JP2003232584A - Air conditioner - Google Patents

Abstract

(57) [Summary] [Problem] A gas-liquid two-phase refrigerant cannot be continuously and effectively supplied to a throttle portion, and the refrigerant flow noise increases. SOLUTION: In an air conditioner provided with a refrigeration cycle to which a compressor, an outdoor heat exchanger, a first flow control device, a first heat exchanger, a second flow control device, and a second indoor heat exchanger are connected, The two flow control devices include an inlet silencing space 19, an inlet-side foam metal 20 communicating with the refrigerant in the flow direction, an orifice 23
It has a constricted portion composed of the outlet-side foamed metal 25 and the outlet silencing space 27, and controls the temperature deviation between the set temperature and the current temperature or the humidity deviation between the set humidity and the current humidity to be within a predetermined value.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention comprises a throttle device suitable for controlling the flow of a refrigerant, a refrigerating cycle device suitable for controlling the flow of a two-phase refrigerant, and controllability of temperature and humidity during cooling or heating operation. The present invention relates to an air conditioner in which the refrigerant flow noise is reduced and the comfort against indoor temperature and humidity and noise is improved.

[0002]

2. Description of the Related Art In a conventional air conditioner, a variable capacity compressor such as an inverter is used to cope with a change in air conditioning load, and the rotation frequency of the compressor is controlled according to the size of the air conditioning load. . However, when the rotation of the compressor is reduced during cooling operation, the evaporation temperature also rises and the dehumidifying capacity of the evaporator decreases, or the evaporation temperature rises above the dew point temperature in the room, making it impossible to dehumidify. .

The following air conditioner has been devised as a means for improving the dehumidifying ability during the cooling low capacity operation. FIG. 13 is a refrigerant circuit diagram of a conventional air conditioner disclosed in, for example, Japanese Patent Laid-Open No. 11-51514, and FIG. 14 is a sectional view of a general throttle valve provided in FIG. In the figure, 1 is a compressor, 2 is a four-way valve, 3 is an outdoor heat exchanger,
Reference numeral 4 is a first flow rate control device, 5 is a first indoor heat exchanger, 6 is a second flow rate control device, and 7 is a second indoor heat exchanger, and these are sequentially connected by piping to form a refrigeration cycle. . Next, the operation of the conventional air conditioner will be described. In the cooling operation, the refrigerant exiting the compressor 1 passes through the four-way valve 2, is condensed and liquefied in the outdoor heat exchanger 3, and the two-way valve 12 of the first flow rate control device 4 is closed. The pressure is reduced at 11 and the gas is evaporated and vaporized in the indoor heat exchanger 5 and returns to the compressor 1 again via the four-way valve 2. In the heating operation, the refrigerant discharged from the compressor 1 passes through the four-way valve 2 contrary to the cooling operation, is condensed and liquefied in the indoor heat exchanger 5, and the two-way valve 12 of the first flow control device 4 is used.
Is closed, it is decompressed by the main expansion device 11 and evaporated to vaporize in the outdoor heat exchanger 3, and then returns to the compressor 1 via the four-way valve 2 again.

On the other hand, during the dehumidifying operation, the main expansion device 11 of the first flow rate control device 4 is closed and the two-way valve 12 is opened.
By controlling the flow rate of the refrigerant with the flow rate control valve 6, the first indoor heat exchanger 5 operates as a condenser, that is, a reheater, and the second indoor heat exchanger 7 operates as an evaporator, and the indoor air is the first indoor heat exchange. Since it is heated in the vessel 5, dehumidification operation with a small decrease in room temperature becomes possible.

[0005]

In the conventional air conditioner as described above, since a flow rate control valve having an orifice is usually used as the second flow rate control valve installed in the indoor unit, this orifice is used. The refrigerant flow noise generated when the refrigerant passed through was a factor that deteriorated the indoor environment. In particular, during the dehumidifying operation, the inlet of the second flow rate control valve becomes a gas-liquid two-phase refrigerant, which causes a problem that the refrigerant flow noise becomes loud.

As a measure for reducing the refrigerant flow noise of the second flow rate control valve during the dehumidifying operation, an orifice-like structure having a plurality of cut grooves and a valve body is provided in the flow rate control valve disclosed in Japanese Patent Laid-Open No. 11-51514. Some have a throttle channel. However, in this refrigerant flow noise reduction measure, the throttle portion is devised so as to continuously flow the gas-liquid two-phase refrigerant through a plurality of orifice-shaped flow passages, but the number of flow passages that can be arranged is limited. Therefore, there is a problem that it is not effective and the flow noise of the refrigerant becomes loud. As a result, additional measures such as providing a sound insulating material and a vibration damping material around the second flow rate control device are required, and there are problems such as an increase in cost, deterioration of installation property, and deterioration of recyclability.

On the other hand, in the flow rate control device used in the air conditioner disclosed in Japanese Unexamined Patent Publication No. 7-146032, as shown in the sectional view of FIG. Porous bodies 32 are provided as filters on the upstream and downstream sides. However, since the distance between the porous body 32 and the throttle portion is large, the gas-liquid two-phase refrigerant cannot be effectively supplied to the throttle portion effectively, and there is a problem that the refrigerant flow noise becomes loud.

FIG. 16 is a sectional view showing the construction of a flow rate control device used in the air conditioner disclosed in Japanese Patent Laid-Open No. 10-131681. A honeycomb pipe 37 as a sound deadening means having a plurality of holes communicating between both ends is provided on the upstream side and the downstream side of the throttle in order to reduce the refrigerant flow noise. A cross-sectional view of the honeycomb pipe is shown in FIG. The multiple holes installed in the pipe have a small refrigerant passage area, are easily blocked by foreign substances flowing in the refrigeration cycle, and there is no problem that performance decreases due to a decrease in the refrigerant flow rate and there is no bypass flow path in the throttle part. Therefore, there is a problem that the refrigerant cannot flow without pressure loss.

The present invention has been made in order to solve the above-mentioned problems, and it is possible to significantly reduce refrigerant flow noise, and a refrigeration cycle apparatus and air using a throttle device that is not blocked by foreign matter in the cycle. The purpose is to obtain a harmony device.

