JPH1151514A - Air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the flow noise of a refrigerant and the consumption of electric power and secure the necessary amount of dehumidification in performing dehumidifying operation while preventing the decrease of a room temperature by a refrigerating cycle. SOLUTION: A utilization side heat exchanger is divided into two, and a dehumidification restriction unit is used between them at the time of dehumidifying operation. In this unit, a refrigerant restriction passage 28 is formed by a cut groove 19 provided in a valve seat 20 and a valve stem 15 in the case where the valve stem 15 is brought into contact with the valve seat 20 to close a valve port 21, and valve chests 23, 24 communicate with each other by this refrigerant restriction passage 28. Even in the case where the refrigerant restriction passage 28 is blocked with dirt, etc., such dirt, etc., are removed by moving the valve stem 15 upward and, accordingly, the refrigerant restriction passage 28 can be made narrower. An evaporation temperature can be lowered by increasing the restriction extent of a refrigerant, and the necessary amount of the circulating refrigerant may be decreased while securing the necessary amount of dehumidification. Therefore, kinetic energy of a refrigerant flow can be reduced, and the flow noise of the refrigerant can also be reduced. Further, since the small amount of the circulating refrigerant is sufficient enough, the number of rotations of a compressor can be reduced, and the consumption of electric power can also be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner for performing cooling, heating and dehumidifying operations using a refrigeration cycle, and more particularly, to a refrigeration cycle provided with two indoor heat exchangers and dehumidifying between them. The present invention relates to an air conditioner having a configuration in which a throttling device is arranged and capable of performing a dehumidifying operation for performing dehumidification while preventing a decrease in room temperature.

[0002]

2. Description of the Related Art As an example of an air conditioner that performs a dehumidifying operation using a refrigeration cycle, a conventional example is disclosed in
JP-A-83776.

[0003] In this method, a compressor, an outdoor heat exchanger, a throttle device, an indoor heat exchanger, and the like are sequentially connected by a refrigerant pipe, and the indoor heat exchanger is thermally divided into two parts (ie, an indoor heat exchanger). Are provided, and a dehumidifying expansion device used during the dehumidifying operation is provided therebetween to constitute a refrigeration cycle. In such a configuration, during the dehumidifying operation, the refrigerant is passed through the dehumidifying expansion device so that the upstream side of the two-part indoor heat exchanger functions as a condenser, and the downstream side functions as an evaporator. By cooling and dehumidifying the air and heating the indoor air with the condenser, the dehumidifying operation for lowering the humidity without reducing the temperature of the air blown into the room from the air conditioner is enabled.

The dehumidifying squeezing device used here includes:
It has the structure of a two-way valve provided with a movable valve, and a small hole is provided in this valve movable part. During the dehumidifying operation, the valve movable portion operates to connect the refrigerant pipe from one indoor heat exchanger and the refrigerant pipe from the other indoor heat exchanger through the small holes, thereby performing the warming / cooling operation. At times, these refrigerant pipes are directly connected so that the valve movable portion does not act.

By the way, in the expansion device provided in the refrigeration cycle of the air conditioner, noise is generated due to the flow of the refrigerant, and various means have conventionally been proposed as means for reducing the flow temperature of the refrigerant. .

[0006] As one prior art example, Japanese Patent Application Laid-Open No. 57-129 shows
In the air conditioner described in Japanese Patent No. 371, in order to reduce the refrigerant flow noise generated in the expansion device provided between the outdoor heat exchanger and the indoor heat exchanger used in the cooling and heating operations, the expansion device is provided with a cooling device. A fixed orifice is provided upstream of a certain expansion valve,
The number of air bubbles in the refrigerant when passing through the expansion valve is increased, and the distribution is made uniform to reduce the noise level.

Another conventional example is disclosed in JP-A-7-24.
In the electromagnetic valve described in Japanese Patent No. 8162, a movable valve stem is provided with a flow hole passing through the center thereof. When the solenoid valve is used as a throttle, the valve stem is actuated to allow the valve stem itself to operate. While shutting off the two refrigerant pipes, and communicating between these refrigerants in a refrigerant leakage passage including the flow hole of the valve stem,
In the refrigerant leakage passage, the pressure of the refrigerant is reduced in a plurality of times, thereby reducing the refrigerant passage noise.

Further, Japanese Patent Laid-Open No. 8-9 as another conventional example
In the electric flow control valve described in Japanese Patent No. 3945, in addition to the main refrigerant throttle passage formed by the gap between the valve rod and the valve seat, a sub-refrigerant throttle communicating the high-pressure refrigerant passage and the low-pressure refrigerant passage of the throttle. A passage is provided in the valve rod, and gas-liquid separation is performed in the valve so that the liquid refrigerant passes through the main refrigerant throttle passage and the gas refrigerant passes through the sub-refrigerant throttle passage.

Further, Japanese Patent Laid-Open Publication No. Hei 5-288286 (particularly FIGS. 12 to 19) discloses an expansion valve in which a groove is provided at the tip of a valve stem.

[0010] This is because a groove is provided at the tip of the movable valve stem, and when the valve stem is disposed in the valve seat, a gap is formed between the valve stem and the valve seat by the groove. The coolant flows through this gap. As the shape of the groove, a groove having a constant depth in the axial direction of the valve stem or a tapered shape in which the depth of the groove gradually decreases in the axial direction of the valve stem is disclosed. By providing a plurality of such grooves in the valve stem, a plurality of refrigerant passages are ensured. As a result, even when a gas-liquid two-phase flow flows in, there is a passage between the gas refrigerant and the liquid refrigerant, so that the restriction by the bubble lump is restricted. This prevents clogging and reduces refrigerant flow noise.

Also, Japanese Utility Model Application Laid-Open No. 61-54164,
In particular, FIGS. 2 and 3 disclose an expansion valve having a valve seat provided with a groove. This expansion valve is provided with one parallel groove from the end of the valve seat to the central orifice in parallel with the axis of the inlet, and when the valve stem and valve seat come into contact and the valve closes, the orifice side is closed. The groove end becomes a small hole to form a diaphragm.

[0012]

Generally, one method for improving the dehumidifying performance is to increase the amount of throttling of the dehumidifying throttling device to lower the evaporation temperature.

Therefore, increasing the throttle amount of the dehumidifying expansion device means that in the dehumidifying expansion device having a two-way valve structure with a small hole described in Japanese Patent Application Laid-Open No. 2-183776, the diameter of the small hole is reduced. It is equivalent to doing. Also, Japanese Patent Application Laid-Open
In the solenoid valve described in -248162, this corresponds to reducing the cross-sectional area of the above-described refrigerant leakage passage or increasing the length thereof. Further, in the electric flow control valve described in JP-A-8-93945, the step area of each of the main refrigerant throttle passage formed by the gap between the valve rod and the valve seat and the sub-refrigerant throttle passage that bypasses the gas refrigerant is reduced. It is equivalent to

However, as described above, when the diameter of the small hole and the step area of the passage are reduced, dust or the like existing in the refrigerant circulating in the refrigeration cycle is liable to be clogged or adhered thereto. Therefore, if dust or the like is clogged or adhered to the small holes or the refrigerant throttle passage, it will not function as a throttle, and in the worst case, the refrigerant will not circulate and will not serve as an air conditioner.

Further, when the diameter of the small hole is small, there is a concern that the flow of the refrigerant passing through the small hole may generate a whistling sound or a fluctuating sound or increase the noise level due to an increase in the flow velocity.

In general, a large refrigerant flow noise as a continuous sound or a discontinuous sound is generated in the expansion device in accordance with the expansion operation, and the magnitude of the refrigerant flow noise, especially the discontinuous sound, is reduced by the expansion device. It is greatly affected by the flow mode of the high-pressure side refrigerant passage that flows in. Among them, intermittent refrigerant flow noise is generated when a slag flow or plug flow in which shell-shaped bubbles and liquid alternately appear in a two-phase flow state where gas and liquid are mixed, and it becomes extremely large It is known.

Here, the continuous flow noise is mainly caused by the liquid refrigerant being decompressed and expanded at the throttle portion of the throttle device to form a high-speed gas-liquid two-phase jet. The discontinuous flow noise is mainly caused by a difference in flow resistance when a gas refrigerant that is a compressible fluid and a liquid refrigerant that is an incompressible fluid alternately pass through a narrow flow path of a throttle device. Fluctuations in the flow rate and pressure are caused by the excitation force.

In the air conditioner described in JP-A-57-129371, a fixed orifice is disposed upstream of the throttle in order to solve the flow noise of the refrigerant.

However, the above-mentioned use-side heat exchanger (for example, in the case of a home air conditioner, an indoor heat exchanger) is provided with two heat exchangers.
In the case of the dehumidification cycle of the divided reheat dehumidification method, the dehumidification expansion device used only during the dehumidification operation is located in the middle of such a use side heat exchanger, so if fixed orifices are arranged before and after it, during cooling and heating operation This is merely a throttling device, and thus causes a pressure drop of the refrigerant, thereby lowering the performance during the cooling and heating operations. In particular, since the dehumidifying expansion device is disposed in the middle of the use side heat exchanger, the state of the refrigerant is a gas-liquid two-phase flow, and as a result, the pressure drop is larger than in the case of the single-phase flow.

In the expansion valve described in Japanese Patent Application Laid-Open No. Hei 5-288286, a plurality of grooves are formed in the valve stem to secure a plurality of refrigerant passages in order to solve the above-described noise of the refrigerant flow. . However, this expansion valve has the following problem.

One of the problems is the problem of dust clogging in the diaphragm. For example, when the above-mentioned valve stem is provided with a parallel groove having a constant depth, when the valve stem is inserted into the valve seat, the distance between the bottom of the groove and the wall surface of the valve seat is constant. Therefore, dust may be clogged between the groove and the wall surface of the valve seat. When this occurs, the valve stem locks and does not move.

Further, since the valve stem is attached to the stator which moves up and down by the feed screw, the valve stem moves up and down while rotating about its axis. Therefore, even if the groove is a parallel groove, even if the groove is clogged with dust, even if the groove is a tapered groove whose depth changes in the axial direction of the valve stem, when the valve stem is to be pulled out of the valve seat, Since the valve stem rotates in the valve seat with the dust trapped in the groove, the dust enters the gap between the valve stem and the valve seat, and the valve stem locks, and the valve stem does not move.

The second problem is valve stem vibration. That is, since the valve stem moves up and down while rotating about its axis by the feed screw, the groove provided in the valve stem rotates together with the valve stem, and the valve seat of the valve stem responds to the flowing refrigerant flow. The groove position, that is, the position of the refrigerant throttle passage, changes according to the insertion height (depth) into the groove. As a result, depending on the groove position,
An unbalanced fluid force acts on the valve stem, causing vibrations in the valve stem and generating refrigerant flow noise. For this reason, the refrigerant flow noise varies and the sound is not stable.

In the expansion valve described in Japanese Utility Model Laid-Open Publication No. 61-54164, a groove is provided in the valve seat, and when the valve stem comes into contact with the valve seat and the valve is closed, the groove end becomes a small hole. Although it has a structure, it has the following problems.

The first problem is the problem of dust clogging in this groove. For example, since the end of the groove on the orifice side is a throttle, dust and the like flowing along with the refrigerant in the refrigeration cycle always pass through the groove when passing through the expansion valve. Therefore, dust and the like that cannot pass through the groove serving as the throttle are deposited on the entire area of the groove. At this time, even if the refrigerant is circulated by separating the valve stem from the valve seat and opening the valve, the refrigerant flow collides with the valve seat because the upper end of the valve seat is located higher than the lower end of the inlet passage of the expansion valve. The main flow of the refrigerant flow thus formed becomes an upward flow, flows above the groove portion, and flows into the orifice. Therefore,
Since the debris accumulated in the entire groove portion is continuous to the entire groove portion, when the valve is lifted and the valve is opened, it is difficult to partially remove the dust in the tightened portion of the groove. Garbage will be more difficult to remove.

