JP2003083641A - Flow control device, restricting device and air conditioning equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a restricting device and a flow control device which enable setting of a different amount of restriction for a refrigerant flow in normal and reverse directions and to obtain air conditioning equipment which can conduct heating, reheating and dehumidifying operations and can reduce the sound of the refrigerant flow. SOLUTION: A communicating flow passage 16a making first and second flow passages 9a and 9b communicate with each other are provided, while a restricting flow passage 16b is provided in parallel to the passage 16a, and first and second restricting parts 13 and 15 are connected to the restricting passage 16b. The passages 16a and 16b are switched over by a switchover means 8 and a flow to the second restricting part 15 is switched over by a check valve 14. A fluid is subjected to pressure reduction by the first restricting part when it flows in the direction A through the restricting passage 16b, and subjected thereto by the second restricting part 15 or by the second restricting part 15 and the first restricting part when it flows in the direction B, so that the amount of restriction is different according to the flowing direction of the fluid. Besides, a porous permeable material is disposed in the restricting flow passage 16b so as to reduce a noise.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a throttle device for decompressing a fluid flowing inside and a flow rate control device for controlling a flow rate of a refrigerant flowing inside in a refrigeration cycle utilizing heat of condensation or heat of evaporation. . The present invention also relates to an air conditioner that cools, heats, and dehumidifies the room by using the expansion device and the flow control device.

[0002]

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

The following air conditioner has been devised as a means for improving the dehumidifying ability during the cooling low capacity operation. FIG. 21 is a refrigerant circuit diagram showing a conventional air conditioner disclosed in, for example, Japanese Patent Laid-Open No. 11-51514.
In the figure, 1 is a compressor, 2 is a four-way valve, 3 is an outdoor heat exchanger, 4 is a first flow controller, 5 is a first indoor heat exchanger, and 6
Is a second flow rate control device, 7 is a second indoor heat exchanger, and these are sequentially connected by piping to form a refrigeration cycle. Reference numeral 9a is a first flow path connecting pipe which is a flow path on one side of the second flow rate control device 6, and 9b is a second flow path connecting pipe which is a flow path on the other side of the second flow rate control device 6. Furthermore, the first flow control device 4 has a configuration in which the main expansion device 41 and the two-way valve 42 are connected in parallel. This air conditioner is separately arranged in an outdoor unit 51 and an indoor unit 52.

Next, the operation of the conventional air conditioner will be described. In the cooling operation, the two-way valve 42 is closed and the second flow rate control device 6 is fully opened. The refrigerant exiting the compressor 1 passes through the four-way valve 2, is condensed and liquefied in the outdoor heat exchanger 3, and flows into the first flow rate control device 4. Since the two-way valve 42 is closed, it is decompressed by the main expansion device 41 and vaporized in the indoor heat exchangers 5 and 7, and then returns to the compressor 1 via the four-way valve 2 again. Also in the heating operation, the two-way valve is closed and the second flow rate control device 6 is fully opened to switch the refrigerant flow in the four-way valve 2. The refrigerant exiting the compressor 1 passes through the four-way valve 2 as opposed to the cooling operation,
The indoor heat exchangers 7 and 5 condense and liquefy, and the first flow control device 4
Flow into. Since the two-way valve 42 is closed, the pressure is reduced by the main expansion device 41 and vaporized in the outdoor heat exchanger 3,
It returns to the compressor 1 via the four-way valve 2 again.

On the other hand, during the dehumidifying operation in the cooling operation and the heating operation, the main throttle device 41 of the first flow rate control device 4 is closed, the two-way valve 42 is opened, and the second flow rate control device 6 controls the refrigerant flow rate. . With this configuration, for example, one of the first indoor heat exchanger 5 and the second indoor heat exchanger 7 operates as a condenser, that is, a reheater, and the other operates as an evaporator. Since the indoor air is cooled and dehumidified by the evaporator and is heated by the reheater, it is possible to perform the dehumidification operation in which the temperature of the air blown into the room is not lowered so much to reduce the humidity. Hereinafter, such an operation is referred to as a reheat dehumidifying operation. FIG. 22 is a partial cross-sectional view showing the second flow rate control device 6 of the conventional air conditioner. The second flow rate control device 6 is provided with an orifice-shaped throttle channel including a plurality of cut grooves 43 and a valve element 44.

[0006]

In the conventional air conditioner as described above, as the second flow rate control device 6 installed in the indoor unit 52, an orifice-shaped throttle channel normally shown in FIG. 22 is used. A flow rate control device having In particular, during the dehumidifying operation, since the inlet of the second flow rate control device 6 becomes a gas-liquid two-phase refrigerant, there is a problem that the flow noise of the refrigerant passing through the orifice of the second flow rate control device 6 becomes loud. This flowing sound becomes a factor that deteriorates the indoor environment,
Additional measures such as providing a sound insulating material and a vibration damping material around the second flow rate control device 6 are required, and there are problems such as an increase in cost, deterioration of installation property, and deterioration of recyclability.

A conventional flow control device 6 for an air conditioner
Then, from the first flow path connecting pipe 9a to the second flow path connecting pipe 9b
There is a problem that the heating reheat dehumidification operation cannot be performed because the flow rate can be controlled only by the one-way flow to, and when the flow is opposite, the flow is in the fully open state. Further, there is a problem that the range of temperature control becomes extremely narrow because the throttle amount when controlling the flow rate is fixed.

As a measure for reducing the refrigerant flow noise of the second flow rate control device during the dehumidifying operation, there is one disclosed in Japanese Patent Application No. 12-127778. A sectional view of the second flow rate control device 6 is shown in FIG. As shown in the figure, the porous permeable material 11 is sandwiched in front of and behind the orifice 12, and the porous permeable material 11 rectifies the gas-liquid two-phase refrigerant to reduce the noise generated. The second flow rate control device 6 is effective in reducing the refrigerant flow noise, and in the normal cooling operation or the normal heating operation in which the refrigerant flows so that there is almost no pressure loss,
An on-off valve 45 is separately provided as shown in FIG. 24, and the flow rate is controlled by opening and closing the on-off valve 45. When the flow rate control device 6 is connected to a pipe as shown in the figure, the flow rate can be controlled only by a one-way flow from the first flow path connection pipe 9a to the second flow path connection pipe 9b. There was a problem that the reheat dehumidification operation could not be performed.

The present invention has been made in order to solve the above-mentioned problems, and in a throttle device and a flow rate control device, which are constituent devices of a refrigeration cycle device that uses heat of condensation or heat of evaporation, An object of the present invention is to obtain a throttle device and a flow rate control device that are suitable for the flow control of a refrigerant, can reduce the noise of the refrigerant flow, and can set different throttle amounts for the refrigerant flows in the forward and reverse directions. Further, the present invention, in an air conditioner that uses the condensation heat of the refrigeration cycle as a heating source for indoor air, enhances controllability of temperature and humidity during cooling, dehumidification, heating, and each operation, and improves cooling season, heating The objective is to obtain an air conditioner that can realize reheat dehumidification operation regardless of the season and can reduce refrigerant flow noise.

[0010]

According to a first aspect of the present invention, there is provided a flow rate control device, a communication channel for communicating the first channel and the second channel, and a first throttle provided in parallel with the communication channel. A flow path including a flow path and a second flow path, and a switching means for switching between the communication flow path and the flow path. The fluid flows from the first flow path of the throttle flow path to the second flow path. At the time, when the pressure is reduced in the first throttle portion and the fluid flows from the second flow passage of the throttle flow passage to the first flow passage, in the second throttle portion or the second throttle portion and the first throttle portion. It is characterized in that the pressure is reduced and the amount of throttling is different depending on the flow direction of the fluid in the throttle channel.

According to a second aspect of the present invention, there is provided the flow rate control device according to the first aspect, wherein the first throttle portion is constituted by an orifice for depressurizing and passing the fluid, and the orifice and the At least one flow path between the one flow path and between the orifice and the second flow path,
It is characterized by comprising a porous permeable material that allows a fluid to pass therethrough.

According to a third aspect of the present invention, there is provided a throttle device having a casing having channel openings at both ends and arranged in the channel, and a valve seat having an opening provided at one end of the casing. The valve seat side, which includes an operating valve that operates in the flow direction of the fluid flowing in the housing, a stopper that is provided at the other end of the housing, and a throttle portion that is provided in the operating valve or the valve seat. When the fluid flows from the stopper valve to the stopper side, the operating valve stops at the stopper and the fluid flows through the opening, and when the fluid flows from the stopper side to the valve seat side, the operating valve operates at the valve seat. It is characterized in that the opening is closed to close the opening and the fluid flows through the throttle portion so that the throttle amount is different depending on the flow direction of the fluid.

According to a fourth aspect of the present invention, there is provided the flow control device according to the first or second aspect, wherein the second throttle portion is constituted by the throttle device according to the third aspect. It is characterized by.

A flow control device according to a fifth aspect of the present invention is the flow control device according to the first or second aspect, wherein the second throttle portion is a capillary tube.
It is characterized in that it is constituted by a check valve which is provided in parallel with this capillary tube and permits only one-way flow.

