expansion valve 38 is appropriately throttled, so that the compressor 35, the four-way valve 36, and the indoor heat exchanger 61 A second heat exchanger 74 (back heat exchanger 64),
Open two-way valve 27b, first heat exchanger 73 of indoor heat exchanger 61 (main first heat exchanger 62, auxiliary first heat exchanger 6)
3), electric expansion valve 38, outdoor heat exchanger 37, four-way valve 3
6, a refrigerant path is formed in the order of the compressor 35, the outdoor heat exchanger 37 acts as an evaporator, and the entire indoor heat exchanger 61 acts as a condenser.

Next, during the dehumidifying operation, the four-way valve 36 is switched to the same side as the cooling operation, the two-way valve 27b is closed and the electric expansion valve 16 is fully opened, so that the compressor 35 and the four-way valve 3 are opened.
6, the outdoor heat exchanger 37, the fully-open electric expansion valve 38, the first heat exchanger 73 of the indoor heat exchanger 61 (the auxiliary first heat exchanger 63, the main first heat exchanger 62), and the capillary tube 27.
a, a refrigerant path is formed in the order of the second heat exchanger 74 (the rear heat exchanger 64) of the indoor heat exchanger 61, the four-way valve 36, and the compressor 35, and together with the outdoor heat exchanger 15, The first heat exchanger 73 (the auxiliary first heat exchanger 63, the main first heat exchanger 62) is used as a condenser, and the second heat exchanger 74 (the rear heat exchanger 64) of the indoor heat exchanger 61 is used as an evaporator. Let it work.

The other operations during the cooling operation, the heating operation, and the dehumidifying operation are performed during the cooling operation of the air conditioner of the third embodiment.
In the description of each operation during the heating operation and the dehumidification operation, the portion that was the dehumidification control valve 27 is replaced by the capillary tube 27.
a and the two-way valve 27b provided in the bypass path that bypasses the capillary tube 27a, and the “open (dehumidify) the dehumidification control valve 27” changes to “open (ku) the dehumidification valve 27b” and the “dehumidification control”. “Valve the valve 27 to a slightly open state” is “close the two-way valve 27b”, and “Fully open dehumidification control valve 27” is “an open two-way valve 27b”.
In addition, since the “slightly opened dehumidification control valve 27” only replaces the “capillary tube 27a”,
Detailed description is omitted.

Further, in the present embodiment, the refrigerant throttle mechanism is constituted by the capillary tube 27a and the two-way valve 27b provided in the bypass which bypasses the capillary tube 27a. Although the road resistance cannot be set arbitrarily and the amount of air dehumidification and the blowing temperature cannot be finely controlled, it can be configured at low cost.

In this embodiment, in the air conditioner (heat exchanger unit) of the third embodiment shown in FIG. 4, the refrigerant throttle mechanism 27 has a fully opened state and a slightly opened state, and the refrigerant throttle mechanism 27 is slightly opened during the dehumidifying operation. Instead of using the dehumidification control valve 27 having the function of opening and performing the throttling action, the capillary tube 27
1 and a two-way valve 27b that is provided in a bypass path that bypasses the capillary tube 27a and that opens during cooling operation and heating operation and closes during dehumidification operation. In the air conditioner (heat exchanger unit) of the first embodiment or the air conditioner (heat exchanger unit) of the second embodiment shown in FIG. 3, the refrigerant throttle mechanism 27 has a fully open state and a slightly open state. Instead of using the dehumidification control valve 27 having a function of performing a throttling operation by being slightly opened during the dehumidification operation, the capillary tube 2
Needless to say, a refrigerant throttle mechanism provided with a two-way valve 27b provided in a bypass path bypassing the capillary tube 7a and the capillary tube 27a and opened during the cooling operation and the heating operation and closed during the dehumidifying operation may be used.

[0261]

As described above, according to the first aspect of the present invention, during the dehumidifying operation, the heat transfer tube immediately after the refrigerant inlet of the first heat exchanger and the heat transfer tube immediately before the refrigerant outlet are connected to each other by the air. Arranged in the upstream row of the flow, the heat transfer tubes immediately after the inlet of the refrigerant of the second heat exchanger during the dehumidification operation, the upstream row of the flow of the air, By placing each in the downstream row of the flow,
The two heat exchangers connected via the refrigerant throttle mechanism are both fin tubes configured so that the refrigerant flow and the air flow become parallel flow during the cooling operation, and the refrigerant flow and the air flow become counter flow during the heating operation. Compared with a conventional air conditioner equipped with an indoor heat exchanger, the deterioration in basic performance during cooling operation and heating operation is reduced, and during dehumidification operation, the liquid refrigerant that has been sufficiently supercooled is a refrigerant throttle mechanism. Therefore, the refrigerant flow noise is reduced, and a predetermined refrigeration cycle can be configured with less power consumption.

According to a second aspect of the present invention, in the air conditioner of the first aspect, the heat transfer tube path of the first heat exchanger is connected to the inside of the first heat exchanger from the entrance during the dehumidifying operation. After the refrigerant flowing into the air flows in the same direction as the air flow, the refrigerant flows in the direction opposite to the air flow, and the first refrigerant flows through the outlet.
By arranging so as to flow out of the heat exchanger, it is possible to further reduce a decrease in basic performance during the cooling operation and the heating operation, and to promote a reduction in refrigerant flow noise and energy saving.