[0010]

An air conditioner according to claim 1 of the present invention is a compressor, an outdoor heat exchanger, a first flow rate control device, a first indoor heat exchanger, a second flow rate control device, and a second flow rate control device. In the air conditioner including a refrigeration cycle in which two indoor heat exchangers are connected, the second flow rate control device has porous permeable materials that communicate in the flow direction of the refrigerant, upstream and downstream of the throttle portion, and the throttle portion. And a porous permeable material, a space is provided between the set temperature and the current indoor air temperature, or the temperature deviation between the set humidity and the current indoor air humidity is controlled to be within a predetermined value. .

In the air conditioner according to claim 2 of the present invention, the rotation frequency of the compressor, the rotation speed of the outdoor fan attached to the outdoor heat exchanger, the rotation speed of the indoor fan attached to the indoor heat exchanger, At least one of the throttle valve opening of the first flow control device and the valve opening / closing of the second flow control device is controlled.

In the air conditioner according to claim 3 of the present invention, when controlling the temperature deviation and the humidity deviation within a predetermined value, the temperature deviation is given priority over the humidity deviation.

In the air conditioner according to claim 4 of the present invention, when the temperature deviation and the humidity deviation are both larger than a predetermined value at the time of starting the air conditioning apparatus, the refrigerant is prevented from flowing to the throttle portion of the second flow rate control device. To control.

The air conditioner according to claim 5 of the present invention is controlled so that the current operation is continued when the temperature deviation and the humidity deviation are within predetermined values.

In the air conditioner according to claim 6 of the present invention, when the temperature deviation is within a predetermined value and the humidity deviation is larger than the predetermined value, the refrigerant is circulated to the throttle portion of the second flow rate control device. It was controlled so that

In the air conditioner according to claim 7 of the present invention, the rotation amount of the outdoor fan or the valve opening degree of the first flow rate control device is adjusted to control the heating amount of the first indoor heat exchanger, and the compression is performed. The cooling frequency of the second indoor heat exchanger is controlled by adjusting the rotation frequency of the machine and the rotation speed of the indoor fan.

The air conditioner according to claim 8 of the present invention is such that the refrigerant is controlled to flow to the throttle portion of the second flow rate control device when the heating operation is started.

In the air conditioner according to claim 9 of the present invention, the rotation speed of the outdoor fan and the valve opening degree of the first flow rate control device are adjusted so that the cooling and dehumidifying capacity of the first indoor heat exchanger becomes zero. Then, the evaporation temperature of the first indoor heat exchanger is controlled to be equal to the indoor air temperature.

An air conditioner according to a tenth aspect of the present invention controls so that the refrigerant does not flow to the throttle portion of the second flow rate control device when a predetermined time has elapsed since the compressor was started.

An air conditioner according to claim 11 of the present invention adjusts the rotation speed of the compressor, the rotation speed of the indoor fan, and the rotation speed of the outdoor fan so that the temperature deviation is within a predetermined value. .

An air conditioner according to a twelfth aspect of the present invention controls the refrigerant to flow through the throttle portion of the second flow rate control device when the humidity deviation is a predetermined value or more.

[0022]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiment 1. FIG. 1 is a refrigerant circuit diagram of an air conditioner showing an example of an embodiment of the present invention.
The same parts as those of the conventional device are represented by the same reference numerals. In the figure, 1 is a compressor, 2 is a flow path switching means for switching the flow of refrigerant in cooling operation and heating operation, for example, a four-way valve, 3 is an outdoor heat exchanger, 4 is a first flow rate control device, and 5 is a first indoor chamber. A heat exchanger, 6 is a second flow rate control device, and 7 is a second indoor heat exchanger, which are sequentially connected by piping to form a refrigeration cycle. The outdoor unit 33 has an outdoor fan 40 attached to the outdoor heat exchanger 3, and the indoor unit 34 has an indoor fan 4 attached to two indoor heat exchangers.
1 is built in each. R410A, which is a mixed refrigerant of R32 and R125, is used as the refrigerant of this refrigeration cycle, and alkylbenzene-based oil is used as the refrigerating machine oil.

FIG. 2 is a diagram showing the configuration of the second flow rate control device of the air conditioner shown in FIG. 1, in which reference numeral 8 connects the first indoor heat exchanger 5 and the second flow rate control device 6. Piping, 11 is a throttle part, 12 is a two-way valve, 15 is a pipe connecting the second flow rate control device 6 and the second indoor heat exchanger, 9 is a pipe 8
A pipe connecting the throttle part 11 and the throttle part 10 is a pipe 8 and a two-way valve 1
Reference numeral 13 is a pipe connecting 2; 13 is a pipe connecting the throttle portion 11 and the pipe 15; 14 is a pipe connecting the two-way valve 12 and the pipe 15. The second flow rate control device 6 includes a two-way valve 12 and a throttle unit 11.
Are connected in parallel by piping. 3 is a configuration cross-sectional view showing the operation of the second flow rate control device 6 shown in FIG. 2, (a) shows the operating state of the second flow rate control device 6 during the cooling operation or the heating operation, (b) ) Indicates the operating state of the second flow rate control device 6 during the reheat dehumidifying operation.
In the figure, 16 is an electromagnetic coil, 17 is a valve element, and 18 is a valve seat.

FIG. 4 is an enlarged cross-sectional view of the throttle portion 11 of the second flow rate control device 6, where 19 is an inlet silencing space, 20 is a foam metal installed on the inlet side, and 21 is a foam metal installed on the inlet side. Bypass channel (through hole), 23 is an orifice that is a throttle, 22 is a space between the foam metal 20 on the inlet side and the orifice 23, 25 is a foam metal on the outlet side, and 24 is an orifice 23
Is a space between the outlet side foam metal 25, 26 is a bypass flow passage (through hole) provided in the outlet side foam metal 25, and 27 is an outlet side silencing space. The foam metal 20 and the foam metal 25 installed at the entrance and exit of the orifice 23 have the same shape, and a cross-sectional view in the flow direction thereof is shown in FIG. The foam metal is a porous permeable material as a whole, and the effect of reducing the flow noise can be obtained if the pores (pores in the porous body surface and the interior where the fluid can permeate) have a pore diameter of 100 μm or more. In consideration of the effect of clogging, the pore diameter is 500 μm and the porosity is 92 ± 6%. Bypass channel 21 (2 provided in foam metal 20 (25)
6) has a location where it does not overlap with the orifice 23, and if the diameter is a through hole having a minimum pore diameter of 100 μm or more, a bypass function can be obtained, which prevents clogging of the foam metal and prevents reliability. Can be improved. In this embodiment, a through hole having a diameter of 2 mm is provided. For foam metal, apply metal powder or alloy powder to urethane foam and heat it to burn out urethane foam
It is formed into a one-dimensional lattice and the material is Ni (nickel). It may be plated with Cr (chrome) in order to increase the strength.

