JP2000346493A - Throttle device, refrigerating cycle apparatus and air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To remarkably reduce a refrigerant flowing sound, to improve temperature and humidity controllability and to improve comfortableness in a room by constituting a throttle of a porous permeable material for communicating in a refrigerant flowing direction. SOLUTION: A first chamber heat exchanger is connected to a first channel 21 of a second flow control valve 6 of the air conditioner, a second chamber heat exchanger is connected to a second channel 22, and a main valve seat 23 opened at the second channel is formed integrally with a valve body. A main valve disc 24 vertically slides along an inner surface of a body of the valve 6, and a throttle is constituted of the seat 23 and the disc 24. An electromagnetic coil 25 for driving the disc 24 is energized or deenergized based on a command from a controller, thereby opening or closing the disc 24. The disc 24 is molded of a porous permeable material. The disc 24 is lifted to an upper portion by deenergizing the coil 25, and the channel 21 is connected to the channel 22 almost without pressure loss by separating the disc 14 from the seat 23.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner which improves the controllability of temperature and humidity during a cooling or heating operation, reduces the flow noise of refrigerant, and improves the indoor temperature, humidity and noise comfort. It concerns the device.

[0002]

2. Description of the Related Art In a conventional air conditioner, a variable displacement compressor such as an inverter is used to cope with fluctuations in air conditioning load, and the rotation frequency of the compressor is controlled according to the magnitude of the air conditioning load. . However, when the rotation of the compressor is reduced during the cooling operation, the evaporating temperature also increases, and the dehumidifying capacity of the evaporator decreases, or the evaporating temperature rises above the dew point temperature in the room, and there is a problem that the dehumidifying cannot be performed. Was.

The following air conditioner has been devised as a means for improving the dehumidifying capacity during the cooling low capacity operation. FIG. 21 shows, for example, a refrigerant circuit configuration of a conventional air conditioner disclosed in Japanese Patent Publication No. 61-43631. In the figure, 1 is a compressor, 3 is an outdoor heat exchanger, 4 is a first flow control valve, 5 is a first indoor heat exchanger, 6 is a second flow control valve,
Reference numeral 7 denotes a second indoor heat exchanger, which is sequentially connected by piping to form a refrigeration cycle. Next, the operation of the conventional air conditioner will be described. First, in a normal cooling operation, the refrigerant that has exited the compressor 1 is condensed and liquefied in the outdoor heat exchanger 3 and decompressed by the first flow control valve 4, and the second indoor heat exchanger 5, the second flow control valve 6, and It returns to the compressor 1 through the second indoor heat exchanger 7. At this time, the second flow control valve is in the fully opened state, and the first indoor heat exchanger 5 and the second indoor heat exchanger 7 operate as evaporators to perform the cooling operation.

On the other hand, during the dehumidifying operation, the first flow control valve 4
Is fully opened, and the refrigerant flow rate is controlled by the second flow control valve 6, whereby the first indoor heat exchanger 5 operates as a condenser or reheater, the second indoor heat exchanger 7 operates as an evaporator, and the indoor heat exchanger 7 operates as an evaporator. Since the air is heated by the first indoor heat exchanger 5, the dehumidifying operation in which the decrease in room temperature is small can be performed.

[0005]

In the conventional air conditioner as described above, a flow control valve having an orifice is usually used as the second flow control valve installed in the indoor unit. The flow noise of the refrigerant generated when the refrigerant passes through is large, which is a factor of deteriorating the indoor environment. In particular, during the dehumidifying operation, the refrigerant at the inlet of the second flow control valve is in a gas-liquid two-phase state, and there is a problem that the refrigerant flow noise is increased.

As measures for reducing the refrigerant flow noise of the second flow control valve during the dehumidifying operation, a method in which a small hole is provided in a main valve body in the flow control valve disclosed in Japanese Patent Application Laid-Open No. Hei 7-91778, Japanese Patent Application Laid-Open No. 10-89803 discloses a flow control valve provided with a spiral flow path downstream of the flow control valve. However, any of these measures for reducing the flow noise of the refrigerant is not effective even if a spiral flow path is added, since the throttle is composed of small holes or orifices. In the case of the state, there is a problem that the refrigerant flow noise increases. In order to reduce the flow noise of the refrigerant, additional measures such as providing a sound insulation material and a vibration damping material in the flow control valve body were necessary, but these additional measures increase costs and increase installation space. Therefore, there is a problem that the indoor unit becomes large and the recyclability at the time of product recovery deteriorates.

[0007] Further, it is possible to reduce the refrigerant flow noise by controlling the operating capacity of the compressor during the dehumidifying operation to be small, thereby reducing the refrigerant flow noise. As a result, the refrigerant flow during the dehumidifying operation is restricted. Therefore, there is a problem that the dehumidification ability cannot be freely controlled, and the temperature and humidity of the room cannot be kept constant.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-described problems, and has as its object to provide a throttling device and a refrigeration cycle device that can significantly reduce refrigerant flow noise. It is an object of the present invention to obtain an air conditioner in which the controllability of temperature and humidity during a heating operation is improved and the comfort in a room is further improved.

[0009]

In the throttle device according to the present invention, the throttle portion is made of a porous permeable material that communicates with the refrigerant in the flow direction.

A first flow path provided with an electromagnetic on-off valve; a second flow path provided in parallel with the first flow path;
A restrictor provided in the second flow path and made of a porous permeable material communicating with the refrigerant in the flow direction.

Further, the refrigerant passage is covered with the porous permeable material.

Further, the porous permeable material has a hollow portion or a hollow body.

Further, the throttle section has a cylindrical shape with one end opened, and a flow path communicating between the inside and the outside of the cylindrical shape through the cylindrical peripheral surface and the bottom surface is formed of a porous permeable material. It is.

[0014] Further, there is provided an adjusting means for adjusting a transmission area of the porous permeable material.

A valve body having a first flow passage opening in a valve chamber side wall, a main valve seat having a second flow passage opening in a valve chamber bottom surface, and a main valve body capable of closing the main valve seat in the valve chamber. And a throttle portion formed by using a porous permeable material for the main valve body.

The porous permeable material has a columnar shape with one end open, and the peripheral surface and the bottom surface of the columnar shape are divided into a flow channel inlet side and an outlet side when the main valve seat is closed. It is.

Also, a valve body having a first flow path opened in a valve chamber side wall, a main valve seat having a second flow path opened in a valve chamber bottom face, and a main valve body capable of closing the main valve seat in the valve chamber. A flow control valve using a porous permeable material for the main valve seat.

A main valve body having a peripheral surface in contact with a side surface of the main valve seat, and a contact area between the peripheral surface and the side surface being varied by movement in the opening and closing direction; And a control means for controlling the movement, wherein the main valve body, the main valve seat and the control means constitute an adjusting means for adjusting the permeation area of the porous permeable material.

Further, the air holes of the porous permeable material are set in the range of 200 to 0.5 micrometers.

Further, the porous permeable material is a sintered metal.

Further, according to a refrigeration cycle apparatus according to the present invention, in the refrigeration cycle provided with the expansion device according to claim 1 or 2, the gas-liquid two-phase refrigerant passes through the porous permeable material.

Also, a valve body having a first flow path opened in a valve chamber side wall, a main valve seat having a second flow path opened in a valve chamber bottom face, and the main valve seat can be closed in the valve chamber and a peripheral surface is formed. A throttle device having a main valve body that abuts on a side surface of the main valve seat and changes an abutting area between the peripheral surface and the side surface by movement in the opening and closing direction, and moving the main valve body in the opening and closing direction. And a control means for controlling the main valve seat or the main valve body to constitute a flow rate control valve using a porous permeable material, and the main valve body, the main valve seat and the control means of the porous permeable material. This constitutes adjusting means for adjusting the transmission area.

Further, the adjusting means adjusts the transmission area according to a pressure difference of the expansion device.

Further, the adjusting means adjusts the transmission area so as to have a predetermined pressure difference.

Further, the air conditioner according to the present invention sequentially connects a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger. An air conditioner equipped with a refrigerating cycle,
The throttle portion of the flow control valve is formed of a porous permeable material that communicates with the refrigerant in the flow direction.

[0026] Further, there is provided an adjusting means for adjusting a transmission area of the porous permeable material. A valve body having a first flow path opened in a valve chamber side wall, a main valve seat having a second flow path opened in a valve chamber bottom face, and a main valve body capable of closing the main valve seat in a valve chamber; A second flow control valve is constituted by using a porous permeable material for the main valve body.

Also, a valve body having a first flow path opened in a valve chamber side wall, a main valve seat having a second flow path opened in a valve chamber bottom face, and a main valve body capable of closing the main valve seat in the valve chamber. And a second flow control valve using a porous permeable material for the main valve seat.

A main valve body having a peripheral surface in contact with a side surface of the main valve seat, and a contact area between the peripheral surface and the side surface being varied by movement in the opening and closing direction; And a control means for controlling the movement, wherein the main valve body, the main valve seat and the control means constitute an adjusting means for adjusting the permeation area of the porous permeable material.

Further, the adjusting means adjusts the permeation area according to the pressure difference of the second flow control valve.

Further, the adjusting means adjusts the permeation area so as to have a predetermined pressure difference during an operation for lowering the latent heat ratio.

In addition, the pores of the porous permeable material are set in the range of 200 to 0.5 micrometers.

Further, a control unit is provided for controlling the second flow control valve to be closed during the operation for lowering the latent heat ratio.

The control section controls the second flow control valve to be closed during cooling or dehumidification and heating operations.

Further, a control unit for controlling the second flow control valve to be closed when the heating operation is started is provided.

Further, a control unit is provided for controlling the second flow control valve to be closed when the difference between the set temperature and the room temperature is equal to or more than a predetermined value during the heating operation.

An air conditioner having a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. In the above, the second flow control valve is constituted by a capillary having an inner diameter of 1 mm or more.

An air conditioner equipped with a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. In the above, the second flow control valve is constituted by a capillary, and a heat exchanger is provided for exchanging heat between the capillary inlet pipe and the pipe between the second indoor heat exchanger and the compressor during a cooling and dehumidifying operation. Things.

An air conditioner having a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. In the above, the second flow control valve is constituted by a capillary tube, and a heat exchanger for exchanging heat with a pipe between the second indoor heat exchanger and the compressor is provided.

[0039] The apparatus further includes a bypass passage for bypassing the second indoor heat exchanger and the second flow control valve, and opening and closing means for opening and closing the bypass passage.

An air conditioner having a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. And a bypass passage for bypassing the second indoor heat exchanger and the second flow control valve, and opening and closing means for opening and closing the bypass passage.

The apparatus further comprises control means for controlling the second flow rate control valve and the opening / closing means, wherein the control means throttles the second flow rate control valve in accordance with the sensible heat capacity during operation for lowering the latent heat ratio. The control is such that the heat exchanger split operation for opening the means and the refrigerant reheating operation for closing the opening / closing means by narrowing the second flow control valve.

The apparatus further comprises control means for controlling the second flow control valve and the opening / closing means, wherein the control means closes the second flow control valve and closes the opening / closing means when the sensible heat ratio decreases. To control.

Further, a control means for controlling the second flow rate control valve and the opening / closing means is provided, and when the heating operation is started, the second flow rate control valve is closed and the opening / closing means is opened.

Further, a receiver for storing the liquid refrigerant during the heating operation is provided in a pipe between the first flow control valve and the first indoor heat exchanger.