According to a sixth aspect of the present invention, there is provided a case in which one end is connected to the first flow path and the other end is connected to the second flow path, and the case is disposed in the flow path. A first throttle portion which is provided on one flow passage side and reduces the pressure of a fluid flowing in the housing to pass through; a space between the first throttle portion and the first flow passage;
A porous permeable material, which is disposed in at least one of the flow passages between the throttle portion and the second flow passage, and allows the fluid to pass therethrough, and a first throttle between the first throttle portion and the second flow passage. A valve seat having an opening provided on the part side, an operating valve that operates in the flow direction of the fluid flowing in the housing, a stopper provided between the operating valve and the second flow path, the operating valve or the A second throttle portion provided on the valve seat, and when the fluid flows from the first flow passage toward the second flow passage, the operating valve is stopped by the stopper and the fluid flows through the first throttle portion and the opening. Flow through the second flow passage to the first flow passage, the operating valve stops at the valve seat to close the opening, and the fluid flows through the second throttle portion and the first throttle portion. It is characterized in that the throttling amount is different depending on the flow direction of the fluid.

According to a seventh aspect of the present invention, there is provided a case in which one end is connected to the first flow path and the other end is connected to the second flow path, and the case is disposed in the flow path. A valve body having a first throttle portion that reduces the pressure of the fluid to pass therethrough, and is disposed at least one of the first throttle portion and the first flow passage and between the first throttle portion and the second flow passage. A porous permeable material that allows the fluid to pass therethrough, an operating valve that operates in the flow direction of the fluid that flows in the housing, a partition plate that has a flow path provided between the operating valve and the second flow path, and An operating valve or a second throttle portion provided in the valve body, and when the fluid flows from the first flow path to the second flow path, the operating valve stops at the partition plate and the fluid flows into the first flow path. When the fluid flows through the flow passage of the throttle portion and the partition plate and the fluid flows from the second flow passage to the first flow passage, the operating valve Closing the first throttle portion is stopped at the valve body, the fluid is characterized in that by flowing through the second aperture unit and configured to different amounts squeezed in the direction of fluid flow.

According to an eighth aspect of the present invention, there is provided the flow rate control device according to the sixth aspect or the seventh aspect, in which the communication channel connecting the first channel and the second channel is provided in parallel with the communication channel. When a fluid flows from the first flow passage of the throttle flow passage to the second flow passage, the throttle flow passage is formed by connecting a throttle device, and the switching passage that switches between the communication flow passage and the throttle flow passage. When the pressure is reduced in the first throttle portion of the throttle device and the fluid flows from the second flow passage of the throttle flow passage to the first flow passage, the second throttle portion of the throttle device or the second throttle portion and the It is characterized in that the pressure is reduced in the first throttle portion so that the throttle amount is different in the flow direction of the fluid in the throttle channel.

According to a ninth aspect of the present invention, in the air conditioner, the air conditioner includes a compressor, an outdoor heat exchanger, a first flow rate control device, a first indoor heat exchanger, a second flow rate control device, and a second flow rate control device. Two
A refrigeration cycle in which indoor heat exchangers are sequentially connected is provided, and the flow rate control device according to claim 1, 2 or 4 or 5 or 8 is used as the second flow control device. When the second indoor heat exchanger is operated as an evaporator or a condenser together, the second flow rate control device connects the first and second indoor heat exchangers through the communication passage, and the first and second indoor heat exchangers are connected. When one of the two indoor heat exchangers is operated as an evaporator and the other is operated as a condenser, the second flow rate control device connects the first and second indoor heat exchangers through a throttle channel. It is characterized in that the switching means is configured to be switched.

Further, in the air conditioner according to claim 10 of the present invention, the second flow rate control in the heating reheat dehumidification operation in which the first indoor heat exchanger is an evaporator and the second indoor heat exchanger is a condenser. The throttle amount of the device is set to be larger than the throttle amount in the cooling reheat dehumidification operation in which the first indoor heat exchanger is a condenser and the second indoor heat exchanger is an evaporator.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiment 1. 1 is a refrigerant circuit diagram showing an air conditioner according to Embodiment 1 of the present invention. The air conditioner uses the condensation heat or the evaporation heat of the refrigeration cycle to cool or heat the room. In the figure, 1 is a compressor, 2 is a flow path switching means for switching the flow of refrigerant in cooling operation and heating operation, for example, a four-way valve, 3 is an outdoor heat exchanger, 4 is a first flow rate control device, and 5 is a first indoor chamber. A heat exchanger, 6 is a second flow rate control device, and 7 is a second indoor heat exchanger, which are sequentially connected by piping to form a refrigeration cycle. R410A, which is a mixed refrigerant of R32 and R125, is used as the refrigerant of this refrigeration cycle, and alkylbenzene-based oil is used as the refrigerating machine oil.

FIG. 2 is a circuit diagram showing the second flow rate control device 6, in which (a), (b) and (c) show the operating states. In the figure, 8 is a switching means, for example, an on-off valve, 9a is a first flow passage, here a first flow passage connecting pipe, 9b
Is a second flow passage, here is a second flow passage connecting pipe, 13 is a throttle device, 14 is a check valve, 15 is a capillary tube, 16
Reference numerals a and 16b are pipes that form a flow path. The first flow path connecting pipe 9a includes two flow paths, a communication flow path 16a and a throttle flow path 16a.
The on-off valve 8 is connected to one of the communication channels 16a, and the fluid flows to the communication channel 16a when the on-off valve 8 is opened, and the refrigerant flows to the throttle channel 16b when the on-off valve 8 is closed. The throttle channel 16b is a throttle device 13 having a first throttle portion.
And the capillary tube 15 serving as the second throttle portion are connected. Further, the check valve 14 is connected in parallel to the capillary tube 15, and the pipe 16b joins with the pipe 16a from the opening / closing valve 8. The check valve 14 is in the flow direction from the first flow path connecting pipe 9a to the second flow path connecting pipe 9b, that is, A
It is installed so that the fluid flows through in the forward direction and blocks the flow in the B direction. Here, the communication channel is
A fluid having a pressure loss of almost zero, and communicating the first and second channels with each other means connecting the first channel and the second channel with a pressure loss of substantially zero. Is.

FIG. 3 is a cross-sectional view showing the diaphragm device 13. In the figure, 11a and 11b are porous permeable materials, and 1
Reference numeral 2 is an orifice serving as a first throttle portion, 17 is a housing, and 18 is a valve body. The porous permeable materials 11a and 11b are fixed to the valve body 18. The porous permeable materials 11a and 11b are
For example, the air holes have a pore diameter of about 500 μm and are arranged in the flow path between the orifice 12 and the pipe 16b to make the refrigerant vapor slag and vapor bubbles fine when permeating the refrigerant which is a fluid. The material is, for example, foam metal, which is obtained by applying metal powder or alloy powder to urethane foam, heat-treating the urethane foam to burn it, and molding the metal into a three-dimensional lattice. ). In order to increase strength, Cr (chromium) may be plated. The shape is disk-like or polygonal, and has a certain thickness in the flow path direction.

Further, a step is formed between the porous permeable materials 11a and 11b and the orifice 12 so that constant gaps 19a and 19b are formed. These gaps 19a and 19b
Is set, for example, between 0 and 3 mm. The porous permeable materials 11a and 11b have a thickness of 1 mm to 5 mm and a passage area of 70 m.
It is set to m ^{2 to} 700 mm ² . The valve body 18 provided with the porous permeable material 11a, the orifice 12, and the porous permeable material 11b is press-fitted and fixed to the housing 17.

When the on-off valve 8 is opened and the refrigerant flows in the direction A as shown in FIG. 2A, most of the refrigerant flows through the communication passage 16a, and the refrigerant flowing inside the flow control device 6 has almost no pressure loss. There is no state. The same applies when the refrigerant flows in the B direction. Next, when the on-off valve 8 is closed and the refrigerant is caused to flow in the direction A as shown in FIG. 2B, the refrigerant flows into the throttle passage 16b and is reduced in pressure by the expansion device 13. At this time, the check valve 14 is installed in a direction in which there is no pressure loss, and therefore the refrigerant hardly flows into the capillary tube 15. Next, when the on-off valve 8 is closed and the refrigerant flows in the B direction, the refrigerant flows in the throttle channel 16b as shown in (c), but does not flow in the check valve 14 and the entire amount of the refrigerant flows in the capillary tube 15. . This refrigerant is decompressed by the capillary tube 15, and further decompressed through the orifice 12 of the expansion device 13. That is, when the refrigerant flows as in (b), it is throttled by the orifice 12 in the expansion device 13, and when the refrigerant flows as in (c), it is restricted by the capillary tube 15 and the orifice 12 in the expansion device 13. To be As described above, the second flow rate control device 6 according to this embodiment is
The throttle amount of the refrigerant can be changed depending on the flow direction of the refrigerant.

Next, the operation of the refrigeration cycle of the air conditioner according to this embodiment will be described. In FIG. 1, the flow of the refrigerant during cooling is indicated by a solid arrow. Cooling operation corresponds to normal cooling operation when the air conditioning sensible load and latent heat load of the room are both large at startup and during summer, and the air conditioning sensible heat load is small but the latent heat load is large, such as in the middle period and rainy season. There is a cooling and dehumidifying operation corresponding to the case. In the normal cooling operation, the opening / closing valve 8 of the second flow rate control device 6 is opened, the refrigerant is allowed to flow as shown in FIG. 2 (a), and the space between the first indoor heat exchanger 5 and the second indoor heat exchanger 7 is almost eliminated. Connect without pressure loss.

At this time, the high-temperature and high-pressure vapor refrigerant leaving the compressor 1 operating at the number of revolutions according to the air conditioning load is the four-way valve 2.
And is condensed and liquefied in the outdoor heat exchanger 3. And
The pressure is reduced by the first flow rate control device 4, becomes a low-pressure two-phase refrigerant, flows into the first indoor heat exchanger 5, and is evaporated and vaporized. Furthermore, the second
After passing through the flow rate control device 6 with almost no pressure loss, it is vaporized again in the second indoor heat exchanger 7 to become low-pressure vapor refrigerant and returns to the compressor 1 again via the four-way valve 2.