When an HFC-based refrigerant is used, contaminants and the like accumulate on the small diameter portion and the narrow portion as a kind of dust. In particular, in the case of an expansion valve or the like, it accumulates on the upper surface of the valve seat. At this time, contamination may accumulate in the groove provided in the expansion valve and fill the groove.

[0027] The second problem is the problem of refrigerant flow noise.
For example, when the valve stem comes into contact with the valve seat to close the valve and a throttle is formed, the refrigerant that has passed through the throttle due to the groove once collides with the valve cap, changes the flow direction, and flows out of the expansion valve. . Therefore, when the refrigerant flow collides with the valve stem and changes the flow direction, a large turbulence occurs in the flow, and the valve stem is vibrated. As a result, loud refrigerant flow noise is generated.

Further, in the above expansion valve, one groove is provided to form one throttle, and all the refrigerant flows pass through one throttle, so that the flow velocity of the refrigerant is greatly accelerated. As a result, the refrigerant flow noise increases. This is because the kinetic energy of the refrigerant jet greatly increases with an increase in the flow velocity. Furthermore, when a gas-liquid two-phase flow, in which the refrigerant flow noise is most remarkable, flows, a gas phase (gas refrigerant) and a liquid phase (liquid refrigerant) alternately flow into one throttle, so that the resistance of each throttle passage resistance decreases. Due to the difference, large flow fluctuations and pressure fluctuations occur,
Intermittent refrigerant flow noise will be generated. Furthermore, since there is only one groove, a unidirectional exciting force is applied to the valve stem by the refrigerant flow, and the valve stem vibrates to generate sound.

The third problem is the passage resistance when the valve stem separates from the valve seat. In the expansion valve, the diameter of the outlet refrigerant passage is smaller than the diameter of the inlet refrigerant passage. Further, in the dehumidification cycle of the reheat dehumidification method particularly targeted in the present invention described later, the dehumidification valve (expansion valve for dehumidification) used for the dehumidification operation serves as a throttle only during the dehumidification operation, and performs cooling, During the heating operation, it is required to be a valve with low pressure loss. That is, when the valve stem comes into contact with the valve seat and the valve is closed, a throttle is formed, and when the valve stem is separated from the valve seat and the valve is opened, the passage becomes a low pressure loss passage. Therefore, when this expansion valve is used, even when the valve stem is separated from the valve seat and the valve is opened, the diameter of the outlet-side refrigerant passage is always smaller than the diameter of the inlet-side refrigerant passage, so that the throttled state is not released. . As a result, when this expansion valve is used, the cooling performance and the heating performance of the air conditioner are reduced.

An object of the present invention is to solve such a problem, to reduce the refrigerant flow noise generated in the dehumidifying expansion device and to reduce the power consumption while securing the required dehumidifying amount during the dehumidifying operation. An object of the present invention is to provide an air conditioner that can be used.

[0031]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides a method of thermally dividing a use side heat exchanger into first and second use side heat exchangers. 1, a dehumidifying throttle device is provided between the second use-side heat exchanger, and the first use-side heat exchanger on the upstream side is used as a condenser during the dehumidification operation;
In an air conditioner in which a second use-side heat exchanger on the downstream side is an evaporator, the dehumidifying expansion device has a valve port that penetrates a high-pressure side refrigerant passage and an open port that penetrates a low-pressure side refrigerant passage. In the valve seat, a refrigerant passage connecting the valve port and the open port is formed, and a dehumidifying throttle valve is formed by a valve rod that opens and closes the refrigerant path and a valve movable part that moves the valve rod. When the dehumidifying throttle valve is in a state where the valve stem and the valve seat are in contact with each other to close the refrigerant passage, the dehumidifying throttle valve is surrounded by the valve stem and the valve seat, and the valve port and the open port are closed. When an independent throttle passage communicating with the valve is formed, and the refrigerant passage in which the valve stem and the valve seat do not contact each other is opened, the independent throttle passage is integrated with the refrigerant passage, The throttle passage is not formed.

Further, in the present invention, when the valve stem of the dehumidifying throttle valve contacts the valve seat to close the refrigerant passage, a plurality of the independent throttle passages are formed, In the case where the refrigerant passage is opened without contact between the refrigerant passage and the valve seat, the plurality of independent throttle passages are integrated with the refrigerant passage.

Further, the present invention provides the valve seat, wherein at least one cut groove is provided, and when the valve rod and the valve seat come into contact with each other to close the refrigerant passage, the cut groove and the valve are provided. The independent throttle passage is formed by the wall surface of the seat.

Further, the present invention provides the valve stem, wherein at least one cut groove is provided, and when the valve stem and the valve seat are in contact with each other to close the refrigerant passage, the cut groove and the valve seat are provided. And the above-mentioned independent throttle passage.

Further, according to the present invention, the shape of the cut groove is V
Groove (notch) shape.

Further, according to the present invention, the shape of the cut groove is a semi-cylindrical shape.

Further, according to the present invention, the shape of the cut groove is a rectangular groove shape.

Further, according to the present invention, the cut groove provided in the valve seat is arranged symmetrically with respect to the axis of the refrigerant passage on the high pressure side.

Further, in the present invention, the cut grooves provided in the valve stem are arranged axially symmetric with respect to the axis of the refrigerant passage on the high pressure side.

Further, in the present invention, the cut groove provided in the valve seat is arranged on the axis of the refrigerant passage on the high pressure side.

Further, in the present invention, the cut groove provided in the valve stem is arranged on the axis of the refrigerant passage on the high pressure side.

Further, the present invention has the structure of the dehumidifying throttle valve described above, and the cross-sectional area of the refrigerant passage connecting the valve port and the open port is larger than the cross-sectional area of the refrigerant passage on the low pressure side.

Further, the present invention has means for detecting the temperature or the evaporation temperature on the downstream side of the dehumidifying expansion device, or the temperature of the air blown out from the use side heat exchanger, and the amount of change of the temperature or the change with time. Is larger than a predetermined value, the dehumidifying expansion device is opened.

Further, in the present invention, the main throttle device provided between the heat source side heat exchanger and the use side heat exchanger has the same structure as the above-mentioned dehumidifying throttle device.

Further, the present invention provides an air conditioner in which the flow direction of a refrigerant in a refrigeration cycle can be switched, as a throttle device provided between a heat source side heat exchanger and the above use side heat exchanger. It has a structure of the above dehumidifying throttle valve, and has a structure in which the cross-sectional area of the refrigerant passage connecting the valve port and the open port is smaller than the cross-sectional area of the refrigerant passage on the high pressure side or the refrigerant passage on the low pressure side. It consists of a valve.

Further, the present invention relates to an air conditioner capable of performing either one of a warming operation and a cooling operation, wherein the dehumidifying device is provided between the heat source side heat exchanger and the use side heat exchanger. A valve having a structure of a throttle valve and having a structure in which a cross-sectional area of a refrigerant passage connecting a valve port and an opening is smaller than a cross-sectional area of the refrigerant passage on the high pressure side or the refrigerant passage on the low pressure side. Have been.

Further, according to the present invention, the refrigerant used is HFC
System refrigerant.

[0048]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the drawings as being installed on a building.

FIG. 3 is a configuration diagram showing a refrigeration cycle in a first embodiment of an air conditioner according to the present invention, wherein 1 is a compressor, 2 is a four-way valve, 3 is an outdoor heat exchanger, and 4 is a throttle. apparatus,
5a and 5b are indoor heat exchangers, 6 is a dehumidifying expansion device, 7 is an outdoor fan, 8 is an indoor fan, 9 is a main expansion device, and 10 is a two-way valve. , A four-way valve 2, an outdoor heat exchanger 3, an expansion device 4, and an indoor heat exchanger are sequentially connected by refrigerant piping to form a refrigeration cycle. In particular, the indoor heat exchanger is composed of two indoor heat exchangers 5a. , 5b, between which a dehumidifying squeezing device 6 which is a feature of this embodiment is provided. An outdoor fan 7 is provided in the outdoor heat exchanger 3, and an indoor fan 8 is provided commonly to the indoor heat exchangers 5a and 5b.

The four-way valve 2 is for switching the flow direction of the refrigerant in the refrigeration cycle between the cooling / dehumidifying operation and the heating operation, and the solid line arrow indicates the refrigerant flow direction during the cooling operation. Dashed-line arrows indicate the flow direction of the refrigerant during the heating operation, and dashed-dotted arrows indicate the flow direction of the refrigerant during the dehumidification operation.

The expansion device 4 allows the outdoor heat exchanger 3 to effectively absorb heat from the outside air during the heating operation, and uses the indoor heat exchangers 5a and 5b to remove heat from the indoor air during the cooling operation. In order to effectively absorb the heat, the refrigerant is depressurized, and the depressurization is prevented during the dehumidifying operation. For this reason, the expansion device 4 has a configuration in which the main expansion device 9 and the two-way valve 10 are arranged in parallel. During the warming and cooling operation, the two-way valve 10 is closed and the refrigerant flows into the main expansion device 9. And during the dehumidifying operation, the two-way valve 10 is opened so that the refrigerant is controlled to pass through the two-way valve 10.

The dehumidifying expansion device 6 is in an open state and serves as a low-pressure-loss refrigerant passage during warming and cooling operations, allowing the refrigerant to pass through as it is, and also functions as a throttle valve during the dehumidifying operation.

In this embodiment, during the heating operation, the outdoor heat exchanger 3 functions as an evaporator that absorbs heat from outdoor air, whereas the indoor heat exchangers 5a and 5b function as condensers that radiate heat indoors. During the cooling operation, the outdoor heat exchanger 3 serves as a condenser that radiates heat to the outside, whereas the indoor heat exchanger 5
The evaporators a and 5b absorb heat from room air.

During the dehumidifying operation, the outdoor heat exchanger 3
However, since the dehumidifying throttle device 6 acts as a throttle valve as in the cooling operation, the indoor heat exchanger 5a on the upstream side becomes a condenser radiating heat to the indoor air, and the indoor heat exchange on the downstream side. The vessel 5b becomes an evaporator that absorbs heat from room air. Here, when the indoor heat exchanger 5b absorbs heat,
The indoor air is cooled and dehumidified, but the heat is released in the indoor heat exchanger 5a to warm the indoor air so as to compensate for the cooling of the air, and the cooled air and the heated air are heated. Are mixed and blown out into the room, whereby dehumidification is performed without lowering the room temperature, and a comfortable dehumidification effect can be obtained.

FIGS. 1 and 2 are longitudinal sectional views showing a first specific example of the dehumidifying squeezing device 6 in FIG. 3, wherein 11 is an electromagnetic coil, 12 is an electromagnetic guide, 13 is a plunger, 14 is a cushioning material, 15 is a valve stem, 16 is a spring, 17 is a stopper, 1
8 is a valve body, 18a is a cylindrical portion, 19 is a cut groove, 20 is a valve seat, 21 is a valve port, 22 is an open port, 23 and 24 are valve chambers,
5 and 26 are refrigerant pipes, and 27 is a tapered surface.

In the same figure, the valve element 18 has two valve chambers 2.
3 and 24 are provided, and during the dehumidifying operation, the valve chamber 23 is provided.
Is on the high pressure side of the refrigerant, and the valve chamber 24 is on the low pressure side of the refrigerant. A refrigerant pipe 25 from the indoor heat exchanger 5a (FIG. 3) is connected to the valve chamber 23, and the indoor heat exchanger 5 is connected to the valve chamber 24.
b (FIG. 3) is connected to the refrigerant pipe 26. During the dehumidifying operation, the refrigerant pipe 25 serves as a refrigerant inlet pipe, the valve chamber 23 serves as a high pressure side, and the refrigerant pipe 26 serves as a refrigerant outlet pipe, so that the valve chamber 24 serves as a low pressure side. The valve rod 15 is provided in the valve chamber 23 so as to be movable in the vertical direction in the drawing.

