JP3375247B2 - Air conditioner - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner, and more particularly, to an arrangement configuration of an indoor heat exchanger that constitutes a refrigeration cycle and a connection with a flow divider connected to a flow path of the indoor heat exchanger. Regarding the improvement of the configuration.

[0002]

2. Description of the Related Art In an air conditioner having a refrigeration cycle circuit for air conditioning such as cooling operation and heating operation, a separation type air conditioner composed of an outdoor unit and an indoor unit is often used.

In the indoor unit, an indoor heat exchanger and a blower are housed in the unit body, the refrigerant is evaporated in the indoor heat exchanger during the cooling operation, and the refrigerant is condensed during the heating operation.

The indoor heat exchanger is provided with a plurality of flow paths (passages) for conducting the refrigerant. This flow path connects a U-shaped bent heat exchange pipe that penetrates through a large number of fins that are arranged in parallel at a predetermined interval and the open ends of the heat exchange pipes that project from the fins. U-bend section.

A diverter is connected to the refrigerant inflow side of the flow passage during the cooling operation, and the refrigerant introduced into the diverter is distributed and guided to the plurality of flow passages. There is.

The above-mentioned flow diverter usually uses a so-called three-way bend pipe connection tool, and is composed of a bend portion bent in an L shape and a bend portion bent in a U shape. The open end of the U-shaped bend portion is connected to approximately the center of the U-shaped bend portion. Also, the open ends of the bends are oriented in the same direction.

In connecting such a flow divider to the above-mentioned flow path, the mounting posture differs depending on the arrangement configuration of the indoor heat exchanger. That is, in order to make the height dimension of the air conditioner body accommodating the indoor heat exchanger as small as possible, the heat exchangers are arranged to be inclined. Obviously, the shunt is also installed diagonally.

However, in order to reduce the space for accommodating the pipes in the main body of the air conditioner, the flow divider is connected to almost the center of the indoor heat exchanger. The refrigerant introduced into the indoor heat exchanger from this flow divider is vertically divided from the central portion of the heat exchanger.

[0009]

By the way, in the dehumidifying operation, the cooling cycle is performed, the expansion mechanism is excessively throttled (hereinafter referred to as over-throttlement), and the operating frequency of the compressor is extremely lowered. An operation method for reducing the flow rate has been proposed.

In this operating system, the liquid refrigerant introduced into the indoor heat exchanger is almost completely evaporated immediately after being introduced into the inlet of the flow path, becomes a dry pipe, and has almost no heat exchange action. The heat-exchanged air is dehumidified by removing moisture while being conducted through the inlet of the flow passage, but the heat-exchanged air conducted through the flow passage on the latter half side is not cooled and dehumidified.

After all, the dehumidification can be continued by blowing out the heat-exchanged air that is in a very cooled state but is sufficiently dehumidified, and the ideal dehumidification is performed so that the people in the living area do not feel the cold wind. .

However, as described above, when the flow divider on the refrigerant introduction side of the indoor heat exchanger is connected to the substantially central portion of the heat exchanger, the refrigerant split in the flow divider during the dehumidifying operation is fed to the indoor heat exchanger. Heat is exchanged immediately after being guided.

The heat-exchanged air that has passed through this portion has its moisture removed, but immediately after that, it passes through the latter half of the flow path. The heat-exchanged air still contains dehumidified water, and the water is dried and re-evaporates in contact with the latter half of the piped flow path.

That is, the heat exchange air blown out from the blowout port of the main body of the air conditioner contains the water once removed again and the humidity rises. As described above, depending on the setting of the connection position of the flow divider, there is a problem that the dehumidifying characteristics are inefficient.

The present invention has been made based on the above circumstances, and an object thereof is to specify an arrangement configuration of an indoor heat exchanger and a flow divider connected to a flow path of the indoor heat exchanger. Thus, it is intended to provide an air conditioner that ensures discharge processing of water condensed in the indoor heat exchanger, improves heat exchange efficiency, and enables stable dehumidifying operation.