In this normal cooling operation, since the second flow rate control device 6 is in a state where there is almost no pressure loss, cooling capacity and efficiency drop do not occur. Further, the first flow rate control device 4 is controlled so that the superheat degree of the refrigerant becomes 10 ° C. in the suction portion of the compressor 1, for example. In such a refrigeration cycle, both the indoor heat exchangers 5 and 7 operate as an evaporator, and the refrigerant evaporates here to remove heat from the room. The outdoor heat exchanger 3 operates as a condenser, and the refrigerant condenses here to release the heat taken indoors outdoors. This cools the room.

FIG. 4 is a characteristic diagram showing the operating state during the cooling / dehumidifying operation, and is a pressure-enthalpy diagram. The operation during the cooling / dehumidifying operation will be described with reference to FIG. It should be noted that points A to G shown in FIG. 4 indicate the state of the refrigerant at the points A to G shown in FIG. During this cooling / dehumidifying operation, the opening / closing valve 8 of the second flow rate control device 6 is closed and the refrigerant is flowed as shown in FIG.

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

At this time, the expansion device 1 of the second flow control device 6
The refrigerant passing through 9 is decompressed by the orifice 12, becomes 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 deprives the sensible heat and latent heat of the indoor air and evaporates. The low-pressure vapor refrigerant (point F) exiting the second indoor heat exchanger 7 passes through the four-way valve 2 (point G) again and returns to the compressor 1. In this cooling and dehumidifying operation,
The indoor air is the first indoor heat exchanger 5 that operates as a condenser.
The second indoor heat exchanger 7 that is heated by
Since it is cooled and dehumidified by, the dehumidification can be performed while preventing the room temperature from decreasing. Such a cooling and dehumidifying operation is also referred to as a cooling and reheating dehumidifying operation because the first indoor heat exchanger 5 is used as a reheater.

In this dehumidifying operation, the rotation frequency of the compressor 1 and the fan rotation speed of the outdoor heat exchanger 3 are adjusted to control the heat exchange amount of the outdoor heat exchanger 3 to control the first indoor heat exchanger. 5
The blowout temperature can be controlled in a wide range by controlling the amount of heating of the indoor air by. In addition, the opening of the first flow control device 4 and the first
It is also possible to control the fan rotation speed of the indoor heat exchanger 5 to control the condensing temperature of the first indoor heat exchanger 5, and to control the heating amount of the indoor air by the first indoor heat exchanger 5. Also, the second
The flow rate control device 6 is controlled, for example, so that the superheat degree of the refrigerant becomes 10 ° C. at the suction portion of the compressor 1.

In FIG. 1, the flow of the refrigerant during heating is indicated by a dotted arrow. Heating operation includes normal heating operation and heating dehumidification operation. At this time, the four-way valve 2 is connected as a dotted line to form a flow path. In the normal heating operation, the opening / closing valve 8 of the second flow rate control device 6 is opened, and the first indoor heat exchanger 5 and the second indoor heat exchanger 7 are connected with almost no pressure loss.

At this time, the compressor 1 is operated at a rotational speed according to the air conditioning load. The high-temperature and high-pressure vapor refrigerant that has left the compressor 1 passes through the four-way valve 2 and is condensed and liquefied in the second indoor heat exchanger 7. Then, it passes through the second flow rate control device 6 with almost no pressure loss, and is liquefied again in the first indoor heat exchanger 5. Further, it is decompressed by the first flow rate control device 4, becomes a low-pressure two-phase refrigerant, flows into the outdoor heat exchanger 3 and is vaporized and evaporated, and becomes a low-pressure vapor refrigerant and returns to the compressor 1 again via the four-way valve 2.

In this normal heating operation, since the second flow rate control device 6 is in a state where there is almost no pressure loss, heating capacity and efficiency are not reduced. Further, the first flow rate control device 4 is controlled so that the superheat degree of the refrigerant becomes 10 ° C. in the suction portion of the compressor 1, for example. In such a refrigeration cycle, the outdoor heat exchanger 3 operates as an evaporator, in which the refrigerant evaporates to remove heat from the outside. The indoor heat exchangers 7 and 5 both operate as a condenser, and the heat condensed outside the room is radiated to the room by condensing the refrigerant. As a result, the room is heated.

FIG. 5 is a characteristic diagram showing an operating state during the heating dehumidifying operation, and is a pressure-enthalpy diagram. The operation of the heating dehumidifying operation will be described with reference to FIG. Points A to G in FIG. 5 indicate the states of the refrigerant at the points A to G shown in FIG. 1 corresponding to the respective English letters. During this heating / dehumidifying operation, the on-off valve 8 is closed to enter the state shown in FIG. 2C, which is the reverse flow of the refrigerant during the cooling / dehumidifying operation.

The refrigerant discharged from the compressor 1 and passed through the four-way valve 2 exchanges heat with indoor air in the second indoor heat exchanger 7 from point F and is condensed to become a gas-liquid two-phase refrigerant or a liquid refrigerant (E
Point), and flows into the second flow control valve 6. The refrigerant passing through the orifice 12 of the second flow rate control device 6 is decompressed and becomes the point D and flows into the first indoor heat exchanger 5. Then, the refrigerant flowing into the first indoor heat exchanger 5 deprives the sensible heat and latent heat of the indoor air and evaporates. After this, the air passes through point C and further through the first flow rate control device 4, and the outdoor heat exchanger 3 and the suction side of the compressor 1 (G
It becomes a refrigeration cycle that returns to point). Note that, in this example, the state in which supercooling is attached at point E has been described, but depending on the operating state, there may be cases where subcooling does not occur.
It becomes the dotted line. Further, the first flow rate control device 4 is fully opened so that no pressure loss occurs.

In this operation, in order for the refrigerant to evaporate and dehumidify in the first indoor heat exchanger 5, the evaporation temperature in the first indoor heat exchanger 5 must be lower than the dew point temperature of the indoor air. The evaporation temperature may be controlled by adjusting the air volume of the blower, adjusting the rotation speed of the compressor, or the like so as to be equal to or lower than the dew point temperature of the room air. As a result, in the indoor unit 52, the air cooled and dehumidified in the first indoor heat exchanger 5 and the air heated in the second indoor heat exchanger 7 are mixed and blown out regardless of the outside air temperature condition. In the case of FIG. 5, when the evaporation temperature in the first indoor heat exchanger 5 becomes too low and the temperature of the air blown out in the room becomes too low, the first flow rate control device 4 is adjusted and evaporation is performed as shown in FIG. The temperature can also be adjusted.

In such a heating / dehumidifying operation, the indoor air is heated by the second indoor heat exchanger 7 operating as a condenser and cooled and dehumidified by the first indoor heat exchanger 5 operating as an evaporator. Dehumidification can be performed while preventing the room temperature from dropping. Since such a heating dehumidifying operation uses the second indoor heat exchanger 7 as a reheater, it is also referred to as a heating reheat dehumidifying operation. By performing the heating reheat dehumidifying operation, it is possible to dehumidify without lowering the room temperature or to dehumidify while raising the room temperature.

That is, regardless of the outside temperature condition, the cooling season and the heating season, if the cooling reheat dehumidifying operation and the heating reheat dehumidifying operation are switched according to the required air conditioning load, the room temperature is controlled (lowered, Dehumidification can be performed while increasing (equal to, rising).

Since the second flow rate control device 6 of this embodiment can control the flow rate even if the flow of the refrigerant is reversed, both cooling reheat dehumidification and heating reheat dehumidification can be realized. Further, according to the pressure-enthalpy curve of FIG. 4, the refrigerant is in a gas-liquid two-phase state at the inlet (point D) of the flow rate control device 5 during the cooling / dehumidifying operation, but according to the pressure-enthalpy curve of FIG. The refrigerant at the inlet (point E) of the flow rate control device 6 may be in a liquid state. When the refrigerant passes through the orifice having the same cross-sectional area, the pressure loss is larger in the gas-liquid two-phase state than in the liquid state. Therefore, in order to flow a predetermined amount of refrigerant, the throttle amount during the heating dehumidifying operation needs to be larger than that during the cooling dehumidifying operation. In the flow rate control device 6 according to this embodiment, the pressure reduction amount of the refrigerant can be set to be different depending on the flow direction of the refrigerant. Therefore, the throttle amount can be changed during the cooling dehumidifying operation and the heating dehumidifying operation, and the optimum dehumidifying operation can be controlled.

A specific example of a configuration in which the throttle amount of the flow control device 6 is set to be different will be described. For example, during the normal cooling operation and the normal heating operation, the flow rate control device 6 is brought into the state of FIG. Next, during the cooling / dehumidifying operation, the on-off valve 8 is closed,
The state shown in FIG. At this time, the second indoor heat exchanger 7
The cross-sectional area of the orifice 12 of the expansion device 13 is set so that the evaporation temperature of the refrigerant in (3) becomes the optimum expansion amount during the cooling / dehumidifying operation. Next, during the heating dehumidification operation, the flow direction is reversed, and the state shown in FIG. At this time, since the refrigerant flows through the capillary tube 15 and the expansion device 13, the expansion amount is larger than that during the cooling / dehumidifying operation by the expansion amount in the capillary tube 15. Therefore, the first indoor heat exchanger 5
The cross-sectional area and the length of the orifice 12 and the cross-sectional area and the length of the capillary tube 15 are set so that the evaporation temperature of the refrigerant is the optimum throttle amount during the heating and dehumidifying operation.