The valve body 18 is provided integrally with a cylindrical portion 18a, and the electromagnetic guide 12 is provided at the upper portion of the inside thereof in the drawing.
Similarly, stoppers 17 are provided at lower portions, respectively, and a plunger 13 integrated with the valve rod 15 is disposed between the stoppers. The plunger 13 has a cylindrical shape, and the cylindrical portion is disposed between the protrusion of the electromagnetic guide 12 and the cylindrical portion 18a. A cushioning material 14 is provided at a portion of the electromagnetic guide 12 facing the tip of the plunger 13, and the portion of the electromagnetic guide 12 where the cushioning material 14 is provided serves as the other stopper for the plunger 13. The plunger 13 is urged upward, that is, in the direction of the electromagnetic guide 12 by a spring 16 fixed to a stopper 17. Furthermore, on the outer surface side of the cylindrical portion 18a,
An electromagnetic coil 11 is provided.

With this configuration, when the electromagnetic coil 11 is energized, an electromagnetic force is generated between the electromagnetic guide 12 and the plunger 12, and the plunger 13 is moved to a position where the electromagnetic force and the biasing force of the spring 16 are balanced. And the valve stem 15 moves up and down.

At the boundary between the valve chambers 23 and 24, a valve seat 20 protruding toward the valve chamber 23 is formed, and the valve chamber 24 defines the boundary between the valve seat 20 and the valve chamber 23 as a valve port 21. The connection with the refrigerant pipe 26 is an open port 22.

The tip of the valve stem 15 is connected to the valve port 21 of the valve seat 20.
It has a cylindrical shape with an outer diameter slightly larger than the diameter of
The tip surface forms a tapered surface 27 inclined outward. Needless to say, the distal end of the valve stem 15 may have a rod shape, but a similar tapered surface 27 is formed at the distal end. Due to the tapered surface 27, the leading end diameter of the valve stem 15 is slightly smaller than the inner diameter of the valve port 21 (that is, the diameter of the valve port 21).

Further, at the end of the valve seat 20 on the valve port 21 side, one or more cut grooves 19 are provided on the inner diameter side.

In this configuration, when the electromagnetic coil 11 is energized, the plunger 13 and therefore the valve rod 15 are pushed down against the urging force of the spring 16 due to the large electromagnetic force generated between the electromagnetic guide 12 and the plunger 13. The tip of the valve stem 15 comes into contact with the valve seat 20. At this time, as shown in the drawing, a part of this tip portion enters the valve port 21 by the tapered surface 27 at the tip portion of the valve rod 15, and the tapered surface 27 is pressed against the inner diameter corner of the valve seat 20. Will be.

As a result, the valve port 21 is closed, and the valve chamber 2 is closed.
3 and 24 are cut off, but a slight gap is formed between the cut groove 19 provided with the valve seat 20 and the tapered surface 27 at the tip of the valve rod 15, and this is caused by the refrigerant throttle passage 28.
The valve chamber 23 and the valve chamber 24 communicate with each other.

When the energization of the electromagnetic coil 11 is stopped, the above-mentioned electromagnetic force disappears, so that the valve stem 15 is lifted by the urging force of the spring 16, and as shown in FIG.
Moves away from the valve seat 20. As a result, the valve port 21 is opened, the refrigerant throttle passage 28 is eliminated, and the valve chambers 23 and 24 are
Communicate with

As described above, this specific example of the structure of the dehumidifying throttle valve has at least the diameter D 1 of the valve chamber 24 and the outlet pipe 26.
If the diameter D2 of the valve stem 15 is equal to or greater than
Only the loss due to the pressure drop due to the bending from the valve chamber 23 to the valve chamber 24 occurs, and a refrigerant passage with low pressure loss is formed. When the valve rod 15 is fully closed, the refrigerant throttle passage 28 Will be formed, resulting in the required pressure drop.

In this specific example, a tapered surface 27 is formed at the tip of the valve stem 15, and as shown in FIG.
When the valve 5 closes the valve port 21, the tapered surface 17 is in a state close to a line contact with the corner of the valve seat 20 on the side of the valve port 21. Since the valve rod 15 is fitted inside, the tip of the valve stem 15 is
As a result, the vibration of the valve stem 15 due to the fluid force is suppressed, and the generation of the refrigerant flow noise is reduced.

FIG. 4 is a plan view showing an example of the arrangement of the cut grooves 19 in the valve seat 20, viewed from the direction of the arrow X in FIG. However, 19a to 19d are cut grooves, and portions corresponding to FIGS. 1 and 2 are denoted by the same reference numerals.

FIG. 4A shows a cut groove 1 provided in the valve seat 20.
9, two cut grooves 19a and 19b are symmetrical to each other with respect to a straight line S passing through the center P of the valve seat 20 and parallel to the flow direction of the refrigerant indicated by the arrow in the refrigerant pipe 25 (FIG. 1). The case where it is provided at the position is shown.

FIG. 4B shows two cut grooves 19 similarly.
a and 19b are arranged at opposing positions on the straight line S.

FIG. 4C shows a cut groove 1 provided in the valve seat 20.
9 and four cut grooves 19a, 19b and 19c,
19d with respect to the straight line S.
In this case, the cut grooves 19a and 19d and the cut grooves 19b and 19c are further arranged at positions symmetrical with respect to a straight line S 'passing through the center P of the valve seat 20 at right angles to the straight line S. .

In addition to these, one or more arbitrary number of cut grooves can be provided, but these are arranged so as to be symmetrical with respect to the straight line S.

From the viewpoint of refrigerant flow noise, the number of cut grooves in the dehumidifying expansion device is preferably plural. This is because a plurality of cut grooves form a plurality of refrigerant throttle passages, and the refrigerant flow is distributed to these refrigerant throttle passages. Energy is reduced, and refrigerant flow noise generated from the dehumidifying expansion device is reduced.

Further, when a gas-liquid two-phase flow with the most pronounced refrigerant flow noise flows in, a plurality of refrigerant throttle passages are formed, and a gas phase (gas refrigerant) and a liquid phase (liquid refrigerant) enter the refrigerant throttle passage. ) Flows simultaneously, the respective refrigerant passages are secured, so that large flow rate fluctuations and pressure fluctuations due to differences in respective throttle passage resistances can be reduced. As a result, intermittent refrigerant flow noise Can be reduced.

When a plurality of cut grooves are provided, the valve rod is evenly applied with a vibrating force due to the refrigerant flow, and the vibration of the valve rod due to the fluid force is suppressed, so that the refrigerant flow noise can be reduced.

Next, the operation in the heating operation, the cooling operation, and the dehumidification operation of this specific example will be described.

During the warming and cooling operations, the electromagnetic coil 11 is not energized. Therefore, as shown in FIG. 2, the valve rod 15 is in a raised state, and the valve chambers 23 and 24 have a large area. Communicate with each other at the valve port 21. At this time, as described above, the outdoor heat exchanger 3 (FIG. 3) operates as an evaporator,
These indoor heat exchangers 5a and 5b (FIG. 3) operate as condensers. During the heating operation, the refrigerant flows from the indoor heat exchanger 5b to the refrigerant pipe 25 through the refrigerant pipe 26, the valve chamber 24, the valve port 21, and the valve chamber 23 in a direction opposite to the arrow, and to the indoor heat exchanger 5a. Sent. During the cooling operation, the refrigerant flows from the indoor heat exchanger 5a to the refrigerant pipe 26 through the refrigerant pipe 25, the valve chamber 23, the valve port 21, and the valve chamber 24 in the direction of the arrow, and is sent to the indoor heat exchanger 5b. Can be At this time, as described above, the outdoor heat exchanger 3 operates as a condenser, and the indoor heat exchangers 5a and 5b operate as evaporators.

During the dehumidifying operation, the valve rod 15 in the dehumidifying throttle valve is operated.
Contacts the valve seat 21 to close the valve port 21, and a region surrounded by the cut groove 19 provided in the valve seat 20 and the tapered surface 27 of the valve rod 15 is formed as a refrigerant throttle passage 28. The valve chambers 23 and 24 communicate with each other through the valve. At this time, the refrigerant flows from the refrigerant pipe 25 to the valve chamber 2 in the same arrow direction as in the cooling operation.
3. The refrigerant flows through the refrigerant throttle passage 28, the valve chamber 24, and the refrigerant pipe 26, and is reduced to an appropriate pressure by the refrigerant throttle passage 28. As a result, the valve chamber 23 is on the high pressure side, and the valve chamber 24 is on the low pressure side. At this time, as described above, the outdoor heat exchanger 3 is a condenser, the indoor heat exchanger 5a is a condenser (reheater), and the indoor heat exchanger 5
b operates as an evaporator (cooler).

Thus, in the indoor heat exchanger 5b,
Although the dehumidification is performed while cooling the indoor air, the indoor air is heated by the indoor heat exchanger 5a. Therefore, it is possible to perform the dehumidification operation of dehumidifying while preventing a decrease in room temperature.

The dehumidifying expansion device 6 shown in FIGS.
However, as shown in FIG. 5, there may be a case where it is installed inclined with respect to the direction of gravity. In such a case, the valve stem 1 is aligned with the axis L1 of the dehumidifying expansion device 6 inclined with respect to the direction of gravity.
The axis L2 of 5 is slightly inclined by the action of gravity on the valve stem 15. That is, the axis L1 of the dehumidifying expansion device 6 does not match the axis L2 of the valve stem 15. When the electromagnetic coil 11 is energized in such a state and the valve stem 15 is pushed down toward the valve seat 20, the valve stem 15 starts to come into contact with the valve seat 20, and a part of the valve port 21 of the valve seat 20. Will be in contact with.

However, since the tapered surface 27 is provided at the distal end of the valve stem 15 as described above,
The tapered surface 27 acts as a guide for the valve port 21 of the valve seat 20, the valve rod 15 is pushed by the electromagnetic force, and the tapered surface 27 is guided into the valve seat 20 along the valve port 27. As a result, as shown in FIG. 6, the posture of the valve stem 15 is corrected in a direction in which its axis L2 coincides with the axis L1 of the dehumidifying expansion device 6, and the valve seat 15 is attached to the valve seat 20 in a state where these axes L1 and L2 coincide. Will be imposed. Therefore, the tapered surface 27 of the valve rod 15 closes the valve port 21 of the valve seat 20 in a correct state, and the valve chambers 23 and 24 communicate with each other only through the refrigerant throttle passage 28 formed by the cut groove 19. In this way, this embodiment will correctly perform the valve operation even if installed in an inclined manner with respect to the direction of gravity.

Further, in the embodiment shown in FIG. 3, the rotation speed of the outdoor fan 7 is made variable, the condensing capacity in the outdoor heat exchanger 3 is changed, or the compressor 1
By changing the rotation speed of the compressor 1, the capacity of the compressor 1 is changed to change the condensing capacity in the indoor heat exchanger 5a, that is, the amount of heat radiation, so that the temperature of the air blown out by the indoor fan 8 is reduced from the cooling tendency. It is possible to control over a wide range up to heating.

Further, the indoor heat exchangers 5a and 5b are not only arranged side by side as viewed from the room, but also arranged back and forth as viewed from the room, and the indoor air is supplied from the indoor heat exchanger 5b by the indoor fan 8 to the indoor heat exchanger. 5a, or may be arranged one above the other as viewed from the room.
As a result, the indoor air is exchanged between the indoor heat exchanger 5a and the indoor heat exchanger 5
b.

In any case, in this embodiment, the refrigerant flow noise generated in the dehumidifying expansion device 6 is reduced while maintaining the characteristics of the dehumidifying operation and dehumidifying performance while preventing a decrease in room temperature. Can be.

Next, in this embodiment, a description will be given of a dehumidifying operation which does not lower the room temperature, and a method which makes it possible to ensure the required amount of dehumidification and to reduce the refrigerant flow noise.