[0045]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 FIG. 1 is a refrigerant circuit diagram of an air conditioner showing an example of an embodiment of the present invention,
Parts similar to those of the conventional device are denoted 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, and 4 is an electric expansion valve which is a first flow control valve. ,
5 is a first indoor heat exchanger, 7 is a second indoor heat exchanger,
A second flow control valve 6 is provided between the first indoor heat exchanger 5 and the second indoor heat exchanger 7, and these are sequentially connected by piping to constitute a refrigeration cycle.
The compressor 1, the four-way valve 2, the outdoor heat exchanger 3, and the first flow control valve 4 constitute an outdoor unit 11, and the first indoor heat exchanger 5, the second indoor heat exchanger 7, and the second flow control valve 6 constitutes the indoor unit 12. The refrigerant of this refrigeration cycle includes R410, which is a mixed refrigerant of R32 and R125.
A is used.

FIG. 2 is a view showing the structure of the second flow control valve 6 of the air conditioner shown in FIG. 1, wherein reference numeral 21 denotes a first flow path, the first indoor heat exchanger 5 is connected, and Is a second flow path, to which the second indoor heat exchanger 7 is connected. Reference numeral 23 denotes a main valve seat in which the second flow path opens, and in this figure, is formed integrally with the valve body. A main valve element 24 slides up and down along the inner surface of the main body of the second flow path control valve 6.
The main valve element 24 and the main valve element 24 constitute a throttle section. Reference numeral 25 denotes an electromagnetic coil for driving the main valve element 24, which cuts off power through the electromagnetic coil 25 based on a command from a control unit (not shown),
Open and close. The main valve body 24 is formed of a porous permeable material. Specifically, a sintered metal (metal powder or alloy powder) having a ventilation hole (pore inside the porous body through which a fluid can pass) of 10 micrometers is used. And press molded
Then, it is manufactured by sintering at a temperature below the melting point. Further, the second flow control valve 6
Is de-energized to the electromagnetic coil 25 so that the main valve body 2
The first flow path 21 and the second flow path 22 are connected with almost no pressure loss by pulling up the upper part 4 and separating the main valve body 24 from the main valve seat 23 (FIG. 2A). When the electromagnetic coil 25 is energized, the main valve body 24 is lowered to the lower portion, and the main valve body 24 is brought into close contact with the main valve seat 23. The flow path 22 is connected (FIG. 2B).

Next, the operation of the air conditioner according to the present embodiment during cooling will be described. In FIG. 1, the flow of the refrigerant during cooling is indicated by solid arrows. Cooling operation is usually performed when the sensible heat load and latent heat load in the room are both large, such as during startup or during the summer. It is divided into dehumidification operation corresponding to a large case. Normal cooling operation is the second
The electromagnetic coil 25 of the flow control valve 6 is turned off. At this time, the high-temperature and high-pressure refrigerant vapor exiting the compressor 1 is supplied to the four-way valve 2.
Then, it flows into the outdoor heat exchanger 3 and exchanges heat with the outside air to condense and liquefy. This high-pressure liquid refrigerant is supplied to the first flow control valve 4
, And becomes a gas-liquid two-phase refrigerant and evaporates in the first indoor heat exchanger 5 and the second indoor heat exchanger 7 by removing the sensible heat and latent heat of the indoor air. In the second flow control valve 6, FIG.
As shown in (a), since the first flow path 21 and the second flow path are connected with a large opening area, there is almost no refrigerant pressure loss when passing through this valve. There is no decrease in The low-pressure vapor refrigerant that has exited the second indoor heat exchanger 7 passes through the four-way valve 2 and returns to the compressor 1 again.
The opening degree of the first flow control valve 4 during the normal cooling operation is controlled so that the superheat degree of the outlet refrigerant of the second indoor heat exchanger is 5 ° C., for example.

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. 3 correspond to the English characters shown in FIG. During this dehumidifying operation, the electromagnetic coil 2 of the second flow control valve
5, the main valve body 24 is brought into close contact with the main valve seat 23 as shown in FIG. 2B, and the first indoor heat exchanger which is the first flow path 21 through the vent hole of the main valve body 24. 5 and the second flow path 22
Is connected to the inlet of the second indoor heat exchanger 7. At this time,
The high-temperature and high-pressure refrigerant vapor (point A) that has exited the compressor 1 flows into the outdoor heat exchanger 3 through the four-way valve 2 and exchanges heat with outside air to condense (point B). This high-pressure liquid refrigerant or gas-liquid two-phase refrigerant is slightly depressurized by the first flow control valve 4 (point C), becomes an intermediate-pressure gas-liquid two-phase refrigerant, and flows into the first indoor heat exchanger 5. The refrigerant that has flowed into the first indoor heat exchanger 5 exchanges heat with indoor air and is further condensed (point D). The intermediate-pressure liquid refrigerant or gas-liquid two-phase refrigerant flowing out of the first indoor heat exchanger 5 flows into the second flow control valve 6. In the second flow control valve 6, since the main valve body 24 is in close contact with the main valve seat 23 as shown in FIG. 2B, the refrigerant flowing into this valve is made of a sintered metal. The gas flows into the second indoor heat exchanger 7 through the ventilation hole in the valve element 24. The ventilation hole of this main valve body 24 is 1
The refrigerant passing through the vent hole is reduced in pressure to become a low-pressure gas-liquid two-phase refrigerant and flows into the second indoor heat exchanger 7 (point E). The refrigerant flowing into the second indoor heat exchanger 7 evaporates by removing the sensible heat and latent heat of the indoor air. The low-pressure vapor refrigerant that has exited the second indoor heat exchanger 7 passes through the four-way valve 2 and returns to the compressor 1 again. The indoor air is heated in the first indoor heat exchanger 5 and cooled and dehumidified in the second indoor heat exchanger 7, so that dehumidification can be performed while preventing the room temperature from lowering.

In this dehumidifying operation, the rotation frequency of the compressor 1 and the number of rotations of the fan of the outdoor heat exchanger 3 are adjusted to control the amount of heat exchange of the outdoor heat exchanger 3 and the first indoor heat exchanger. 5
To control the amount of indoor air heating to control the blowout temperature over a wide range. Further, by controlling the opening degree of the first flow control valve 7 and the number of rotations of the indoor fan, the condensation temperature of the first indoor heat exchanger 5 is controlled, and the amount of indoor air heated by the first indoor heat exchanger 5 is controlled. You can also. The degree of opening of the second flow control valve 4 is, for example, such that the degree of superheat of the outlet refrigerant of the second indoor heat exchanger is 5 ° C.
It is controlled so that

In this embodiment, the sintered metal is
Since the second flow control valve 6 used in Step 4 is disposed between the first indoor heat exchanger 5 and the second indoor heat exchanger 7 and used as a throttle device during the cooling and dehumidifying operation, the second flow control valve is used. The refrigerant flow noise when a liquid refrigerant or a gas-liquid two-phase refrigerant passes through 6 can be greatly reduced. When the gas-liquid two-phase refrigerant passes through the ordinary orifice type expansion device, a loud refrigerant flow noise is generated. Particularly, it is known that a large refrigerant flow noise is generated when the flow mode of the gas-liquid two-phase refrigerant is a slag flow. The reason for the generation of the refrigerant flow noise is that when the slag flow passes through a small hole such as an orifice in the expansion device, the refrigerant vapor slag or the refrigerant bubble larger than the small hole is broken, and the refrigerant vapor slag or the refrigerant bubble It is conceivable that vibrations are generated due to collapse of the gas, and that the vapor refrigerant and the liquid refrigerant alternately pass through the small holes, so that the pressure loss generated when the refrigerant passes through the small holes varies greatly.
In the second flow control valve shown in FIG. 2, the gas-liquid two-phase refrigerant or the liquid refrigerant that has exited the first indoor heat exchanger 5 during the cooling and dehumidifying operation is discharged from the main valve body 24 made of sintered metal. At this time, the refrigerant passes through the fine ventilation holes and is decompressed and flows into the second indoor heat exchanger 7, so that the refrigerant vapor slag and the collapse of the refrigerant bubbles do not occur, and the vapor refrigerant and the liquid refrigerant are simultaneously discharged from the main valve body 24. Since the gas passes through the vent hole, no large fluctuation in pressure loss occurs. For this reason, noise reduction means such as wrapping a sound insulating material or a vibration damping material around the outer periphery of the valve, which is required in the conventional device, becomes unnecessary, so that the cost can be reduced and the recyclability of the air conditioning equipment 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 general problem of a refrigeration cycle such as a refrigerator. A similar effect can be obtained by widely applying such a refrigeration cycle in general.

The flow rate characteristics of the second flow rate control valve 6 during the cooling and dehumidifying operation (the relationship between the flow rate of the refrigerant and the pressure loss) are determined by the diameter of the vent hole of the sintered metal used for the main valve body 24 and the length of the flow path through which the refrigerant passes. It can be adjusted by adjusting the height. That is, when a certain refrigerant flow rate is caused to flow with a small pressure loss, it is only necessary to increase the size of the sintered metal vent or to reduce the diameter of the valve body. In addition, as shown in FIG.
6 may be provided to reduce the length of the flow path passing through the sintered metal. Conversely, when a certain refrigerant flow rate is caused to flow with a large pressure loss, the sintered metal vent holes may be reduced, or the diameter of the valve body may be increased. The diameter of the sintered metal vent hole used for the main valve body 24 and the shape of the valve body are optimally designed at the time of equipment design. Note that, instead of the hollow portion 26 in which the tip of the main valve body 24 is open, a hollow portion surrounded by a sintered metal may be used. Further, when the main valve body 24 is closed, the columnar main valve body 24 is closed.
If the peripheral surface side and the bottom surface side are divided into the flow channel inlet side and the outlet side, adjustment of pressure loss and the like can be performed independently on the peripheral surface side and the bottom surface side. It has been confirmed by experiments that if the diameter of the vent hole of the sintered metal is from 200 to 0.5 micrometers, a sufficient effect of reducing the flow noise of the refrigerant and reducing the original can be obtained. As a preferred example, the refrigerant is R410A,
When the pressure difference between before and after the sintered metal is about 1 MPa (megapascal), it is preferable that the diameter of the vent hole is about 10 micrometers. When the pressure difference is large, the diameter of the vent hole is smaller, and when the pressure difference is small, the diameter of the vent hole is designed to be larger. The vents of this sintered metal
The smaller the diameter is, the smaller the sintered metal becomes.
The flow control valve 6 is also compact. When a sintered metal having a small air hole is used for the valve body, a metal mesh or the like is provided upstream of the second flow control valve 6 in order to prevent the air hole from being clogged with foreign matter or sludge in the refrigeration cycle. A filter may be installed.

In the present embodiment, the second flow control valve is described as performing opening and closing operations by energizing or de-energizing the electromagnetic coil 25. However, the main valve body 24 is continuously driven by the stepping motor. Alternatively, the flow characteristics of the second flow control valve may be continuously changed. By continuously controlling the flow characteristics in this manner, the controllability of temperature and humidity during the cooling and dehumidifying operation is further improved, and a comfortable indoor space can be realized.

Next, an 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 during operation of the air conditioner in order to set a favorable temperature and humidity environment for a resident in the room.
The set temperature and the set humidity may be input directly by the occupant from the remote control of the indoor unit, and the set temperature and the set humidity of the indoor unit such as for a hot person, a cold person, a child, and an elderly person. The remote controller may store an optimum value table of temperature and humidity determined for each target resident, and directly input only the target resident. The indoor unit 12 is provided with sensors for detecting the temperature and humidity of the air taken into the indoor unit in order to detect the indoor temperature and humidity.