Normally, noise is generated when the gas-liquid two-phase refrigerant passes through the orifice 12. However, in the throttling device 13 according to this embodiment, the throttling passages 1 before and after the orifice 12 are generated.
Since 6b has the porous permeable materials 11a and 11b, the refrigerant flow noise generated when the gas-liquid two-phase refrigerant passes can be significantly reduced. That is, the gas-liquid two-phase state or liquid state refrigerant flowing from the first flow path connecting pipe 9a into the second flow rate control device 6 is
The flow is rectified by passing through the minute and innumerable fine holes of the porous permeable material 11a. For this reason, vapor slag (large bubbles) such as slag flow in which gas and liquid flow intermittently becomes small bubbles, and the flow state of the refrigerant becomes a homogeneous gas-liquid two-phase flow in which the vapor refrigerant and the liquid refrigerant are well mixed. The vapor refrigerant and the liquid refrigerant simultaneously pass through the orifice 12. Therefore, the speed does not fluctuate and the pressure does not fluctuate. In the high-speed gas-liquid two-phase jet downstream of the orifice 12, the flow velocity of the refrigerant is sufficiently reduced inside the porous permeable material 11b, and the speed distribution is made uniform. Since it does not collide with and no large vortex is generated in the flow, jet noise can be reduced. Therefore, in the conventional device, it was necessary to take measures such as winding a sound insulating material or a vibration damping material around the flow control device 6, but in the flow control device 6 according to this embodiment, the cost is unnecessary and the air conditioning is further improved. The recyclability of the device is also improved. Furthermore, the space 19a between the porous permeable material 11a and the orifice 12, and the porous permeable material 11b.
Since the space 19b between the orifice 12 and most of the porous permeable materials 11a and 11b serves as the refrigerant flow path, the function as the expansion device can be maintained and the reliability can be ensured.

In the present embodiment, the structure in which the refrigerant also flows into the outdoor heat exchanger 3 during the heating reheat dehumidifying operation has been described. However, as shown in FIG. 7, the refrigerant discharged from the first indoor heat exchanger 5 is A bypass circuit that bypasses the outdoor heat exchanger 3 and is directly sucked into the compressor 1 via the flow rate control device 10 may be added. With the addition of this bypass circuit, the evaporation temperature in the first indoor heat exchanger 5 can be controlled without being affected by the outside air temperature, and the dehumidification capacity can be controlled more stably.

Embodiment 2. FIG. 8 is a circuit configuration diagram showing a second flow rate control device 6 according to the second embodiment of the present invention, and (a), (b), and (c) respectively show operating states. In the figure, 8 is a switching means, for example, an on-off valve, 9
Reference numeral a is a first flow passage, here a first flow passage connecting pipe, 9b is a second flow passage here, a second flow passage connecting pipe, 13 is a first throttle device having a first throttle portion, and 16a and 16b are flow passages. The constituent piping, 20 is a second expansion device having a second expansion part.
The first flow passage connecting pipe 9a is divided into two flow passages, a communication flow passage 16a and a throttle flow passage 16b, and an open / close valve 8 is connected to one of the communication flow passages 16a. The fluid flows to 16a, and the refrigerant flows to the throttle channel 16b when closed. A throttle device 13 having a first throttle portion and a second throttle device 20 having a second throttle portion are connected in series to the throttle passage 16b. The pipe 16b joins the pipe 16a from the opening / closing valve 8 and is connected to the second flow path connecting pipe 9b.

The first diaphragm device 13 has the same structure as that of the diaphragm device 13 shown in FIG. 3 of the first embodiment, and operates similarly. However, the first diaphragm device 1 in this embodiment
3 does not have a connecting portion with the capillary tube 15 in the configuration of the first embodiment. As shown in FIG. 3, the porous permeable materials 11 a and 11 b are fixed to the valve body 18. Also,
A step is formed between the porous permeable materials 11a and 11b and the orifice 12 so that constant gaps 19a and 19b are formed. The valve body 18 provided with the porous permeable material 11a, the orifice 12, and the porous permeable material 11b is press-fitted and fixed to the housing 17.

FIG. 9 is a sectional view showing the second diaphragm device 20, and FIGS. 9 (a) and 9 (b) show the operating state.
Further, FIG. 10 is a plan view showing the operating valve 23, and the stopper 2
It is the figure seen from the 4 side. The second expansion device 20 has flow path openings at both ends and is arranged in the expansion flow path 16b. In FIG. 9, 21 is a housing, 22 is a valve seat having a conical opening provided at one end in the housing 21, 23 is an operating valve that moves left and right toward the drawing by the flow of the refrigerant, and 24 is It is a stopper provided at the other end of the housing 21. The front surface, which is the left end in the drawing of the operating valve 23, is shaped so as to closely contact the opening of the valve seat 22 and close the opening when the operating valve 23 moves to the left. For example, four grooves 25 are provided behind the operating valve 23 on the right side in the drawing. Further, an orifice 26 that serves as a second throttle portion is provided at the center of the operating valve 23. As shown in FIG. 8, the first expansion device 13 is connected in series in the direction in which the valve seat 22 is installed.

Next, the operation will be described. Figure 8 (a)
When the on-off valve 8 is opened and the refrigerant is caused to flow in the A direction as described above, the refrigerant almost flows into the communication flow path 16a, and the refrigerant flowing inside the flow rate control device 6 has almost no pressure loss. The same applies when the refrigerant flows in the B direction. Next, when the on-off valve 8 is closed and the refrigerant is caused to flow in the direction A as shown in FIG. 8B, the refrigerant flows into the throttle passage 16b to which the first throttle device 13 and the second throttle device 20 are connected, First, the pressure is reduced by the orifice 12 of the first expansion device 13. After that, the refrigerant flows into the second expansion device 20, but as shown in FIG. 9A, the operating valve 23 moves rightward with the flow of the refrigerant and hits the stopper 24 to stop. The refrigerant flowing in from the left is
As indicated by the arrow, the gas flows through the opening of the valve seat 22 and through the groove 25 provided in the operating valve 23. If the cross-sectional area of the groove 25 is made sufficiently larger than that of the orifice 26, the refrigerant will flow with almost no pressure loss. Therefore, FIG.
In the state of (b), the refrigerant is throttled only by the first expansion device 13.

Next, with the on-off valve 8 closed, the refrigerant is caused to flow in the B direction as shown in FIG. 8 (c). The refrigerant flows into the throttle flow passage 16b in which the second expansion device 20 and the first expansion device 13 are connected, and first flows into the second expansion device 20. At this time, FIG.
As shown in (b), the operating valve 23 is pushed by the flow of the refrigerant, and the conical portion on the front surface is in close contact with the valve seat 22 to close the opening. Therefore, the refrigerant flows through the orifice 26 and is throttled. After this,
The refrigerant flows into the first expansion device 13 and the porous permeable material 11
b, the orifice 12, the porous permeable material 11a in this order,
The pressure is reduced at the orifice 12. Therefore, in the state of FIG. 8C, both the first diaphragm device 13 and the second diaphragm device 20 are used for diaphragming. As described above, the second flow rate control device 6 according to the present embodiment has the configuration shown in FIGS.
As shown in (c), the refrigerant can flow in three different throttle amounts depending on the flow direction of the refrigerant.

The operation on the refrigerating cycle is the same as that of the first embodiment, and during the normal cooling operation and the normal heating operation, the opening / closing valve 8 of the second flow rate control device 6 is opened, as shown in FIG. 8 (a). The refrigerant is made to flow so that there is almost no pressure loss. During the cooling reheat dehumidifying operation, the on-off valve 8 is closed and the refrigerant is flown as shown in FIG. 8B. At this time, the cross-sectional area of the orifice 12 of the first expansion device 13 is set so that the evaporation temperature of the refrigerant in the second indoor heat exchanger 7 becomes the optimal throttle amount for the cooling reheat dehumidification operation. During the heating reheat dehumidification operation, the flow direction is opposite, so the refrigerant flows as shown in FIG. 8C. At this time, since the refrigerant flows through both the first expansion device 13 and the second expansion device 20,
The throttle amount becomes larger than that during the cooling / dehumidifying operation by the throttle amount of the second throttle device 20. Therefore, the inner diameter and the length of the orifice 12 of the first expansion device 13 and the second expansion device 20 are adjusted so that the evaporation temperature of the refrigerant in the first indoor heat exchanger 5 becomes the optimum expansion amount for the heating reheat dehumidification operation. The inner diameter and length of the orifice 26 are set. By using this flow rate control device 6 as the second flow rate control device 6 of the air conditioner, the cooling reheat dehumidification operation can be performed according to the required air conditioning load regardless of the outside air temperature condition, the cooling season, and the heating season. By switching the heating / reheat dehumidifying operation, dehumidification can be performed while controlling (decreasing, equalizing, increasing) the room temperature. In particular, the throttle channel 16b of the second flow control device 6 according to this embodiment is configured separately from the first throttle device 13 and the second throttle device 20, so that the throttle device of the conventional device shown in FIG. The above effect can be obtained by a simple modification in which the second expansion device 20 is connected to the flow path.