FIG. 7 shows a block diagram of the entire control device incorporated in this air conditioner. The control device 42 is composed of a microprocessor or the like. For example, an operation mode signal for setting the operation state of the air conditioner, a target temperature signal, and
When the target humidity signal, the air volume switching signal, the operation start / stop signal, etc. are given, the compressor 1, the four-way valve 2, the outdoor fan 40, and the room are monitored while monitoring the outputs of the room temperature detecting means 50 and the room humidity detecting means 51. The fan 41, the first flow control device 4,
The second flow control device 6 is controlled.

Next, the operation of the refrigeration cycle of the air conditioner according to the present embodiment will be described. In FIG. 1, the flow of the refrigerant during cooling is indicated by a solid arrow. The cooling operation corresponds to the case where both the sensible heat load and the latent heat load of the room are large at startup and during the summer, and the sensible heat load of the air conditioner is small, but the latent heat load is large, such as in the middle period and the rainy season. It is divided into dehumidification operation corresponding to the case. Normal cooling operation is
The two-way valve of the second flow rate control device 6 receives the command from the control device 42 and is in an open state, so that the refrigerant connects the first indoor heat exchanger and the second indoor heat exchanger with almost no pressure loss.

At this time, the high-temperature and high-pressure vapor refrigerant leaving the compressor 1 operating at the number of revolutions according to the air conditioning load is the four-way valve 2.
Through the outdoor heat exchanger 3, condensed and liquefied in the outdoor heat exchanger 3, reduced in pressure by the first flow rate control device 4 to become a low-pressure two-phase refrigerant, flown into the first indoor heat exchanger 5 and evaporated and vaporized, and then the second flow rate control device After passing through 6 without significant pressure loss, it is evaporated and vaporized again in the second indoor heat exchanger 7, becomes low-pressure vapor refrigerant, and returns to the compressor 1 again via the four-way valve 2.

The first flow rate control device 4 is controlled so that the superheat degree of the refrigerant in the suction portion of the compressor 1 becomes 10 ° C., for example. In such a refrigeration cycle, the indoor heat exchanger 5 evaporates the refrigerant to take heat from the room, and the outdoor heat exchanger 3 condenses the refrigerant to release the heat taken indoors to the outside of the room. To cool.

Next, the operation during the dehumidifying operation will be described with reference to the pressure-enthalpy diagram shown in FIG. The English characters shown in FIG. 6 correspond to the English characters shown in FIG. During this dehumidifying operation, the second
The two-way valve 12 of the flow control device 6 is closed.

At this time, the high-temperature and high-pressure vapor refrigerant (point A) exiting the compressor 1 operating at the number of revolutions corresponding to the air conditioning load passes through the four-way valve 2 and is transferred to the outside air by the outdoor heat exchanger 3. It heat-exchanges and condenses to become a gas-liquid two-phase refrigerant (point B). This high-pressure two-phase refrigerant is slightly decompressed by the first flow rate control device 4, becomes an intermediate-pressure gas-liquid two-phase refrigerant, and flows into the first indoor heat exchanger 5 (C
point). The intermediate-pressure gas-liquid two-phase refrigerant flowing into the first indoor heat exchanger 5 exchanges heat with the indoor air and is further condensed (D
point). The gas-liquid two-phase refrigerant flowing out of the first indoor heat exchanger is the second
It flows into the flow control device 6.

Since the two-way valve 12 is closed in the second flow control device 6, the refrigerant flows from the inlet pipe 8 of the second flow control device to the throttle portion 11 through the connecting pipe 9. Throttle 11
Then, from the connection pipe 9 through the inlet side silencing space 19, the inlet side foam metal 20, the space 22 between the inlet side foam metal 20 and the orifice 23, the pressure is reduced by the orifice 23 to become the low pressure gas-liquid two-phase refrigerant, and the orifice 23 And the outlet-side foamed metal 25, the outlet-side foamed metal 25, the outlet-side muffling space 27, and the connection pipe 13 in order to pass through the second indoor heat exchanger 7
Flows in (point E). The thickness of the foam metal installed at the entrance and exit of the orifice in the refrigerant flow direction may be 1 mm or more in view of the effect of reducing the flow noise and the ease of processing, and is about 3 mm in this embodiment. The inner diameter of the orifice is 1 millimeter and the thickness is about 3 millimeters. The refrigerant flowing into the second indoor heat exchanger 7 deprives the sensible heat and latent heat of the indoor air and evaporates.
The low-pressure vapor refrigerant that has left the second indoor heat exchanger returns to the compressor 1 via the four-way valve 2 again. Since the indoor air is heated by the first indoor heat exchanger 5 and cooled and dehumidified by the second indoor heat exchanger 7, it is possible to perform dehumidification while preventing the room temperature from decreasing in the room.

In the dehumidifying operation, the rotation frequency of the compressor 1 and the rotation speed of the outdoor fan 40 of the outdoor heat exchanger 3 are adjusted to control the amount of heat exchange of the outdoor heat exchanger 3 to control the first indoor chamber. The blowout temperature can be controlled in a wide range by controlling the heating amount of the indoor air by the heat exchanger 5. Further, the opening temperature of the first flow rate control device 4 and the rotation speed of the indoor fan 41 are controlled to control the condensation temperature of the first indoor heat exchanger, and the heating amount of the indoor air by the first indoor heat exchanger 5 is controlled. You can also do it. Further, the second flow rate control device 6 has, for example, a superheat degree of the compressor suction refrigerant of 10 ° C.
Is controlled so that

In the first embodiment, in the throttle portion 11, the throttle process is the orifice 23. Foamed metal, which is a porous permeable material, is installed on the inlet side and the outlet side of the orifice 23, and the spaces 19 and 27 for providing a silencing effect are installed upstream of the inlet side foamed metal 20 and downstream of the outlet side foamed metal 25, respectively. The refrigerant flow noise generated when the gas-liquid two-phase refrigerant passes can be significantly reduced.