When the air conditioner is started, the difference between the set temperature and the current indoor suction air temperature is calculated as a temperature deviation, and the difference between the set humidity and the current indoor suction air humidity is calculated as a humidity deviation. The rotational frequency of the compressor 1 of the air conditioner is set so that these deviations become zero or within a predetermined value.
The controller controls the outdoor fan speed, the indoor fan speed, the throttle opening of the first flow control valve 4, and the opening and closing of the second flow control valve 6. At this time, when controlling the temperature and humidity deviations to be zero or within a predetermined value, the air conditioner is controlled by giving priority to the temperature deviations over the humidity deviations. That is, when both the temperature deviation and the humidity deviation are large at the time of starting the air conditioner, the second flow control valve 7 is opened, and the temperature deviation in the room is preferentially reduced to zero or within a predetermined value in the normal cooling operation. Drive so that When the cooling capacity of the air conditioner matches the heat load of the room and the temperature deviation is zero or within a predetermined value, a humidity deviation is detected. At this time, the humidity deviation becomes zero or within a predetermined value. If you have
Continue the current operation.

If 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 control valve 6 is throttled to switch to the cooling and dehumidifying operation. In this cooling and dehumidifying operation, the heating amount of the second indoor heat exchanger 7 is controlled so that the indoor temperature deviation can be maintained at zero or within a predetermined value, and the humidity deviation is set at zero or within a predetermined value. Next, the amount of cooling and dehumidification of the first indoor heat exchanger 5 is controlled. The heating amount of the second indoor heat exchanger 7 is controlled by adjusting the fan speed of the outdoor heat exchanger 3 and the opening of the first flow control valve 4. The amount of cooling and dehumidification of the first indoor heat exchanger 5 is controlled by the rotation frequency of the compressor 1, the number of fan rotations of the indoor unit 12, and the like.

As described above, in this embodiment, the refrigerant circuit is switched between the normal cooling operation and the cooling and dehumidifying operation according to the load on the room during the cooling operation, so that the temperature and humidity environment in the room can be changed according to the occupants' preference. Can be controlled to an optimum state according to

Embodiment 2 FIG. 5 is a configuration diagram of a second flow control valve of an air conditioner showing another example of the embodiment of the present invention. Components that are the same as or similar to those shown in FIG. Therefore, the duplicate description will be omitted. In this embodiment, an ordinary metal valve is used for the main valve body 24, and a sintered metal is used for the main valve seat 23. As in FIG. 2, when the electromagnetic coil 25 is de-energized, the main valve body 24 separates from the main valve seat 23 and the first flow path 21 and the second flow path
Channel 22 leads to almost no pressure loss (FIG. 5).
(A)). By energizing the electromagnetic coil 25,
The main valve element 24 is brought into close contact with the main valve seat 23, and the first flow path 21 and the second flow path 22 are connected via the vent hole of the main valve seat 23 (FIG. 2B). During the cooling and dehumidifying operation, the first indoor heat exchanger 5 is energized by energizing the electromagnetic coil as shown in FIG.
Is depressurized through the ventilation hole of the main valve seat 23 in the second flow control valve 6 and flows into the second indoor heat exchanger 7, so that no refrigerant flow noise is generated and a comfortable room is generated. Space can be realized. During normal cooling, the main coil 24 is pulled away from the main valve seat 23 as shown in FIG. 5A by turning off the electromagnetic coil, so that the first flow path 21 and the second flow path 22 Since there is no pressure loss, there is no pressure loss between the first indoor heat exchanger 5 and the second indoor heat exchanger 7, and there is no decrease in cooling capacity or efficiency.

As shown in the embodiment shown in FIG.
Forming the main valve seat 23 with a sintered metal as shown in the present embodiment is relatively simpler than forming the main valve seat 4 with a sintered metal as shown in the present embodiment, so that it is relatively easy, and as a result, In addition, it is possible to obtain a flow control valve that does not generate refrigerant flow noise. Also, the flow characteristics of the flow control valve can be designed easily because the shape is simple. The flow characteristic of the flow control valve is adjusted by adjusting the diameter of the vent of the sintered metal used for the main valve seat 23 and the length of the flow path through which the refrigerant passes, as in the embodiment of FIG. Can be. That is, when a certain flow rate of the refrigerant is caused to flow with a small pressure loss, the ventilation hole of the sintered metal may be increased, or the length of the passage of the main valve seat through which the refrigerant passes may be reduced. Conversely, when a certain refrigerant flow rate is caused to flow with a large pressure loss, the ventilation hole of the sintered metal is reduced or the flow path length of the main valve seat through which the refrigerant passes is increased as shown in FIG. Is also good.

In the first and second embodiments,
An example in which an on-off valve in which the valve body is formed of sintered metal and an on-off valve in which the main valve seat is formed of sintered metal is used as the second flow control valve has been described. However, the present invention is not limited thereto.
Any location where a decompression action occurs in the valve may be used, and both the valve body and the main valve seat may be formed of sintered metal.
As the material of the sintered metal, iron is the main component, carbon,
Low alloy steel with added copper, nickel, etc., stainless steel,
Alternatively, bronze may be used.

Further, in the first and second embodiments, an example was described in which sintered metal was used for the valve body or the main valve seat. However, the present invention is not limited to this, and the gas-liquid two-phase refrigerant is changed to liquid and gas. It is sufficient that the pressure is reduced without separation, and for example, a porous material such as a resin foam material can exert the same effect.

In the first and second embodiments, an example in which a second flow control valve using a sintered metal is used between the first indoor heat exchanger 5 and the second indoor heat exchanger 7 will be described. However, the present invention is not limited to this. By using a valve using a sintered metal for the first flow control valve 4, it is possible to prevent the refrigerant flow noise from being generated at the first flow control valve. Further, the use of the sintered metal is not limited to the flow control valve, but can be applied to all locations where the refrigerant flow noise is generated in the refrigeration cycle, and the generation of the refrigerant flow noise can be suppressed. For example, by using a sintered metal inside a refrigerant distributor used for a heat exchanger divided into a plurality of flow paths, generation of refrigerant flow noise from the refrigerant distributor can be prevented. Also, in a device using a capillary tube or the like as a conventional expansion device such as a home refrigerator, the use of a sintered metal as an expansion device instead of a capillary tube can prevent generation of refrigerant flow noise.

Embodiment 3 FIG. 7 is a configuration diagram of a second flow control valve of an air conditioner showing another example of the embodiment of the present invention. Components that are the same as or similar to those shown in FIG. Therefore, the duplicate description will be omitted. In this embodiment, the main valve body 24 is made of a metal valve such as copper or brass, and the main valve seat 23 is made of a porous permeable material, for example, the vent hole 1.
It is composed of 0 micromillimeter sintered metal.
Reference numeral 25 denotes a drive unit for continuously driving the main valve element 24, which is constituted by, for example, a stepping motor, and controls the main valve element 24 to move in the opening and closing direction by control means (not shown).

In the second flow control valve 6 according to this embodiment, when the first indoor heat exchanger 5 and the second indoor heat exchanger 7 are connected without pressure loss in the circuit configuration of FIG. As shown in FIG. 7A, the main valve body 24 is pulled up by the stepping motor 25 so that the refrigerant flows through the gap between the main valve body 24 and the main valve seat 23. On the other hand, when a pressure difference is generated between the first indoor heat exchanger 5 and the second indoor heat exchanger 7 such as during a cooling and dehumidifying operation, the main valve body 24 is pulled down by the stepping motor 25 as shown in FIG. The gap between the main valve body 24 and the main valve seat 23 is eliminated so that the refrigerant flows through the vent holes in the main valve seat 23 which is a sintered metal. At this time, by adjusting the amount by which the main valve element 24 is lowered by the stepping motor 25, the passage area of the sintered metal through which the refrigerant passes can be changed, and the pressure loss of the refrigerant when passing through the sintered metal can be reduced. Can be controlled. That is, the main valve element 24 by the stepping motor 25
, The pressure loss of the refrigerant passing through the second flow control valve 6 can be freely changed, and the pressure difference between the first indoor heat exchanger 5 and the second indoor heat exchanger 7 can be reduced. Can be controlled.

During the cooling and dehumidifying operation, the first indoor heat exchanger 5
The temperature difference between the substantially middle refrigerant temperature and the middle refrigerant temperature of the second indoor heat exchanger 7 causes
Is indirectly detected, and the amount of movement of the main valve element 24 of the second flow control valve 6 is controlled so that the pressure difference becomes a predetermined value, thereby making the indoor temperature and humidity environment more comfortable. Can be controlled.

As shown in FIG. 8, a part of the main valve body 24 is constituted by a metal valve 24a, the other part is constituted by a sintered metal 24b, and the main valve seat 23 is constituted by a metal. The moving amount of the seat 24 may be continuously controlled by the stepping motor 25 so that the pressure difference between the front and rear of the second flow control valve 6 can be freely adjusted. In addition to the case where the main valve body moves continuously up and down, a mechanism is provided to change the passage area of the sintered metal through which the refrigerant passes due to rotational movement and the like,
The pressure loss of the refrigerant passing through the sintered metal may be freely controlled.

Embodiment 4 Hereinafter, an air conditioner according to Embodiment 3 of the present invention will be described. The present embodiment relates to a heating operation, and a refrigerant circuit constituting an air conditioner is, for example, the same as FIG. 1 in the first embodiment,
The structure of the second flow control valve 6 is the same as that of FIG. The operation during heating of the air-conditioning apparatus according to the present embodiment will be described. In FIG. 1, the flow of the refrigerant at the time of heating is indicated by a dashed arrow. In the normal heating operation, the electromagnetic coil 25 of the second flow control valve 6 is set in a non-energized state. At this time, the high-temperature and high-pressure refrigerant vapor exiting the compressor 1 flows into the second indoor heat exchanger 7 and the first indoor heat exchanger 5 through the four-way valve 2, and exchanges heat with indoor air to condense and liquefy. I do. Note that the second flow control valve 6 corresponds to FIG.
As shown in (a), since the first flow path 21 and the second flow path are connected with a large opening area, there is almost no refrigerant pressure loss when passing through this valve, and the heating capacity and the efficiency due to the pressure loss are reduced. There is no decrease in The high-pressure liquid refrigerant that has exited the first indoor heat exchanger 5 is reduced in pressure to a low pressure by the first flow control valve 4, becomes a gas-liquid two-phase refrigerant, exchanges heat with outdoor air in the outdoor heat exchanger 3, and evaporates. I do. The low-pressure vapor refrigerant that has exited the outdoor heat exchanger 3 is:
It returns to the compressor 1 again through the four-way valve 2. The degree of opening of the first flow control valve 4 during the normal cooling operation is controlled, for example, so that the degree of superheating of the refrigerant at the outlet of the outdoor heat exchanger 3 is 5 ° C.

Next, the operation during the heating and dehumidifying operation will be described with reference to FIG.
This will be described with reference to the pressure-enthalpy diagram shown in FIG. The English characters shown in FIG. 9 correspond to the English characters shown in FIG. During the heating and dehumidifying operation, the electromagnetic coil 25 of the second flow control valve is energized to bring the main valve body 24 into close contact with the main valve seat 23 as shown in FIG. The outlet of the second indoor heat exchanger 7 which is the second flow path 22 and the inlet of the first indoor heat exchanger 5 which is the first flow path 21 are connected.
At this time, high-temperature and high-pressure refrigerant vapor exiting the compressor 1 (point F)
Flows into the second indoor heat exchanger 7 through the four-way valve 2 and exchanges heat with indoor air to condense (point E). This high-pressure liquid refrigerant or gas-liquid two-phase refrigerant flows into the second flow control valve 6. In the second flow control valve 6, since the main valve body 24 is in close contact with the main valve seat 23 as shown in FIG. 2B, the refrigerant flowing into this valve is made of a sintered metal. The gas flows into the first indoor heat exchanger 5 through the ventilation hole in the valve element 24. The ventilation hole of the main valve body 24 is about 10 micrometers, and the refrigerant passing through this ventilation hole is decompressed, becomes a gas-liquid two-phase refrigerant of an intermediate pressure, and flows into the first indoor heat exchanger 5 ( D
point). 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 evaporates by removing the sensible heat and latent heat of the indoor air (point C). The intermediate-pressure gas-liquid two-phase refrigerant that has exited the first indoor heat exchanger 5 flows into the first flow control valve 4, is decompressed to a low pressure, further flows into the outdoor heat exchanger 3, and exchanges heat with outdoor air. And evaporate. The low-pressure vapor refrigerant that has exited the indoor / outdoor heat exchanger 4 passes through the four-way valve 2 and returns to the compressor 1 again.