To improve the dehumidifying performance, there is a method of lowering the temperature of the refrigerant in the indoor heat exchanger 5b used as the evaporator, that is, the evaporating temperature in the dehumidifying operation. In general, as a method of lowering the evaporation temperature, a method of increasing the rotation speed of the compressor 1, a method of increasing the throttle amount of the dehumidifying expansion device 6, and a method of increasing the rotation speed of the outdoor fan 7 to increase the air volume in the outdoor heat exchanger 3 To increase the heat radiation amount of the outdoor heat exchanger 3.

FIG. 7 shows the rotational speed of the compressor 1 and the indoor heat exchanger 5.
6B is a characteristic diagram showing a relationship with the evaporation temperature at b. A characteristic curve 30 shows a characteristic when a dehumidifying throttle amount of the dehumidifying diaphragm device has a certain value, and a characteristic curve 32 shows a dehumidifying diaphragm less than this value. This shows characteristics when the amount is large. In either case, the evaporating temperature decreases as the rotational speed of the compressor increases, but the evaporating temperature decreases as the dehumidifying throttle amount increases.

FIG. 8 shows the rotational speed of the compressor 1 and the indoor heat exchanger 5.
6B is a characteristic diagram showing a relationship between b and the amount of dehumidification, and a characteristic curve 3
Numeral 5 indicates the characteristic when the dehumidifying diaphragm amount of the dehumidifying diaphragm device has a certain value, and the characteristic curve 37 indicates the characteristic when the dehumidifying diaphragm amount is larger than this value. In either case, the rotational speed of the compressor is increased, and the amount of dehumidification increases. The larger the amount of dehumidification throttle, the greater the amount of dehumidification.

FIG. 9 is a characteristic diagram showing the relationship between the number of revolutions of the compressor 1 and the flow rate of the refrigerant flowing in the refrigeration cycle per unit time. The characteristic 40 shows the characteristic as the number of revolutions of the compressor increases. This shows that the refrigerant flow rate also increases.

FIG. 10 is a characteristic diagram showing the relationship between the refrigerant flow rate per unit time and the kinetic energy of the refrigerant.
This characteristic 43 indicates that the kinetic energy increases as the refrigerant flow rate increases.

FIG. 11 is a characteristic diagram showing the relationship between the kinetic energy of the refrigerant and the flow noise of the refrigerant.
This shows that as the kinetic energy increases, the refrigerant flow noise also increases.

As can be seen from FIGS. 7 to 11 described above, when the rotation speed of the compressor is increased to lower the evaporation temperature and enhance the dehumidifying performance, the refrigerant flow rate increases, the kinetic energy increases, and the refrigerant flow noise increases. Becomes larger.

When the number of revolutions of the outdoor fan 7 is increased to increase the air flow in the outdoor heat exchanger 3 in order to lower the evaporation temperature and enhance the dehumidifying performance, the temperature of the refrigerant is reduced. In 5a, the heating amount for heating the indoor air decreases, and the temperature of the air blown into the room by the indoor fan 8 tends to decrease. When the dehumidifying operation is performed, the room temperature decreases.

On the other hand, in this embodiment, in order to lower the evaporation temperature and improve the dehumidifying performance, the amount of the dehumidifying diaphragm of the dehumidifying diaphragm device 6 is increased.
This will be described with reference to FIG.

In FIG. 7, if the dehumidifying throttle amount of the dehumidifying diaphragm device 6 is increased from the state of the characteristic 30 to the state of the characteristic 32, the evaporation speed is not increased for the same rotation speed N1 of the compressor 1. The temperature drops from B1 at point 31 on characteristic 30 to B2 at point 33 on characteristic 32. Further, assuming that the same evaporation temperature B1 is maintained, the point moves from the point 31 of the characteristic 30 to the point 34 of the characteristic 32, and the rotation speed of the compressor 1 is changed from N1 to N.
It can be reduced to 2.

In FIG. 8, when the amount of the dehumidifying diaphragm of the dehumidifying diaphragm device 6 is increased from the state of the characteristic 35 to the state of the characteristic 37, the indoor heat exchanger for the same rotation speed N1 of the compressor 1 is obtained. The dehumidification amount of 5b increases from H1 at the point 36 of the characteristic 35 to H2 at the point 38 of the characteristic 37. Further, assuming that the same dehumidification amount H1 is maintained, the point moves from the point 36 of the characteristic 35 to the point 39 of the characteristic 37, and the rotation speed of the compressor 1 can be reduced from N1 to N2.

On the other hand, if the indoor environment is determined, the required amount of dehumidification to be secured at that time is determined. Therefore, in FIG.
As described above, assuming that the dehumidifying amount to be secured at that time is H1, by increasing the dehumidifying throttle amount of the dehumidifying throttle device 6, the rotation speed of the compressor 1 is N2 smaller than N1.
It can be.

As described above, when the number of rotations of the compressor is reduced, the flow rate of the refrigerant is reduced as shown in FIG. 9, and the number of rotations of the compressor is reduced from N1 to N2.
G1 at point 41 on characteristic 40 decreases to G2 at point 42. Therefore, in FIG. 10, the kinetic energy decreases from E1 at point 44 to E2 smaller than this on the characteristic 43, and eventually, as shown in FIG. From P1 to P2, which is smaller than P1.

In this way, by increasing the amount of dehumidifying throttle of the dehumidifying throttle device, it is possible to reduce the refrigerant flow noise generated from the dehumidifying throttle device and the indoor heat exchanger.

FIG. 12 is a characteristic diagram showing the relationship between the rotation speed of the compressor 1 and the power consumption of the air conditioner. The characteristic 49 indicates that the power consumption increases as the rotation speed of the compressor 1 increases. It shows that it increases.

As shown in FIG. 12, the amount of electric power required for the operation of the air conditioner decreases as the rotational speed of the compressor decreases. Therefore, as described above, the rotational speed of the compressor 1 can be reduced from N1 to N2 by increasing the dehumidifying throttle amount of the dehumidifying throttle device 6, so that the power consumption is a characteristic. The point on 49 shifts from point 50 to point 51, and the power consumption decreases from W1 to W2.

As described above, by increasing the throttle amount of the dehumidifying expansion device 6, not only the dehumidifying capacity can be increased, but also the refrigerant flow noise and the power consumption can be reduced.

However, increasing the throttle amount of the dehumidifying throttle device decreases the sectional area of the refrigerant throttle passage. This causes the following problem in the conventional dehumidifying expansion device. This will be described with reference to FIG. However,
50a and 50b are small holes, 51a and 51b are floating substances, and portions corresponding to FIG. 1 are denoted by the same reference numerals.

In FIG. 13A, in the dehumidifying throttle valve of the conventional dehumidifying throttle device, small holes 50a,
0b is provided, and as shown in FIG.
When the valve port 21 is closed by contact with the small holes 50,
The refrigerant flow passages a and 50b communicate with the valve chambers 23 and 24. Therefore, the refrigerant flows from the valve chamber 23 to the small hole 50.
a, when it is sent to the valve chamber 24 through 50b, the pressure is reduced.

When the dehumidifying expansion device is used as the dehumidifying expansion device 6 in FIG. 3 and the dehumidifying operation is performed in the state shown in FIG. 13 (a), the indoor heat exchanger 5
In order to lower the evaporation temperature of b and increase the dehumidifying capacity, small holes 5
When the diameters of the small holes 50a and 50b are reduced, the floating substances 51a and 51b flowing while mixing with the refrigerant are reduced.
b and small holes 50a, 50
b will be clogged. Here, the suspended matter 51a, 51b
Are refuse and contaminants in the refrigeration cycle. As this state progresses, all the small holes 50a, 50b
When the air is blocked by the floating substances 51a and 51b, the dehumidifying operation cannot be performed.

In this state, after that, FIG.
As shown in (b), the valve stem 15 is lifted and the valve port 2 is lifted.
Even if 1 is fully opened, the suspended matter 54a, 54b that has clogged the small holes 50a, 50b cannot be removed. Accordingly, the dehumidifying throttle valve in which the small holes 50a and 50b are clogged does not function as a throttle and closes the refrigeration cycle, so that the dehumidifying operation cannot be performed.

On the other hand, the dehumidifying expansion device 6 according to the present embodiment shown in FIGS. 1 and 2 can also solve such a problem. This will be described with reference to FIG. However, parts corresponding to those in FIGS. 1 and 2 are denoted by the same reference numerals.

In FIG. 14A, during the dehumidifying operation,
The valve stem 15 contacts the valve seat 20, the valve port 21 is closed, and the valve chamber 2 is closed by the refrigerant throttle passage formed by the notch grooves 19a and 19b.
3, 24 are in communication. At this time, when these refrigerant throttle passages are narrowed to improve the dehumidifying efficiency,
As in the case of the above-described conventional dehumidifying expansion device, floating substances 51a and 51b are caught or accumulated in these refrigerant expansion passages.

However, as shown in FIG. 14 (b), when the valve stem 15 is lifted, these floating matters 51a, 51
1b is simply placed on the upper end surface of the valve seat 20, or the floating substances 51a, 51b are inserted into the cut grooves 19a, 19b.
Even if b enters, when the valve stem 15 is lifted,
It is in a state of being exposed at the valve port 21, and is therefore pushed away by the flow of the refrigerant and removed.

In this way, the floating substances 51a and 51b in the refrigerant throttle passage can be eliminated by lifting the valve rod 15, and therefore, the cut grooves 19a and 19b can be removed.
And the diameter of the refrigerant throttle passage can be reduced, and the dehumidifying ability can be increased.

In the dehumidifying expansion device 6 according to the present embodiment shown in FIGS. 1 and 2, since the cut grooves 19a and 19b are provided at the end of the valve seat 20 on the valve port 21 side, the cut-out grooves 19a and 19b are provided in the refrigerant throttle passage. Even if suspended matter enters, the valve stem 15 can be pulled up without locking the valve stem 15 to the valve seat 20, and clogging of the refrigerant throttle passage due to suspended matter can be easily removed.

Further, by providing the cut groove 19 in the valve seat 20, the position of the cut groove 19 with respect to the flow of the refrigerant can be fixed irrespective of the movement of the valve rod 15, whereby the refrigerant throttle The passage position can be formed at a predetermined position, and variation in generation of the refrigerant flow noise can be reduced. If the position of the refrigerant throttle passage with respect to the flow of the refrigerant is different, the refrigerant flow noise becomes loud or different, and the noise generated for each dehumidifying expansion device, and therefore for each air conditioner, differs. Become. In the conventional dehumidifying expansion device in which the small holes 50a and 50b are provided in the valve rod 15 as shown in FIG. 14, the small holes 50a and 50b with respect to the flow of the refrigerant depend on the contact state of the valve rod 15 with the valve seat 20. The positions are different, and the generated refrigerant flow noise is also different. On the other hand, in this embodiment, the refrigerant throttle passage can be arranged at a position where the refrigerant flow noise is minimized, so that the problem that the flow noise generated for each dehumidification throttle differs can be avoided.

As described above, by using the dehumidifying expansion device shown in FIGS. 1 and 2 as the dehumidifying expansion device 6 in FIG. 3, the refrigerant expansion passage is provided with a highly reliable expansion device which is free from clogging with floating substances. As a result, a dehumidifying squeezing device having a large amount of dehumidifying squeezing, that is, a small squeezing diameter, can be provided, and the number of rotations of the compressor 1 for securing a required dehumidifying amount can be reduced. Therefore, in this embodiment, the refrigerant flow noise can be significantly reduced, and the power consumption can also be reduced, so that a dehumidification operation for performing dehumidification while preventing a decrease in room temperature can be performed.