When the gas-liquid two-phase refrigerant passes through the ordinary orifice type flow rate control device, a large refrigerant flow noise is generated before and after the throttle portion. In particular, when the gas-liquid two-phase refrigerant flow mode is a slag flow, a large refrigerant flow noise is generated upstream of the throttle portion. This is because when the flow mode of the gas-liquid two-phase refrigerant is a slag flow, as shown in FIG. 6, the steam refrigerant flows intermittently in the flow direction, and steam slag or steam bubbles larger than the throttle passage are throttled. When the steam slag or vapor bubbles in the upstream of the throttle passage collapses when passing through the partial passage, they vibrate and the vapor refrigerant and the liquid refrigerant alternately pass through the throttle portion. The reason is that when the vapor refrigerant passes, it becomes fast and when the liquid refrigerant passes, it becomes slow, so that the pressure upstream of the throttle portion also changes accordingly. Further, at the outlet of the conventional second flow rate control device 6, the outlet flow path is at one to four places, so that the refrigerant flow velocity is high, and at the outlet portion, a high-speed gas-liquid two-phase flow occurs, and the refrigerant collides with the wall surface. The main body of the part and the outlet flow path constantly vibrate and generate noise. In addition, jet noise is increased due to turbulence and eddies generated by the high-speed gas-liquid two-phase jet at the outlet.

The gas-liquid two-phase refrigerant and the liquid refrigerant flowing into the throttle portion 11 of the second flow control device 6 shown in FIG. 4 pass through the minute and innumerable vent holes of the foam metal 20 on the inlet side and the flow is rectified.
Therefore, steam slag (large bubbles) such as slag flow in which gas and liquid flow intermittently becomes small bubbles, and the flow state of the refrigerant is a homogeneous gas-liquid two-phase flow (a state in which the vapor refrigerant and the liquid refrigerant are well mixed).
Therefore, the vapor refrigerant and the liquid refrigerant are simultaneously supplied to the orifice 23.
Since the refrigerant passes through, the speed of the refrigerant does not fluctuate and the pressure does not fluctuate. In addition, a porous permeable material such as the inlet-side foamed metal 20 has a complicated internal flow path, and pressure fluctuations are repeated in this interior, and there is an effect of making the pressure fluctuations constant while partially converting it into heat energy. Therefore, even if a pressure fluctuation occurs in the orifice 23, it has an effect of absorbing the pressure fluctuation, and it is difficult to convey the influence upstream thereof. Further, the high-speed gas-liquid two-phase jet flow downstream of the orifice 23 is sufficiently decelerated by the outlet-side foamed metal 25 in the flow velocity of the refrigerant and the velocity distribution is uniformized. Since it does not collide with the wall surface and a large vortex is not generated in the flow, jet noise is reduced.

Further, since the inlet silencing space 19 is provided on the inlet side of the throttle portion 11, it is possible to reduce pressure fluctuations at a low frequency which cannot be suppressed by the foam metal 20 on the inlet side. Similarly, since the outlet silencing space 27 is also provided on the outlet side of the throttle portion 11, it is possible to reduce pressure fluctuations at low frequencies that cannot be suppressed by the outlet side foam metal 20.

Therefore, it is not necessary to take a measure such as winding a sound insulating material or a vibration damping material around the diaphragm device 6, which is required in the conventional device, and the cost is reduced, and the recyclability of the air conditioner is improved. Note that the problem of the refrigerant flow noise caused by the gas-liquid two-phase refrigerant described above is not limited to the air conditioner, but is a problem regarding the refrigeration cycle in general such as a refrigerator, and the expansion device of the present embodiment is The same effect can be obtained by widely applying it to such refrigeration cycle in general.

The flow rate characteristics of the second flow rate control device 6 (relationship between refrigerant flow rate and pressure loss) during the cooling and dehumidifying operation are the orifice 23.
It can be adjusted by adjusting the diameter, the length of the passage through which the refrigerant passes, and the number of orifices. That is, when a certain flow rate of the refrigerant is caused to flow with a small pressure loss, the diameter of the orifice may be increased, the flow path length may be shortened, or a plurality of orifices may be used. On the contrary, when a certain flow rate of the refrigerant is caused to flow with a large pressure loss, the diameter of the orifice 23 may be reduced, the flow path length may be increased, or one orifice may be used. The shape of the orifice used for such a narrowed portion, such as the diameter and the flow path length, is optimally designed when the device is designed.

The element of the porous permeable material used for the inlet side and the outlet side of the narrowed portion has been described in the present embodiment as being the case of foam metal, but ceramic, sintered metal, foam resin, wire mesh or the like may be used. The same effect can be obtained.

Further, bypass flow paths (through holes) 21 and 2 are provided in the inlet side foam metal 20 and the outlet side foam metal 25, respectively.
Since 6 is provided at a position that does not overlap the orifice 23, even if the foam metal 20 on the inlet side and the foam metal 25 on the outlet side are clogged by foreign matter in the refrigeration cycle, the performance deterioration due to the clogging can be prevented. Can be done.
Further, since the space 22 between the inlet-side foamed metal 20 and the orifice 23 and the space 24 between the orifice 23 and the outlet-side foamed metal 25 are provided, most of the foamed metal serves as a refrigerant flow path, and thus the expansion device. Since it can maintain its function as and has sufficient reliability as a diaphragm device,
It is possible to provide an air conditioner with sufficient reliability. In the present embodiment, the bypass passage shape is described as a single cylindrical shape, but the present invention is not limited to this, and the cutout shape or a plurality of cylindrical bypass passages shown in FIGS. The same effect can be obtained.

FIG. 9 shows the results of measurement of the frequency characteristics of noise generated by the conventional diaphragm device and the frequency characteristics of the noise of the diaphragm device of this embodiment. In the figure, the horizontal axis is frequency [H
z], and the vertical axis is the sound pressure (SPL) [dBA]. Further, the dotted line shows the second flow rate control device of this embodiment, and the two-dot chain line shows the conventional second flow rate control device. It can be seen that the sound pressure level is reduced in the entire frequency range in the present embodiment as compared with the related art. Especially from 2000Hz to 70, which is good for human ears
It can be seen that a significant reduction effect is obtained in the range of 00 Hz.