In this heating and dehumidifying operation, the room air is
Since it is heated by the indoor heat exchanger 7 and cooled and dehumidified by the first indoor heat exchanger 5, dehumidification can be performed while heating the room. In the heating and 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 amount of heat exchange of the outdoor heat exchanger 3, and the indoor air by the first indoor heat exchanger 5 is controlled. By controlling the amount of heating, the blowing temperature can be controlled over a wide range. Further, the evaporating temperature of the first indoor heat exchanger 5 is controlled by adjusting the opening degree of the first flow control valve 7 and the number of rotations of the indoor fan, and the amount of indoor air dehumidified by the first indoor heat exchanger 5 is controlled. You can also. The degree of opening of the second flow control valve 4 is controlled such that the degree of supercooling of the refrigerant at the outlet of the second indoor heat exchanger 7 becomes 10 ° C., for example.

As described above, in the present embodiment, since the second flow control valve using the sintered metal as the valve body is used,
The dehumidifying operation during heating becomes possible, and the generation of refrigerant flow noise during the heating and dehumidifying operation can be prevented, so that a comfortable space can be realized in terms of temperature and humidity environment and noise.

Further, by supplying a current to the electromagnetic coil 25 of the second flow control valve at the time of starting heating or the like, the temperature of the heating air can be increased. That is, the heating dehumidification cycle is formed at the time of starting heating, and the evaporation temperature of the first indoor heat exchanger 5 is controlled by the second flow control valve so as to be substantially equal to the suction air temperature in the room. Since the evaporation temperature of the first indoor heat exchanger 5 is almost equal to the temperature of the intake air in the room, the first indoor heat exchanger 5 hardly performs cooling and dehumidification, and as a result, the heat transfer area of the condenser during heating is normally The heating operation becomes about half of that of the conventional heating operation. Therefore, the condensing temperature is higher than that in the normal heating operation, and the outlet temperature can be increased. Further, even during the heating high-temperature blowing operation, the second flow control valve 6
There is no generation of refrigerant flow noise at the time, and there is no problem in terms of noise.

Next, an example of a specific heating operation control method of the air conditioner of this embodiment will be described. As described in Embodiment 1, the set temperature and the set humidity and the intake air temperature and the humidity are input to this air conditioner. This air conditioner performs a high-temperature blowing operation for a predetermined time, for example, 5 minutes when heating is started, and then shifts to a normal heating operation. Thereafter, the normal heating operation and the heating dehumidification operation are switched and controlled in accordance with the temperature deviation and the humidity deviation of the room.

When the heating operation is started, the second flow control valve 6 is closed, and the compressor 1 is started. At this time, the fan rotation speed of the outdoor heat exchanger 3, the valve opening of the first flow control valve 4, and the like are adjusted so that the cooling and dehumidifying capacity of the first indoor heat exchanger 5 becomes zero. Control is performed so that the evaporation temperature of the indoor heat exchanger 5 becomes equal to the intake air temperature. When a predetermined time of 5 minutes elapses from the start of the compressor, the second flow control valve 6 is opened, and the operation shifts to the normal heating operation. 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 becomes zero or within a predetermined value. If the temperature deviation becomes zero or within a predetermined value due to this heating normal operation, a humidity deviation is detected, and if this humidity deviation is within zero or a predetermined value,
Even when the humidity deviation is equal to or more than a predetermined value, if humidification is required, the normal heating operation is continued. On the other hand, when the humidity deviation is zero or a predetermined value or more and dehumidification is required, the second flow control valve 6 is closed, and the heating dehumidification operation is performed. In this heating and dehumidifying operation, the amount of heating of the second indoor heat exchanger 7 is controlled so that the indoor temperature deviation can be maintained at zero or within a predetermined value, and the humidity deviation is within zero or within a predetermined value. Next, the amount of cooling and dehumidification of the first indoor heat exchanger 5 is controlled. The amount of heating of the second indoor heat exchanger 7 is controlled by the rotation frequency of the compressor 1, the number of rotations of the fan of the indoor unit 12, and the like. The control of the amount of cooling and dehumidification of the first indoor heat exchanger 5 includes the outdoor heat exchanger 3.
And the opening degree of the first flow control valve 4 and the like.

As described above, in this embodiment, the refrigerant circuit is switched to the high-temperature blowing operation, the normal heating operation, or the heating dehumidification operation in accordance with the operation time during the heating operation and the load on the room, so that the temperature inside the room is changed. The humidity environment can be controlled to an optimum state according to the occupants' preferences.

Embodiment 5 FIG. 10 is a refrigerant circuit diagram of an air conditioner showing another example of the embodiment of the present invention.
The same reference numerals are given to the same or similar components as those shown in (1), and the overlapping description is omitted. In this embodiment, the upper part of the two rows of indoor heat exchangers folded in multiple stages is the first indoor heat exchanger 5 and the lower part is the second indoor heat exchanger 7. The suction air of the indoor unit is heated by the indoor heat exchanger 5, the suction air is cooled and dehumidified by the lower second indoor heat exchanger 7, and the suction air is mixed by an indoor fan (not shown). It is blowing into the room. During the heating and dehumidifying operation, the lower second indoor heat exchanger 7 heats the suction air of the indoor unit, and the upper first indoor heat exchanger 5 cools and dehumidifies the suction air. They are mixed by a fan (not shown) and blown into the room. Further, also in this embodiment, since the second flow control valve 6 uses the main valve body 24 formed of the sintered metal shown in FIG. 2, the generation of the refrigerant flow noise occurs during the cooling dehumidification and the heating dehumidification operation. And a low-noise indoor unit can be realized.

The refrigerant flow path during cooling of the indoor heat exchanger is as follows:
The inlet is formed as one flow path, and is branched into two flow paths by a three-way pipe 8a on the way to form a first indoor heat exchanger 5. The two flow paths are merged into one flow path by a three-way pipe 8b. 2 Connected to the flow control valve 6. Further, the outlet pipe of the second flow control valve 6 is again branched into two flow paths by a three-way pipe 8c to form a second indoor heat exchanger 7, and a three-way pipe 8d is formed at the outlet of the second indoor heat exchanger 7. By
The two flow paths merge into one flow path. In this way, the inlet refrigerant flow path of the indoor heat exchanger during cooling is made into one flow path, and by branching into two flow paths in the middle, refrigerant pressure loss during cooling can be reduced, and during normal cooling operation and cooling dehumidification operation. Performance is improved. In addition, at the time of heating, the inlet refrigerant flow path has two flow paths and the outlet flow path has one flow path, so that the flow velocity of the refrigerant near the condenser outlet having a small heat transfer coefficient of the refrigerant is increased, and the heat exchanger performance is improved.
Further, since the flow path between the first indoor heat exchanger 5 and the second indoor heat exchanger 7 is made into one flow path by a three-way pipe, only one second flow control valve 6 is required, and the indoor unit is inexpensive. Become.

In this embodiment, the configuration in which the upper part of the two rows of heat exchangers is the first indoor heat exchanger 5 and the lower part is the second indoor heat exchanger has been described, but the present invention is not limited to this. The first row of the two-row heat exchanger may be the second indoor heat exchanger 7, and the second row may be the first indoor heat exchanger 5. Further, a three-row heat exchanger or a mixed type of two-row and three-row heat exchangers may be used.

In this embodiment, a receiver 30 for storing a liquid refrigerant is provided in the outdoor unit 11 in a pipe between the first flow control valve 4 and the first indoor heat exchanger 5. This receiver stores excess refrigerant generated during normal heating operation or heating dehumidification operation, and prevents performance degradation due to excessive refrigerant during these operations. That is, in the cooling and dehumidifying operation, the outdoor heat exchanger 3 and the first indoor heat exchanger 5 operate as condensers, and the internal volume of the condenser is the largest, so that the required refrigerant amount is the largest. Therefore, the refrigerant charging amount of the air conditioner is determined from the refrigerant amount required during the cooling and dehumidifying operation. During the heating operation, the first indoor heat exchanger 5 and the second indoor heat exchanger 7 having smaller internal volumes than the outdoor heat exchanger 3 serve as condensers. During the heating and dehumidifying operation, the second indoor heat exchanger 7 is used. Since only the condenser is used, the required refrigerant amount during these operations is smaller than during the cooling and dehumidifying operation. When the heating operation or the heating dehumidifying operation is performed without providing the receiver 30,
Since the operation is performed in a state where the amount of the refrigerant is excessive, the amount of liquid back to the compressor 1 increases, and the reliability of the compressor decreases and the performance of the cycle decreases. Therefore, in this embodiment,
Excess liquid refrigerant during the heating operation or the heating and dehumidifying operation is stored in the receiver 30, and the amount of the refrigerant during all operations is optimally controlled, thereby improving the reliability and performance of the compressor. Note that the internal volume of the receiver 30 can be determined in advance by, for example, testing the optimal amount of refrigerant during each operation and determining the difference between the maximum refrigerant amount and the minimum refrigerant amount as an internal volume that can be stored. Further, since the receiver 30 is installed in the outdoor unit 11, the size of the indoor unit 12 does not increase.

Embodiment 6 FIG. FIG. 11 is a refrigerant circuit diagram of an air conditioner showing another example of the embodiment of the present invention.
The same reference numerals are given to the same or similar components as those shown in (1), and the overlapping description is omitted. In this embodiment, a throttle device 31 using a sintered metal and an electromagnetic on-off valve 37 are connected in parallel to a pipe between the first indoor heat exchanger 5 and the second indoor heat exchanger 7, and a second flow rate is set. It constitutes a control valve.
As shown in FIG. 12, the drawing device 31 using this sintered metal has a cylindrical shape with one end inside the container closed and the other end open, and communicates with the inside and outside of the cylindrical shape via the peripheral surface and the bottom surface. The sintered metal 32 is inserted to form a drawing portion, and both ends of the sintered metal 32 are fixed in the container by fixing plates 33 and 34 and springs 35 and 36. The fixing plate 34 is formed in a disk shape in which a circumferential portion is partially cut.