According to a third aspect of the present invention, in the air conditioner of the first aspect of the present invention, two rows of heat transfer tubes are provided in the air flow direction, and two heat transfer pipe paths are arranged in parallel. During the dehumidifying operation, the refrigerant flows in from the inlet of the refrigerant during the dehumidifying operation and is divided into the two heat transfer tube paths. In each of the heat transfer tube paths, first, a plurality of refrigerants in the upstream row of the air flow are arranged. After passing through a predetermined number of heat transfer tubes continuously, and then continuously passing through a plurality of heat transfer tubes in the downstream row of the air flow, the remaining heat transfer tubes in the upstream row of the air flow are passed through. The first heat exchanger is configured to continuously pass, merge, and flow out of the outlet of the refrigerant during the dehumidifying operation, thereby further reducing a decrease in basic performance during the cooling operation and the heating operation, In addition, it is possible to promote a reduction in refrigerant flow noise and an energy saving.

In the first heat exchanger, since two heat transfer tube paths are formed in parallel, the pressure loss during the cooling operation is reduced, and the performance can be prevented from deteriorating.

According to a fourth aspect of the present invention, in the air conditioner of the first aspect, the first heat exchanger is provided with two rows of heat transfer tubes in the direction of air flow and two heat transfer tubes. A main first heat exchanger in which the paths are configured in parallel, and a length of a stepped direction having one row of heat transfer tubes in the air flow direction and substantially perpendicular to the air flow direction than the main first heat exchanger. And a short first auxiliary heat exchanger. During the dehumidifying operation, the refrigerant flows into the auxiliary first heat exchanger from the inlet of the refrigerant during the dehumidifying operation, and the plurality of auxiliary first heat exchangers After successively passing through the heat transfer tubes, flows out of the auxiliary first heat exchanger, is divided into two heat transfer tube paths, flows into the main first heat exchanger, and in each of the heat transfer tube paths, First, a predetermined number of tubes are continuously passed through a plurality of heat transfer tubes in the upstream row of the air flow, and then the air is After successively passing through the plurality of heat transfer tubes in the downstream row, the remaining heat transfer tubes in the upstream row of air flow are continuously passed, and merged and the refrigerant outlet during the dehumidifying operation And the auxiliary first heat exchanger is located upstream of the air flow of the main first heat exchanger, and during the cooling operation and the dehumidifying operation of the main first heat exchanger. By arranging the heat transfer tube immediately before the outlet of the refrigerant so as not to be located on the upstream side of the air flow, the deterioration of the basic performance during the cooling operation and the heating operation is further reduced, and the refrigerant flow noise is reduced, Energy saving can be promoted.

In the cooling operation, the main first heat exchanger through which the refrigerant flows after the auxiliary first heat exchanger has two heat transfer tube paths arranged in parallel, so that the pressure loss during the cooling operation is reduced. The size can be reduced, and a decrease in performance can be prevented.

Further, in the first heat exchanger, the flow rate of the refrigerant flowing through the auxiliary first heat exchanger is increased, the heat transfer coefficient in the pipe is increased, and the heat transfer performance is improved. Therefore, during the heating operation, the sufficiently cooled refrigerant can flow out of the first heat exchanger, and the heating performance is improved.

Further, since the first heat exchanger is constructed by connecting the main first heat exchanger and the auxiliary first heat exchanger in series, the heat transfer tubes of the main first heat exchanger having different refrigerant temperatures flowing through the tubes are provided. There is no heat conduction through the plate fins between the heat transfer tubes of the auxiliary first heat exchanger and the heat transfer tubes of the auxiliary first heat exchanger, and the heat exchange performance is improved.

According to a fifth aspect of the present invention, in the air conditioner according to any one of the first to fourth aspects, the air flow immediately before the outlet of the refrigerant during the dehumidifying operation of the first heat exchanger. By providing cuts in the plate-like fins between the heat transfer tubes in the upstream row and the heat transfer tubes in the downstream row of the air flow to eliminate heat conduction between the heat transfer pipe rows, during dehumidification operation The low-temperature supercooled liquid refrigerant in the heat transfer tube immediately before the outlet of the refrigerant of the first heat exchanger has a low temperature without being heated by the relatively high-temperature superheat or the gas-liquid two-phase refrigerant in the heat transfer tube on the leeward side. Since the air is sufficiently cooled by the air, it is possible to promote a reduction in refrigerant flow noise and an energy saving.

According to a sixth aspect of the present invention, in the air conditioner according to any one of the first to fifth aspects, the first heat exchanger constituting the indoor heat exchanger is provided with a suction grill on a front surface. A second heat exchanger that constitutes the indoor heat exchanger by exchanging heat with air that has passed through the suction grille on the front surface and the front side of the suction grille on the upper surface between the suction grille and the once-through fan. The first heat exchanger is located between the suction grille on the upper surface and the fan and exchanges heat with the air passing through the rear part of the suction grille on the upper surface. Since the wind speed of the airflow passing through the first heat exchanger is faster than the wind speed of the airflow passing through the second heat exchanger, the heating performance in the first heat exchanger during the dehumidifying operation is good, But easily becomes a supercooled liquid. In addition, since the wind speed of the airflow passing through the second heat exchanger is low, the dehumidifying efficiency of the air passing through the second heat exchanger is good.