Next, the operation control method of the air conditioner of this embodiment will be described. In the air conditioner, for example, a set temperature and a set humidity are set when the air conditioner is operating in order to set a temperature / humidity environment preferred by a resident in the room. The set temperature and set humidity may be entered directly by the resident from the remote controller 43 of the indoor unit, and may be used for people who are hot, people who are cold, children and the elderly. It is also possible to store an optimum value table of temperature and humidity determined for each target resident in the remote controller of the unit and directly input only the target resident. Further, the indoor unit 33 is provided with sensors for detecting the temperature and humidity of the indoor unit in order to detect the temperature and humidity of the room.

When the air conditioner is activated, the difference between the set temperature and the current indoor intake air temperature is calculated as a temperature deviation, and the difference between the set humidity and the current indoor intake air humidity is calculated as a humidity deviation, and finally the difference is calculated. The rotation frequency of the compressor 1 of the air conditioner so that these deviations are zero or within a predetermined value,
The number of rotations of the outdoor fan, the number of rotations of the indoor fan, the throttle opening of the first flow rate control valve 4, and the opening / closing of the second flow rate control valve 6 are controlled. At this time, when controlling the temperature and humidity deviations to be zero or within a predetermined value, the temperature deviation is prioritized over the humidity deviations to control the air conditioner.

That is, when both the temperature deviation and the humidity deviation are large when the air conditioner is started, the second flow rate control 1
As shown in FIG. 3A, the control valve 6 is provided with a valve body 17 of a two-way valve 12.
The control unit directs the to be in the open position. Since the refrigerant passing through the second flow rate control device has almost no pressure loss, cooling capacity and efficiency are not deteriorated. Second like this
The flow control valve 6 is opened, and first, in normal cooling operation, the temperature deviation in the room is preferentially operated to be zero or within a predetermined value. Humidity deviation is detected when the cooling capacity of the air conditioner matches the heat load of the room and the temperature deviation is within zero or within a specified value.At this time, the humidity deviation is within zero or within a specified value. If so, continue the current operation.

When the temperature deviation is zero or within a predetermined value and the humidity deviation at this time is still a large value, the second flow rate control valve 6 is moved to the valve body 1 as shown in FIG. 3 (b).
7 is brought into a position in which it closely contacts with the valve seat 18. Thus, the second flow control valve 6 is throttled to switch to the cooling / dehumidifying operation. In this cooling / dehumidifying operation, the heating amount of the first indoor heat exchanger 5 is controlled so that the temperature deviation in the room can be maintained within zero or within a predetermined value, and the humidity deviation is controlled within zero or within a predetermined value. In addition, the cooling / dehumidifying amount of the second indoor heat exchanger 7 is controlled. The heating amount of the first indoor heat exchanger 5 is controlled by adjusting the rotation speed of the outdoor fan of the outdoor heat exchanger 3, the opening degree of the first flow control valve 4, and the like. Further, the cooling / dehumidifying amount of the second indoor heat exchanger 7 is controlled by the rotation frequency of the compressor 1 and the rotation speed of the indoor fan of the indoor unit 34.

As described above, according to this embodiment, the refrigerant circuit is switched between the normal cooling operation and the cooling / dehumidifying operation in accordance with the load on the room during the cooling operation, so that the temperature and humidity environment in the room can be adjusted by the occupants. It can be controlled to an optimum state according to. In addition, even if the phase state of the refrigerant passing through the expansion device or the gas-liquid mixture ratio changes due to changes in modes such as cooling, dehumidification, and heating, or changes in the air conditioning load, the refrigerant in the expansion part 11 is stable with low noise. Can flow to.

In this embodiment, the refrigerating machine oil is difficult to dissolve in the refrigerant,
Alkylbenzene oil is used, but there are foreign substances that are not soluble in the refrigerant and foreign substances that are soluble in the refrigeration oil in the refrigeration cycle.If the foreign substances adhere to the foam metal that is the porous permeable material, they will dissolve in the refrigerant. When the refrigerating machine oil, which is difficult to pass through, passes through the foam metal, it has an effect of cleaning the foreign matter, so that the reliability against clogging of the throttle portion is improved.

If the refrigerating machine oil that is easily dissolved in the refrigerant is used, the refrigerating machine oil adhered by the refrigerant is washed when the compressor is started next time even if the compressor is stopped with the refrigerating machine oil attached to the foam metal. Therefore, reliability can be improved.

Embodiment 2. Hereinafter, an air conditioner according to Embodiment 2 of the present invention will be described. The present embodiment relates to heating operation, and the refrigerant circuit forming the air conditioner is the same as, for example, FIG. 1 in the first embodiment,
The structure of the second flow control valve 6 is the same as that of FIG.
The detailed structure of 1 is the same as that of FIG. The operation of the air-conditioning apparatus according to this embodiment during heating will be described. Figure 1
In, the flow of the refrigerant during heating is indicated by the broken line arrow. In the normal heating operation, the control unit instructs the second flow control valve 6 to bring the valve body 17 of the two-way valve 12 to the open position as shown in FIG.

At this time, the high-temperature high-pressure refrigerant vapor leaving the compressor 1 passes through the four-way valve 2 and the second indoor heat exchanger 7 and the first indoor heat exchanger 7.
It flows into the indoor heat exchanger 5, exchanges heat with the indoor air and condenses,
Liquefy. In the second flow rate control valve 6, since the pipe 8 and the pipe 15 are connected with a large opening area as shown in FIG. 3 (a), there is almost no refrigerant pressure loss when passing through this valve, and the pressure is reduced. There is no loss in heating capacity or efficiency due to loss. The high-pressure liquid refrigerant exiting the first indoor heat exchanger 5 is
It is decompressed to a low pressure by the flow rate control valve 4, becomes a gas-liquid two-phase refrigerant, and exchanges heat with outdoor air in the outdoor heat exchanger 3 to evaporate. The low-pressure vapor refrigerant that has exited the outdoor heat exchanger 3 passes through the four-way valve 2 and returns to the compressor 1 again. The opening degree of the first flow rate control valve 4 during the normal heating operation is controlled so that the superheat degree of the outlet refrigerant of the outdoor heat exchanger 3 is 5 ° C., for example.

Next, the operation during the heating dehumidifying operation will be described with reference to FIG.
The explanation will be made in correspondence with the English characters shown in. During this heating / dehumidifying operation, the control unit instructs the second flow rate control valve 6 to be in a position where the valve body 17 of the two-way valve 12 is in close contact with the valve seat 18 as shown in FIG. 3B. At this time, the high-temperature and high-pressure refrigerant vapor (point A) exiting the compressor 1 passes through the four-way valve 2 and flows into the second indoor heat exchanger 7, where it is heat-exchanged with indoor air and condensed (E
point). This high-pressure liquid refrigerant or gas-liquid two-phase refrigerant is
It flows into the flow control valve 6.