In the conventional device, noise is generated when the gas-liquid two-phase refrigerant passes through the orifice 12 of the first expansion device 13 during the cooling and dehumidifying operation, but in the expansion device 13 according to this embodiment, the orifice 12 Porous permeable material 11 before and after
Since a and 11b are provided, the refrigerant flowing noise generated when the gas-liquid two-phase refrigerant passes can be significantly reduced. Further, even during the heating / dehumidifying operation, the refrigerant squeezed by the orifice 26 of the second expansion device 20 passes through the porous permeable materials 11a, 11b of the first expansion device 13, so that the refrigerant flow noise can be significantly reduced. Therefore, in the conventional device, it was necessary to take a measure such as winding a sound insulating material or a vibration damping material around the flow control device 6, but in the flow control device 6 according to this embodiment, the cost can be reduced because it is unnecessary. Furthermore, the recyclability of the air conditioner is also improved.

Further, since the second expansion device 20 can be made to have almost the same diameter as the pipe 16b, it has an advantage that it can be downsized as compared with the first embodiment constituted by the capillary tube 15.

The second diaphragm device 20 may be constructed as shown in FIG. In this configuration, the orifice 26 is provided in the valve seat 22 instead of being provided in the center of the operating valve 23.
The operation and effect are similar to those of the configuration of FIG. Also,
Even if the groove 27 is installed in the valve seat 22 as shown in FIG. 12, the same effect is obtained. However, in FIGS. 11B and 12B, when the operating valve 23 moves toward the left to close the opening, the orifice 26 or the groove 27 is not blocked by the operating valve 23 and the refrigerant flows. Need to be configured.
Further, the orifice 26 of FIGS. 9 and 11 and the groove 27 of FIG.
A plurality may be provided, but since the throttling amount is increased or decreased, it is necessary to consider so that the flow resistance is within the set value.

Embodiment 3. FIG. 13 is a circuit configuration diagram showing a second flow rate control device 6 according to the third embodiment of the present invention, in which (a), (b), and (c) show operating states. In the figure, 8 is a switching means, such as an on-off valve,
Reference numeral 9a is a first flow passage, here a first flow passage connecting pipe, 9b is a second flow passage here, a second flow passage connecting pipe, 16a and 16b are pipes constituting a flow passage, 28 is a first throttle portion and a second A diaphragm device having a diaphragm portion. The first flow passage connecting pipe 9a is divided into two flow passages, a communication flow passage 16a and a throttle flow passage 16b, and an open / close valve 8 is connected to one of the communication flow passages 16a. The fluid flows to 16a, and the refrigerant flows to the throttle channel 16b when closed. A throttle device 28 having first and second throttle portions is connected to the throttle channel 16b. The pipe 16b joins the pipe 16a from the opening / closing valve 8 and is connected to the second flow path connecting pipe 9b.

FIG. 14 is a cross-sectional view showing the diaphragm device 28, and (a) and (b) show the operating state, respectively. In the figure, the same reference numerals as those in the first or second embodiment indicate the same or corresponding portions. The diaphragm device 28 is configured by integrating the first diaphragm device 13 and the second diaphragm device 20 in the second embodiment into the housings 17 and 21. This throttling device 28 has flow path openings at both ends,
A first flow path connecting pipe 9a connected to the left side of the drawing,
It is arranged in the throttle channel 16b between the second channel connecting pipes 9b connected to the right side. In the figure, 11a, 1
1b is a porous permeable material, 12 is an orifice serving as a first throttle portion opened in the center of the valve body 18, 17 is a casing, 18 is a valve body, 19a and 19b are the orifice 12 and the porous permeable material 1
It is a gap provided between 1a and 11b. Also,
Reference numeral 21 is a housing formed integrally with the housing 17, 22 is a valve seat having a conical opening, and 24 is a stopper that stops the operating valve 23 that operates by the flow of the refrigerant. The front surface of the operating valve 23, which is the connection side of the first connection pipe 9a, is shaped so as to closely contact the opening of the valve seat 22 and close the opening when the operating valve 23 moves to the left. Second connection pipe 9b of operating valve 23
For example, four grooves 25 are provided behind the connection side. Further, an orifice 26 that serves as a second throttle portion is provided at the center of the operating valve 23.

Next, the operation will be described. FIG.
When the on-off valve 8 is opened and the refrigerant is caused to flow in the direction A as shown in (a), the refrigerant almost flows into the communication passage 16a, and the refrigerant flowing inside the flow rate control device 6 is in a state where there is almost no pressure loss. The same applies when the refrigerant flows in the B direction. Next, when the on-off valve 8 is closed and the refrigerant is caused to flow in the direction A as shown in FIG. 13B, the refrigerant flows into the throttle flow passage 16b connected to the expansion device 28, passes through the porous permeable material 11a, The pressure is reduced by the orifice 12 and passes through the porous permeable material 11b. After this, the refrigerant flows from the opening of the valve seat 22 into the portion where the operating valve 23 is present, but as shown in FIG. 14A, the operating valve 23 moves to the right toward the flow of the refrigerant and hits the stopper 24 to stop. . Therefore, as shown by the arrow, the refrigerant that has passed through the opening of the valve seat 22 flows through the groove 25 provided in the operating valve 23. If the cross-sectional area of the groove 25 is made sufficiently larger than that of the orifice 12, the refrigerant will flow in the portion of the housing 21 with almost no pressure loss. Therefore, FIG. 13 (b)
In this state, the refrigerant flowing into the expansion device 28 is restricted only by the orifice 12 that is the first restriction part.

Next, with the on-off valve 8 closed, the refrigerant flows in the B direction as shown in FIG. 13 (c). The refrigerant flows into the throttle channel 16b connected to the throttle device 28 and flows into the housing 21 side. At this time, as shown in FIG. 14B, the operating valve 23 is pushed by the flow of the refrigerant, and the conical portion on the front surface closely contacts the valve seat 22 to close the opening. Therefore, the refrigerant flows through the orifice 26 and is throttled. After that, the refrigerant flows into the casing 17 side, and the porous permeable material 11b, the orifice 12, and the porous permeable material 11a.
And the pressure is reduced at the orifice 12. Therefore, in the state of FIG.
Both the orifice 26 which is the second throttle portion and the orifice 12 which is the first throttle portion are throttled. As described above, the second flow rate control device 6 according to this embodiment causes the refrigerant to flow in three different throttle amounts depending on the direction of the refrigerant flow, as shown in FIGS. 13A, 13B, and 13C. be able to.

The operation on the refrigerating cycle is the same as that of the first embodiment, and during the normal cooling operation and the normal heating operation, the opening / closing valve 8 of the second flow rate control device 6 is opened as shown in FIG. 13 (a). The refrigerant is made to flow so that there is almost no pressure loss. During the cooling / dehumidifying operation, the on-off valve 8 is closed and the refrigerant is flown as shown in FIG. 13 (b). At this time, the cross-sectional area of the orifice 12 of the expansion device 28 is set so that the evaporation temperature of the refrigerant in the second indoor heat exchanger 7 has an optimum expansion amount during the cooling / dehumidifying operation. During the heating / dehumidifying operation, the flow direction is opposite, so that FIG.
The refrigerant flows as in (c). At this time, the orifice 26
Since the refrigerant flows in both the orifice 12 and the orifice 12, the throttle amount becomes larger than that during the cooling / dehumidifying operation. Therefore, the inner diameter and length of the orifice 12 and the inner diameter and length of the orifice 26 are set so that the evaporation temperature of the refrigerant in the first indoor heat exchanger 5 is optimal during the heating and dehumidifying operation. Flow control device 6 shown in FIG.
Is used as the second flow rate control device 6 of the air conditioner, the cooling reheat dehumidifying operation and the heating reheat dehumidifying operation are performed according to the required air conditioning load regardless of the outside air temperature condition, the cooling season, and the heating season. By switching between, it is possible to perform dehumidification while controlling (decreasing, equalizing, raising) the room temperature.

In the conventional device, noise is generated when the gas-liquid two-phase refrigerant passes through the orifice 12 of the expansion device 28 during the cooling and dehumidifying operation, but the expansion device 28 according to this embodiment is used.
Then, before and after the orifice 12, the porous permeable materials 11a, 1
Since 1b is provided, the refrigerant flowing noise generated when the gas-liquid two-phase refrigerant passes can be significantly reduced. Further, even during the heating / dehumidifying operation, the refrigerant throttled by the orifice 26 is
Since it passes through the porous permeable materials 11a and 11b, the refrigerant flow noise can be significantly reduced. Therefore, in the conventional device, the flow rate control device 6
Although it was necessary to take measures such as wrapping a sound insulating material or a vibration damping material around the air conditioner, it is not necessary in the flow rate control device 6 according to this embodiment, the cost can be reduced, and the recyclability of the air conditioner is improved. To do.

Further, since the flow rate control device 6 in this embodiment is constructed by integrating the first and second throttle devices in the second embodiment, the second flow control device in the second embodiment.
It has the advantage that it can be made smaller than the flow control device 6.

Further, the diaphragm device 28 may be constructed as shown in FIG. In this configuration, the orifice 26 is connected to the operating valve 2
Instead of being provided at the center of 3, the valve seat 22 is provided. The operation and effect are similar to those of the configuration of FIG. Further, as shown in FIG. 16, the same effect can be obtained by providing the groove 27 in the valve seat 22. However, in FIGS. 15B and 16B, when the operating valve 23 moves toward the left to close the opening,
The orifice 26 or the groove 27 needs to be configured to allow the refrigerant to flow without being blocked by the operating valve 23. Further, the orifice 26 of FIGS. 14 and 15 and the groove 27 of FIG.
A plurality may be provided, but since the throttling amount is increased or decreased, it is necessary to consider so that the flow resistance is within the set value.