According to a seventh aspect of the present invention, in the air conditioner according to any one of the first to sixth aspects, the air flow immediately before the refrigerant outlet during the dehumidifying operation of the first heat exchanger. By arranging the heat transfer tubes in the upstream row of the first heat exchanger at a relatively high air flow rate in the first heat exchanger, the heat transfer tubes pass through the heat transfer tubes immediately before the refrigerant outlet of the first heat exchanger during the dehumidifying operation. The cooling efficiency of the refrigerant is improved, and the flow noise of the refrigerant can be reduced and the energy saving can be promoted.

In the invention according to claim 8, the heat transfer tubes through which a plurality of plate-like fins are inserted at right angles and through which the refrigerant flows are formed in a plurality of rows in the direction of air flow.
The heat transfer tubes adjacent to the two refrigerant inlets and outlets are both inserted at right angles to a fin tube type first heat exchanger arranged in a row on the upstream side of the air flow, and a plurality of plate-like fins arranged in parallel. The heat transfer tubes through which the refrigerant flows are formed in a plurality of rows in the direction of air flow, and the heat transfer tubes near the one of the two refrigerant inlets and outlets are arranged on the upstream side of the air flow. A fin tube-shaped second heat exchanger arranged in a row in which the heat transfer tubes arranged and adjacent to the inlet and outlet of the other refrigerant are on the downstream side of the flow of air; and two inlets and outlets of two refrigerants of the first heat exchanger The flow path resistance of the refrigerant provided in the middle of the connecting pipe connecting the inlet / outlet of one of the refrigerants and the inlet / outlet of the refrigerant arranged in the upstream row of the air flow of the second heat exchanger is large. Cold with a state and a low flow path resistance of the refrigerant A heat exchanger in which the first heat exchanger and the second heat exchanger are arranged such that the first heat exchanger and the second heat exchanger do not overlap in the direction of air flow. It is an exchange unit.

This heat exchanger unit is used for an indoor heat exchanger of an air conditioner. During the cooling operation, the refrigerant flows through the first heat exchanger, the refrigerant throttle mechanism having a small flow path resistance of the refrigerant, and the second heat exchanger. The refrigerant flows in the order of the heat exchanger, and during the heating operation, the refrigerant is the second heat exchanger, a refrigerant throttle mechanism in a state where the flow path resistance of the refrigerant is small,
The refrigerant flows in the order of the first heat exchanger, and during the dehumidifying operation, the refrigerant flows into the first heat exchanger.
In the case where the refrigeration cycle is configured to flow in the order of the heat exchanger, the refrigerant throttle mechanism having a large flow path resistance of the refrigerant, and the second heat exchanger, two heat exchangers connected via the refrigerant throttle mechanism are provided. In both cases, compared with the case of using a fin tube type heat exchanger unit configured so that the refrigerant flow and the air flow become parallel flows during the cooling operation, and the refrigerant flow and the air flow become counter flow during the heating operation, In the dehumidifying operation, the liquid refrigerant that has been sufficiently supercooled flows into the refrigerant throttle mechanism to reduce the deterioration of the basic performance during the operation and the heating operation. A predetermined refrigeration cycle can be configured.

According to the ninth aspect of the present invention, in the heat exchanger unit of the eighth aspect, the refrigerant flowing from the inlet / outlet of the refrigerant on the side opposite to the refrigerant restricting mechanism of the first heat exchanger is air. After the refrigerant flows in the same direction as the flow, the refrigerant flows in the direction opposite to the air flow, and the heat transfer tube path of the first heat exchanger is configured to flow out of the refrigerant inlet / outlet on the refrigerant throttle mechanism side. , Further reduce the decrease in basic performance during cooling operation and heating operation, and reduce refrigerant flow noise,
Energy saving can be promoted.

According to a tenth aspect of the present invention, in the heat exchanger unit of the eighth aspect, the heat exchanger unit has two rows of heat transfer tubes in the air flow direction, and the two heat transfer tube paths are arranged in parallel. When the refrigerant flows from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism to the inlet / outlet of the refrigerant on the side of the refrigerant throttle mechanism, the refrigerant flows in from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism and the two heat transfer tubes. In each of the heat transfer tube paths, first, a predetermined number of heat transfer tubes continuously pass through a row on the upstream side of the air flow, and then a row on the downstream side of the air flow. After continuously passing through the plurality of heat transfer tubes, the air continuously passes through the remaining heat transfer tubes in the row on the upstream side of the air flow, merges and flows out from the refrigerant inlet / outlet on the refrigerant throttle mechanism side. In addition, by configuring the first heat exchanger, the cooling operation And further reducing the deterioration of basic performance of the heating operation, and, reduction of the refrigerant flow noise, can promote energy saving.

In the first heat exchanger, since two heat transfer tube paths are formed in parallel, the pressure loss during the cooling operation is reduced, and the performance can be prevented from deteriorating.