In the second flow control valve 6, the valve body 17 of the two-way valve 12 is in close contact with the valve seat 18 as shown in FIG. Then, it is decompressed and expanded to become a low-pressure gas-liquid two-phase refrigerant and flows into the first indoor heat exchanger 5 through the pipes 9 and 8 (point D). The saturation temperature of the refrigerant flowing into the first indoor heat exchanger 5 is equal to or lower than the dew point temperature of the indoor air, and the sensible heat and latent heat of the indoor air are taken to evaporate (point C). The low-pressure gas-liquid two-phase refrigerant that has exited the first indoor heat exchanger 5 flows into the first flow rate control valve 4, is further depressurized, flows into the outdoor heat exchanger 3, and exchanges heat with outdoor air to evaporate. . The low-pressure vapor refrigerant that has exited the indoor / outdoor heat exchanger 4 returns to the compressor 1 through the four-way valve 2.

In this heating / dehumidifying operation, the room air is
Since the indoor heat exchanger 7 is heated and the first indoor heat exchanger 5 is cooled and dehumidified, it is possible to perform dehumidification while heating the room. In the heating dehumidifying operation, the rotation frequency of the compressor 1 and the fan rotation speed of the outdoor heat exchanger 3 are adjusted to control the heat exchange amount of the outdoor heat exchanger 3, and the indoor air by the first indoor heat exchanger 5 is controlled. The blowout temperature can be controlled in a wide range by controlling the heating amount. Also, the opening temperature of the first flow control valve 4 and the indoor fan rotation speed are adjusted to control the evaporation temperature of the first indoor heat exchanger 5, and to control the dehumidification amount of the indoor air by the first indoor heat exchanger 5. You can also The opening degree of the second flow rate control valve 6 is controlled so that the degree of supercooling of the outlet refrigerant of the second indoor heat exchanger 7 is 10 ° C, for example.

Thus, in this embodiment, the diaphragm 11
Since the second flow rate control valve having the structure in which the orifice 23 is sandwiched by the foam metal is used, the dehumidifying operation during heating can be performed, and the generation of the refrigerant flow noise during the heating dehumidifying operation can be prevented, A comfortable space can be realized in terms of temperature and humidity environment and noise.

Next, an example of a specific heating operation control method of the air conditioner of this embodiment will be described. As described in the first embodiment, the set temperature and the set humidity and the intake air temperature and the humidity are input to the air conditioner. This air conditioner performs a high-temperature blowout operation operation for a predetermined time, for example, 5 minutes when the heating is started, and then shifts to the normal heating operation. After that, the normal heating operation and the heating dehumidifying operation are switched and controlled according to the temperature deviation and the humidity deviation of the room.

When the heating operation is started, the valve body 17 of the two-way valve 12 is moved to the valve seat 18 of the second flow control valve 6 as shown in FIG. 3 (b).
Then, the compressor 1 is started up in a squeezed state in which the compressor 1 is brought into close contact with. At this time, the fan rotation speed of the outdoor heat exchanger 3 and the valve opening degree of the first flow control valve 4 are adjusted so that the cooling / dehumidifying capacity of the first indoor heat exchanger 5 becomes zero, and The evaporation temperature of the indoor heat exchanger 5 is controlled to be equal to the intake air temperature. After a lapse of a predetermined time of 5 minutes from the start of the compressor, the second flow rate control valve 6 is brought into the open state as shown in FIG. 3 (a), and the normal heating operation is started.

At this time, the rotation frequency of the compressor 1, the rotation speed of the indoor fan, and the rotation speed of the outdoor fan are adjusted so that the temperature deviation is zero or within a predetermined value. If the temperature deviation is zero or within a predetermined value due to this heating normal operation, the humidity deviation is detected.If the humidity deviation is zero or within a predetermined value, and if the humidity deviation is equal to or more than a predetermined value. Also, when humidification is required, the normal heating operation is continued. On the other hand, when the humidity deviation is zero or more than a predetermined value and dehumidification is required, the second flow control valve 6
Is set to the throttle state as shown in FIG. 3B, and the heating dehumidifying operation is performed.

In this heating / dehumidifying operation, the heating amount of the second indoor heat exchanger 7 is controlled so that the temperature deviation in the room can be maintained within zero or within a predetermined value, and the humidity deviation is within zero or within a predetermined value. The cooling / dehumidifying amount of the first indoor heat exchanger 5 is controlled so as to enter. To control the heating amount of the second indoor heat exchanger 7, the rotation frequency of the compressor 1 and the indoor unit 2 are controlled.
It is controlled by the fan rotation speed of 2. Further, the cooling and dehumidifying amount of the first indoor heat exchanger 5 is controlled by adjusting the fan speed of the outdoor heat exchanger 3, the opening degree of the first flow control valve 4, and the like.

As described above, in this embodiment, the temperature in the room is changed by switching the refrigerant circuit to the heating high temperature blowing operation, the normal heating operation, or the heating dehumidifying operation according to the operating time during the heating operation and the load on the room. The humidity environment can be controlled to an optimum condition according to the occupants' preference.

Embodiment 3. FIG. 10 shows a second flow rate control device 6 of an air conditioner showing another example of the embodiment of the present invention.
5 is a detailed cross-sectional view of the throttle unit 11, in which the same or similar components as those shown in FIG. 4 are designated by the same reference numerals, and the duplicate description thereof will be omitted. In this embodiment, a convex block 28 is provided around the inside of the entrance silencing space 19.

As shown in the present embodiment, the convex block 28 is formed in the inlet silencing space rather than the inlet silencing space 19 as in the embodiment shown in FIG. A stagnation portion is formed before and after the convex block 28 due to the flow, and foreign matter flowing in the refrigeration cycle can be retained at the stagnation portion, and the inlet side foam metal 20
Can be prevented from adhering to the air conditioner, and the reliability of the air conditioner can be further improved. In the present embodiment, the case of the convex block for forming the stagnation portion has been described, but the present invention is not limited to this, and may be, for example, a concave groove or the like as long as the stagnation is formed by the flow.