[0016]

In order to satisfy the above-mentioned object, the air conditioner of the present invention has a front side in an air conditioner body.
Heat exchanger, rear heat exchanger and auxiliary heat exchange along the upper surface
A side-by-side indoor V-shaped indoor heat exchanger is placed as an auxiliary
From the heat exchanger to the rear heat exchanger or the front heat exchanger
Multiple refrigerant channels are connected to each channel of the auxiliary heat exchanger
A shunt equipped with multiple shunts
The refrigerant is split and guided to each flow path, and it is located below the front heat exchanger.
On the lower part of the front drain pan, rear heat exchanger and auxiliary heat exchanger
A rear drain pan is installed at each position and each flow in the auxiliary heat exchanger is
The shunt section of the shunt is
Connect so that there is a head in the force direction, and the gravity direction of the shunt.
Connect the bottom shunt to the flow path closest to the rear drain pan.
This flow path is connected to the rear side heat via the lower side of the auxiliary heat exchanger.
Lead to the bottom of the exchanger.

[0017]

Further , the indoor heat exchanger performs a cooling cycle during dehumidifying operation, and an expansion mechanism constituting the refrigeration cycle is used to over-throttle the refrigerant so that evaporation of the refrigerant ends in a part of the indoor heat exchanger. A controlled refrigerant is introduced.

[0019] Then, the expansion mechanism is an electronic expansion valve, the electronic expansion valve, the control device, is over aperture control during dehumidifying operation.

Further , in the indoor heat exchanger, a temperature sensor for detecting freezing of the indoor heat exchanger during the cooling cycle is attached to the lowermost flow path in the gravity direction .

[0021]

[0022]

[0023] adopting a means for solving the problems of the above-mentioned
By specifying the arrangement of the indoor heat exchanger and the flow divider,
During the dehumidifying operation, a large amount of the liquid refrigerant component subjected to the action of gravity in the flow divider is guided to the lower flow path in the gravity direction and does not divide evenly. By utilizing such a diversion directivity, intentionally stable diversion characteristics are obtained.

Moisture contained in the heat exchange air is dropped into the drain pan immediately after it is heat-exchanged with the indoor heat exchanger and condensed. That is, since the condensed water does not come into contact with the dry pipe-shaped flow path, it is discharged without being re-evaporated on the way, so that an efficient dehumidifying action is performed.

[0025]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. As shown in FIG. 1, an indoor unit of the air conditioner is configured. The unit body 1, which is the air conditioner body, includes a front panel 2 and a rear plate (not shown). On the front side of the front panel 2, the front suction port 2
The grill 4 provided with a is fitted, and the grill 5 provided with the upper suction port 2b is fitted on the upper surface side. An outlet (not shown) is opened in the lower part of the front surface of the unit body 1.

An indoor heat exchanger 7 and a blower 8 are arranged in the unit body 1. The indoor heat exchanger 7 includes a front heat exchanger 7A at a position facing the front suction port 2a, a rear heat exchanger 7B at a position facing the upper suction port 2b, and upper surfaces of the rear heat exchanger 7B. The auxiliary heat exchanger 7C is arranged along the section, and is formed in a substantially inverted V shape in a side view.

The blower 8 is arranged at an internal position where the indoor heat exchanger 7 is used as an umbrella, that is, at a position where it is covered with a front heat exchanger 7A and a rear heat exchanger 7B having an inverted V shape. Further, the cross-flow fan 9 has the same axial dimension as the width dimension of the indoor heat exchanger 7, and a fan motor (not shown here) connected to one side portion of the cross-flow fan via a rotary shaft. .

In the unit body 1, a cross flow fan 9 is installed.
The front suction port 2a and the upper suction port 2
An air passage 10 is formed that guides the air in the air-conditioned room sucked from b to the indoor heat exchanger 7 and further guides it from the cross flow fan 9 to the outlet.