In this embodiment, the outdoor temperature 2
4 ° C, outdoor humidity 80%, indoor temperature 24 ° C, indoor humidity 60
%, When the actual dehumidifying operation is performed, the throttle amount of the dehumidifying expansion device 6 can be tripled as compared with the conventional one, and as a result, the compressor 1 for securing the required dehumidifying amount (510 ml / h). Rotation speed is reduced by half, and the power consumption is
The power was reduced from 50 W to about 280 W which is about half. Further, by reducing the flow rate of the refrigerant by half, the kinetic energy was also reduced by half, and the refrigerant flow noise was reduced by about 4 dB. Of course, even in this dehumidification operation, dehumidification is performed while preventing the temperature of the air blown into the room from dropping below room temperature, and the required amount of dehumidification is ensured, and the objective function of this embodiment is maintained. ing.

FIG. 15 is a longitudinal sectional view showing a main part of a second specific example of the dehumidifying squeezing device 6 in FIG. 3, and 15a is a side surface of the valve stem 15 and corresponds to FIGS. Are denoted by the same reference numerals, and redundant description is omitted.

In the figure, the tapered surface 27 as described above is not provided at the distal end of the valve stem 15, and the distal end surface forms a flat surface perpendicular to the side surface 15 a of the valve stem 15. . When the valve stem 15 is pressed against the valve seat 20 by the electromagnetic force of the electromagnetic coil, the flat distal end surface of the valve stem 15 comes into contact with the flat upper end surface of the valve seat 20, whereby the valve port 21 of the valve seat 20 is opened. Closes. At this time, the cut groove 19 formed at the upper end of the valve seat 20 has a part on the valve chamber 23 side protruding partly outside the side surface 15 a of the valve stem 15. Even when the valve 15 closes the valve port 21 of the valve seat 20, the coolant throttle passage 28 is formed by the cut groove 19 to communicate the valve chambers 23 and 24.

In this way, the structure of the valve stem 15 can be simplified as compared with the specific examples shown in FIGS.
Valve operation can be performed. Also in this specific example, by lifting the valve rod 15, the suspended matter clogged in the cut groove 19 can be removed, and therefore, the refrigerant throttle passage 28 can be narrowed.

FIG. 16 (a) is a longitudinal sectional view showing a main part of a third specific example of the dehumidifying expansion device 6 in FIG. 3, and FIG. 16 (b) is a view showing the valve port 21 in FIG. 15 is an enlarged longitudinal sectional view, in which 20a is a counterbore portion, 20b is a counterbore side surface, and portions corresponding to FIG.

15A and 15B, this specific example is different from the second specific example shown in FIG. 15 in that a counterbore portion 20a is provided on the upper end surface of the valve seat 20, and this counterbore portion is provided. The flat end face of the valve stem 15 abuts on 20a.

By providing such a counterbore portion 20a, the valve stem 15 can be roughly positioned, and the lateral displacement of the valve stem 15 in the drawing can be reduced.

When the valve stem 15 is fitted into the counterbore 20a and the side surface 20b of the counterbore 20a is parallel to the side surface 15a of the distal end of the valve stem 15, the end of the valve stem 15 is If the outer diameter is not much different from the inner diameter of the counterbore portion 20a, the outer peripheral portion of the distal end portion of the valve rod 15 enters most of the cut groove 19 and blocks most of the refrigerant throttle passage 28. 15 becomes a throttle of the refrigerant throttle passage 28, and the side face 20b of the counterbore 20a and the valve stem 15
There is also a possibility that the floating material may be clogged between the valve stem 15 and the side surface 15a and the valve stem 15 may be locked by the valve seat 20 so that the valve stem 15 cannot be pulled out. In order to prevent this, the side face 2 of the counterbore 20a
The inside diameter of the counterbore 20a is made sufficiently larger than the diameter of the distal end of the valve stem 15 so that there is a sufficient distance L between 0b and the side surface 15a of the valve stem 15. Of course, in this case, if the diameter of the counterbore portion 20a is too large, when the valve stem 15 is displaced to one side largely in the counterbore portion 20a,
A large gap is formed in a portion of the counterbore portion 20a where the cut groove 19 is not provided, whereby the valve chambers 23 and 24 communicate with each other. For this reason, the inner diameter of the spot facing portion 20a also has an upper limit.

As described above, in the specific example shown in FIG. 16, the cut groove 19 extends from the inside of the counterbore portion 20a of the valve seat 20 to the inner surface of the valve seat 20.

On the other hand, the dehumidifying expansion device 6 shown in FIG.
The fourth specific example is that the side surface 20c of the counterbore portion 20a is tapered so that the counterbore surface becomes wider from the counterbore portion 20a to the upper end surface of the valve seat 20 as going toward the upper end surface of the valve seat 20. Thus, the counterbore portion 20a has a shape that extends toward the upper end surface of the valve seat 20. That is, the side surface 15 of the tip of the valve stem 15
a and the gap between the side surface 20c of the counterbore 20a
Are formed so as to spread toward the upper end surface of the. The cut groove 19 extends from inside the counterbore 20 a of the valve seat 20 to the inner surface of the valve seat 20.

For this reason, even if the floating material is clogged between the side surface 20c and the side surface 15a of the valve stem 15, when the valve stem 15 is lifted from the counterbore 20a, the floating material rises as the valve stem 15 rises. It will be easier to remove. Therefore, the valve stem 15
Is not locked to the valve seat 20.

FIG. 18 is a longitudinal sectional view showing a main part of a fifth specific example of the dehumidifying squeezing device 6 in FIG. 3, and reference numeral 60 denotes a cut groove, and a portion corresponding to FIGS. The same reference numerals are given and duplicate explanations are omitted.

In the same figure, the tip of the valve stem 15 is
As in the first specific example shown in FIG. 1, a tapered surface is provided, and one or more cut grooves 60 are further provided on this tapered surface. That is, in this specific example, instead of providing the cut groove on the valve seat 20 side as in the first specific example shown in FIG. 1, a cut groove 60 is provided on the valve rod 15 side. When the valve stem 15 contacts the valve seat 20 as shown in FIG.
A part of the distal end of the valve stem 15 enters the inner diameter side of the valve seat 20, and the cut groove 60 and the valve seat 20 define the valve chamber 23,
24 is formed as a refrigerant throttle passage.

In this embodiment, as in the first embodiment, the distal end of the valve rod 15 is held by the valve seat 20, so that the vibration of the valve rod 15 due to the fluid force of the refrigerant is suppressed and the refrigerant flow is suppressed. The generation of noise can be reduced, and even if the dehumidifying expansion device 6 is installed inclined as a whole, the valve stem 15 is kept in a correct posture and the valve seat 20 is in place.
Further, even if the refrigerant throttle passage is clogged with suspended matter in the state shown in FIG. 18, it can be removed by lifting the valve rod 15.
This refrigerant throttle passage can be narrowed to increase the dehumidifying ability.

FIG. 19 is a longitudinal sectional view showing a main part of a sixth specific example of the dehumidifying squeezing device 6 in FIG. 3, in which 61 is a cut groove, 62 is a space, and corresponds to FIGS. The same reference numerals are given to the same parts, and the duplicate description will be omitted.

In the figure, the tip of the valve stem 15 is
As described in the above, a cylindrical shape is provided, and one or more notched grooves 61 reaching the space 62 in the cylindrical portion from the outer surface are provided at the tip of the cylindrical portion. This space 62 is open to the valve chamber 24. The cutout groove 61 is formed so as to be orthogonal to the central axis of the cylindrical portion. The other configuration is the same as the specific example shown in FIG.

As shown in the figure, when the valve stem 15 is in contact with the valve seat 20, the space 6
2 is integrated with the valve chamber 24, and the cut groove 61 forms the refrigerant throttle passage 28 that connects the valve chamber 23 and the space 62.

This specific example is also similar to FIG.
18 has the same configuration as the specific example shown in FIG.
The same effect as that of the specific example shown in FIG.

In this specific example, as described above, the valve stem 15 is controlled by the electromagnetic force and the urging force of the spring 16.
Is configured to move up and down, so that the valve stem 15
It moves up and down without rotating around its central axis.

However, now, in FIG.
Are provided with two cutting grooves 60 (each having a cutting groove 60a,
60b) and the valve stem 15 from the arrow YY direction in FIG.
As shown in FIG. 20 (a), even if it is arranged at a symmetrical position orthogonal to the flow direction of the refrigerant indicated by the arrow, or three cut grooves 60 are formed in the valve stem 15. (Respective cut grooves 60a, 60b, and 60c), and as shown in FIG. 20B, even when the refrigerant is disposed at a position symmetrical with respect to the flow direction of the refrigerant indicated by the arrow. The valve stem 15
In some cases, the movement of the robot involves rotation. In such a case, the cut groove 60 provided in the valve stem 15 is also attached to the valve stem 1.
There is a possibility that it will rotate with 5. For example, FIG.
In the case of the arrangement of the cut grooves 60 shown in FIG. 0 (a) and FIG. 20 (b), the cut grooves 60a and 60b and the cut grooves 60a and 60b,
There is a possibility that the position of 60c is rotated by about 45 ° at the maximum. When such rotation occurs, the position of the refrigerant throttle passage changes, and the refrigerant flow in the dehumidifying expansion device 6 changes, causing variation in the refrigerant flow noise.

The same applies to the specific example shown in FIG.

FIG. 21 is a longitudinal sectional view showing a seventh specific example of the dehumidifying expansion device 6 in FIG. 3 in which the rotation of the valve rod 15 can be prevented. 63 is a guide groove, and 64 is a guide. 18 are given the same reference numerals, and redundant description will be omitted.

In the figure, a guide groove 63 is provided on the valve stem 15, a guide 64 is provided on the stopper 17 attached to the valve element 18, and a guide 3 is provided in these guide grooves 63.
4 is fitted. As a result, the valve stem 15 cannot rotate around its central axis. As a result, even when the cut groove 60 is provided in the valve stem 15, the valve stem 15
The position of the refrigerant throttle passage formed by the cut groove 60 when the abutment comes into contact with the valve seat 20 is always fixed, and the generated refrigerant flow noise is stabilized.

This is the same for the specific example shown in FIG.

In the specific example of the dehumidifying expansion device 6 described above, for example, as is apparent from FIG. 2, the valve rod 15 is disposed in the refrigerant flow. It is divided into two parts, and flows into the refrigerant throttle passage 28 from the cut groove 19 provided in the valve port 21. Therefore, FIG.
At 0 (a), by arranging the cut grooves 19a and 19b at positions symmetrical with respect to the straight line S, the fluid force applied to the valve stem 15 becomes uniform, and the vibration of the valve stem 15 is suppressed to reduce the refrigerant flow noise. can do.

In the specific examples shown in FIGS. 18, 19 and 21, the arrangement of the cut grooves 60, 61 provided in the valve stem 15 is the same as in the specific examples described in FIGS. Are arranged symmetrically with respect to the straight line S parallel to the flow direction of the flowing refrigerant. FIGS. 20A and 20B also show an example thereof.

Further, in addition to the specific example shown in FIG.
In the specific example shown in FIG. 21 provided with the guide groove 63 and the guide 64, the shape of the cut groove 61 may be a groove having a constant groove width and a square cross section as shown in FIG. Alternatively, as shown in FIG. 22B, the cross section in which the groove width becomes narrower toward the groove bottom may be a trapezoidal groove. In this case, floating substances (dust, contaminants, etc.)
Is easily removed by the flow of the coolant.
It should be noted that the shape of the cut groove is not limited to the above-described one, but may be any shape such as a V-shape (notch shape), a semi-cylindrical shape, or a rectangular shape as needed.

In the specific example shown in FIG. 15, by providing two or more guide mechanisms including the guide grooves 63 and the guides 64 shown in FIG. The displacement of the valve stem 15 in the radial direction of the valve stem 20 can be reduced.