Fourth Embodiment FIG. 11 shows a second flow rate control device 6 of an air conditioner showing another example of the embodiment of the present invention.
5 is a detailed cross-sectional view of the throttle unit 11, in which the same or similar components as those shown in FIG. 4 are designated by the same reference numerals, and the duplicate description thereof will be omitted. In this embodiment, a strainer 29 formed of a wire net inside the entrance silencing space 19 and the exit silencing space 27 is installed. The strainer has an average pore diameter smaller than the average pore diameter of the inlet foam metal 20 and the outlet foam metal 25 of 500 micrometers.

Rather than providing the convex block 28 in the entrance silencing space as in the third embodiment shown in FIG. 10, the wire mesh strainer 2 in the entrance silencing space as shown in this embodiment.
It is possible to more reliably prevent foreign matter in the refrigerant cycle from adhering to the inlet-side foam metal 20 by installing 9.
It is possible to obtain the second flow rate control device with further improved reliability, and an air conditioner with high reliability is realized.

Further, in Embodiments 1 to 4, the case where R410A is used as the refrigerant of the air conditioner has been described. R410A is an HFC-based refrigerant that is suitable for global environmental protection that does not destroy the ozone layer, and has a higher refrigerant vapor density and a lower refrigerant flow rate than R22 that has been used as a conventional refrigerant, resulting in a pressure loss. Is small, the diameter of the vent hole of the porous body used for the throttle portion of the second flow rate control device 6 can be made small, and the refrigerant flow noise reducing effect can be further obtained.

Furthermore, the refrigerant of this air conditioner is not limited to R410A, but may be R407C, R404A, R507A which are HFC refrigerants.
Further, from the viewpoint of preventing global warming, R32 alone, R152a alone or a mixed refrigerant such as R32 / R134a, which are HFC refrigerants having a small global warming coefficient, may be used. Further, HC-based refrigerants such as propane, butane, and isobutane, natural refrigerants such as ammonia, carbon dioxide, ether, and mixed refrigerants thereof may be used. In particular, propane, butane, isobutane, and their mixed refrigerants have a lower operating pressure than R410A and a small pressure difference between the condensing pressure and the evaporating pressure. Therefore, it is possible to increase the inner diameter of the orifice and improve the reliability against clogging. It can be further improved.

In the above description, the combination of the throttle portion and the two-way valve which constitutes the second flow rate control device has been described, but the invention is not limited to the two-way valve, and a multi-way valve such as a three-way valve is used. A two-flow rate control device may be used, and the same effect can be obtained. As a method of using the three-way valve in this case, in addition to the flow passage connected in parallel with the throttle portion, the divided flow passage has a refrigerant circuit connected to the outlet side pipe of the second indoor heat exchanger, and depending on the air conditioning load condition. It is also possible to bypass the refrigerant as a means of reducing the dehumidifying capacity.

[0067]

The air conditioner of the present invention comprises a compressor, an outdoor heat exchanger, a first flow rate control device, a first indoor heat exchanger, and a second indoor heat exchanger.
In an air conditioner equipped with a flow control device and a refrigeration cycle in which a second indoor heat exchanger is connected, the second flow control device has a porous permeable material communicating in the flow direction of the refrigerant upstream and downstream of the throttle portion. However, a space is provided between the throttle portion and the porous permeable material so that the temperature deviation between the set temperature and the current room air temperature or the humidity deviation between the set humidity and the current room air humidity is within a predetermined value. Since the control is performed, the temperature and humidity of the comfortable indoor space can be adjusted while effectively reducing the refrigerant flow noise.

The rotation frequency of the compressor, the rotation speed of the outdoor fan attached to the outdoor heat exchanger, the rotation speed of the indoor fan attached to the indoor heat exchanger, the throttle valve opening of the first flow control device, Since at least one of the valve opening and closing of the second flow rate control device is controlled, it is possible to obtain the effect of being able to adjust the set temperature and humidity in a short time.

Further, when controlling the temperature deviation and the humidity deviation within the predetermined values, the temperature deviation is prioritized over the humidity deviation, so that the temperature controllability of the indoor space is improved and the comfort is improved. .

Further, when both the temperature deviation and the humidity deviation are larger than the predetermined values when the air conditioner is started, the refrigerant is controlled so as not to flow to the throttle portion of the second flow rate control device, so that the rapid cooling property of the indoor space is achieved. There is an effect that can improve the comfortable cooling.

Further, since the current operation is controlled to continue when the temperature deviation and the humidity deviation are within the predetermined values, there is an effect that a comfortable indoor space can be maintained.

Further, when the temperature deviation is within the predetermined value and the humidity deviation is larger than the predetermined value, the refrigerant is controlled to flow to the throttle portion of the second flow rate control device.
There is an effect that the temperature of the indoor space can be maintained and only the humidity can be adjusted.

Further, the rotation amount of the outdoor fan or the valve opening degree of the first flow rate control device is adjusted to control the heating amount of the first indoor heat exchanger, and the rotation frequency of the compressor and the rotation number of the indoor fan are adjusted. Since the cooling and dehumidifying amount of the second indoor heat exchanger is adjusted to control, the temperature and humidity can be controlled appropriately during the cooling operation.

Further, when the heating operation is started, the refrigerant is controlled so as to flow to the throttle portion of the second flow rate control device, so that the effect of dehumidifying while heating can be obtained with low noise.

Further, the rotation speed of the outdoor fan and the valve opening degree of the first flow rate control device are adjusted so that the cooling / dehumidifying capacity of the first indoor heat exchanger is zero, and the evaporation of the first indoor heat exchanger is performed. Since the temperature was controlled to be equal to the indoor air temperature,
The effect is obtained that the air temperature is raised to a high level and the heating feeling is enhanced to provide comfortable heating.

Further, after a lapse of a predetermined time from the start-up of the compressor, the refrigerant is controlled so as not to flow to the throttle portion of the second flow rate control device, so that the air conditioner can stably exhibit the heating capacity, which is comfortable. It has the effect of heating.

Further, since the rotation speed of the compressor, the rotation speed of the indoor fan, and the rotation speed of the outdoor fan are adjusted so that the temperature deviation is within a predetermined value, a comfortable heating space can be obtained in a short time. effective.

If the humidity deviation exceeds a predetermined value, the second
Since the refrigerant is controlled to flow through the throttle portion of the flow rate control device, the dehumidifying operation can be performed during the heating operation.