Further, the rear heat exchanger 7B and the auxiliary heat exchanger 7
A rear drain pan 11 is arranged below the lower end of C. The front drain pan is also arranged at a lower portion of the lower end portion (not shown) of the front heat exchanger 7A.

Next, the front side heat exchanger 7A, the rear side heat exchanger 7B and the auxiliary heat exchanger 7C constituting the indoor heat exchanger 7 will be described in detail. These heat exchangers 7A to 7C
Are all composed of a large number of fins F arranged side by side at predetermined intervals and a heat exchange pipe P penetrating the fins. The heat exchange pipe P is bent into a substantially U-shape at one end, and the U-shape and the opening end project from the fin end plate.

The U-bend portion B connects the open ends of the adjacent heat exchange pipes P, and the heat exchange pipes P and the U-bend portion B conduct the refrigerant.
S is formed. This flow path S has front and rear heat exchangers 7
A, 7B and auxiliary heat exchanger 7C are respectively provided in plurality.

As shown in FIG. 2, the auxiliary heat exchanger 7C
And the inlet side refrigerant pipe 14 is configured. That is, as the auxiliary heat exchanger 7C, a large number of fins F arranged in parallel at a predetermined interval, a U-shaped heat exchange pipe P penetrating the fins, and open end portions of adjacent heat exchange pipes. As described above, the U-bend portion B (not shown here) is in communication with each other.

Two sets of the heat exchange pipes P are provided, and the U-shaped portion a and the pair of open end portions b, b are aligned with each other on the same side end portion of the auxiliary heat exchanger 7C. Mutual heat exchange pipe P
The flow dividers 13b and 13b of the flow divider 13 are connected to the adjacent open ends b and b.

To the base end portion 13a of the flow divider 13, one open end portion of the U-shaped inlet side refrigerant pipe 14 is connected. The inlet-side refrigerant pipe 14 is detachably attached and fixed to the auxiliary heat exchanger 7C via the pipe fixture 15.

FIG. 3 shows the details of the flow passage S configuration in the front and rear heat exchangers 7A and 7B and the auxiliary heat exchanger 7C that constitute the indoor heat exchanger 7. The indoor heat exchanger 7 as a whole is first guided by the diversion from the diversion device 13 in two directions.
And a second channel B.

The first flow path A, after being branched from the flow distributor 13, is guided to the upper side of the auxiliary heat exchanger 7C, and from the flow portion 7-1 through the jumping pipe 16 to the middle of the front heat exchanger 7A. Guided to the department.

Then, from the flow portion 6-1 is temporarily lowered to the flow portion 4-1 via the flow portion 5-1 at the upper end of the rear heat exchanger 7B. It rises again from the distribution part 3-1 and is guided again to the front heat exchanger side 7A via the distribution part 2-1 and after the outlet 0-1 via the distribution part 1-1, the second flow path. It joins B.

The second flow path B, after being branched from the flow distributor 13, is guided to the lower side of the auxiliary heat exchanger 7C and from the flow passage 7-2 to the lowermost part of the rear heat exchanger 7B. Then, after passing through the distribution portion 6-2, which is the lowermost portion on the front surface side, it rises and is guided to the middle portion of the front heat exchanger 7A via the jumping pipe 17.

From here, it is guided to the lowermost distribution site 3-2 through the distribution parts 5-2 and 4-2 on the lower side,
This time, it goes up to the upper side and the distribution part 2-2 and the distribution part 1
It is designed to join the first flow path A after the outlet section 0-2 via -2.

The auxiliary heat exchanger 7C and the rear heat exchanger 7B are arranged in a state of being inclined by a predetermined angle. Therefore, each of the flow paths A in the heat exchangers 7C and 7B,
B will be provided in multiple stages in the direction of gravity.

The flow divider 13 connected to the auxiliary heat exchanger 7C is connected to the heat exchange pipe in a state where the flow dividing portions 13b and 13b are inclined, and the connecting portions have a drop in the direction of gravity.