According to the eleventh aspect of the present invention, in the heat exchanger unit of the tenth aspect, one of the two heat transfer tube paths arranged in parallel is connected to the refrigerant on the side opposite to the refrigerant throttle mechanism. From the entrance and exit of the heat exchanger to the upper end of the heat exchanger. In the vicinity of the center of the heat exchanger, the heat exchanger moves to a row on the upstream side of the air flow and is formed toward the lower end of the heat exchanger to the refrigerant inlet / outlet on the refrigerant throttle mechanism side. Formed from the inlet / outlet of the refrigerant on the side of the refrigerant throttle mechanism to the heat exchanger lower end near the center of the heat exchanger, and further moved to a row near the center of the heat exchanger on the downstream side of the flow of air toward the lower end of the heat exchanger. Formed and with heat exchanger bottom end In addition to the effect of the invention according to claim 10, by moving to a row on the upstream side of the flow of air and forming up to the inlet and outlet of the refrigerant on the refrigerant throttle mechanism side toward the upper end of the heat exchanger, The following effects can be obtained.

That is, in a wall-mounted type air conditioner having a suction grill at the front and top surfaces of the main body and a blow-out opening at the lower front portion, and having a built-in once-through fan, a space between the front suction grill and the fan. The first heat exchanger is arranged to exchange heat between the air passing through the front side suction grille and the front side of the upper side suction grille and the refrigerant in the first heat exchanger. In the case where the second heat exchanger is disposed between the first heat exchanger and the air passing through the rear part of the suction grill on the upper surface and heat exchanges the refrigerant in the second heat exchanger, the refrigerant throttle of the first heat exchanger is provided. The heat transfer tube close to the inlet / outlet of the refrigerant on the mechanism side, that is, the heat transfer tube immediately before the outlet of the refrigerant during the dehumidifying operation of the first heat exchanger is the air at the portion of the first heat exchanger where the flow of air is relatively fast. Upstream of the stream Therefore, the cooling efficiency of the refrigerant passing through the heat transfer tube immediately before the outlet of the refrigerant in the first heat exchanger during the dehumidifying operation is improved, and the sufficiently cooled low-temperature supercooled liquid refrigerant flows into the refrigerant throttle mechanism. Can be
Reducing the flow noise of the refrigerant and saving energy can be promoted. Further, in the first heat exchanger, the ratio of the heat transfer tube path in which the refrigerant flow and the air flow become parallel flow during the cooling operation and the refrigerant flow and the air flow become counter flow during the heating operation increases, and the heat of the first heat exchanger increases. Exchange performance is improved.

[0279] In the twelfth aspect of the present invention, in the heat exchanger unit of the eighth aspect, the first heat exchanger is provided with two rows of heat transfer tubes in the direction of air flow and two transfer pipes. A main first heat exchanger in which heat pipe paths are configured in parallel;
An auxiliary first heat exchanger having a single row of heat transfer tubes in the direction of air flow and having a shorter stepwise length substantially perpendicular to the direction of air flow than the main first heat exchanger; When the refrigerant flows from the inlet / outlet of the refrigerant on the mechanism side to the inlet / outlet of the refrigerant on the refrigerant throttle mechanism side, the refrigerant flows into the auxiliary first heat exchanger from the inlet / outlet of the refrigerant on the anti-refrigerant throttle mechanism side, and After successively passing through a plurality of heat transfer tubes of the first heat exchanger, it flows out of the auxiliary first heat exchanger, is divided into two heat transfer tube paths, flows into the main first heat exchanger, In each of the heat transfer pipe paths, first, a predetermined number of heat transfer pipes continuously pass through a plurality of heat transfer pipes in the row on the upstream side of the air flow, and then a plurality of heat transfer pipes in the row on the downstream side of the air flow. After successively passing through the heat tubes, it continuously passes through the remaining heat transfer tubes in the row that is upstream of the air flow The auxiliary first heat exchanger is arranged so as to flow out of an inlet / outlet of the refrigerant on the side of the refrigerant throttle mechanism, and the auxiliary first heat exchanger is on the upstream side of the air flow of the main first heat exchanger and on the side of the refrigerant throttle mechanism. By further arranging the main first heat exchanger so as not to be located on the upstream side of the flow of air in the heat transfer tube close to the inlet / outlet of the refrigerant, the deterioration of the basic performance during the cooling operation and the heating operation is further reduced. In addition, the refrigerant flow noise can be reduced and energy saving can be promoted.

In the cooling operation, the main first heat exchanger through which the refrigerant flows after the auxiliary first heat exchanger has two heat transfer tube paths arranged in parallel, so that the pressure loss during the cooling operation is reduced. The size can be reduced, and a decrease in performance can be prevented.

In the first heat exchanger, the flow rate of the refrigerant flowing through the auxiliary first heat exchanger is increased, the heat transfer coefficient in the pipe is increased, and the heat transfer performance is improved. Therefore, during the heating operation, the sufficiently cooled refrigerant can flow out of the first heat exchanger, and the heating performance is improved.