[Brief description of drawings]

FIG. 1 is a refrigerant circuit diagram of an air conditioner according to a first embodiment of the present invention.

FIG. 2 is a configuration diagram of a diaphragm device according to the first embodiment of the present invention.

FIG. 3 is a configuration cross-sectional view showing an operation of the diaphragm device according to the first embodiment of the present invention.

FIG. 4 is an enlarged detailed view of a diaphragm unit according to the first embodiment of the present invention.

FIG. 5 is an enlarged view of the porous permeable material according to the first embodiment of the present invention.

FIG. 6 is a pressure-enthalpy diagram showing an operating state during the cooling / dehumidifying operation according to the first embodiment of the present invention.

FIG. 7 is a block configuration diagram of an entire control device incorporated in the air conditioner according to the first embodiment of the present invention.

FIG. 8 is a flow pattern diagram of the refrigerant at the inlet of the throttle unit according to the first embodiment of the present invention.

FIG. 9 is a diagram showing noise characteristics of the diaphragm device according to the first embodiment of the present invention.

FIG. 10 is an enlarged detailed view showing another form of the diaphragm device according to the third embodiment of the present invention.

FIG. 11 is an enlarged detailed view showing another mode of the diaphragm device according to the fourth embodiment of the present invention.

FIG. 12 is an enlarged view of a porous permeable material showing another form of the diaphragm device according to the first embodiment of the present invention.

FIG. 13 is an enlarged view of a porous permeable material showing another form of the diaphragm device according to the first embodiment of the present invention.

FIG. 14 is a refrigerant circuit diagram showing a conventional air conditioner.

FIG. 15 is a cross-sectional view of a configuration of a conventional diaphragm device.

FIG. 16 is a sectional view showing the configuration of another example of a conventional diaphragm device.

FIG. 17 is a configuration cross-sectional view showing another example of the conventional diaphragm device.

18 is a cross-sectional view of a sound deadening part of the diaphragm device in FIG.

[Explanation of symbols]

1 compressor, 2 4-way valve, 3 outdoor heat exchanger, 4 1st
Flow control device, 5 1st indoor heat exchanger, 6 2nd flow control device, 7 2nd indoor heat exchanger, 8, 9, 10 piping, 1
1 throttle, 12 two-way valve, 13, 14, 15 piping,
16 electromagnetic coil, 17 valve body, 18 valve seat, 19 inlet silencing space, 20 inlet side foam metal, 21 bypass flow passage provided in inlet side foam metal 22 space between inlet side foam metal and orifice, 23 orifice, 24 space between outlet side foam metal and orifice, 25 outlet side foam metal, 26 bypass flow path provided in outlet side foam metal, 27 outlet silencing space, 28 convex block, 29
Wire mesh, 30 stepping motor 31, groove notch, 32 porous body, 33 outdoor unit, 34 indoor unit, 36 silencer, 37 honeycomb pipe, 38a,
38b cylindrical tube, 39 small diameter tube, 40 outdoor fan, 4
1 indoor fan, 42 control device, 43 controller.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Hiroyuki Makino             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd. (72) Inventor Atsushi Mochizuki             2-6-2 Otemachi 2-chome, Chiyoda-ku, Tokyo             Ryoden Engineering Co., Ltd. F-term (reference) 3L060 AA05 CC02 CC07 DD02 EE04                       EE05 EE06 EE09

Claims (12)

[Claims] 1. An air conditioner comprising a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow rate control device, a first indoor heat exchanger, a second flow rate control device, and a second indoor heat exchanger are connected. The second flow rate control device has a porous permeable material that communicates with the flow direction of the refrigerant at upstream and downstream of the throttle portion, and provides a space between the throttle portion and the porous permeable material to set a preset temperature and a current value. An air conditioner, which is controlled so that a temperature deviation from an indoor air temperature or a humidity deviation between a set humidity and a current indoor air humidity is within a predetermined value. 2. The rotation frequency of the compressor, the rotation speed of an outdoor fan attached to the outdoor heat exchanger, the rotation speed of an indoor fan attached to the indoor heat exchanger, and a throttle of the first flow control device. The air conditioner according to claim 1, wherein at least one of a valve opening degree and a valve opening / closing of the second flow rate control device is controlled. 3. The air conditioner according to claim 1, wherein when the temperature deviation and the humidity deviation are controlled within a predetermined value, the temperature deviation is given priority over the humidity deviation. 4. When the air conditioner is started up, when both the temperature deviation and the humidity deviation are larger than a predetermined value, the refrigerant is controlled so as not to flow to the throttle portion of the second flow control device. The air conditioner according to any one of claims 1 to 3. 5. The air according to claim 1, wherein the current operation is controlled to continue when the temperature deviation and the humidity deviation are within predetermined values. Harmony device. 6. When the temperature deviation is within a predetermined value and the humidity deviation is larger than a predetermined value, the second
The air conditioner according to any one of claims 1 to 3, wherein the refrigerant is controlled so as to flow through the throttle portion of the flow rate control device. 7. The rotation speed of the outdoor fan or the first
The second indoor heat exchanger is adjusted by adjusting the valve opening of the flow control device to control the heating amount of the first indoor heat exchanger, and adjusting the rotation frequency of the compressor and the rotation speed of the indoor fan. 2. The cooling and dehumidifying amount of the water is controlled.
The air conditioner according to claim 3. 8. The air conditioner according to claim 1, wherein when the heating operation is started, the refrigerant is controlled so as to flow through the throttle portion of the second flow rate control device. 9. The first indoor heat is adjusted by adjusting the rotation speed of the outdoor fan and the valve opening degree of the first flow rate control device so that the cooling / dehumidifying capacity of the first indoor heat exchanger becomes zero. The air conditioner according to claim 8, wherein the evaporation temperature of the exchanger is controlled to be equal to the room air temperature. 10. The control according to claim 1, wherein when a predetermined time has elapsed from the start of the compressor, the refrigerant is controlled so as not to flow to the throttle portion of the second flow rate control device. Air conditioner. 11. The rotation speed of the compressor, the rotation speed of the indoor fan, and the rotation speed of the outdoor fan are adjusted so that the temperature deviation is within a predetermined value. Item 10. The air conditioner according to Item 10. 12. The air conditioner according to claim 10, wherein when the humidity deviation is equal to or larger than a predetermined value, the refrigerant is controlled to flow through the throttle portion of the second flow rate control device.