The lowermost flow dividing portion 13b of the flow divider 13 in the direction of gravity is connected to the second flow passage B, and one of the heat exchange pipes P constituting the flow passage B closest to the rear drain pan 11 is formed. Connected to the open end.

A Ti sensor 18 which is an inlet side temperature sensor is provided in the inlet side pipe 14 which is the refrigerant introduction side of the flow divider 13.
On the other hand, a Tc sensor 19 which is an outlet side temperature sensor is attached to the lower front surface of the front heat exchanger 7A. The attachment site of the Tc sensor 19 is the second flow path B.
Corresponds to the middle part.

On the other hand, an outdoor heat exchanger 22 is connected to the discharge part of the compressor 20 via a four-way valve 21, and an electronic expansion valve 23 which is an expansion mechanism is connected. This electronic expansion valve 23
The opening degree changes continuously according to the number of input drive pulses.

The electronic expansion valve 23 is connected to the auxiliary heat exchanger 7C constituting the indoor heat exchanger 7 via the flow divider 13. The flow path S configuration of the refrigerant in the indoor heat exchanger 7 is as described above. The merging portion of the flow path S is connected to the suction portion of the compressor 20 via the four-way valve 21. In this way, a heat pump type refrigeration cycle is configured.

The Ti sensor 18 mounted on the refrigerant introduction side of the flow divider 13 and the Tc sensor 19 mounted along the second flow path B of the front heat exchanger 7A are control units 24 which are control devices for each other. Connected to.

The control unit 24 includes the inverter circuit 2
5. The electronic expansion valve 23, the four-way valve 21, and the compressor 20
Are connected. In addition, a commercial AC power supply 26, a speed control circuit of a compressor (not shown), a fan motor, and the like are connected to the control unit 24.

The air conditioner thus configured can perform both cooling operation and heating operation depending on the switching direction of the four-way valve 21. When the dehumidifying operation instruction is issued to the control unit 24, the control unit switches the four-way valve 21 in the same direction as the cooling cycle and controls the compressor 20 to operate at a low frequency. Then, the electronic expansion valve 23 is controlled to be in an over-throttled state, and is throttled so that the flow rate of the refrigerant guided to the indoor heat exchanger 7 becomes extremely small.

The refrigerant is guided to the flow divider 13 and then to the auxiliary heat exchanger 7C constituting the indoor heat exchanger 7, and the first flow path A is supplied.
And is divided into the second flow path B. As shown in FIG. 4, the auxiliary heat exchanger 7C is arranged in a state of being inclined at a predetermined angle, and is provided with a plurality of stages of flow paths A and B in the gravity direction. The flow dividing parts 13b, 13b of the flow divider 13 are connected to one open end of the heat exchange pipe P in a tilted state, and the connecting parts have a drop in the gravity direction.

Therefore, the liquid refrigerant affected by gravity is guided to the lower flow dividing portion 13b more than to the upper flow dividing portion 13b. That is, under the above-described conditions, the flow distributor 13 has non-uniform flow distribution characteristics, and the liquid refrigerant is guided to the second flow passage B more than to the first flow passage A. By utilizing such a diversion directivity, a stable diversion can be intentionally obtained.

In each of the flow paths A and B, the liquid refrigerant under the influence of gravity is guided to the lower side, and the evaporated refrigerant having a low specific gravity is guided to the lower side. The ratio of the liquid refrigerant to the evaporated refrigerant differs depending on the level difference of the flow path in the gravity direction.

That is, in the first flow path A, the evaporated refrigerant is mostly occupied on the upper side. On the connection side with the flow divider 13 on the lower side, the ratio of the evaporated refrigerant is much larger than that of the liquid refrigerant.