FIG. 23 is a diagram showing a control system of the dehumidifying expansion device 6 in the embodiment shown in FIG. 3, in which 70 is a controller, 71 is a rotation speed detection control device of the compressor 1, 72
Numeral 73 denotes an outlet air temperature detecting device of the outdoor heat exchanger 3, 73 denotes an intake air temperature detecting device of the outdoor heat exchanger 3, 74 denotes a rotational speed detection control device of the outdoor fan 7, and 75 denotes indoor heat exchangers 5a and 5
b, 76a and 76b are suction air temperature and humidity detectors of the indoor heat exchangers 5a and 5b, respectively.
Denotes an evaporating temperature or a temperature detection device downstream of the dehumidifying expansion device 6. Numeral 78 denotes a rotation speed detection control device of the indoor fan 8, and portions corresponding to those in FIG. .

In this control system, the above-mentioned suspended matter removal control in the dehumidifying expansion device 6 is also performed. Since the clogging of the refrigerant throttle passage formed by the above-mentioned cut grooves with the floating substance is the same as the increase in the throttle amount,
As described above with reference to FIG. 7, the characteristic line is lowered and the evaporation temperature is lowered. Further, as the evaporation temperature decreases, the cooling capacity of the air conditioner also increases, and the temperature of the air blown out from the indoor heat exchanger also decreases. Further, the amount of dehumidification also increases.

Accordingly, in FIG.
b, the temperature of the refrigerant pipe downstream of the dehumidifying expansion device 6 (substantially equal to the temperature of the refrigerant), the temperature of the air blown from the indoor heat exchangers 5a and 5b, the temperature of the indoor heat exchangers 5a and 5b,
5b detects the temperature and humidity of the suction air and the temperature and humidity of the blown air,
With this value, it is possible to determine whether or not the refrigerant throttle passage is clogged by the floating substance.

Here, the controller 70 detects the number of rotations of the compressor 1 and controls the number of rotations in accordance with a control signal from the controller 70.
1, an outlet air temperature detector 72 for detecting the temperature of the air blown out of the outdoor heat exchanger 3, an intake air temperature detector 73 for detecting the temperature of the air sucked in the outdoor heat exchanger 3, and rotation of the outdoor fan 7. A rotation speed detection control device 74 for detecting the rotation speed and controlling the rotation speed in accordance with a control signal from the controller 70, and a blowing air temperature and humidity detecting for detecting the temperature and humidity of the blowing air of the indoor heat exchangers 5a and 5b. A device 75, a suction air temperature / humidity detecting device 76a for detecting the temperature and humidity of the suction air of the indoor heat exchanger 5a, and a suction air temperature / humidity detecting device 76b for detecting the temperature and humidity of the suction air of the indoor heat exchanger 5b And a temperature detecting device 7 for detecting an evaporation temperature in the indoor heat exchanger 5b or a temperature downstream of the dehumidifying expansion device 6.
7 and a rotation speed detection control device 78 for detecting the rotation speed of the indoor fan 8 and controlling the rotation speed by a control signal from the controller 70.

The controller 70 detects the rotation speed information detected by the rotation speed detection control device 71 and the rotation speed detection control devices 74 and 78, and the rotation speed detection device 72, the suction air temperature detection device 73, and the temperature detection device 77. Temperature information, outlet air temperature / humidity detector 75 and suction air temperature / humidity detector 76
a, the temperature and humidity information detected by the suction air temperature / humidity detecting device 76b is fetched, respectively, and stored and determined, and the compressor 1, the outdoor fan 7, the indoor fan 8
And the like, but the electromagnetic coil 11 in the dehumidifying expansion device 6 is controlled.
Is also controlled.

The rotation speed detection control device 71 of the compressor 1
The rotation speed detection control device 74 of the outdoor fan 7 and the rotation speed detection control device 74 of the indoor fan 8 may be incorporated in the controller 70. As a method for detecting the number of rotations, any method such as a method for measuring the number of rotations of a motor and a method for measuring a voltage value or a current value of the motor may be used. Further, as a method of controlling these rotation speeds, any method such as a method of varying the frequency, voltage value, and current value of the motor current may be used. Further, a thermistor or a thermocouple may be used as a method of detecting the air temperature, and a humidity sensor may be used as a method of detecting the air humidity.

FIG. 24 is a timing chart showing changes in the state of the air conditioner and operation control when a floating substance is clogged in the refrigerant throttle passage of the dehumidifying expansion device 6.

Here, the evaporation temperature in the indoor heat exchanger 5b (this can be replaced by the temperature information detected by the temperature detection device 77 in FIG. 23) is used as the information amount for determining the blockage of the refrigerant throttle passage. The operation of the compressor 1 and the opening and closing of the dehumidification throttle valve in the dehumidification expansion device 6 are used as the cycle operation control targets of the air conditioner.

The dehumidifying squeezing device 6 shown in FIGS.
23 and FIG. 24, the evaporating temperature shows a substantially constant value T0 before the refrigerant throttle passage 28 is clogged with the floating substance (period S to S1). If suspended matter accumulates in the refrigerant throttle passage 28 or becomes clogged, the amount of throttle increases, and the evaporation temperature decreases (time S1 to S1).
2 period ΔS0). At this time, the difference ΔT (evaporation temperature drop amount) between the appropriate evaporation temperature T0 and the reduced evaporation temperature T1, or the time change rate (= ΔT / ΔS0) of the evaporation temperature during the period ΔS0 between times S1 and S2 is detected. Thereby, the accumulation and clogging of the suspended matter can be determined.

If it is determined that the refrigerant throttle passage is clogged at time S2, the operation of the compressor 1 is stopped. At this time, since a refrigerant pressure difference exists between the high pressure side (for example, the valve chamber 23 side) and the low pressure side (for example, the valve chamber 24 side) of the dehumidifying throttle valve of the dehumidifying throttle device 6, the valve rod 10 From the valve seat 20 to open the throttle valve. The greater the pressure difference, the greater the spring force of the spring 16 needs to lift the valve stem 10 with the valve port 21 closed.

Therefore, in this embodiment, in order to eliminate the differential pressure before and after the dehumidifying throttle valve and open the valve rod 10, the operation of the compressor 1 is stopped (time S3) and a time ΔS1 later. At time S3, the dehumidifying throttle valve is opened. When the spring force of the spring 16 at the dehumidifying throttle valve is sufficiently large, the delay time ΔS1 may be shortened or may not be provided.

At time S3 after the dehumidifying throttle valve is opened at time S3.
The period ΔS2 up to 4 is a period for balancing the pressure of the entire refrigeration cycle, and is a period required for switching the four-way valve 2 and the like, and may be set as necessary. After the elapse of this period ΔS2, during the period ΔS3 of the next time S4 to S5, the compressor 1 is started to operate with the dehumidification throttle valve being open, and the suspended matter accumulated and clogged at the valve port 21 of the dehumidification throttle valve is removed. The fluid is collected by a strainer provided on the suction side of the compressor 1. Thereafter, the electromagnetic coil 11 is energized to bring the valve rod 10 into contact with the valve seat 20, close the dehumidifying throttle valve, and restart the dehumidifying operation.

FIG. 25 is a flowchart showing a specific example of the control operation of the controller in FIG. 23 during the dehumidifying operation of the first embodiment shown in FIG.

In this specific example, the change in the evaporation temperature is detected to detect the clogging of the refrigerant throttle passage in the dehumidification expansion device 6. The change in the evaporation temperature is caused by the eye of the refrigerant throttle passage. Not only clogging, but also when the user changes the set indoor temperature or indoor humidity, or when the indoor and outdoor air temperature (air load condition) changes rapidly. This is because the rotation speed of the compressor 1 and the rotation speeds of the indoor and outdoor fans 8 and 7 may change depending on the set temperature and humidity or the air load conditions.

Therefore, in this specific example, when a change in the evaporating temperature is detected in FIG. 25, first, whether the rotation speed of the compressor 1 has been changed (step 80), the rotation speed of the outdoor fan 7 is changed. (Step 8
1) It is determined whether or not the number of revolutions of the indoor fan 8 has been changed (step 82), and when any of them has changed, it is assumed that a change in the evaporation temperature has occurred. In general, under the condition of the dehumidifying operation, since the air load condition inside and outside the room rarely changes suddenly,
These pieces of information may be detected as needed.

When the evaporation temperature changes without changing any of these rotation speeds and the detected evaporation temperature sharply decreases, the amount of decrease in the evaporation temperature is detected and the predetermined specified amount is determined. judge whether it is more than α (Step 8
3) If the value is equal to or larger than the specified value α, it is considered that the dehumidifying expansion device 6 is clogged with dust, and the operation described with reference to FIG. 24 is performed.

That is, first, the compressor 1 is stopped (step 84). Otherwise, dehumidification operation is continued. At this time, the amount of decrease in the evaporating temperature is used because the evaporating temperature is generated by the operation of the air conditioner according to the combination of the air load condition and the air temperature and humidity set by the user. This is because it is difficult. Compressor 1
When the refrigerant is running and the refrigerant is flowing, the valve rod 15 is pressed against the valve seat 20 by the fluid force in the dehumidifying expansion device 6, so that a large force is required to open the valve rod 15. Therefore, after the compressor 1 is stopped, the pressure difference between before and after the dehumidifying throttle valve is small, and after waiting for the lapse of the period ΔS1, the valve rod 15 is lifted and the dehumidifying throttle valve is opened (step 85). Subsequently, a period ΔS2 during which the pressure in the refrigeration cycle is balanced.
Thereafter, the compressor 1 is operated again (Step 86) to circulate the refrigerant in the refrigeration cycle, and the dust adhering to the valve rod 15 of the dehumidifying throttle valve and the cut groove 19 of the valve port 21 is caused to flow. This refuse flows in the refrigeration cycle and is captured by a mesh in a strainer provided at the inlet of the compressor 1. After a period ΔS3 during which the refrigerant is sufficiently circulated, the valve rod 15 is moved by the dehumidifying throttle valve.
Is brought into contact with the valve seat 20 to close the valve port 21 (step 8).
7) Restart the dehumidifying operation.

FIG. 26 is a flowchart showing another specific example of the control operation of the controller 70 in FIG. 23 during the dehumidifying operation of the first embodiment shown in FIG.

In this specific example, a gradient of the evaporation temperature, that is, a time change rate of the evaporation temperature is used in place of the amount of the decrease in the evaporation temperature in order to determine the clogging of the dehumidifying expansion device 6 with the suspended matter. It is. 26, this determination is made in step 88, and the other control processes are the same as those in FIG.

In step 88, the detected evaporating temperature sharply drops, and its time change rate is detected and compared with a predetermined amount β, and this time change rate is equal to or more than the specified value β. At this time, it is determined that the dehumidifying squeezing device 6 is clogged, and the flow proceeds to the control operation from step 84 on.

FIG. 27 is a flowchart showing still another specific example of the control operation of the controller 70 in FIG. 23 during the dehumidifying operation of the first embodiment shown in FIG.

In this specific example, the amount of drop in the temperature of the air blown out of the indoor heat exchanger is used in place of the amount of decrease in the evaporating temperature, in order to determine the clogging of the dehumidifying expansion device 6 with suspended matter. 27, this determination is made in step 90, and the other control processing is the same as in FIG.

However, in this case, the temperature of the intake air of the indoor heat exchanger is detected, and when the temperature is maintained substantially constant without change (step 89), the detected blowout of the indoor heat exchanger is performed. When the temperature of the air suddenly drops and the detected amount of drop is equal to or larger than the predetermined amount γ (step 90), it is determined that the dehumidifying expansion device 6 is clogged with dust, and the process proceeds to step 84 and subsequent control processes. .

FIG. 28 is a flowchart showing still another specific example of the control operation of the controller 70 in FIG. 23 during the dehumidifying operation of the first embodiment shown in FIG.

In this specific example, the temperature of the air blown out of the indoor heat exchanger is replaced with the temperature of the air blown out of the indoor heat exchanger in order to determine the clogging of the dehumidifying expansion device 6 due to the suspended matter. This is the case where the gradient, that is, the time change rate of the indoor blown air temperature is used. In FIG. 28, this determination is made in step 91, and the other control processing is the same as in FIG.