The operation of this embodiment during normal cooling operation, cooling dehumidification operation, normal heating operation, heating dehumidification operation, and heating high-temperature blowing operation is the same as that of the embodiment of FIG. The operation of the expansion device 31 and the on-off valve 37 using the sintered metal during each operation will be described below. During the normal cooling operation and the normal heating operation, the electromagnetic on-off valve 37 is opened to configure a refrigeration cycle. At this time, since the throttle device 31 using the sintered metal has a larger flow resistance than the electromagnetic on-off valve 37 in the open state, most of the refrigerant does not flow through the throttle device 31 but flows through the electromagnetic on-off valve 37. On the other hand, during the cooling dehumidifying operation, the heating dehumidifying operation, and the heating high-temperature blowing operation, the electromagnetic on-off valve 37 is closed, and the refrigerant is caused to flow through the expansion device 31 using the sintered metal to perform the decompression operation. The gas-liquid two-phase refrigerant or liquid refrigerant that has flowed into the expansion device 31 passes through a vent in the cylindrical sintered metal 32.
The air holes of the sintered metal 32 are about 200 to 0.5 micrometers, and the refrigerant passing through the fine air holes is decompressed, so that the refrigerant vapor slag and the collapse of the refrigerant bubbles do not occur. Since both the liquid refrigerant passes through the ventilation holes of the sintered metal 32, there is no large fluctuation in pressure loss.
Generation of refrigerant flow noise can be prevented. As a result, a low-noise indoor environment can be realized during the cooling and dehumidifying operation, the heating and dehumidifying operation, and the heating and high-temperature blowing operation. Therefore, the cost can be reduced, and the recyclability of the air conditioning equipment can be improved. Further, as compared with the second flow control valve using the sintered metal for the main valve element 24 shown in FIG. 2, complicated processing of the sintered metal is not required, and a normal electromagnetic valve is used as the electromagnetic on-off valve. Since it is possible, the second flow control valve can be obtained at low cost.

In this embodiment, the diaphragm device 31 is used.
I would like to describe an example in which the sintered metal 32 provided inside is formed in a cylindrical shape with one end closed, but the present invention is not limited to this, and any shape such as a disk shape, a column shape, or a rectangular parallelepiped shape can be used. What is necessary is just to be able to obtain a predetermined pressure reducing action when the refrigerant flows through the sintered metal part.

Embodiment 7 FIG. FIG. 13 is a refrigerant circuit diagram of an air conditioner showing another example of the embodiment of the present invention.
The same reference numerals are given to the same or similar components as those shown in (1), and the overlapping description is omitted. In this embodiment, a capillary 38 and an electromagnetic on-off valve 37 are connected in parallel to a pipe between the first indoor heat exchanger 5 and the second indoor heat exchanger 7 to form a second flow control valve. . The capillary 38 is a copper pipe having an inner diameter of 1 mm or more, for example, an inner diameter of 2 mm.

The operation of this embodiment during the normal cooling operation, the cooling dehumidification operation, the normal heating operation, the heating dehumidification operation, and the heating high-temperature blowing operation is the same as that of the embodiment of FIG. 1, and will be described in detail. The operation of the capillary tube 38 and the solenoid on-off valve 37 during each operation will be described below. During the normal cooling operation and the normal heating operation, the electromagnetic on-off valve 37 is opened to configure a refrigeration cycle. At this time, since the flow resistance of the capillary tube 38 is larger than that of the electromagnetic on-off valve 37 in the open state, most of the refrigerant does not flow through the capillary tube 38 but flows through the electromagnetic on-off valve 37. On the other hand, during the cooling dehumidifying operation, the heating dehumidifying operation, and the heating high-temperature blowing operation, the electromagnetic on-off valve 37 is closed, and the refrigerant is caused to flow through the capillary tube 38 to reduce the pressure.

The flow noise of the refrigerant when the gas-liquid two-phase refrigerant flows through the capillary largely depends on the flow velocity of the refrigerant in the capillary.
FIG. 14 is a measurement result of the refrigerant flow noise when the inner diameter of the capillary is changed under the condition that the refrigerant flow rate is constant at 30 kg / h. The horizontal axis of the figure is the inner diameter of the capillary, and the vertical axis is the refrigerant flow noise of the capillary. .
The refrigerant flow noise when the gas-liquid two-phase refrigerant flows through the capillary increases as the inner diameter of the capillary decreases, that is, as the flow velocity of the refrigerant in the capillary increases. This is thought to be due to the fact that the higher the flow rate of the refrigerant inside the capillary tube, the larger the pressure fluctuation inside the capillary tube, the higher the refrigerant outflow speed at the capillary outlet portion, and the higher the refrigerant energy at the capillary outlet portion. Can be According to the refrigerant flow noise measurement result shown in FIG. 14, the refrigerant flow noise generated from the capillary becomes less than the allowable value by setting the inner diameter of the capillary to 1 mm or more, and is low during the cooling dehumidification operation, the heating dehumidification operation, and the heating high-temperature blowing operation. In addition to realizing a noisy indoor environment, noise reduction measures such as wrapping sound insulation and vibration damping materials around the valve, which were required for conventional equipment, are no longer necessary, and costs can be reduced. Recyclability also improves.
Further, an inexpensive throttle device can be obtained as compared with the second flow control valve using a sintered metal for the valve body shown in FIG. Note that the measurement results of the refrigerant flow noise when the inner diameter of the capillary shown in FIG. 14 is changed are the results when the refrigerant flow rate is constant at 30 kg / h. When the flow rate of the refrigerant is smaller than 30 kg / h, the flow rate of the refrigerant becomes smaller as a whole. However, the flow rate of the refrigerant is substantially reduced by using a capillary having an inner diameter of 1 mm or more. It can be reduced below the allowable value.

Embodiment 8 FIG. FIG. 15 is a refrigerant circuit diagram of an air conditioner showing another example of the embodiment of the present invention.
The same reference numerals are given to the same or similar components as those shown in (1), and the overlapping description is omitted. In this embodiment, a capillary 38 and an electromagnetic on-off valve 37 are connected in parallel to a pipe between the first indoor heat exchanger 5 and the second indoor heat exchanger 7, and a capillary 38 inlet pipe at the time of the cooling and dehumidifying operation. And the second
A heat exchanger 40 for exchanging heat with the low-pressure pipe at the outlet of the indoor heat exchanger is provided. This heat exchanger comprises a double tube heat exchanger, a contact heat exchanger, a plate heat exchanger, or the like.

The operation of the normal cooling operation and the cooling and dehumidifying operation of this embodiment is the same as that of the embodiment of FIG. 1, and the detailed description thereof is omitted. The operation of the valve 37 and the heat exchanger 40 will be described with reference to the pressure-enthalpy diagram during the cooling and dehumidifying operation shown in FIG. The English characters shown in FIG. 16 correspond to the English characters shown in FIG. In the normal cooling operation, the refrigeration cycle is configured by opening the electromagnetic on-off valve 37. At this time, since the flow resistance of the capillary tube 38 is larger than that of the electromagnetic switching valve 37 in the open state, most of the refrigerant does not flow through the capillary tube 38, flows through the electromagnetic switching valve 37, and the heat exchanger 40 does not operate. On the other hand, in the cooling and dehumidifying operation, the electromagnetic on-off valve 37 is closed, and the refrigerant is caused to flow through the capillary tube 38 to reduce the pressure. The intermediate-pressure gas-liquid two-phase refrigerant exiting the first indoor heat exchanger 5 (point D) flows into the heat exchanger 40, where it is cooled by the low-temperature low-pressure refrigerant exiting the second indoor heat exchanger 7. Then, the refrigerant becomes an intermediate-pressure liquid refrigerant and flows into the capillary tube 38 (point E). This liquid refrigerant is reduced in pressure from the intermediate pressure to the low pressure by the capillary tube, becomes a low-pressure gas-liquid two-phase refrigerant, and flows into the second indoor heat exchanger 7 (point F).

The noise of the refrigerant flowing through the capillary is smaller in the liquid state of the refrigerant at the capillary inlet than in the gas-liquid two-phase state.
This is because the amount of vapor refrigerant generated by depressurization in the capillary is smaller when the capillary inlet refrigerant is in the liquid state than in the gas-liquid two-phase state, and the average flow velocity of the refrigerant in the capillary is smaller. In this embodiment, the second cooling operation is performed during the cooling and dehumidifying operation.
The refrigerant at the inlet of the capillary tube 38, which is a flow control valve, is supplied to the heat exchanger 4.
Since the refrigerant is cooled and liquefied by the refrigerant at the outlet of the second indoor heat exchanger 7 within 0, the refrigerant at the capillary inlet is in a liquid state, and the generation of refrigerant flow noise can be reduced. In addition, the capillary tube 38
The refrigerant state does not necessarily need to be cooled to the liquid state, and the effect of reducing the refrigerant flow noise can be obtained only by reducing the ratio (dryness) of the vapor refrigerant of the gas-liquid two-phase refrigerant. In addition, since the outlet refrigerant of the second indoor heat exchanger 7 is heated by the heat exchanger 40, the outlet refrigerant of the second indoor heat exchanger 7 becomes a wet refrigerant, as compared with the embodiment shown in FIG. Second
The refrigerant heat transfer performance in the indoor heat exchanger is improved, and the efficiency during the cooling and dehumidifying operation is also improved.

In this embodiment, an example has been described in which the inlet refrigerant of the capillary tube 38 is cooled by the outlet refrigerant of the second indoor heat exchanger 7. However, the present invention is not limited to this. The same effect can be obtained even if the cooling is performed by the cooling device.

Embodiment 9 FIG. 17 is a refrigerant circuit diagram of an air conditioner showing another example of the embodiment of the present invention.
The same reference numerals are given to the same or similar components as those shown in (1), and the overlapping description is omitted. In this embodiment, a capillary tube 38 and an electromagnetic on-off valve 37 are connected in parallel to a pipe between the first indoor heat exchanger 5 and the second indoor heat exchanger 7, and the capillary tube 38 and the second A heat exchanger 40 for exchanging heat with the low-pressure pipe at the outlet of the indoor heat exchanger is provided. This heat exchanger is composed of a double tube heat exchanger, a contact heat exchanger, and the like.

The operation of the normal cooling operation and the cooling / dehumidifying operation of this embodiment is the same as that of the embodiment of FIG. 1, and the detailed description thereof is omitted. The operation of the valve 37 and the heat exchanger 40 will be described using a pressure-enthalpy diagram during the cooling and dehumidifying operation shown in FIG. The English characters shown in FIG. 18 correspond to the English characters shown in FIG. In the normal cooling operation, the refrigeration cycle is configured by opening the electromagnetic on-off valve 37. At this time, since the flow resistance of the capillary tube 38 is larger than that of the electromagnetic switching valve 37 in the open state, most of the refrigerant does not flow through the capillary tube 38, flows through the electromagnetic switching valve 37, and the heat exchanger 40 does not operate. On the other hand, in the cooling and dehumidifying operation, the electromagnetic on-off valve 37 is closed, and the refrigerant is caused to flow through the capillary tube 38 to reduce the pressure. The intermediate-pressure gas-liquid two-phase refrigerant exiting the first indoor heat exchanger 5 (point D) flows into the capillary tube 38, and further flows into the heat exchanger 40.
While being cooled by the low-temperature and low-pressure refrigerant that has exited the second indoor heat exchanger 7, the pressure is reduced from the intermediate pressure to the low pressure, and the refrigerant flows into the second indoor heat exchanger 7 as a low-pressure gas-liquid two-phase refrigerant (F
point).

Generally, the gas-liquid two-phase refrigerant flowing in the capillary is decompressed with the flow, so that refrigerant vapor is generated from the liquid refrigerant and the dryness increases in the flow direction. The refrigerant flow noise of the gas-liquid two-phase refrigerant flowing in the capillary tube is caused by the fact that the speed of the refrigerant increases due to the refrigerant vapor generated in the capillary tube, the fluctuation of the pressure loss in the capillary tube increases, and the refrigerant speed at the outlet of the capillary tube increases. This is due to the increase in In this embodiment, the capillary 38 serving as the second flow control valve during the cooling and dehumidifying operation is used.
Is cooled by the outlet refrigerant of the second indoor heat exchanger 7 in the heat exchanger 40, so that there is almost no generation of vapor refrigerant in the capillary tube, so that the fluctuation of the pressure loss inside the capillary tube is small, and An increase in the refrigerant speed at the outlet can be suppressed. For this reason, the refrigerant flow noise generated in the capillary can be reduced, and the indoor noise environment can be improved. In addition, since the outlet refrigerant of the second indoor heat exchanger 7 is heated by the heat exchanger 40, the outlet refrigerant of the second indoor heat exchanger 7 becomes a wet refrigerant, as compared with the embodiment shown in FIG. The refrigerant heat transfer performance in the second indoor heat exchanger is improved, and the efficiency during the cooling and dehumidifying operation is also improved.