In the second flow path B, the ratio of the evaporative refrigerant to the liquid refrigerant is substantially equal on the connection side with the flow divider 13 on the upper side, and the ratio of the liquid refrigerant is lower than the ratio of the evaporative refrigerant on the lower side. Will also be much larger.

The heat exchange action with the heat exchange air is originally performed in the flow path through which the liquid refrigerant is conducted. Here, the first channel A
The small amount of the liquid refrigerant introduced into the second flow passage B has a small amount of heat exchange action with the heat exchange air, whereas the small amount of the liquid refrigerant introduced into the second flow path B has a sufficient heat exchange action with the heat exchange air.

Therefore, while the first flow path A condenses a small amount of water contained in the heat exchange air,
In the second flow path B, more water will be condensed from the heat exchange air.

In particular, the second flow path B is formed in a position in the vicinity of the rear drain pan 11 from the connection portion with the flow divider 13, and the drain water which is condensed water is immediately dropped to the rear drain pan 11. To do.

After all, the water condensed in the auxiliary heat exchanger 7C is discharged immediately after it becomes drain water, and is not re-evaporated during this process and mixed with the heat exchange air. That is, unlike the conventional case, the moisture once removed does not re-evaporate into the heat exchange air on the downstream side, and the dehumidified heat exchange air is blown out as it is.

Since the electronic expansion valve 13 is controlled to be excessively throttled, the amount of the refrigerant introduced into the indoor heat exchanger 7 is small and the amount of the liquid refrigerant introduced into the second flow path is also small. All the liquid refrigerant evaporates almost completely in the second flow path B near the rear drain pan 11, and the dehumidifying action is performed only in this portion, so that an efficient dehumidifying characteristic is obtained.

When the electronic expansion valve 13 is overthrottled in the cooling cycle to perform the dehumidifying operation as described above, the opening degree of the electronic expansion valve 13 is set such that the temperature at which the heat exchange air is blown out is higher than the dew point temperature in the air. It is better to set it higher.

That is, the Tc sensor 19 and the Ti sensor 1
Reference numeral 8 detects the heat exchanger outlet side temperature and the heat exchanger inlet side temperature, which are the respective attachment parts, and sends the detection signals to the control unit 24.

In the controller 24, the superheat amount S
H (n) is calculated from the Tc (n) -Ti (n-1) equation, and ΔSH is calculated from the SH (n) -SH (n-1) equation. Here, SH0 is a target SH stored and set in the control unit 24 in advance.
Then, the required amount ΔPLS of the opening degree of the electronic expansion valve 23 is calculated from the fuzzy table.

Then, the newly set absolute value PLS
(n) is obtained from the sum of the present opening PLS (n-1) and the required opening amount ΔPLS. PLS (n) = PLS (n-1) + ΔPLS As a result, the heat exchange pipe P forming the flow path S is formed according to the change in the refrigeration cycle throttle amount with respect to the electronic expansion valve 23.
While the wet part becomes small, the dry part occupies most of it.

That is, the blowing temperature of the heat exchange air blown from the indoor unit rises and becomes higher than the dew point temperature in the air, so that dew condensation in the blower path 10 such as the cross flow fan 9 is prevented. Therefore, the drain water is not blown out to the air-conditioned room and is not scattered, and the comfortable air conditioning is maintained.

Further, as described above, the second flow path B
Is larger than the flow rate of the refrigerant introduced through the first flow path A. From this, the second flow path B freezes before the first flow path A in a state where the room temperature is lowered during the dehumidifying operation and the cooling operation.

Particularly, the Tc temperature sensor 19 is connected to the second flow path B.
Since the temperature of the indoor heat exchanger 7 is detected in the middle part of the indoor heat exchanger 7, the temperature of the indoor heat exchanger 7 is prevented by immediately determining the freezing if the above-mentioned freezing phenomenon occurs.

That is, in the indoor heat exchanger 7 having a plurality of flow paths A and B, the flow divider 1 connected to these flow paths 1
It is possible to prevent delay in freezing detection by utilizing the diversion directivity in which the diversion characteristics of No. 3 cause variations.