Further, since the first heat exchanger is constituted by connecting the main first heat exchanger and the auxiliary first heat exchanger in series, the heat transfer tubes of the main first heat exchanger having different refrigerant temperatures flowing through the tubes are provided. There is no heat conduction through the plate fins between the heat transfer tubes of the auxiliary first heat exchanger and the heat transfer tubes of the auxiliary first heat exchanger, and the heat exchange performance is improved.

According to the thirteenth aspect of the present invention, in the heat exchanger unit of the twelfth aspect, the heat transfer tube path of the auxiliary first heat exchanger is provided near the lower end of the auxiliary first heat exchanger. Formed from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism disposed toward the upper end of the heat exchanger to the heat transfer tube near the upper end of the heat exchanger, and two paths configured in parallel with the main first heat exchanger. One of the heat transfer tube paths is formed from a branch portion connected to the heat transfer tube near the upper end of the heat exchanger of the auxiliary first heat exchanger toward the upper end of the heat exchanger. To the lower row of the heat exchanger to the lower end of the heat exchanger and to the vicinity of the center of the heat exchanger, and further to the upper row of the air flow near the center of the heat exchanger and to the lower stream of the heat exchanger toward the lower end of the heat exchanger. The main first heat is formed up to the refrigerant inlet / outlet on the throttle mechanism side. The other of the two heat transfer tube paths configured in parallel with the heat exchanger is heat-exchanged from the branching portion connected to the heat transfer tube near the heat exchanger upper end of the auxiliary first heat exchanger toward the heat exchanger lower end. Formed near the center of the heat exchanger, and then moved to a row downstream of the air flow near the center of the heat exchanger and formed toward the lower end of the heat exchanger, and further upstream of the air flow near the lower end of the heat exchanger In addition to the effect of the invention according to claim 12, by moving to the row and forming a structure up to the inlet and outlet of the refrigerant on the refrigerant throttle mechanism side toward the upper end of the heat exchanger,
The following effects can be obtained.

That is, in a wall-mounted type air conditioner having a suction grill at the front and upper surfaces of the main body and a blow-out port at the lower front, and having a built-in once-through fan, a space between the front suction grill and the fan. The first heat exchanger is arranged to exchange heat between the air passing through the front side suction grille and the front side of the upper side suction grille and the refrigerant in the first heat exchanger. In the case where the second heat exchanger is disposed between the first heat exchanger and the air passing through the rear part of the suction grill on the upper surface and heat exchanges the refrigerant in the second heat exchanger, the refrigerant throttle of the first heat exchanger is provided. The heat transfer tube close to the inlet / outlet of the refrigerant on the mechanism side, that is, the heat transfer tube immediately before the outlet of the refrigerant during the dehumidifying operation of the first heat exchanger is the air at the portion of the first heat exchanger where the flow of air is relatively fast. Upstream of the stream Therefore, the cooling efficiency of the refrigerant passing through the heat transfer tube immediately before the outlet of the refrigerant in the first heat exchanger during the dehumidifying operation is improved, and the sufficiently cooled low-temperature supercooled liquid refrigerant flows into the refrigerant throttle mechanism. Can be
Reducing the flow noise of the refrigerant and saving energy can be promoted. Further, in the first heat exchanger, the ratio of the heat transfer tube path in which the refrigerant flow and the air flow become parallel flow during the cooling operation and the refrigerant flow and the air flow become counter flow during the heating operation increases, and the heat of the first heat exchanger increases. Exchange performance is improved. Also, at this time, the auxiliary first heat exchanger is disposed in a surplus space between the suction grilles on the front and upper surfaces and the main first heat exchanger, so that the air conditioner is not enlarged. , By adding an auxiliary first heat exchanger,
The heat exchange performance of the heat exchanger can be improved.

According to a fourteenth aspect of the present invention, in the heat exchanger unit according to any one of the eighth to thirteenth aspects, the heat exchanger unit is located near the refrigerant inlet / outlet of the first heat exchanger on the side of the refrigerant throttle mechanism. A cut is provided in the plate-like fin between the row of heat transfer tubes on the upstream side of the air flow and the row of heat transfer tubes on the downstream side of the air flow to eliminate heat conduction between the rows of heat transfer tubes. As a result, during the dehumidifying operation, the low-temperature supercooled liquid refrigerant in the heat transfer tube immediately before the refrigerant outlet of the first heat exchanger is replaced with the relatively high-temperature superheated or gas-liquid two-phase refrigerant in the leeward heat transfer tube. Since the cooling air is sufficiently cooled by the low-temperature air without being heated, the noise of the refrigerant flowing can be reduced and the energy saving can be promoted.

According to a fifteenth aspect of the present invention, in the heat exchanger unit according to any one of the eighth to fourteenth aspects, the refrigerant throttle mechanism is constituted by a control valve having a fully opened state and a slightly opened state. By doing so, a refrigerant throttle mechanism having a state in which the flow path resistance of the refrigerant is large and a state in which the flow path resistance of the refrigerant is small can be configured with one control valve. In addition, since the flow path resistance can be arbitrarily set during the dehumidifying operation, the amount of dehumidified air and the blowing temperature can be finely controlled.