Fourth Embodiment FIG. 17 is a circuit configuration diagram showing a second flow rate control device according to Embodiment 4 of the present invention, in which (a), (b) and (c) respectively show operating states. In the figure, 8 is a switching means, for example, an on-off valve, 9
Reference numeral a is a first flow passage, here a first flow passage connecting pipe, 9b is a second flow passage here, a second flow passage connecting pipe, 16a and 16b are pipes forming a flow passage, and 29 is a diaphragm device. The first flow passage connecting pipe 9a includes two flow passages, a communication flow passage 16a and a throttle flow passage 1.
The on-off valve 8 is connected to one of the communication channels 16a, and the fluid flows to the communication channel 16a when the on-off valve 8 is opened, and the refrigerant flows to the throttle channel 16b when the on-off valve 8 is closed. A throttle device 29 having first and second throttle portions is connected to the throttle passage 16b. The pipe 16b joins the pipe 16a from the opening / closing valve 8 and is connected to the second flow path connecting pipe 9b.

FIG. 18 is a sectional view showing the diaphragm device 29, and FIGS. 18 (a) and 18 (b) respectively show the operating state. In the figure, the same reference numerals as those in the first embodiment, the second embodiment or the third embodiment indicate the same or corresponding portions. The expansion device 29 is configured by incorporating the mechanism of the operating valve 23 of the second expansion device 20 in the center of the first expansion device 13 in the second embodiment. This diaphragm device 29
Has a flow passage port at both ends, and is provided in the throttle flow passage 16b between the first flow passage connecting pipe 9a connected to the left side in the drawing and the second flow passage connecting pipe 9b connected to the right side in the figure. To be done. In the figure, 11a and 11b are porous permeable materials, and 12
Is a conical orifice serving as a first throttle portion formed in the center of the valve body 18, 17 is a housing, 18 is a valve body, and 19a, 19
Reference symbol b is a gap provided between the orifice 12 and the porous permeable materials 11a and 11b. Orifice 1 of valve body 18
2 is connected to a space 32 partitioned by a partition plate 31. One or a plurality of flow paths 33 are installed in the partition plate 31, and the space 32 and the gap 19b communicate with each other. In the space 32, there is an operating valve 34 that operates by the flow of the refrigerant, and the front surface of the operating valve 34, which is the connection side of the first connection pipe 9a, has a hole of the conical orifice 12 when the operating valve 34 moves to the left. It has a shape that closes and closes. Working valve 3
When 4 moves to the right, it hits the partition plate 31 and stops. Further, an orifice 35 serving as a second throttle portion is provided at the center of the operating valve 34.

Next, the operation will be described. FIG. 17
When the on-off valve 8 is opened and the refrigerant is caused to flow in the direction A as shown in (a), the refrigerant almost flows into the communication passage 16a, and the refrigerant flowing inside the flow rate control device 6 is in a state where there is almost no pressure loss. The same applies when the refrigerant flows in the B direction. Next, when the on-off valve 8 is closed and the refrigerant is caused to flow in the A direction as shown in FIG. 17B, the refrigerant flows into the throttle flow passage 16b to which the expansion device 28 is connected. At this time, as shown in FIG. 18A, the operating valve 23 moves rightward with the flow of the refrigerant, hits the partition plate 31, and stops. Therefore, as shown by the arrow, the refrigerant that has passed through the porous permeable material 11a and the orifice 12 has a flow path 3
3. Flow through the porous permeable material 11b. If the cross-sectional area of the flow path 33 is made sufficiently larger than that of the orifice 12, the flow path 33 will flow with almost no pressure loss. Therefore, in the state of FIG. 17B, the refrigerant flowing into the expansion device 29 is restricted by the orifice 12 which is the first restriction part.

Next, with the on-off valve 8 closed, the refrigerant is caused to flow in the B direction as shown in FIG. 17 (c). The refrigerant is the expansion device 29
Flows into the throttle channel 16b connected to the above, and flows into the housing 17 from the right side. At this time, as shown in FIG. 18B, the operating valve 34 is pushed by the flow of the refrigerant, and the conical portion on the front surface is in close contact with the valve body 18 to close the orifice 12. Therefore, the refrigerant that has flowed in from the right direction has a porous permeable material 11
b, the flow path 33 passes through the space 32, flows through the orifice 35, and is narrowed. Therefore, in the state of FIG. 17B, the refrigerant is throttled by the throttle device 29 at the orifice 35 that is the second throttle portion. Therefore, for example, the orifice 35 that is the second throttle portion and the orifice 1 that is the first throttle portion
The diameter and length of 2 are different, and the orifice 35
If the flow resistance of the orifice 12 is changed, the second flow rate control device 6 according to the present embodiment has the configuration shown in FIG.
As shown in (b) and (c), depending on the flow direction of the refrigerant, 3
The refrigerant can be made to flow with the same throttle amount.

The operation on the refrigerating cycle is the same as that of the first embodiment, and during the normal cooling operation and the normal heating operation, the opening / closing valve 8 of the second flow rate control device 6 is opened and as shown in FIG. 17 (a). The refrigerant is made to flow so that there is almost no pressure loss. During the cooling and dehumidifying operation, the on-off valve 8 is closed and the refrigerant is flown as shown in FIG. 17 (b). At this time, the cross-sectional area and the length of the orifice 12 of the expansion device 29 are set so that the evaporation temperature of the refrigerant in the second indoor heat exchanger 7 has the optimum expansion amount during the cooling / dehumidifying operation. During the heating / dehumidifying operation, the flow direction is opposite, so the refrigerant flows as shown in FIG. 17 (c). At this time, if the flow resistance is configured such that the flow resistance of the orifice 12 <the flow resistance of the orifice 35, the throttle amount becomes larger than that during the cooling / dehumidifying operation. Therefore, the inner diameter and the length of the orifice 35 are set so that the evaporation temperature of the refrigerant in the first indoor heat exchanger 5 is optimal during the heating / dehumidifying operation. This flow control device 6
Is used as the second flow rate control device 6 of the air conditioner, the cooling reheat dehumidifying operation and the heating reheat dehumidifying operation are performed according to the required air conditioning load regardless of the outside air temperature condition, the cooling season, and the heating season. By switching between, it is possible to perform dehumidification while controlling (decreasing, equalizing, raising) the room temperature.

Here, if the diameter or length of the flow path 33 is set smaller than the diameter or length of the orifice 12, the refrigerant will be throttled in the flow path 33 as well. That is, when the refrigerant flows as shown in FIG. 18A, the refrigerant is throttled by the orifice 12 and the flow passage 33, and when the refrigerant flows as shown in FIG. Squeeze at 33. Even with this configuration, if the flow resistances of the orifice 35 and the orifice 12 are changed, it is possible to obtain the throttling device 29 having different throttling amounts in the A-direction and B-direction flow directions. In this case, the cross-sectional area of the orifice 12 and the inner diameter and length of the flow path 33 are set so that the evaporation temperature of the refrigerant in the second indoor heat exchanger 7 has the optimum throttle amount during the cooling / dehumidifying operation. Further, the inner diameter and length of the orifice 35 and the inner diameter and length of the flow path 33 are set so that the evaporation temperature of the refrigerant in the first indoor heat exchanger 5 is optimal during the heating dehumidifying operation during the heating dehumidifying operation.

In the conventional device, noise is generated when the gas-liquid two-phase refrigerant passes through the orifice 12 of the expansion device 29 during the cooling and dehumidifying operation, but the expansion device 29 according to this embodiment is used.
Then, before and after the orifice 12, the porous permeable materials 11a, 1
Since 1b is provided, the refrigerant flowing noise generated when the gas-liquid two-phase refrigerant passes can be significantly reduced. Also, during the heating / dehumidifying operation, the orifice 35 of the expansion device 29 is similarly provided.
Since the refrigerant squeezed by (4) passes through the porous permeable materials 11a and 11b, the refrigerant flow noise can be significantly reduced. Therefore, in the conventional device, it was necessary to take measures such as winding a sound insulating material or a vibration damping material around the flow control device 6, but in the flow control device 6 according to this embodiment, it is not necessary and the cost can be further reduced. The recyclability of the air conditioner is also improved.

Further, as in the third embodiment, the second flow rate control device 6 in this embodiment is constructed by integrating the first and second throttle devices in the second embodiment.
It has the advantage that it can be made smaller than the second flow rate control device 6 in the second embodiment. Further, due to its configuration, it can be made smaller than the second flow rate control device 6 in the third embodiment.

Further, the diaphragm device 29 may be constructed as shown in FIG. In this configuration, the orifice 35 is connected to the operating valve 3
4 instead of being provided in the center, the orifice 12 of the valve body 18
It is provided in the part where is not provided. The operation and effects are similar to those of the configuration of FIG. Further, as shown in FIG. 20, the same effect can be obtained by providing the groove 36 in the orifice 12. However, in FIGS. 19B and 20B, when the operating valve 34 moves to the left to close the opening, the orifice 35 or the groove 36 is not blocked by the operating valve 34 and the refrigerant flows. Need to be configured. Further, a plurality of orifices 35 in FIG. 18 and FIG. 19 or a plurality of grooves 36 in FIG. 20 may be provided, but it is necessary to consider so that the flow resistance is within the set value because the throttle amount is increased or decreased.