Further, in the indoor heat exchanger 7 formed in the inverted V shape, in the auxiliary heat exchanger 7C to which the flow divider 13 is connected and the refrigerant is first introduced, the heat exchange air guided to the blower path 10 The wind speed distribution is at a position slower than that of the front heat exchanger 7A.

Therefore, the auxiliary heat exchanger 7C is a so-called wet portion in which the degree of refrigerant evaporation is lower than that of the front heat exchanger 7A. With respect to the heat exchange air, the contained water is sufficiently condensed, and an efficient dehumidifying property can be obtained.

A flow path structure as shown in FIG. 5 may be adopted. Here, the first flow path Aa is diverted from the flow diverter 13, and then the circulation portion 6-1A on the upper side of the auxiliary heat exchanger 7C.
And is immediately guided to the lower part of the front heat exchanger 7A via the jumping pipe 30.

The flow passage portion 5-at the bottom of the heat exchanger 7A
1A is guided to a distribution site 4-1A diagonally crossing upward, and from there, a distribution site 3-1A and a distribution site 2-1A.
Via another jumping pipe 31 to the lower side again. Ascend again to exit 0-from the distribution site 1-1A
It is guided to 1A and merges with the second flow path Bb.

The second flow path Bb, after being branched from the flow distributor 13, is guided to the lower side of the auxiliary heat exchanger 7C and from the flow portion 7-2A to the lowermost part of the rear heat exchanger 7B. Then, after passing through the circulation portion 6-2A, it is guided to the upper portion of the front heat exchanger 7A via the jumping pipe 32.

From here, it is guided to the rear heat exchanger 7B via the circulation portion 5-2A, and further on the lower side circulation portion 4-2.
Distribution site 3-2 diagonal from A and distribution site 2 on the front side 2-
2A to be guided to the front heat exchanger 7A again, to be guided from the flow portion 1-2A to the outlet portion 0-2A to the first flow path Aa.
It is supposed to join.

With such first and second flow passages Aa and Bb, the refrigerant diverted from the flow divider 13 to each flow passage is immediately and most immediately in the front drain pan 33 and the rear drain pan 11, respectively. Heat is exchanged by being guided to a nearby site.

That is, as described above, the second refrigerant for guiding the refrigerant to the portion closest to the rear drain pan 11 and exchanging heat therewith.
In the flow path Bb, the condensed drain water is immediately discharged to prevent re-evaporation of water in the heat exchange air on the downstream side.

Also in the first flow path Aa for guiding the heat to the portion closest to the front drain pan 33 for heat exchange,
Immediately discharge the condensed drain water to prevent re-evaporation of water in the heat exchange air on the downstream side. Therefore, the total dehumidification characteristics can be further improved.

An indoor heat exchanger configuration as shown in FIG. 6 may be used. In the case of FIG. 3A, the indoor heat exchanger 40 is
There is a notch in the middle of the up and down direction, and it is divided into an upper heat exchanger 40A and a lower heat exchanger 40B, and is bent and formed in a dogleg shape.

The flow divider 13 is attached to the lowermost end of the lower side heat exchanger 40B to divide the refrigerant in the vertical direction. The flow path 13 includes a first flow path 41a that guides the refrigerant drawn to the upper side and a second flow path 41b that guides the refrigerant drawn to the lower side, and these flow paths are the upper heat exchanger. Merge on the upper back side of 40A.

Each flow path 41 of such an indoor heat exchanger 40
a and 41b are provided in a plurality of stages in the gravity direction, are connected to the flow dividing portion of the flow divider 13 with a head in the gravity direction, and the flow dividing portion at the bottom of the flow divider in the gravity direction is connected to the drain pan 42. Since it is connected to the closest flow path part, the same effects as the above-mentioned effects can be obtained.