In this embodiment, the example in which the capillary tube 38 is cooled by the refrigerant at the outlet of the second indoor heat exchanger 7 has been described. However, the present invention is not limited to this, and the capillary tube 38 is cooled by room air. However, the same effect is exhibited.

Embodiment 10 FIG. FIG. 19 is a refrigerant circuit diagram of an air conditioner showing another example of the embodiment of the present invention. The same or similar components as those shown in FIG. Is omitted. This embodiment relates to improvements in the cooling dehumidifying operation and the heating high-temperature blowing operation of the embodiment shown in FIG.
A bypass flow path that bypasses a pipe between the flow control valve 4 and the first indoor heat exchanger 5 and a pipe between the second flow control valve 6 and the second indoor heat exchanger 7 is connected. An electromagnetic valve 41 as an opening / closing means is provided in the flow path. The first flow control valve 4, the second flow control valve, and the solenoid valve 41 are opened and closed in association with each other according to an instruction from a control unit (not shown).

First, the operation of this embodiment during the cooling and dehumidifying operation will be described. During normal cooling operation, the solenoid valve 41
Is closed, the second flow control valve 6 is opened, and the same operation as in the embodiment of FIG. 1 is performed. When the cooling sensible heat load decreases, the dehumidifying operation is performed by splitting the heat exchanger with the electromagnetic valve 41 opened and the second flow control valve 6 closed. In the dehumidifying operation by this heat exchanger division, the high-temperature and high-pressure refrigerant vapor exiting the compressor 1 flows into the outdoor heat exchanger 3 through the four-way valve 2,
Condenses and liquefies by exchanging heat with the outside air. The high-pressure liquid refrigerant is reduced to a low pressure by the first flow control valve 4, becomes a gas-liquid two-phase refrigerant, flows into the second indoor heat exchanger 7 through the electromagnetic valve 41, and generates sensible heat of the indoor air. And take away latent heat and evaporate. At this time, the opening degree of the first flow control valve 4 is controlled such that the superheat degree of the outlet refrigerant of the second indoor heat exchanger becomes 5 ° C., for example. In the dehumidifying operation by this heat exchanger division, the normal cooling operation uses the first indoor heat exchanger 5 and the second indoor heat exchanger 7 as evaporators, whereas only the second indoor heat exchanger 7 evaporates. Since the cooling unit is used, the evaporating temperature can be reduced as compared with the normal cooling operation, and a sufficient amount of dehumidification can be ensured even when the cooling capacity is small and the rotation frequency of the compressor 1 is reduced.

Further, when the cooling sensible heat capacity of the room is reduced, and when the rotation frequency of the compressor 1 is reduced in the dehumidifying operation by dividing the heat exchanger, the evaporation temperature rises and the amount of dehumidification cannot be sufficiently secured. When the cooling sensible heat is zero, that is, when the dehumidifying operation is performed without lowering the room temperature, the dehumidifying operation by reheating the refrigerant is performed. In the dehumidifying operation by the reheating of the refrigerant, the electromagnetic valve 41 is opened, the second flow control valve 6 is closed, and the first indoor heat exchanger is connected to the condenser and the second indoor heat exchange is performed as described in the first embodiment. A dehumidifying operation is performed using the vessel 7 as an evaporator. At this time, since the second flow control valve 6 uses a sintered metal in the throttle portion or uses a capillary tube, it is possible to prevent the generation of refrigerant flow noise.

Next, a specific operation control method of the air conditioner of this embodiment during cooling will be described. In the air conditioner, for example, a set temperature and a set humidity are set during operation of the air conditioner in order to set a favorable temperature and humidity environment for a resident in the room. The set temperature and the set humidity may be input directly by the occupant from the remote control of the indoor unit, and the set temperature and the set humidity of the indoor unit such as for a hot person, a cold person, a child, and an elderly person. The remote controller may store an optimum value table of temperature and humidity determined for each target resident, and directly select only the target resident. The indoor unit 12 is provided with sensors for detecting the temperature and humidity of the air taken into the indoor unit in order to detect the indoor temperature and humidity.

When the air conditioner is started, the difference between the set temperature and the current indoor suction air temperature is calculated as a temperature deviation, and the difference between the set humidity and the current indoor suction air humidity is calculated as a humidity deviation. The rotational frequency of the compressor 1 of the air conditioner is set so that these deviations become zero or within a predetermined value.
The controller controls the outdoor fan speed, the indoor fan speed, the throttle opening of the first flow control valve 4, the opening and closing of the second flow control valve 7, and the electromagnetic valve 41. At this time, when controlling the temperature and humidity deviations to be zero or within a predetermined value, the air conditioner is controlled by giving priority to the temperature deviations over the humidity deviations. That is, when both the temperature deviation and the humidity deviation are large at the time of starting the air-conditioning apparatus, the second flow control valve 7 is opened, and the solenoid valve 41 is closed. The operation is preferentially performed so as to be zero or within a predetermined value. When the cooling capacity of the air conditioner matches the thermal load of the room by adjusting the rotation frequency of the compressor 1 and the rotation speed of the indoor fan, and when the temperature deviation becomes zero or within a predetermined value, the humidity deviation is detected. At this time, if the humidity deviation is zero or within a predetermined value, the current operation is continued.

If the temperature deviation is zero or within a predetermined value and the humidity deviation at this time is still a large value, the cooling and dehumidifying operation by splitting the heat exchanger according to the rotation frequency of the compressor 1 at that time. And the cooling and dehumidifying operation by the reheating of the refrigerant are selected, and the refrigerant circuit is switched. That is, the cooling sensible heat capacity is larger in the cooling dehumidifying operation by splitting the heat exchanger than in the cooling dehumidifying operation by reheating the refrigerant, so that the cooling sensible heat required to maintain the temperature deviation to zero or within a predetermined value is obtained. The capacity is indirectly detected by the rotation frequency of the compressor 1 during the normal cooling operation, and the refrigerant circuit is selected. That is, when the rotation frequency of the compressor 1 in which the temperature deviation is zero or within a predetermined value is equal to or higher than a predetermined value, for example, 30 Hz, the second flow control valve 6 is throttled, and the electromagnetic valve 41 is opened. Switch to cooling / dehumidifying operation by splitting the heat exchanger. In the cooling and dehumidifying operation by the division of the heat exchanger, the rotation frequency of the compressor 1 and the rotation speed of the indoor fan are adjusted so that the temperature deviation and the humidity deviation are both controlled to be zero or within a predetermined value.

On the other hand, when the temperature deviation during normal cooling operation is zero or within a predetermined value, the humidity deviation at this time is still a large value, and the rotation frequency of the compressor 1 is lower than a predetermined value, for example, 30 Hz. Or, as described above, after shifting from the normal cooling operation to the cooling dehumidification operation by splitting the heat exchanger, the air conditioning load of the room is reduced, and the air in the room is maintained to maintain the temperature deviation within zero or within a predetermined value. If it is determined that heating is necessary, the second flow control valve 6 is throttled, the solenoid valve 41 is closed, and the operation is switched to the cooling and dehumidifying operation by refrigerant reheating. In the cooling and dehumidifying operation by the refrigerant reheating, the heating amount of the second indoor heat exchanger 7 is controlled so that the indoor temperature deviation can be maintained at zero or within a predetermined value, and the humidity deviation is zero or at a predetermined value. The amount of cooling and dehumidification of the first indoor heat exchanger 5 is controlled so as to fall within the range. To control the heating amount of the second indoor heat exchanger 7, the outdoor heat exchanger 3
And the opening degree of the first flow control valve 4 and the like. The amount of cooling and dehumidification of the first indoor heat exchanger 5 is controlled by the rotation frequency of the compressor 1, the number of fan rotations of the indoor unit 12, and the like.

As described above, in this embodiment, during cooling,
Depending on the sensible heat and latent heat load in the room, three operation modes can be switched: normal cooling operation, dehumidification operation by splitting the heat exchanger, and dehumidification operation by refrigerant reheating. The environment can be optimally controlled. Further, since the second flow control valve 6 uses a sintered metal or a capillary tube for the throttle portion, the generation of refrigerant flow noise can be prevented, and a quiet indoor environment can be realized.

Next, the operation of the heating high-temperature blowing operation of this embodiment will be described. During normal heating operation, the solenoid valve 4
1 is closed and the second flow control valve 6 is opened, and the same operation as in the third embodiment of FIG. 1 is performed. When a high blowing temperature is required, such as at the time of startup, the heating operation is performed by splitting the heat exchanger with the solenoid valve 41 opened and the second flow control valve 6 closed. In the heating operation by this heat exchanger division, the high-temperature and high-pressure refrigerant vapor exiting the compressor 1 flows into the second indoor heat exchanger 7 through the four-way valve 2 and exchanges heat with the indoor air to condense and liquefy. I do. This high-pressure liquid refrigerant passes through the solenoid valve 41. First
It flows into the flow control valve 4, is decompressed to a low pressure, flows into the outdoor heat exchanger 3, exchanges heat with outdoor air, evaporates, and returns to the compressor 1 again through the four-way valve 2. At this time, the degree of opening of the first flow control valve 4 is controlled such that the degree of superheating of the refrigerant at the outlet of the outdoor heat exchanger 3 becomes 5 ° C., for example. In the heating operation by this heat exchanger division, the normal heating operation includes the first indoor heat exchanger 5, the second indoor heat exchanger 7, and the condenser, whereas only the second indoor heat exchanger 7 is used as the condenser. And so
As compared with the normal cooling operation, the condensing temperature can be increased, and the temperature of the air heated by the condenser and blown into the room can be increased. Furthermore, when performing the indoor dehumidifying operation during the heating operation, the heating and dehumidifying operation described in the third embodiment can be performed by closing the electromagnetic valve 41 and closing the second flow control valve 6. In addition, since the second flow control valve 6 uses a sintered metal for the throttle portion or uses a capillary tube, it is possible to prevent the generation of refrigerant flow noise.

As described above, in this embodiment, during heating,
Since the three operation modes of the normal heating operation, the heating high-temperature blowing operation by splitting the heat exchanger, and the heating dehumidifying operation can be switched, it is possible to optimally control the temperature and humidity environment in the room according to the user's preference. it can. Further, since the second flow control valve 6 uses a sintered metal or a capillary tube for the throttle portion, the generation of refrigerant flow noise can be prevented, and a quiet indoor environment can be realized.

In the present embodiment, an example has been described in which the solenoid valve 41 is installed in parallel with the first indoor heat exchanger 5 and the second flow control valve 6, but the present invention is not limited to this.
As shown in FIG. 7, a three-way valve 42 in which the electromagnetic valve 41 and the second flow control valve 6 are integrated may be used. Thus, the solenoid valve 41
By using the three-way valve 42 in which the and the second flow control valve 6 are integrated, the indoor unit can be downsized.

In Embodiments 1 to 9, the case where R410A is used as the refrigerant of the air conditioner has been described. R410A is an HFC-based refrigerant, which is suitable for global environmental protection without destroying the ozone layer, and has a smaller refrigerant pressure loss than R22 which has been conventionally used as a refrigerant. This is a refrigerant that can reduce the diameter of the vent hole of the sintered metal used for the narrowed portion and can further obtain the refrigerant flow noise reduction effect.