In the first to fourth embodiments,
The porous permeable materials 11a and 11b have, for example, a ventilation hole with a diameter of 1
The foam metal is made of Ni, Ni—Cr, or stainless steel, for example, having a thickness of 1 μm to 10 mm and a thickness of 00 μm to 500 μm. The porous permeable material is not limited to the foamed metal, but may be a sintered metal obtained by sintering a metal powder, or a ceramic porous permeable material, a wire mesh, or a stack of several wire meshes, or a number of wire meshes. The same effect can be obtained with a sintered wire net or a laminated wire net that is obtained by stacking and sintering one sheet. Also,
The porous permeable materials 11a and 11b that allow the refrigerant to pass through are the first
If it is provided in at least one of the narrowed portion between the orifice 12 and the first connection flow passage 9a and between the orifice 12 and the second connection flow passage 9b, there is some noise reduction effect. Further, since the porous permeable materials 11a and 11b are provided, even if the pipe forming the second flow rate control device 6 is bent to some extent, it is possible to absorb the refrigerant flowing sound caused by the bending. Therefore, when the second flow rate control device 6 is stored in the indoor unit 52, it can be stored according to the empty space of the indoor unit 52, which facilitates assembly.

In addition, in the first to fourth embodiments, the pipes 16a and 16b constituting the second flow rate control device 6 are arranged.
If the inner diameter of the throttle channel 16b is smaller than the inner diameter of the communication channel 16a, the device 6 itself can be downsized. However, the inner diameter of the throttle channel 16b is set to the communication channel 16a.
If it is made too small as compared with the inner diameter of, the refrigerant flow noise will be generated at that portion, so it is preferable to configure the pipe diameter so that the refrigerant flow noise is not generated.

Also, the problem of foreign matter in the refrigerant circuit is 100 μm to 500, in which the diameter of the ventilation holes of the porous permeable materials 11a and 11b is larger than that of a filter used in a general refrigerant circuit.
By setting the thickness to μm, stable operation can be performed without clogging.

The flow control device 6 may be installed horizontally, vertically, or obliquely with respect to the flow of the refrigerant, with the same effect. In the case of vertical or oblique installation, the refrigerant may flow from either the bottom to the top or the top to the bottom.

As the refrigerant of the refrigeration cycle device, R410A of HFC type refrigerant was used. This refrigerant is a refrigerant suitable for global environment protection that does not destroy the ozone layer, and has a smaller refrigerant loss and a smaller pressure loss than R22, which has been used as a conventional refrigerant, because the refrigerant vapor density is large and the refrigerant flow velocity is high.
The pore diameter of the porous permeable material arranged in the throttle portion of the second flow rate control device 6 can be reduced, and the refrigerant flow noise can be further reduced.
However, the refrigerant is not limited to R410A, but H
FC refrigerants R407C, R404A, R507A
May be From the viewpoint of preventing global warming, R32 alone, which is an HFC-based refrigerant with a small global warming coefficient,
R152a alone or a mixed refrigerant such as R32 / R134a may be used. Further, HC-based refrigerants such as propane, butane, and isobutane, natural refrigerants such as ammonia, carbon dioxide, ether, and mixed refrigerants thereof may be used. In particular, propane, butane, isobutane, and their mixed refrigerants have a lower operating pressure than R410A, and the pressure difference between the condensation pressure and the evaporation pressure is small, so it is possible to increase the inner diameter of the orifice and improve the reliability against clogging. Can be further improved.

[0075]

As described above, according to the flow rate control device according to the first aspect of the present invention, the communication flow passage that connects the first flow passage and the second flow passage and the communication flow passage are provided in parallel with each other. A fluid flow path comprises: a throttle channel having a first throttle section and a second throttle section; and a switching means for switching the communication channel and the throttle channel, wherein a fluid flows from the first channel of the throttle channel to the second channel. When the fluid flows to the passage, the pressure is reduced by the first throttle portion, and when the fluid flows from the second passage of the throttle passage to the first passage, the second throttle portion or the second throttle portion and the first passage Reduce the pressure at the throttle,
Since the throttle amount is configured to be different in the flow direction of the fluid of the throttle channel, it is possible to switch between the case where the first and second channels are communicated with each other and the case where the throttle section is provided, and the forward and reverse flow It is possible to obtain the effect that different aperture amounts can be set depending on the direction.

According to the second aspect of the flow control device of the present invention, the first throttle portion is constituted by an orifice for reducing the pressure of the fluid to pass therethrough, and between the orifice and the first flow path and between the orifice. At least one of the second flow passages is provided with a porous permeable material that allows a fluid to pass therethrough, thereby switching between the case where the first and second flow passages are connected and the case where the narrowed portion is provided. In addition, it is possible to set different throttle amounts in the forward and reverse flow directions, and it is possible to obtain the effect of reducing the flow noise of the fluid.

Further, according to the diaphragm device of the third aspect of the present invention, a valve having a flow path opening at both ends and disposed in the flow path, and an opening provided at one end of the flow path in the case. Zodiac,
An operating valve that operates in the flow direction of the fluid flowing in the housing, a stopper provided at the other end of the housing, and a throttle portion provided at the operating valve or the valve seat, and from the valve seat side. When the fluid flows to the stopper side, the operating valve stops at the stopper and the fluid flows through the opening. When the fluid flows from the stopper side to the valve seat side, the operating valve stops at the valve seat. Then, by closing the opening and flowing the fluid through the throttle portion, it is possible to obtain the effect that different throttle amounts can be set in the forward and reverse flow directions.

According to the flow rate control device of the fourth aspect of the present invention, the second throttle portion of the flow rate control device of the first or second aspect is constituted by the throttle device of the third aspect. As a result, it is possible to switch between the case where the first and second flow paths are communicated with each other and the case where the first and second flow paths are communicated with each other, and it is possible to obtain an effect that different throttle amounts can be set in the forward and reverse flow directions.

According to the fifth aspect of the flow control device of the present invention, the second throttle portion is provided in parallel with the capillary tube, and the check valve is provided in parallel with the capillary tube to permit only one-way flow. With the above configuration, it is possible to switch between the case where the first and second flow paths are communicated with each other and the case where the first and second flow paths are communicated with each other, and it is possible to obtain an effect that different throttle amounts can be set in the forward and reverse flow directions.

Further, according to the diaphragm device of the sixth aspect of the present invention, there is provided a case in which one end is connected to the first flow path and the other end is connected to the second flow path, and the case is provided in the flow path. Between the first throttle portion and the first flow passage, and between the first throttle portion and the second flow passage, the first throttle portion provided on the first flow passage side of A valve seat having a porous permeable material disposed in at least one of the flow passages and allowing passage of the fluid, and an opening provided on the first throttle portion side between the first throttle portion and the second flow passage. An operating valve that operates in the flow direction of the fluid flowing in the housing; a stopper provided between the operating valve and the second flow path; and a second throttle portion provided on the operating valve or the valve seat. When the fluid flows from the first flow path toward the second flow path, the operating valve stops at the stopper. The fluid flows through the first throttle portion and the opening, and when the fluid flows from the second flow passage to the first passage, the operating valve stops at the valve seat to close the opening, and the fluid is the second throttle portion. Also, since the flow rate of the fluid flows through the first throttle portion so that the throttle amount varies depending on the flow direction of the fluid, it is possible to obtain an effect that the throttle amount is small, the noise is low, and different throttle amounts can be set in the forward and reverse flow directions. .

According to the seventh aspect of the present invention, in the case where the one end is connected to the first flow path and the other end is connected to the second flow path, the case is disposed in the flow path. A valve body having a first throttle portion for depressurizing and passing the fluid flowing therethrough, and at least one of the first throttle portion and the first flow passage and the first throttle portion and the second flow passage. A porous permeable material that allows the fluid to pass therethrough, an operating valve that operates in the flow direction of the fluid that flows in the housing, and a partition plate that has a channel provided between the operating valve and the second channel. When the fluid flows from the first flow path to the second flow path, the working valve stops at the partition plate and the fluid is When the fluid flows from the second passage to the first passage through the passage of the throttle portion and the partition plate, The valve is stopped at the valve body to close the first throttle portion, and the fluid flows through the second throttle portion, so that the throttle amount is different depending on the flow direction of the fluid. Thus, there is an effect that different throttle amounts can be set in the forward and reverse flow directions.

According to the eighth aspect of the flow control device of the present invention, the communication passage connecting the first passage and the second passage and the communication passage arranged in parallel with the communication passage. A throttling flow path formed by connecting the throttling device described above, and a switching means for switching the communication flow path and the throttling flow path, wherein a fluid flows from the first flow path of the throttle flow path to the second flow path. When flowing, the pressure is reduced by the first throttle portion of the throttle device, and when the fluid flows from the second flow passage of the throttle flow passage to the first flow passage, the second throttle portion or the second throttle portion of the throttle device. In the case where the first and second flow paths are communicated with each other in a small size and with low noise, the pressure is reduced in the first throttle part and the throttle amount is different in the flow direction of the fluid in the throttle flow path. It is possible to switch between the flow rate and the flow rate through the throttle section. An effect that can be set is obtained.

According to the air conditioner of claim 9 of the present invention, the compressor, the outdoor heat exchanger, the first flow rate control device, the first indoor heat exchanger, the second flow rate control device, the second indoor space. A refrigeration cycle in which heat exchangers are sequentially connected is provided, and
Alternatively, the flow control device according to claim 2, 4 or 5, or 8 is used as the second flow control device, and the first and second indoor heat exchangers are both operated as an evaporator or a condenser. At this time, the second flow rate control device connects the first and second indoor heat exchangers via a communication flow path, and one of the first and second indoor heat exchangers is an evaporator and the other is condensed. When operating as a heat exchanger, the second flow rate control device is configured to switch the switching means so as to connect the first and second indoor heat exchangers via the throttle passage, so that the noise is stable with low noise. In addition, the flow resistance of the refrigerant can be controlled, and it is possible to obtain the effect that the cooling reheat dehumidification operation control and the heating reheat dehumidification operation control can be supported.