In the case of FIG. 7B, the indoor heat exchanger 50 is
It is divided into a front heat exchanger 50A and a rear heat exchanger 50B. The heat exchangers are inclined to some extent, and the rear heat exchanger 50B is arranged on the upper back surface side of the front heat exchanger 50A.

Needless to say, front and rear drain pans 51 and 52 are arranged below the front and rear heat exchangers 50A and 50B, respectively. The flow divider 13 is the rear heat exchanger 5
It is attached to the back side of OB. The first and second flow paths 53a and 53b connected to the lead-out portion are connected to the rear heat exchanger 50.
From the front side of B, the jumping pipes 54a and 54b are connected to the front side midway part of the front side heat exchanger 50A, and from there, it is divided in the vertical direction again and joins at the outlet side on the back side of this heat exchanger. There is.

Such an indoor heat exchanger 50 and each flow path 5
3a and 53b are provided in a plurality of stages in the direction of gravity and are connected to the flow dividing portion of the flow divider 13 with a drop in the direction of gravity, and in particular, the flow divider 1 for the second flow path 53b.
Since the lowermost flow dividing portion of the gravity direction 3 is connected to the flow path portion closest to the drain pan 52, the same operational effect as described above can be obtained.

An indoor heat exchanger configuration as shown in FIG. 7C may be used. This is an integral heat exchanger 60 that is curved. Therefore, all the portions of the unit body 61 facing the indoor heat exchanger 60 serve as the suction port 62.

The flow divider 13 is attached to the upper surface of the right end portion in the figure. The first flow path 63a led out from the flow divider to the upper side is connected to the left side portion via a jumping pipe, and further from here to the vicinity of the flow divider, returns to the position near the jumping pipe, and the lower surface portion Is connected to the outlet of the.

The second flow path 63b branched from the flow divider 13 to the lower side makes a U-turn at the lower right end of the indoor heat exchanger 60, and is connected to the left side portion from here through a jumping pipe. Further, the lower end portion on the left side is U-turned and then connected to the outlet portion.

Here again, the connection between the flow dividing portion of the flow divider 13 and the flow passage is arranged so as to have a drop in the gravity direction, and in particular, the flow dividing portion at the lowermost portion of the flow divider 13 in the gravity direction with respect to the second flow passage 63b is arranged. Since it is connected to the flow path portion closest to the drain pan 64, the same operational effect can be obtained.

[0086]

As described above, according to the present invention, the front heat
Side view of the exchanger, rear heat exchanger and auxiliary heat exchanger
In a letter-shaped indoor heat exchanger, each flow path in the auxiliary heat exchanger is provided in multiple stages in the direction of gravity, and the flow dividing parts of the flow divider are connected so as to have a drop in the direction of gravity. The flow dividing part is connected to the flow path part closest to the rear drain pan ,
This flow path is through the lower side of the auxiliary heat exchanger and the rear heat exchanger
Guided to the bottom.

[0087]

Furthermore , during the dehumidifying operation, the indoor heat exchanger is
The expansion mechanism that constitutes the refrigeration cycle guides the refrigerant that has been over-throttled so that the evaporation of the refrigerant ends in a part of the indoor heat exchanger.

Furthermore , an electronic expansion valve is used as the expansion mechanism, and the over-throttle control is performed by the control device during the dehumidifying operation.
Therefore, according to the present invention , it is condensed from the indoor heat exchanger by specifying the arrangement configuration of the indoor heat exchanger and the flow divider connected to the flow path of the auxiliary heat exchanger in the indoor heat exchanger. It is possible to ensure the treatment of water, improve heat exchange efficiency, and perform stable dehumidifying operation.

[0090]

[0091]

[0092]

[0093]

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view showing an embodiment of the present invention, in which an indoor unit that is an air conditioner is partially omitted.

FIG. 2 is a front view showing a form of an auxiliary heat exchanger and a connection pipe that constitute the indoor heat exchanger according to the same embodiment.