Further, as a refrigerant of this air conditioner,
It is not limited to R410A, but R4 which is an HFC-based refrigerant
07C, R404A and R507A. Also, from the viewpoint of preventing global warming, H with a small global warming potential
R32a alone or R152a alone or R
It may be a mixed refrigerant such as 32 / R134a. Further, hydrocarbon refrigerants such as propane and butane, natural refrigerants such as ammonia, carbon dioxide and ether, and mixed refrigerants thereof may be used.

In the first to ninth embodiments, no particular reference is made to the lubricating oil of a compressor, but the lubricating oil may be a synthetic oil such as mineral oil or alkylbenzene. Ester oil or ether oil developed for refrigerants may be used.

[0106]

As described above, according to the expansion device of the present invention, since the expansion portion is formed of the porous permeable material communicating in the refrigerant flow direction, it is possible to prevent the generation of the refrigerant flow noise and reduce the noise. Is obtained.

A first flow path provided with an electromagnetic on-off valve, a second flow path provided in parallel with the first flow path,
And a throttle portion provided in the second flow path and made of a porous permeable material communicating with the refrigerant in the flow direction. Therefore, generation of the refrigerant flow noise can be achieved without requiring complicated processing of the porous permeable material. The effect of preventing noise and reducing noise can be obtained.

Further, since the refrigerant passage is covered with the porous permeable material, fluctuations in pressure loss can be suppressed, and the effect of preventing generation of refrigerant flow noise and reducing noise can be obtained.

Further, since the porous permeable material has a hollow portion or a hollow body structure, the effect of appropriately selecting the size of the through-hole and the pressure loss of the porous permeable material can be obtained.

[0110] Also, the throttle section has a cylindrical shape with one end open, and a flow passage communicating between the inside and the outside of the cylindrical shape through the cylindrical peripheral surface and the bottom surface is made of a porous permeable material. In addition, an effect that a large passage area of the porous permeable member can be obtained can be obtained.

Further, since the adjusting means for adjusting the permeation area of the porous permeable material is provided, the effect of appropriately adjusting the pressure difference caused by passing through the porous permeable material can be obtained.

Further, a valve body having a first flow path opened in the valve chamber side wall, a main valve seat having a second flow path opened in the valve chamber bottom face, and a main valve body capable of closing the main valve seat in the valve chamber are provided. Since the throttle portion is formed by using a porous permeable material for the main valve body, it is possible to prevent refrigerant flow noise from being generated and to prevent performance loss due to pressure loss when a normal valve is opened. .

Further, the porous permeable material has a columnar shape with one end opened, and when the main valve seat is closed, the peripheral surface and the bottom surface of the columnar shape are separated into a flow channel inlet side and an outlet side. Thus, the effect of appropriately selecting the size of the passage hole of the porous permeable material and the pressure loss on the peripheral surface side and the bottom surface side is obtained.

Further, a valve body having a first flow path opened in the valve chamber side wall, a main valve seat having a second flow path opened in the valve chamber bottom surface, and a main valve body capable of closing the main valve seat in the valve chamber are provided. Since the flow control valve is constituted by using a porous permeable material for the main valve seat, the design of the throttle portion is facilitated, and the effect of being inexpensive and low noise is obtained.

A main valve body whose peripheral surface is in contact with the side surface of the main valve seat and the contact area between the peripheral surface and the side surface is varied by moving the main valve body in the opening and closing direction. Control means for controlling the movement, and the main valve body, the main valve seat and the control means constitute adjusting means for adjusting the permeation area of the porous permeable material. Thus, the effect of appropriately adjusting the pressure difference utilizing the porous permeable material can be obtained.

Further, since the pores of the porous permeable material are set in the range of 200 to 0.5 μm, the effect of preventing generation of refrigerant flow noise when liquid refrigerant or gas-liquid two-phase refrigerant passes is obtained. Can be

Further, since the porous permeable material is made of sintered metal, an effect that a drawing device having excellent durability can be obtained can be obtained.

Further, according to the refrigeration cycle of the present invention,
Since the gas-liquid two-phase refrigerant is allowed to pass through the porous permeable material in the apparatus provided with the above-described expansion device, there is no occurrence of collapse of refrigerant vapor slag or refrigerant bubbles, and an effect of preventing generation of refrigerant flow noise can be obtained. .

Further, a valve body having a first flow path opened in the valve chamber side wall, a main valve seat having a second flow path opened in the valve chamber bottom face, and the main valve seat can be closed in the valve chamber and the peripheral surface is formed. A throttle device having a main valve body that abuts on a side surface of the main valve seat and changes an abutting area between the peripheral surface and the side surface by movement in the opening and closing direction, and moving the main valve body in the opening and closing direction. And a control means for controlling the main valve seat or the main valve body to constitute a flow rate control valve using a porous permeable material, and the main valve body, the main valve seat and the control means of the porous permeable material. Since the adjusting means for adjusting the permeation area is configured, the effect of adjusting the flow rate while preventing the generation of the refrigerant flow noise can be obtained.

Further, since the adjusting means adjusts the transmission area according to the pressure difference of the expansion device, the effect of adjusting the pressure difference can be obtained.

Since the adjusting means adjusts the transmission area so as to have a predetermined pressure difference, the effect of suppressing the influence of pressure fluctuation can be obtained.

Further, according to the air conditioner of the present invention,
A compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a refrigeration cycle in which a second indoor heat exchanger is sequentially connected, wherein the second flow control is performed. The throttle section of the valve is made of a porous permeable material that communicates with the refrigerant in the direction of flow of the refrigerant. The effect that can be provided is obtained.

Further, since there is provided an adjusting means for adjusting the permeation area of the porous permeable material, the flow rate can be adjusted while preventing the generation of the refrigerant flow noise, so that the effect that the air conditioning operation can be performed comfortably and finely can be obtained. .

Further, a valve body having a first flow path opened on the valve chamber side wall, a main valve seat having a second flow path opened on the bottom face of the valve chamber, and a main valve body capable of closing the main valve seat in the valve chamber are provided. Having a second flow control valve using a porous permeable material for the main valve body,
Generation of refrigerant flow noise can be prevented, and performance degradation due to pressure loss during normal cooling operation or normal heating operation does not occur. Further, conventional measures for reducing the flow noise of the refrigerant, such as wrapping a vibration isolator around the valve, become unnecessary, and the apparatus is inexpensive and the recyclability at the time of disposal of the apparatus is improved.

Further, a valve body having a first flow path opened in the valve chamber side wall, a main valve seat having a second flow path opened in the valve chamber bottom face, and a main valve body capable of closing the main valve seat in the valve chamber are provided. Having a second flow control valve using a porous permeable material for the main valve seat,
The effect of easily changing the shape of the throttle portion, simplifying the design, and providing an inexpensive and low-noise flow control valve is obtained.

A main valve body whose peripheral surface is in contact with the side surface of the main valve seat, and the contact area between the peripheral surface and the side surface is varied by moving the main valve body in the opening and closing direction. Control means for controlling the movement, and the main valve body, the main valve seat and the control means constitute adjusting means for adjusting the permeation area of the porous permeable material. In addition, since the flow rate can be adjusted, it is possible to obtain a comfortable and detailed air conditioning operation.

Further, since the adjusting means adjusts the permeation area according to the pressure difference of the second flow control valve, it is possible to obtain a comfortable and efficient air conditioning. .

Further, since the adjusting means adjusts the permeation area so as to have a predetermined pressure difference at the time of operation for lowering the latent heat ratio, an effect of more comfortably guiding the indoor temperature and humidity environment can be obtained.

Further, the ventilation hole of the sintered metal is set at 200 to 0.
Since it is in the range of 5 micrometers, the effect of preventing generation of refrigerant flow noise when the liquid refrigerant or the gas-liquid two-phase refrigerant passes can be obtained.

Further, since the control unit for controlling the second flow control valve to be closed at the time of the operation for lowering the latent heat ratio is provided, the temperature can be controlled over a wide range while reducing the refrigerant flow noise, and comfortable dehumidification can be performed. The effect is obtained.

Further, the control section controls the second flow control valve to be closed during the cooling, dehumidifying and heating operations, so that the refrigerant flow noise can be reduced even when the refrigerant phase changes due to the difference in the operation mode. The effect that comfortable dehumidification can be obtained while reducing the temperature is obtained.

Further, since the control section for controlling the second flow control valve to be closed at the time of starting the heating operation is provided, it is possible to obtain the effect that the temperature of the air is raised to a high temperature so that the feeling of quick warming can be improved and the comfortable heating can be performed.

In addition, since the control unit is provided to control the second flow control valve to be closed when the difference between the set temperature and the room temperature is equal to or more than a predetermined value during the heating operation, the room temperature is controlled with respect to the set temperature. When the temperature is sufficiently low, the high-temperature blown air can be blown out, so that an effect of providing comfortable heating without giving a feeling of cool air can be obtained.

An air conditioner having a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. In the above, since the second flow control valve is formed of a capillary tube having an inner diameter of 1 mm or more, it is possible to reliably reduce the generation of the refrigerant flow noise when the liquid refrigerant or the gas-liquid two-phase refrigerant passes below an allowable value, In addition, an effect that an inexpensive indoor unit with improved recyclability can be provided can be obtained.

An air conditioner having a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. In the above, the second flow control valve is constituted by a capillary, and a heat exchanger for exchanging heat between the capillary inlet pipe and the pipe between the second indoor heat exchanger and the compressor during a cooling and dehumidifying operation is provided. Therefore, the vapor component of the refrigerant at the capillary inlet can be reduced, and the refrigerant flow noise generated from the capillary can be greatly reduced. Further, the heat transfer performance of the indoor heat exchanger during the cooling and dehumidifying operation is improved, and the effect of improving the performance of the device is obtained.

An air conditioner equipped with a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. In the above, the second flow rate control valve is constituted by a capillary tube, and a heat exchanger for exchanging heat with a pipe between the second indoor heat exchanger and the compressor is provided, so that generation of refrigerant vapor in the capillary tube is suppressed. Thus, the flow noise of the refrigerant generated from the capillary can be greatly reduced. Further, the heat transfer performance of the indoor heat exchanger during the cooling and dehumidifying operation is improved, and the effect of improving the performance of the device is obtained.

Further, since the air conditioner is provided with a bypass passage for bypassing the second indoor heat exchanger and the second flow control valve and an opening / closing means for opening and closing the bypass passage, the indoor temperature and humidity environment can be controlled in a wide range. In addition to being able to control, it is also possible to perform fine-tuned operation to lower the latent heat ratio while keeping the temperature conditions comfortable, and to reduce the generation of refrigerant flow noise,
The effect of realizing a low noise indoor environment is obtained.

An air conditioner equipped with a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. In the above, since the air conditioner includes the bypass passage that bypasses the second indoor heat exchanger and the second flow control valve, and the opening and closing unit that opens and closes the bypass passage, the indoor temperature and
In addition to controlling the humidity environment, it is possible to obtain an effect that it is possible to perform a detailed operation for lowering the latent heat ratio while keeping the temperature condition comfortable.

Further, a control means for controlling the second flow rate control valve and the opening / closing means is provided, and the control means throttles the second flow rate control valve in accordance with the sensible heat capacity during operation for lowering the latent heat ratio. Since the heat exchanger split operation for opening the means and the refrigerant reheating operation for closing the second flow control valve and closing the opening / closing means are controlled, a fine adjustment for lowering the latent heat ratio while keeping the temperature conditions comfortable. The effect that operation becomes possible according to sensible heat capacity is obtained.

Further, a control means for controlling the second flow control valve and the opening / closing means is provided, and the control means closes the second flow control valve and closes the opening / closing means when the sensible heat ratio decreases. Since the control is performed, there is an effect that when the air conditioning load is small, fine air conditioning control by the refrigerant reheating method can be performed.