According to the tenth aspect of the present invention, in the air conditioner according to the ninth aspect, the first indoor heat exchanger is an evaporator and the second indoor heat exchanger is a condenser. The throttle amount of the second flow control device in the heating reheat dehumidification operation is larger than the throttle amount in the cooling reheat dehumidification operation in which the first indoor heat exchanger is the condenser and the second indoor heat exchanger is the evaporator. As a result, there is an effect that the flow rate can be efficiently controlled with low noise, and the cooling reheat dehumidifying operation and the heating reheat dehumidifying operation can be operated with good controllability regardless of the season.

[Brief description of drawings]

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

FIG. 2 is a circuit configuration diagram showing a second flow rate control device according to the first embodiment.

FIG. 3 is a cross-sectional view showing a diaphragm device according to the first embodiment.

FIG. 4 is a characteristic diagram showing an operating state of the air-conditioning apparatus according to Embodiment 1 during a cooling / dehumidifying operation.

FIG. 5 is a characteristic diagram showing an operating state of the air-conditioning apparatus according to Embodiment 1 during a heating dehumidifying operation.

FIG. 6 is a characteristic diagram showing another operating state of the air-conditioning apparatus according to Embodiment 1 during the heating / dehumidifying operation.

FIG. 7 is a refrigerant circuit diagram showing another example of the air-conditioning apparatus according to Embodiment 1.

FIG. 8 is a circuit configuration diagram showing a second flow rate control device according to Embodiment 2 of the present invention.

FIG. 9 is a cross-sectional view showing a diaphragm device according to a second embodiment.

FIG. 10 is a plan view showing an operating valve according to the second embodiment.

FIG. 11 is a cross-sectional view showing another example of the diaphragm device according to the second embodiment.

FIG. 12 is a sectional view showing still another example of the diaphragm device according to the second embodiment.

FIG. 13 is a circuit configuration diagram showing a flow rate control device according to a third embodiment of the present invention.

FIG. 14 is a cross-sectional view showing a diaphragm device according to a third embodiment.

FIG. 15 is a cross-sectional view showing another example of the diaphragm device according to the third embodiment.

FIG. 16 is a cross-sectional view showing still another example of the diaphragm device according to the third embodiment.

FIG. 17 is a circuit configuration diagram showing a flow rate control device according to a fourth embodiment of the present invention.

FIG. 18 is a sectional view showing a diaphragm device according to a fourth embodiment.

FIG. 19 is a cross-sectional view showing another example of the diaphragm device according to the fourth embodiment.

FIG. 20 is a cross-sectional view showing still another example of the diaphragm device according to the fourth embodiment.

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

FIG. 22 is a partial cross-sectional view showing a second conventional flow rate control device.

FIG. 23 is a sectional view showing another example of a conventional second flow rate control device.

FIG. 24 is a sectional view showing still another example of a conventional second flow rate control device.

[Explanation of symbols]

1 compressor, 2 flow path switching means, 3 outdoor heat exchanger, 4
1st flow control device, 5 1st indoor heat exchanger, 6 2nd
Flow control device, 7 second indoor heat exchanger, 8 switching means,
9a 1st flow path, 9b 2nd flow path, 10 check valve, 11
a, 11b Porous permeable material, 12 First throttle part, 13
1st throttling device, 14 check valve, 15 capillary tube, 16a communication channel, 16b throttling channel, 17 casing, 18 valve body, 19a, 19b space, 20 2nd throttling device, 21 casing, 22 valve seat , 23 working valve, 24
Stopper, 25 groove, 26 2nd throttle part, 27 groove, 2
8 diaphragm device, 29 diaphragm device, 31 partition plate, 32
Space, 33 flow paths, 34 working valve, 35 second throttle part, 3
6 grooves, 51 outdoor units, 52 indoor units.

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) // F16K 47/04 F16K 47/04 A (72) Inventor Yoshihiro Sumida 2-2 Marunouchi, Chiyoda-ku, Tokyo No. 3 F term in Sanryo Electric Co., Ltd. (reference) 3H066 AA01 BA17 BA32 BA33 CA02 EA13 EA18

Claims (10)

[Claims] 1. A communication channel that connects the first channel and the second channel, a throttle channel that is provided in parallel with the communication channel and has a first throttle section and a second throttle section, and the communication channel. And a switching means for switching the throttle channel, when the fluid flows from the first channel of the throttle channel to the second channel, the pressure is reduced in the first throttle section, and the fluid is the throttle channel. When flowing from the second flow path to the first flow path, the pressure is reduced by the second throttle portion or the second throttle portion and the first throttle portion, and the throttle amount is reduced in the fluid flow direction of the throttle passage. A flow control device characterized by being configured differently. 2. The first throttle portion is constituted by an orifice for reducing the pressure of a fluid and allows the fluid to pass therethrough, and is provided in at least one of the passages between the orifice and the first passage and between the orifice and the second passage. The flow rate control device according to claim 1, further comprising a porous permeable material that allows the fluid to pass therethrough. 3. A casing having flow passage openings at both ends and arranged in the flow passage, a valve seat having an opening provided at one end in the casing, and a valve seat operating in a flow direction of a fluid flowing in the casing. An operating valve, a stopper provided at the other end of the housing, and a throttle provided at the operating valve or the valve seat, and when the fluid flows from the valve seat side to the stopper side, the operation is performed. The valve stops at the stopper and the fluid flows through the opening. When the fluid flows from the stopper side to the valve seat side, the operating valve stops at the valve seat and closes the opening, and the fluid is A throttling device, wherein the throttling device is configured so that the throttling amount varies depending on the flow direction of the fluid by flowing through the throttling portion. 4. The flow rate control device according to claim 1 or 2, wherein the second throttle portion is constituted by the throttle device according to claim 3. 5. The first throttle portion is constituted by a capillary tube and a check valve which is provided in parallel with the capillary tube and permits only a one-way flow. 2. The flow control device according to 2. 6. A casing having one end connected to the first flow passage and the other end connected to the second flow passage and disposed in the flow passage, and a fluid which is provided on the first flow passage side in the casing and flows in the casing. A first throttle portion that is reduced in pressure and passes through, and the fluid disposed in at least one of the passages between the first throttle portion and the first passage and between the first throttle portion and the second passage. A porous permeable material, a valve seat having an opening provided on the first throttle portion side between the first throttle portion and the second flow path, and operating in the flow direction of the fluid flowing in the housing. An operating valve, a stopper provided between the operating valve and the second passage, and a second throttle portion provided in the operating valve or the valve seat, and the first passage to the second passage. When the fluid flows in the direction, the operating valve stops at the stopper, the fluid flows through the first throttle portion and the opening, and the second flow path When the fluid flows from the first flow passage to the first flow passage, the operating valve stops at the valve seat to close the opening, and the fluid flows through the second throttle portion and the first throttle portion, thereby reducing the throttle amount in the fluid flow direction. A diaphragm device having different configurations. 7. A casing having one end connected to the first flow passage and the other end connected to the second flow passage and disposed in the flow passage, and a first throttle unit for decompressing and passing the fluid flowing in the casing. A valve body having, and a porous permeable material for passing the fluid, which is disposed between at least one of the first throttle portion and the first flow passage and between the first throttle portion and the second flow passage, An operating valve that operates in the flow direction of the fluid flowing in the housing, a partition plate having a flow passage provided between the operating valve and a second flow passage, and a second throttle portion provided in the operating valve or the valve body. When the fluid flows from the first flow path to the second flow path, the operating valve stops at the partition plate and the fluid flows through the flow paths of the first throttle section and the partition plate, When the fluid flows from the second flow path to the first flow path, the operation valve stops at the valve body and
A throttling device, wherein the throttling portion is closed and the fluid flows through the second throttling portion so that the throttling amount is different depending on the flow direction of the fluid. 8. A communication channel that connects the first channel and the second channel, and a throttle channel that is formed by connecting the throttle device according to claim 6 or 7 in parallel to the communication channel, A switching passage for switching between the communication passage and the throttle passage, and when a fluid flows from the first passage of the throttle passage to the second passage, the pressure is reduced in the first throttle portion of the throttle device, When the fluid flows from the second flow passage of the throttle flow passage to the first flow passage, the pressure is reduced by the second throttle portion or the second throttle portion and the first throttle portion of the throttle device, and the throttle passage The flow rate control device is characterized in that the throttle amount is different depending on the flow direction of the fluid. 9. A refrigeration cycle in which a compressor, an outdoor heat exchanger, a first flow rate control device, a first indoor heat exchanger, a second flow rate control device, and a second indoor heat exchanger are sequentially connected, and Alternatively, the flow control device according to claim 2, 4 or 5, or 8 is used as the second flow control device, and the first and second indoor heat exchangers are both operated as an evaporator or a condenser. At this time, the second flow rate control device connects the first and second indoor heat exchangers via a communication flow path, and one of the first and second indoor heat exchangers is an evaporator and the other is condensed. When operating as an air conditioner, the second flow rate control device is configured to switch the switching means so as to connect the first and second indoor heat exchangers through the throttle passage. . 10. The throttle amount of the second flow rate control device in the heating reheat dehumidification operation in which the first indoor heat exchanger is an evaporator and the second indoor heat exchanger is a condenser, The air conditioner according to claim 9, wherein the amount of throttle is larger than that in the cooling reheat dehumidifying operation in which the condenser is used and the second indoor heat exchanger is used as the evaporator.