FIG. 3 is a view for explaining a refrigeration cycle configuration, an electric circuit, and a flow channel configuration of an indoor heat exchanger according to the same embodiment.

FIG. 4A is a diagram illustrating a refrigerant state and a drain water generation state in the auxiliary heat exchanger according to the embodiment.
(B) is a figure explaining the refrigerant state in a flow path.

FIG. 5 is a diagram illustrating a flow path configuration of an indoor heat exchanger according to another embodiment.

FIG. 6 shows still another embodiment, in which (A) is a schematic vertical sectional view of an indoor unit. (B) is a schematic vertical sectional view of the indoor unit. (C) is a schematic longitudinal sectional view in which a part of the indoor unit is omitted.

[Explanation of symbols]

1 ... Air conditioner body (unit body), F ... Fin, A
... 1st flow path, B ... 2nd flow path, 7 ... Indoor heat exchanger, 1
3 ... Flow divider, 13b ... Flow dividing part, P ... Heat exchange pipe, B ...
U bend part, 23 ... Expansion mechanism (electronic expansion valve), 19 ... Temperature sensor (Tc sensor), 11 ... Rear drain pan, 7A ...
Front heat exchanger, 7B ... Rear heat exchanger, 7C ... Auxiliary heat exchanger.

─────────────────────────────────────────────────── --- Continuation of the front page (56) References JP-A-5-126355 (JP, A) JP-A-7-120077 (JP, A) JP-A-8-49913 (JP, A) JP-A-9- 42706 (JP, A) Actual development 3-77167 (JP, U) Actual development 2-131170 (JP, U) Actual development 2-34920 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F24F 1/00 391 F25B 39/02 F24F 1/00 451 F24B 1/00 303 F24F 11/02 102

Claims (3)

(57) [Claims] Claim: What is claimed is: 1. An air conditioner main body, a front heat exchanger, and a rear heat exchanger arranged inside the air conditioner main body.
The side heat exchanger and the supplement along the upper surface of the rear side heat exchanger.
From the auxiliary heat exchanger, it is formed in an almost inverted V shape in side view,
If the indoor heat exchanger that constitutes the refrigeration cycle and the auxiliary heat exchanger of this indoor heat exchanger
It is installed over the front heat exchanger,
Number of flow passages, a plurality of flow dividing portions connected to each flow passage of the auxiliary heat exchanger, a flow divider for guiding the refrigerant introduced during cooling operation to each flow passage, and the indoor heat exchanger Located in the lower part of the front heat exchanger of
That before the drain pan and is disposed <br/> lower portion of the auxiliary heat exchanger and the rear heat exchanger, the air conditioner comprising a drain pan after receiving drain water dropping from the heat exchanger, the auxiliary Each flow path in the heat exchanger is provided with a plurality of stages in the gravity direction, and the flow dividing parts of the flow divider are connected so as to have a drop in the gravity direction, and the flow dividing part at the bottom of the flow divider in the gravity direction is , A flow path connected to the flow path portion closest to the rear drain pan and connected to the flow dividing section at the bottom of the flow divider in the gravity direction
Is the bottom of the rear heat exchanger through the lower side of the auxiliary heat exchanger
An air conditioner characterized by being configured to be guided to . 2. The indoor heat exchanger performs a cooling cycle during a dehumidifying operation, and an expansion mechanism constituting the refrigeration cycle is used to over-throttle the refrigerant so that evaporation of the refrigerant ends in a part of the indoor heat exchanger. The controlled refrigerant is introduced , the expansion mechanism is an electronic expansion valve, and the electronic expansion valve is controlled.
The air conditioner according to claim 1 , wherein an over-throttle control is performed during the dehumidifying operation by the control device . Wherein said indoor heat exchanger, the bottom of the channel in the direction of gravity, characterized in that the temperature sensor for detecting the freezing of the indoor heat exchanger during a cooling cycle is installed 請
Motomeko 1 and the air conditioner according to claim 2.