In this case as well, the temperature of the intake air of the indoor heat exchanger is detected, and when it is substantially constant and does not change (step 89), the detected temperature of the blown air of the indoor heat exchanger is reduced. If the rate of change over time falls abruptly and the rate of change over time is equal to or greater than a predetermined amount δ (step 91), it is determined that the dehumidifying expansion device 6 is clogged with dust, and step 8
The process proceeds to the control operation from Step 4.

[0167] In the case of suspended matter that is gradually deposited over time, such as contaminants, it is preferable to combine both the amount of fall and the rate of change with time.

Further, in addition to the evaporation temperature and the temperature of the air blown out of the indoor heat exchanger, the temperature and humidity of the suction air and the blown air of the indoor heat exchanger are detected, and the rising amount or the gradient (depending on time) of the dehumidification amount is detected. The same control can be performed by using (ratio).

FIG. 29 is a block diagram showing a refrigeration cycle of an air conditioner according to a second embodiment of the present invention.
Denotes an expansion valve, parts corresponding to those in FIG. 3 are denoted by the same reference numerals, and redundant description is omitted.

As shown in FIG. 29, the second embodiment has a refrigeration cycle having the same configuration as that of the first embodiment shown in FIG. 3, but the cooling and heating operation shown in FIG. Instead of the expansion device 4 for time use, it is used as an expansion valve 100 provided with an expansion valve having the same configuration as the dehumidification expansion device 6 shown in FIGS. 1, 2, 18, 19, and 21. .

The expansion valve 100 has a throttling function during the cooling and heating operations, and has almost no pressure loss during the dehumidifying operation. The configuration is simpler than that of the expansion device 4 shown in FIG. 3 and the number of parts can be reduced, and the function of the refrigeration cycle is the same as that shown in FIG.

FIG. 30 is a configuration diagram showing a refrigeration cycle in an air conditioner according to a third embodiment of the present invention, where 5 is an indoor heat exchanger, 101 is an expansion valve, and a portion corresponding to FIG. Are denoted by the same reference numerals, and redundant description is omitted.

In this embodiment, as shown in FIG. 30, the compressor 1, the four-way valve 2 for switching the flow direction of the refrigerant between the heating operation and the cooling operation, the outdoor heat exchanger 3, and the indoor heat exchanger 5 It is connected by piping, and the outdoor fan 7 is connected to the outdoor heat exchanger 3.
However, each of the indoor fans 8 is provided in the indoor heat exchanger 5,
Although the conventional refrigeration cycle has the same configuration, an expansion valve 101 that can switch the throttle amount of the refrigerant in a plurality of stages as a pressure reducer provided between the outdoor heat exchanger 3 and the indoor heat exchanger 5. Is used.

FIGS. 31 and 32 are longitudinal sectional views showing a specific example of the expansion valve 101 in FIG. 30. Reference numeral 24 'denotes a valve chamber, and portions corresponding to those in FIG. The description of the operation is omitted.

FIG. 31 shows a state where the expansion valve 101 is closed. In the same drawing, as in the dehumidifying expansion device 6 shown in FIG.
The valve seat 20 is provided with a cut groove 19 so that the valve stem 1
5 comes into contact with the valve seat 20, so that the valve chambers 23 and 24 ′
The valve chamber 2 is closed through a refrigerant throttle passage 28 formed by the cut groove 19 and the tapered surface at the tip of the valve rod 15.
3, 24 'communicate. Therefore, the refrigerant throttle amount in this case is determined by the refrigerant throttle passage 28.

Here, in the above specific example of the dehumidifying expansion device 6, for example, as shown in FIGS. 1 and 2, the diameter D1 of the valve chamber 24 which is on the low pressure side during the dehumidifying operation is connected to the diameter D1. Although the diameter D2 of the refrigerant pipe 26 is equal to the diameter D2 of the refrigerant pipe 26, in this specific example, the diameter D3 of the valve chamber 24 'is smaller than the diameter D2 of the refrigerant pipe 26 as shown in FIG. Therefore, the valve stem 15 is tapered so that its tapered surface can partially enter the valve chamber 24 ′ having the diameter D3, as compared with the valve stem 15 in the dehumidifying expansion device 6.

Then, the energization of the electromagnetic coil 11 is released and the valve rod 15 is raised, and as shown in FIG.
24 'communicates directly, but at this time, the diameter D of the valve chamber 24'
Since 3 is smaller than the diameter D2 of the refrigerant pipe 26, the refrigerant is throttled in the valve chamber 24 '.

As described above, in the expansion valve 101, even if the valve is closed or opened, the refrigerant is throttled. However, the diameter D3 of the valve chamber 24 'and the diameter of the refrigerant throttle passage 28 formed in the state of FIG. 31 (in this case, when a plurality of refrigerant throttle passages 28 are formed, the diameter with respect to the total cross-sectional area thereof) and Therefore, the throttle amount of the refrigerant differs when the valve is opened and when the valve is closed. Therefore,
The expansion valve 101 can switch the refrigerant throttle amount between two stages.

Therefore, in the embodiment shown in FIG. 30 using the expansion valve 101 having such a function, the operation range can be expanded as compared with an air conditioner having one fixed throttle such as a conventional capillary tube. Moreover, the expansion valve 101
As shown in FIGS. 31 and 32, since the basic configuration is the same as that of the dehumidifying expansion device 6, there is no dust clogging and the reliability is high, and the number of parts is small. I will do it.

In the expansion valve 101, in the state shown in FIG. 31, the refrigerant throttle passage 28 may be clogged with a floating substance, but the floating substance may be clogged in the same manner as in the control of the dehumidifying expansion device 6 described above. It is clear that can be removed.

Further, whether the cut groove in the expansion valve 101 is provided in the valve stem or the valve seat, and the shape and arrangement thereof are the same as in the case of the dehumidifying expansion device 6 described above.

FIG. 33 is a block diagram showing a refrigeration cycle of an air conditioner according to a fourth embodiment of the present invention.
The same reference numerals are given to the portions corresponding to and the duplicate description will be omitted.

In this embodiment, as shown in FIG. 33, except for the four-way valve, the flow of the refrigerant is made only in one direction, and either the cooling operation or the heating operation can be performed. The expansion valve 101 described with reference to FIGS. 31 and 32 can be used.

As described above, the embodiments of the present invention have been described, but the present invention is not limited only to such embodiments.

For example, in the above-described embodiment, the driving means for the valve rod 15 of the dehumidifying expansion device 6 and the expansion valve 101 is constituted by the electromagnetic coil 11, the electromagnetic guide 12, the spring 16, and the like. It may be used, or a mechanically driven one may be used, or may be applied to pressure control using a temperature-sensitive cylinder, and the driving means may be of various configurations. The same effect can be obtained.

[0186] So far, cooling, heating and dehumidifying have been performed.
Although the refrigeration cycle having two operation states has been described, the present invention is not limited to this and can be applied to other refrigeration cycles. For example, in the refrigeration cycle shown in FIGS. 3 and 29, the refrigeration cycle in which the four-way valve 2 is not provided and the dehumidification operation in the cooling cycle is possible, that is, the indoor heat exchanger 5b, the compressor 1, and the outdoor heat exchanger Even when 3 are connected in series, by applying the present invention, an air conditioner having a low refrigerant flow noise can be formed in the dehumidifying operation without lowering the room temperature and securing a necessary dehumidifying amount. be able to.

Further, in the refrigerating cycle shown in FIGS. 3 and 29, the refrigerating cycle in which the four-way valve 2 is not provided and the dehumidifying operation in the heating cycle is possible, that is, the outdoor heat exchanger 3, the compressor 1, and the indoor Even when the heat exchangers 5b are connected in series, by applying the present invention,
Similarly, in the dehumidifying operation, it is possible to configure an air conditioner having a smaller refrigerant flow noise without lowering the room temperature and securing a necessary dehumidifying amount.

In the refrigerating cycle shown in FIGS. 3 and 29, an accumulator may be provided on the suction side of the compressor 1 (between the indoor heat exchanger 5b and the compressor 1). Depending on the type, the type of the main throttle device, and the control method, a refrigeration cycle with an accumulator can be configured.

Further, the type of the refrigerant flowing in the refrigeration cycle is a single refrigerant such as HCFC22 generally used in an air conditioner, or an alternative refrigerant which replaces HCFC22 in terms of depletion of the ozone layer and global warming. A mixed refrigerant, which is one of the above, can be used.

For example, when an HFC-based refrigerant, which is one of the alternative refrigerants, is used, since it does not have a chlorine atom, it has a strong polarity. Therefore, the refrigerating machine oil used is also
A refrigerating machine oil having a polarity that dissolves in the HFC-based refrigerant is used. However, impurities such as contaminants remain in the refrigeration cycle during the manufacturing process of the air conditioner and installation on site. Many of the contaminants are non-polar substances. In addition, highly reactive impurities and additives contained in refrigerating machine oil react in a high-temperature portion or the like inside the compressor to form sludge, which is a nonpolar substance. These non-polar substances precipitate in the liquid refrigerant,
Deposits in the refrigeration cycle. This is particularly likely to accumulate in narrow refrigerant throttle passages such as throttles. Some refrigerants, such as some mixed refrigerants, have a higher working pressure than the pressure of a conventionally used refrigerant. At this time, since the pressure fluctuation also increases, the generation level of the refrigerant flow noise may increase.

In any of these cases, by applying the present invention, the clogging of the refrigerant throttle passage can be solved, and as a result, the required refrigerant flow rate can be reduced. Driving becomes possible.

Further, in the above-described embodiment, the description has been made on the assumption that the air conditioner is in a building. However, the present invention is not limited to this, and the present invention can be applied to a device for other uses requiring a dehumidifying operation. In such a case, generally, the heat exchanger is not always used indoors or outdoors, and in this case, the indoor heat exchangers 5, 5a, 5b in FIG. The outdoor heat exchanger 3 is a heat source side heat exchanger, the indoor fan 8 is a use side fan, and the outdoor fan 7 is a heat source side fan.

Further, the type of the compressor 1 may be a constant-speed rotating machine or a variable-speed rotating machine using an inverter. In any case, the same effect as described above is obtained. Is obtained.

As described above, according to the present invention, the indoor heat exchanger (use-side heat exchanger) is divided into two parts, and the dehumidification expansion device used during the dehumidification operation is provided therebetween. In a refrigeration cycle in which one is an evaporator and the other is a condenser, and the air is cooled, dehumidified and heated by a refrigeration cycle, the valve stem or the valve is contacted with the dehumidifying expansion device only when the valve stem and the valve seat come into contact with each other. With the structure in which the area surrounded by the cut groove provided in the seat and the valve rod or the valve seat is a refrigerant throttle passage, even if the throttle diameter is reduced in order to increase the amount of refrigerant throttle, the refrigerant throttle passage is formed. Clogging and the like can be prevented, and as a result, the refrigerant throttle amount can be increased, and the refrigerant flow rate required to secure the required dehumidification amount while preventing the room temperature from lowering can be reduced. Is also reduced , Because it requires a small number of revolutions of the compressor, it can be reduced power consumption required for the dehumidifying operation.

Further, in the present invention, since the heat pump air conditioner and the air conditioner for cooling only have a two-stage throttle expansion valve, the air conditioner having one fixed throttle device such as a capillary tube can be used. The operation range can be expanded, and the throttle valve is highly reliable without clogging of the throttle valve and the number of parts is small, so that an inexpensive air conditioner can be provided.