[0141] Further, a control means for controlling the second flow rate control valve and the opening / closing means is provided. When the heating operation is started, the second flow rate control valve is closed and the opening / closing means is opened. As a result, it is possible to obtain the effect of comfortable heating with a quick feeling of warmth.

Further, since the receiver for storing the liquid refrigerant during the heating operation is provided in the pipe between the first flow control valve and the first indoor heat exchanger, the amount of the refrigerant can be controlled according to the operation mode, and the apparatus can be controlled. The effect of improving performance and reliability can be obtained.

[Brief description of the drawings]

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

FIG. 2 is a diagram illustrating a configuration of a second flow control valve according to the first embodiment.

FIG. 3 is a characteristic diagram illustrating an operation state of the air-conditioning apparatus according to Embodiment 1 during a cooling and dehumidifying operation.

FIG. 4 is a diagram showing another configuration example of the second flow control valve according to the first embodiment.

FIG. 5 is a diagram showing a configuration of a second flow control valve according to the second embodiment of the present invention.

FIG. 6 is a diagram showing another configuration example of the second flow control valve according to the second embodiment.

FIG. 7 is a diagram illustrating a configuration of a second flow control valve according to the third embodiment of the present invention.

FIG. 8 is a diagram showing another configuration example of the second flow control valve according to the third embodiment.

FIG. 9 is a characteristic diagram illustrating an operation state during a heating and dehumidifying operation according to the fourth embodiment of the present invention.

FIG. 10 is a refrigerant circuit diagram of an air conditioner according to Embodiment 5 of the present invention.

FIG. 11 is a refrigerant circuit diagram of an air conditioner according to Embodiment 6 of the present invention.

FIG. 12 is a diagram illustrating a configuration of a second flow control valve according to the sixth embodiment.

FIG. 13 is a refrigerant circuit diagram of an air conditioner according to Embodiment 7 of the present invention.

FIG. 14 is a diagram illustrating a measurement result of a refrigerant flow noise of a capillary according to the seventh embodiment.

FIG. 15 is a refrigerant circuit diagram of an air conditioner according to Embodiment 8 of the present invention.

FIG. 16 is a characteristic diagram illustrating an operation state of the air-conditioning apparatus according to Embodiment 8 during the cooling and dehumidifying operation.

FIG. 17 is a refrigerant circuit diagram of an air conditioner according to Embodiment 9 of the present invention.

FIG. 18 is a characteristic diagram illustrating an operation state of the air-conditioning apparatus according to Embodiment 9 during a cooling and dehumidifying operation.

FIG. 19 is a refrigerant circuit diagram of an air conditioner according to Embodiment 10 of the present invention.

FIG. 20 is a refrigerant circuit diagram showing another example of the air-conditioning apparatus according to Embodiment 10.

FIG. 21 is a refrigerant circuit diagram showing a conventional air conditioner.

[Explanation of symbols]

1 compressor, 3 outdoor heat exchanger, 4 first flow control valve, 5 first indoor heat exchanger, 6 second flow control valve,
7 second indoor heat exchanger, 21 first flow path, 22 second flow path, 23 main valve seat, 24 valve body, 30 receiver, 31 sintered metal, 38 capillary tube, 40
Heat exchanger

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Masahiro Nakayama 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsui Electric Co., Ltd. (72) Inventor Shigeki Onishi 2-3-2 Marunouchi, Chiyoda-ku, Tokyo F term (reference) in Ryo Denki Co., Ltd. 3H106 DA07 DB32 DB34 DC02 DC17 EE20 GB11 GB18 KK23 3L049 BB20 BC01 3L092 AA03 AA10 BA14 BA27 BA28 DA01 DA03 DA04 DA14 DA15 EA02 FA23 FA24

Claims (37)

[Claims] 1. An expansion device, wherein the expansion unit is made of a porous permeable material that communicates in the flow direction of the refrigerant. 2. A first flow path provided with an electromagnetic on-off valve,
A second flow path provided in parallel with the first flow path; and a throttle portion provided in the second flow path and formed of a porous permeable material that communicates in a refrigerant flow direction. Characteristic squeezing device. 3. The expansion device according to claim 1, wherein the refrigerant passage is covered with the porous permeable material. 4. The aperture device according to claim 1, wherein the porous permeable material has a hollow portion or is a hollow body. 5. The throttle section has a cylindrical shape with one end open, and a flow passage communicating between the inside and the outside of the cylindrical shape through a peripheral surface and a bottom surface of the cylindrical shape is formed of a porous permeable material. The aperture device according to any one of claims 1 to 3, wherein: 6. The diaphragm device according to claim 1, further comprising an adjusting means for adjusting a transmission area of the porous transmission material. 7. A valve body having a first flow path opened in a valve chamber side wall, a main valve seat having a second flow path opened in a valve chamber bottom face, and a main valve body capable of closing the main valve seat in the valve chamber. The throttle device according to claim 1, wherein a throttle portion is configured by using a porous permeable material for the main valve body. 8. The porous permeable material has a columnar shape with one end opened, and when the main valve seat is closed, a peripheral surface side and a bottom surface side of the columnar shape are separated into a flow path inlet side and an outlet side. The diaphragm device according to claim 7, wherein 9. A valve body having a first flow path opened in a valve chamber side wall, a main valve seat having a second flow path opened in a valve chamber bottom face, and a main valve body capable of closing the main valve seat in the valve chamber. The throttle device according to claim 1, wherein a flow control valve is configured by using a porous permeable material for the main valve seat. 10. A main valve body having a peripheral surface in contact with a side surface of a main valve seat, and a contact area between the peripheral surface and the side surface being varied by movement in an opening and closing direction. 10. A control means for controlling movement, wherein said main valve body, main valve seat and control means constitute an adjusting means for adjusting a permeation area of a porous permeable material. Aperture device. 11. The throttle device according to claim 1, wherein the air holes of the porous permeable material are set in a range of 200 to 0.5 μm. 12. The drawing device according to claim 1, wherein said porous permeable material is a sintered metal. 13. A refrigeration cycle equipped with the expansion device according to claim 1 or 2, wherein a gas-liquid two-phase refrigerant is passed through the porous permeable material. 14. A valve body having a first flow passage opening in a valve chamber side wall, a main valve seat having a second flow passage opening in a bottom surface of the valve chamber, and a main valve seat capable of being closed in the valve chamber and having a peripheral surface. A throttle device having a main valve body that abuts on a side surface of the main valve seat and changes a contact area between the peripheral surface and the side surface by movement in the opening and closing direction; and moving the main valve body in the opening and closing direction. Control means for controlling;
A flow control valve is formed by using a porous permeable material for the main valve seat or the main valve body, and an adjustment for adjusting a permeable area of the porous permeable material by the main valve body, the main valve seat and the control means. A refrigeration cycle apparatus comprising means. 15. The refrigeration cycle apparatus according to claim 14, wherein the adjusting means adjusts the transmission area according to a pressure difference of the expansion device. 16. The apparatus according to claim 15, wherein the adjusting means adjusts the transmission area so as to have a predetermined pressure difference.
A refrigeration cycle apparatus as described in the above. 17. An air conditioner having a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. The air conditioner according to any one of claims 1 to 3, wherein a throttle portion of the second flow control valve is formed of a porous permeable material that communicates in a refrigerant flow direction. 18. The air conditioner according to claim 17, further comprising adjusting means for adjusting a transmission area of the porous permeable material. 19. A valve body having a first flow path opened in a valve chamber side wall, a main valve seat having a second flow path opened in a valve chamber bottom face, and a main valve body capable of closing the main valve seat in the valve chamber. The air conditioner according to claim 17, wherein a second flow control valve is configured using a porous permeable material for the main valve body. 20. A valve body having a first flow path opened in a valve chamber side wall, a main valve seat having a second flow path opened in a valve chamber bottom face, and a main valve body capable of closing the main valve seat in the valve chamber. The air conditioner according to claim 17, wherein a second flow control valve is configured using a porous permeable material for the main valve seat. 21. A main valve body having a peripheral surface in contact with a side surface of a main valve seat, and a contact area between the peripheral surface and the side surface being varied by movement in the opening and closing direction. 21. A control means for controlling movement, wherein an adjusting means for adjusting a permeation area of a porous permeable material is constituted by the main valve body, the main valve seat and the control means. Air conditioner. 22. The air conditioner according to claim 21, wherein the adjusting means adjusts the permeation area according to a pressure difference of the second flow control valve. 23. The air conditioner according to claim 22, wherein the adjusting means adjusts the permeation area so as to have a predetermined pressure difference during an operation for lowering a latent heat ratio. 24. The air conditioner according to claim 17, wherein the air holes of the porous permeable material are in a range of 200 to 0.5 micrometers. 25. The method according to claim 25, wherein the second heat is applied during an operation for lowering the latent heat ratio.
The air conditioner according to claim 17, further comprising a control unit that controls the flow control valve to close. 26. The air conditioner according to claim 25, wherein the control unit controls to close the second flow control valve during cooling, dehumidification, and heating operations. 27. The air conditioner according to claim 17, further comprising a control unit that controls the second flow control valve to be closed when the heating operation is started. 28. The air conditioner according to claim 1, further comprising a control unit that controls the second flow control valve to close when a difference between the set temperature and the room temperature is equal to or more than a predetermined value during the heating operation.
8. The air conditioner according to 7. 29. An air conditioner having a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. 2. The air conditioner according to claim 1, wherein the second flow control valve comprises a capillary having an inner diameter of 1 mm or more. 30. An air conditioner having a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. In the above, the second flow control valve is constituted by a capillary, and a heat exchanger for exchanging heat between the capillary inlet pipe and the pipe between the second indoor heat exchanger and the compressor during a cooling and dehumidifying operation is provided. An air conditioner characterized by the above-mentioned. 31. An air conditioner including a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. The air conditioner according to claim 1, wherein the second flow control valve is formed of a capillary tube, and a heat exchanger for exchanging heat with a pipe between the second indoor heat exchanger and the compressor is provided. 32. The apparatus according to claim 1, further comprising: a bypass passage for bypassing the second indoor heat exchanger and the second flow control valve; and opening and closing means for opening and closing the bypass passage.
The air conditioner according to any one of claims 7 to 31. 33. An air conditioner having a refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow control valve, a first indoor heat exchanger, a second flow control valve, and a second indoor heat exchanger are sequentially connected. The air conditioner according to claim 1, further comprising: a bypass passage that bypasses the second indoor heat exchanger and the second flow control valve; and an opening / closing unit that opens and closes the bypass passage. 34. Control means for controlling the second flow valve and the opening / closing means, wherein the control means throttles the second flow control valve in accordance with the sensible heat capacity at the time of operation for reducing the latent heat ratio, and controls the opening / closing means. 34. The air conditioner according to claim 32, wherein the air conditioner is controlled so as to perform a heat exchanger split operation for opening a heat exchanger and a refrigerant reheating operation for narrowing the second flow control valve and closing the opening / closing means. . 35. Control means for controlling the second flow control valve and the opening / closing means, wherein the control means closes the second flow control valve and closes the opening / closing means when the sensible heat ratio decreases. The air conditioner according to claim 32 or 33, wherein the air conditioner is controlled. 36. A control device for controlling the second flow rate control valve and the opening / closing means, wherein the control means controls to close the second flow rate control valve and open the opening / closing means when heating operation is started. An air conditioner according to claim 32 or claim 33. 37. A piping according to claim 17, further comprising a receiver for storing a liquid refrigerant during a heating operation in a pipe between the first flow control valve and the first indoor heat exchanger. Item 2. The air conditioner according to item 1.