According to a sixteenth aspect of the present invention, in the heat exchanger unit according to any one of the eighth to fourteenth aspects, the refrigerant throttle mechanism includes a capillary tube,
The refrigerant throttle mechanism having a state in which the flow resistance of the refrigerant is large and a state in which the flow resistance of the refrigerant is small is configured by a two-way valve provided in a bypass path that bypasses the capillary tube. By valve
Inexpensive configuration.

[Brief description of the drawings]

FIG. 1 is a side sectional view of an indoor unit according to Embodiment 1 of an air conditioner according to the present invention.

FIG. 2 is a refrigeration cycle diagram of the air conditioner of the embodiment.

FIG. 3 is a side sectional view of an indoor unit according to Embodiment 2 of the air conditioner according to the present invention.

FIG. 4 is a side sectional view of an indoor unit according to Embodiment 3 of the air conditioner of the present invention.

FIG. 5 is a side sectional view of an indoor unit according to Embodiment 4 of the air conditioner of the present invention.

FIG. 6 is a side sectional view of an indoor unit of a conventional air conditioner.

FIG. 7 is a refrigeration cycle diagram of a conventional air conditioner.

[Explanation of symbols]

21, 41, 61 Fin tube type indoor heat exchanger 25, 45, 65 Plate fin 25a, 45a, 65a Break 26 Heat transfer tube 27 Refrigerant throttle mechanism (dehumidification control valve) 27a Capillary tube 27b Two-way valve 30 Fan 31a, 31b Suction grille 33, 53, 73 First heat exchanger 33a, 53a, 73a Refrigerant inlet (refrigerant inlet / outlet) 33b, 53b, 73b Refrigerant outlet (refrigerant inlet / outlet) 34, 54, 74 Second heat exchanger 34a, 54a, 74a Refrigerant inlet (refrigerant inlet / outlet) 34b, 54b, 74b Refrigerant outlet (refrigerant inlet / outlet) 62 Main first heat exchanger 63 Auxiliary first heat exchanger

Claims (16)