[0196]

As described above, according to the present invention,
An indoor heat exchanger (use-side heat exchanger) is divided into two parts, and a dehumidification expansion device used during dehumidification operation is provided between them. During the dehumidification operation, one of the use-side heat exchangers is used as an evaporator and the other is used as a refrigeration cycle. In a refrigeration cycle that performs cooling, dehumidification and heating of air by providing a cut groove in a refrigerant passage connecting a valve port and an open port to a dehumidifying expansion device,
When the valve is fully opened, it serves as a refrigerant passage for pressure loss, and when the valve is fully closed, the cut groove is partitioned by a valve rod to form an independent refrigerant throttle passage, so that the dehumidification throttle valve has an improved dehumidification performance. Therefore, even when the refrigerant throttle amount is increased, that is, even when the throttle diameter is reduced, it is possible to cancel the formation of the throttle by fully opening the valve and prevent the refrigerant throttle passage from being clogged. Become.

Further, according to the present invention, the refrigerant circulating amount required for securing the required dehumidification amount can be reduced by increasing the refrigerant throttle amount and lowering the evaporation temperature. Kinetic energy can be reduced, and refrigerant flow noise can be reduced.

Further, according to the present invention, since the amount of circulating refrigerant is small, the number of revolutions of the compressor can be reduced, and therefore, the power consumption required for operating the air conditioner can be reduced.

From the above, it can be seen that the present invention does not reduce the cooling / heating performance, reduces the flow noise of the refrigerant, and operates with less power consumption. Can be provided, and a comfortable dehumidifying operation can be performed.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a valve open state of a first specific example of a dehumidifying expansion device in a first embodiment of an air conditioner according to the present invention.

FIG. 2 is a longitudinal sectional view showing a closed state of the valve of the specific example shown in FIG. 1;

FIG. 3 is a configuration diagram showing a refrigeration cycle of a first embodiment of an air conditioner according to the present invention using the dehumidifying expansion device shown in FIGS. 1 and 2;

FIG. 4 is a plan view showing an example of the arrangement of cut grooves in FIG. 1;

FIG. 5 is a view showing a state in which the valve stem of the specific example shown in FIGS. 1 and 2 when installed at an angle starts to contact a valve seat;

FIG. 6 is a view showing a state in which a valve stem subsequent to the state shown in FIG. 5 is pressed against a valve seat.

FIG. 7 is a characteristic diagram showing a relationship between a rotation speed of a compressor and an evaporation temperature in the embodiment shown in FIG.

FIG. 8 is a characteristic diagram showing a relationship between the number of rotations of the compressor and the amount of dehumidification by the dehumidifying expansion device in the embodiment shown in FIG.

FIG. 9 is a characteristic diagram showing a relationship between a rotation speed of a compressor and a refrigerant flow rate in the embodiment shown in FIG.

FIG. 10 is a characteristic diagram showing a relationship between a refrigerant flow rate and a kinetic energy of the refrigerant flow in the embodiment shown in FIG.

FIG. 11 is a characteristic diagram showing a relationship between kinetic energy and refrigerant flow noise in the embodiment shown in FIG.

12 is a characteristic showing a relationship between the number of revolutions of the compressor and the amount of power consumption in the embodiment shown in FIG.

FIG. 13 is a diagram showing a state in which a floating substance is clogged in a refrigerant throttle passage in a conventional dehumidifying throttle device.

FIG. 14 is a diagram showing clogging of floating substances in a refrigerant throttle passage in the dehumidifying throttle device shown in FIGS. 1 and 2, and a method of removing the same.

FIG. 15 is a longitudinal sectional view showing a main part of a second specific example of the dehumidifying expansion device in FIG. 3;

FIG. 16 is a longitudinal sectional view showing a main part of a third specific example of the dehumidifying expansion device in FIG. 3;

FIG. 17 is a longitudinal sectional view showing a main part of a fourth specific example of the dehumidifying expansion device in FIG. 3;

FIG. 18 is a longitudinal sectional view showing a main part of a fifth specific example of the dehumidifying expansion device in FIG. 3;

FIG. 19 is a longitudinal sectional view showing a main part of a sixth specific example of the dehumidifying expansion device in FIG. 3;

FIG. 20 is a plan view showing an example of the arrangement of cut grooves in the specific example shown in FIG. 18;

FIG. 21 is a longitudinal sectional view showing a main part of a seventh specific example of the dehumidifying expansion device in FIG. 3;

FIG. 22 is a side view showing the cross-sectional shape of the cut groove in the specific example shown in FIGS. 19 and 21.

FIG. 23 is a configuration diagram showing a refrigeration cycle detection control system in the embodiment shown in FIG. 3;

FIG. 24 is a timing diagram showing operation control when a suspended matter clogging occurs in the dehumidifying expansion device in FIG. 23;

FIG. 25 is a flowchart showing a first specific example of a suspended matter removal operation of the dehumidifying expansion device by the controller in FIG. 23;

FIG. 26 is a flowchart showing a second specific example of the operation of the controller shown in FIG. 23 for removing a suspended matter clog in the dehumidifying expansion device.

FIG. 27 is a flowchart showing a third specific example of the suspended matter clogging removal operation of the dehumidifying expansion device by the controller in FIG. 23;

FIG. 28 is a flowchart showing a fourth specific example of the suspended matter clogging removal operation of the dehumidifying expansion device by the controller in FIG. 23;

FIG. 29 is a configuration diagram showing a refrigeration cycle in a second embodiment of the air conditioner according to the present invention.

FIG. 30 is a configuration diagram showing a refrigeration cycle in a third embodiment of the air conditioner according to the present invention.

FIG. 31 is a longitudinal sectional view showing a valve closed state of a specific example of the expansion valve in FIG. 30;

FIG. 32 is a longitudinal sectional view showing a valve open state of the specific example shown in FIG. 31;

FIG. 33 is a configuration diagram showing a refrigeration cycle in a fourth embodiment of the air conditioner according to the present invention.

[Explanation of symbols]

 Reference Signs List 1 compressor 2 four-way valve 3 outdoor heat exchanger (heat source side heat exchanger) 4 expansion device 5, 5a, 5b indoor heat exchanger (use side heat exchanger) 6 dehumidification expansion device 7 outdoor fan 8 indoor fan 9 main throttle Apparatus 10 Two-way valve 11 Electromagnetic coil 12 Electromagnetic guide 13 Plunger 14 Buffer material 15 Valve rod 16 Spring 17 Stopper 18 Valve element 19, 19a to 19d Cut groove 20 Valve seat 21 Valve port 22 Open port 23, 24, 24 'Valve Chamber 25, 26 Refrigerant pipe 27 Tapered surface 28 Refrigerant throttle passage 60, 61, 61a-61c Cut groove 62 Space in valve stem 63 Guide groove 64 Guide 70 Controller 71 Compressor rotation speed detection control device 72 Outdoor blown air temperature detection Device 73 Outdoor suction air temperature detection device 74 Outdoor fan rotation speed detection control device 75 Indoor air temperature and humidity detection device 76a, 76b Room Internal suction air temperature / humidity detection device 77 Evaporation temperature or dehumidification expansion device downstream temperature detection device 78 Indoor fan rotation speed detection control device 100, 101 Expansion valve

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hidenori Yokoyama 800, Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Pref.Hitachi Co., Ltd. Within Hitachi, Ltd.

Claims (17)

[Claims] 1. A use side heat exchanger forming a refrigerant cycle is thermally divided into two parts to form first and second use side heat exchangers between the first and second use side heat exchangers. A dehumidifying throttle device is provided at the time of the dehumidifying operation, and the dehumidifying throttle device evaporates the first use side heat exchanger on the upstream side and the second use side heat exchanger on the downstream side. An air conditioner provided with a refrigeration cycle each used as a heat exchanger, wherein the dehumidifying expansion device includes a valve port that penetrates a first refrigerant passage communicating with the first use side heat exchanger; An open port penetrating a second refrigerant passage communicating with the second use-side heat exchanger; a valve seat formed with a third refrigerant passage connecting the valve port and the open port; and the third refrigerant Having a dehumidifying throttle valve formed of a valve stem for opening and closing the passage and a valve movable part for moving the valve stem,
When the valve rod moves to form a valve that opens and closes the third refrigerant passage, and when the valve rod comes into contact with the valve seat to close the third refrigerant passage, the valve rod and the valve are closed. An independent throttle passage surrounded by the wall surface of the valve seat is formed, and when the valve rod and the valve seat are separated to open the third refrigerant passage, the independent throttle passage is connected to the third throttle passage.
An air conditioner characterized in that it is configured so as to be integral with the refrigerant passage of (1) and form a part of the third refrigerant passage. 2. The air conditioner according to claim 1, wherein a plurality of the independent throttle passages are formed. 3. The valve seat according to claim 1, wherein at least one notch groove is provided in the valve seat, and when the third refrigerant passage is closed, the notch groove and the wall surface of the valve stem are used to form the valve seat. An air conditioner characterized by forming an independent throttle passage. 4. The valve stem according to claim 1, wherein at least one cut groove is provided in the valve stem, and when the third refrigerant passage is closed, the cut groove and the wall surface of the valve seat form the groove. An air conditioner characterized by forming an independent throttle passage. 5. The air conditioner according to claim 3, wherein the cut groove has a V-groove (notch) shape. 6. The air conditioner according to claim 3, wherein the cut groove has a semi-cylindrical shape. 7. The air conditioner according to claim 3, wherein the cut groove has a rectangular groove shape. 8. The air according to claim 3, wherein the cut groove provided in the valve seat is arranged at a position symmetrical with respect to an axis of the first refrigerant passage. Harmony machine. 9. The air according to claim 4, wherein the cut groove provided in the valve stem is arranged at a position symmetric with respect to an axis of the first refrigerant passage. Harmony machine. 10. The air conditioner according to claim 3, wherein a cut groove provided in the valve seat is arranged on an axis of the first refrigerant passage. 11. The air conditioner according to claim 4, wherein a cut groove provided in the valve stem is arranged on an axis of the first refrigerant passage. 12. The air conditioner according to claim 1, wherein a step area of the third refrigerant passage is equal to or larger than a cross-sectional area of the second refrigerant passage. 13. The temperature detecting device according to claim 1, further comprising a temperature detecting unit configured to detect a temperature of the refrigerant in the second refrigerant passage, an evaporation temperature, or a temperature of the air discharged from the use-side heat exchanger. The air conditioner, wherein the dehumidifying expansion device opens the third refrigerant passage when a change amount or a time change of the temperature detected by the temperature detecting means becomes larger than a predetermined value. 14. The dehumidifying throttle device according to claim 1, wherein a main throttle device provided between a heat source side heat exchanger forming the refrigerant cycle and the use side heat exchanger is provided. An air conditioner having a valve structure using the same dehumidifying throttle valve. 15. A flow of a refrigerant provided between the compressor, the heat source side heat exchanger, the use side heat exchanger, and the compressor, the heat source side heat exchanger, and the use side heat exchanger. A refrigeration cycle is formed by a switching valve for switching the direction and a throttle device provided between the heat source side heat exchanger and the use side heat exchanger,
An air conditioner capable of performing a cooling operation and a heating operation by switching a flow direction of a refrigerant by the switching valve, wherein the expansion device is the dehumidifying expansion device according to any one of claims 1 to 13. A valve structure using the same dehumidifying throttle valve as the device is formed, and the cross-sectional area of the refrigerant passage connecting the valve port and the open port in the valve structure is equal to or less than the cross-sectional area of the refrigerant passage connected to the throttle passage. An air conditioner characterized by the following. 16. A refrigeration cycle includes a compressor, a heat source side heat exchanger, a use side heat exchanger, and a throttling device provided between the heat source side heat exchanger and the use side heat exchanger. Formed,
An air conditioner capable of performing either one of a cooling operation and a heating operation, wherein the expansion device is the same as the dehumidification expansion device according to any one of claims 1 to 13. And a cross-sectional area of a refrigerant passage connecting the valve port and the open port in the valve structure is equal to or smaller than a cross-sectional area of a refrigerant passage connected to the throttle passage. Air conditioner. 17. An air conditioner according to claim 1, wherein the refrigerant used is an HFC-based refrigerant.