[Claims] 1. A fin tube type indoor heat exchanger in which a plurality of heat transfer tubes which are inserted at right angles through a plurality of parallelly arranged plate-like fins and through which a refrigerant flows is formed in a plurality of rows in the direction of air flow. While thermally dividing into a first heat exchanger and a second heat exchanger in a stage direction substantially perpendicular to the flow direction, the flow resistance of the refrigerant between the first heat exchanger and the second heat exchanger is reduced. Connected via a refrigerant throttle mechanism having a large state and a state in which the flow path resistance of the refrigerant is small, the first state is used during the cooling operation and the dehumidifying operation.
A refrigeration cycle is configured such that the refrigerant flows from the heat exchanger to the second heat exchanger, and the refrigerant flows from the second heat exchanger to the first heat exchanger during a heating operation, and the refrigerant throttle mechanism during a dehumidifying operation. An air conditioner that is capable of dehumidifying indoor air with the second heat exchanger while heating the indoor air with the first heat exchanger while setting the flow path resistance of the refrigerant to be large. The heat transfer tubes immediately after the inlet of the refrigerant of the first heat exchanger and the heat transfer tubes immediately before the outlet of the refrigerant in the first heat exchanger are arranged in a row on the upstream side of the flow of air during the operation, and the second heat exchanger during the dehumidification operation is An air conditioner wherein the heat transfer tubes immediately after the inlet of the refrigerant are arranged in a row on the upstream side of the air flow, and the heat transfer tubes immediately before the outlet of the refrigerant are arranged in a row on the downstream side of the air flow. 2. The first heat exchanger is configured such that during the dehumidifying operation, the refrigerant flows in from the inlet of the refrigerant during the dehumidifying operation, flows in the same direction as the air flow, and then flows in the direction opposite to the air flow. The air conditioner according to claim 1, wherein the heat transfer tube path is configured such that the refrigerant flows through the outlet of the refrigerant during the dehumidifying operation. 3. The first heat exchanger has two rows of heat transfer tubes in a flow direction of air, and two heat transfer tube paths are configured in parallel. It flows in from the inlet and is divided into two of the heat transfer tube paths. In each of the heat transfer tube paths, first, a predetermined number of the heat transfer tubes continuously pass through a plurality of heat transfer tubes in an upstream row of the air flow, and then the air After successively passing through the plurality of heat transfer tubes in the downstream row of the flow of air, the refrigerant continuously passes through the remaining heat transfer tubes in the upstream row of the air flow, and merges to form a refrigerant in the dehumidifying operation. 2. The method according to claim 1, wherein the outlet is configured to flow out of the outlet.
The air conditioner as described. 4. The first heat exchanger includes a main first heat exchanger having two rows of heat transfer tubes in the air flow direction and two heat transfer tube paths arranged in parallel, and a first heat exchanger in the air flow direction. An auxiliary first heat exchanger having a row of heat transfer tubes and a shorter length in a step direction substantially perpendicular to the air flow direction than the main first heat exchanger; Flows into the auxiliary first heat exchanger from the inlet of the refrigerant, passes through the plurality of heat transfer tubes of the auxiliary first heat exchanger continuously, and then flows out of the auxiliary first heat exchanger. The heat is diverted to the heat transfer tube path and flows into the main first heat exchanger. In each of the heat transfer tube paths, first, a predetermined number of heat transfer tubes continuously pass through a plurality of heat transfer tubes in an upstream row of air flow. Then, after successively passing through a plurality of heat transfer tubes in a row on the downstream side of the air flow,
It is configured to continuously pass through the remaining heat transfer tubes in the row on the upstream side of the air flow, to merge and to flow out from the outlet of the refrigerant at the time of the dehumidifying operation, and the auxiliary first heat exchanger is The main first heat exchanger should not be located upstream of the air flow and upstream of the air flow of the heat transfer tube immediately before the refrigerant outlet during the cooling operation and the dehumidifying operation of the main first heat exchanger. The air conditioner according to claim 1, wherein the air conditioner is disposed in a space. 5. A row of heat transfer tubes between a row of heat transfer tubes in an upstream row of air flow and a row of heat transfer tubes in a downstream row of air flow immediately before a refrigerant outlet during a dehumidifying operation of the first heat exchanger. The air conditioner according to any one of claims 1 to 4, wherein a cut for eliminating heat conduction between the plate fins is provided. 6. An indoor unit accommodating the indoor heat exchanger, which has a built-in once-through type fan and has suction grills on a front surface and an upper surface of the indoor unit main body, wherein the first unit constituting the indoor heat exchanger is provided. The heat exchanger is located between the suction grill on the front and the fan, and exchanges heat with air passing through the front side of the suction grill on the front and the suction grill on the top, and The second heat exchanger that is configured is located between the suction grill on the upper surface and the fan, and exchanges heat with the air that has passed through the rear part of the suction grill on the upper surface. 5. The air conditioner according to any one of 5. 7. The heat transfer tubes in the upstream row of the air flow immediately before the outlet of the refrigerant during the dehumidifying operation of the first heat exchanger are arranged in the first heat exchanger at locations where the air flow is relatively high. The air conditioner according to any one of claims 1 to 6, wherein: 8. A plurality of heat transfer tubes, which are inserted at right angles to a large number of plate-like fins arranged in parallel and through which a refrigerant flows, are arranged in a plurality of rows in the direction of air flow, and wherein the heat transfer tubes are close to two refrigerant inlets / outlets. The first heat exchanger is a fin tube type arranged in a row on the upstream side of the air flow, and the heat transfer tube through which a refrigerant flows inside at right angles through a large number of parallel plate-shaped fins is formed by air. The heat transfer tubes that are arranged in a plurality of rows in the flow direction of the two refrigerants and that are close to the one of the refrigerant inlets and outlets are arranged in a row on the upstream side of the air flow and that are close to the other refrigerants. A fin tube-shaped second heat exchanger in which the heat transfer tubes are arranged in a row on the downstream side of the air flow; an inlet / outlet of one of the two refrigerant inlets / outlets of the first heat exchanger; Rows upstream of heat exchanger airflow The first heat exchange is constituted by a refrigerant throttle mechanism having a state in which the flow path resistance of the refrigerant is high and a state in which the flow path resistance of the refrigerant is low, which is provided in the middle of the connection pipe connecting the arranged inlet and outlet of the refrigerant. A heat exchanger unit in which the first heat exchanger and the second heat exchanger are arranged such that a heat exchanger and the second heat exchanger do not overlap in the direction of air flow. 9. When the refrigerant flows from the inlet / outlet of the refrigerant on the side of the refrigerant restricting mechanism to the inlet / outlet of the refrigerant on the side of the refrigerant restricting mechanism, the first heat exchanger converts the refrigerant into and out of the refrigerant on the side of the anti-refrigerant restrictor. After flowing in from the refrigerant in the same direction as the air flow,
The heat exchanger unit according to claim 8, wherein the heat transfer tube path is configured such that the refrigerant flows in a direction facing the air flow and flows out of the refrigerant inlet / outlet on the refrigerant throttle mechanism side. 10. The first heat exchanger has two heat exchangers in the air flow direction.
When the refrigerant flows from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism to the inlet / outlet of the refrigerant on the side of the refrigerant throttle mechanism, the refrigerant becomes an anti-refrigerant. The refrigerant flows in from the inlet / outlet of the throttle mechanism side and is divided into two heat transfer tube paths. In each of the heat transfer tube paths,
First, after continuously passing a predetermined number of heat transfer tubes in a row on the upstream side of the air flow, and then continuously passing through a plurality of heat transfer tubes in a row on the downstream side of the air flow. 9. The air conditioner according to claim 8, wherein the heat exchanger continuously passes through the remaining heat transfer tubes in the row on the upstream side of the air flow, merges and flows out from the refrigerant inlet / outlet on the refrigerant throttle mechanism side. A heat exchanger unit as described. 11. The first heat exchanger includes two heat exchangers in the air flow direction.
With two rows of heat transfer tubes, two heat transfer tube paths are configured in parallel, and the heat transfer tubes near the refrigerant inlet / outlet on the refrigerant throttle mechanism side are located below the heat transfer tubes near the refrigerant inlet / outlet on the anti-refrigerant throttle mechanism side. One of the two heat transfer tube paths, which are located in stages and are formed in parallel, is formed from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism to the upper end of the heat exchanger. To the lower row of the heat exchanger to the lower end of the heat exchanger and to the vicinity of the center of the heat exchanger, and further to the upper row of the air flow near the center of the heat exchanger and to the lower stream of the heat exchanger toward the lower end of the heat exchanger. The other of the two heat transfer tube paths formed in parallel to the refrigerant inlet and outlet on the throttle mechanism side is formed from the refrigerant inlet and outlet on the anti-refrigerant throttle mechanism side to the heat exchanger lower end and near the center of the heat exchanger. Air flow near the center of the heat exchanger. Of the refrigerant on the side of the refrigerant throttle mechanism toward the upper end of the heat exchanger, moving to the row on the upstream side of the air flow near the lower end of the heat exchanger. 9. The heat exchanger unit according to claim 8, wherein the heat exchanger unit is formed up to the entrance. 12. The heat exchanger according to claim 1, wherein the first heat exchanger is provided in the air flow direction.
A main first heat exchanger having a row of heat transfer tubes and two heat transfer tube paths arranged in parallel, and a flow of air having a row of heat transfer tubes in the direction of air flow, which is higher than that of the main first heat exchanger. The auxiliary first heat exchanger having a short length in a step direction substantially perpendicular to the direction, and when the refrigerant flows from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism to the inlet / outlet of the refrigerant on the side of the refrigerant throttle mechanism, The auxiliary first heat exchanger flows into the auxiliary first heat exchanger from the inlet / outlet of the refrigerant on the side of the anti-refrigerant throttle mechanism and continuously passes through a plurality of heat transfer tubes of the auxiliary first heat exchanger. Leaked from
The heat is divided into two heat transfer tube paths and flows into the main first heat exchanger. In each of the heat transfer tube paths, first, a predetermined number of heat transfer tubes in a row on the upstream side of the air flow are continuously arranged. After passing successively through the plurality of heat transfer tubes in the row on the downstream side of the air flow, and continuously passing through the remaining heat transfer tubes in the row on the upstream side of the air flow. The auxiliary first heat exchanger is configured to flow out of an inlet / outlet of the refrigerant on the side of the refrigerant throttle mechanism, and the auxiliary first heat exchanger is provided on the upstream side of the air flow of the main first heat exchanger, and the refrigerant throttle mechanism is provided. 9. The heat exchanger unit according to claim 8, wherein the heat exchanger unit is arranged so as not to be located on the upstream side of the air flow of the heat transfer tube of the main first heat exchanger that is close to the inlet / outlet of the refrigerant on the side. 13. The heat exchanger according to claim 1, wherein the first heat exchanger is provided in the air flow direction.
A main first heat exchanger having a row of heat transfer tubes and two heat transfer tube paths arranged in parallel, and a flow of air having a row of heat transfer tubes in the direction of air flow, which is higher than that of the main first heat exchanger. The auxiliary first heat exchanger having a short length in a step direction substantially perpendicular to the direction, and a heat transfer tube of the main first heat exchanger that is close to the refrigerant inlet / outlet on the side of the refrigerant throttle mechanism, The heat transfer pipe path of the auxiliary first heat exchanger is located near the lower end of the auxiliary first heat exchanger. Two heat transfer tubes formed from the refrigerant inlet / outlet on the anti-refrigerant throttle mechanism side to the heat exchanger upper end in the vicinity of the heat exchanger upper end, and arranged in parallel with the main first heat exchanger. One of the paths is from a branch portion connected to a heat transfer tube near the upper end of the heat exchanger of the auxiliary first heat exchanger. Formed toward the upper end of the heat exchanger, further moved to the row on the downstream side of the air flow near the upper end of the heat exchanger, and formed near the center of the heat exchanger toward the lower end of the heat exchanger, and further near the center of the heat exchanger It moves to a row on the upstream side of the flow of air, and is formed toward the lower end of the heat exchanger up to the inlet and outlet of the refrigerant on the side of the refrigerant throttle mechanism, and the two heat transfer tube paths configured in parallel with the main first heat exchanger The other is formed from the branching portion connected to the heat transfer tube near the upper end of the heat exchanger of the auxiliary first heat exchanger to the center of the heat exchanger toward the lower end of the heat exchanger, and further, the air is formed near the center of the heat exchanger. To the lower row of the heat exchanger, and form toward the lower end of the heat exchanger, and further to the row closer to the upper stream of the air flow near the lower end of the heat exchanger, on the side of the refrigerant throttle mechanism toward the upper end of the heat exchanger. It is characterized in that it is configured to form up to the inlet and outlet of the refrigerant The heat exchanger unit according to claim 8, wherein. 14. A row of heat transfer tubes in a row on the upstream side of the air flow and a row of heat transfer tubes on the downstream side of the air flow near the inlet / outlet of the refrigerant on the refrigerant throttle mechanism side of the first heat exchanger. Between,
14. The heat exchanger unit according to claim 8, wherein a cut for eliminating heat conduction between the heat transfer tube rows is provided in the plate-like fin. 15. The heat exchanger unit according to claim 8, wherein the refrigerant throttle mechanism includes a control valve having a fully opened state and a slightly opened state. 16. The heat pump according to claim 8, wherein the refrigerant throttle mechanism includes a capillary tube and a two-way valve provided in a bypass that bypasses the capillary tube. Exchanger unit.