JP2003042583A - Air conditioner and controller therefor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a re-heating capacity as well as a dehumidifying efficiency and reduce an electric power consumption in the heating and dehumidifying operation as well as the cooling and dehumidifying operation of an air conditioner. SOLUTION: A flow passage switching means 91 for switching the flow passage of a refrigerating cycle in an indoor heat exchanger 9A for an indoor unit is provided. Upon heating and dehumidifying operation or cooling and dehumidifying operation, fluid (refrigerant) is conducted to flow in the same direction as a first heat exchanger 9A1, to a second choking device 9A3, to a second heat exchanger 9A2. A valve body is seated on the valve seat by a pressure difference generated by the flow of the same direction in the second choking device 9A3. the dehumidifying operation is effected while retaining the seating condition of the valve body by the pressure difference under the non-exciting condition of a solenoid coil for the second choking device. In the other case, the seating/separating of the main valve seat is controlled without stopping the compressor, by a method wherein the second choking device 9A3 having the control valve is employed to retain the seating condition of the main valve body by the pressure difference generated by the flow of the same direction, and control the flow rate of the refrigerant passing through the control valve.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to an air conditioner control device and an air conditioner for controlling an air conditioner capable of performing a heating dehumidifying operation and a cooling dehumidifying operation.

[0002]

2. Description of the Related Art Conventionally, control of dehumidifying operation has been disclosed in JP-A-8-105672, JP-A-2000-81239, and JP-A-11-325636.

(Prior Art-1) Japanese Patent Laid-Open No. 8-105672
In the one disclosed in the publication, a dehumidifying expansion device is provided between a first heat exchanger and a second heat exchanger forming an indoor heat exchanger, and the dehumidification expansion device is opened during a cooling operation or a heating operation. ,
The first heat exchanger and the second heat exchanger are made to function as an indoor heat exchanger. On the other hand, during the dehumidifying operation, the upstream side (high pressure side) of the first heat exchanger and the second heat exchanger is connected to the condenser and the downstream side (low pressure side) is controlled by controlling the flow rate of the refrigerant with the dehumidifying expansion device. The dehumidifying operation is performed by functioning as an evaporator and offsetting the cooling action by the heating action.

(Prior Art-2) Japanese Patent Laid-Open No. 2000-8123
As disclosed in FIG. 4 and FIG. 5 of the publication, the No. 9 publication stops the compressor when switching between the weak heating operation and the dehumidifying operation. That is, weak heating operation (S5) →
Four-way valve heating side (S11) → compressor stop (S15) → dehumidification operation (S6), or dehumidification operation (S6) → four-way valve cooling side (S31) → compressor stop (S35) → weak heating operation (S5) The dehumidification is controlled by the process.

(Prior Art-3) Japanese Patent Laid-Open No. 11-32563
The one disclosed in Japanese Patent No. 6 has a heating dehumidifying operation and a cooling dehumidifying operation. In both dehumidifying operations, the flow direction of the refrigerant in the indoor heat exchanger is the same, and the reheating capacity and the dehumidifying efficiency are improved. Is.

[0006]

DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention
In JP-A-05672 (Prior Art-1), the flow rate during the dehumidifying operation is controlled by energizing the electromagnetic coil of the dehumidifying expansion device, and the electromagnetic coil is always energized except during the dehumidifying operation. As a result, the dehumidifying diaphragm device is opened so that it is necessary to energize the electromagnetic coil for a long time.

The above-mentioned Japanese Patent Application Laid-Open No. 2000-81239 (Prior Art-2) requires the start / stop of the compressor in order to control the switching between the "heating operation mode" and the "dehumidification (dry) operation mode". Repeats frequently. This accelerates mechanical wear of the compressor and shortens its life significantly, so it is not preferable from the viewpoint of global resources, it is economically expensive, and since the compressor is stopped, energy loss is large. There was a problem.

The above-mentioned Japanese Patent Application Laid-Open No. 11-325636 (Prior Art-3) does not describe the detailed structure of the electric expansion valve 23 for dehumidification in the indoor heat exchanger. It is important to reduce the energy loss in the dehumidifying operation in the heating mode.

The present invention has been made in view of the above circumstances, and it is an object of the present invention to provide an air conditioner control device and an air conditioner that reduce power consumption and are excellent in energy saving and resource saving.

[0010]

A control device for an air conditioner according to claim 1 of the present invention is provided at a connecting portion between an outdoor unit and an indoor unit and flows through an indoor heat exchanger in a cooling mode and a heating mode. An air conditioner provided with a flow path switching means for switching the flow paths so that the fluid flows in the same direction and a second expansion device provided in the indoor unit is controlled to configure the indoor unit during dehumidification operation. In the control device of the air conditioner, the flow path switching means is switched so that the fluid flows in the order of the first heat exchanger, the second expansion device, and the second heat exchanger of the indoor heat exchanger. The diaphragm device
An electromagnetic coil for seating the valve body on the valve seat by energization is provided, and the valve body is seated on the valve seat by a differential pressure generated by the fluid flowing in the same direction in the second throttle device. It is characterized in that the energization of the electromagnetic coil is cut off to maintain the valve closed state.

A control device for an air conditioner according to a second aspect of the present invention is provided in a connecting portion between an outdoor unit and an indoor unit, and the flow directions of fluids flowing through the indoor heat exchanger in the cooling mode and the heating mode are the same. Of an indoor heat exchanger that constitutes an indoor unit during dehumidification operation by controlling an air conditioner equipped with a flow path switching means for switching the flow path so that the direction becomes a direction and a second expansion device provided in the indoor unit. In a control device of an air conditioner for switching and controlling the flow path switching means so that a fluid flows in the order of a first heat exchanger, a second expansion device, and a second heat exchanger, the second expansion device is the fluid. Is provided with a main valve body seated on a valve seat by a differential pressure generated by flowing through the second throttle device in the same direction, and a control valve provided on the main valve body, and the differential pressure of the fluid causes Maintaining the valve closed state of the main valve To, and controlling the flow rate of fluid by controlling the control valve through the second throttle device.

An air conditioner according to a third aspect of the present invention is provided at the connecting portion between the outdoor unit and the indoor unit, and the flow directions of the fluids flowing through the indoor heat exchanger in the cooling mode and the heating mode are the same. The first heat exchanger and the second throttle device of the indoor heat exchanger that constitute the indoor unit during the dehumidifying operation are provided with the flow passage switching means for switching the flow passages as described above and the second throttle device provided in the indoor unit. , And an air conditioner that controls switching of the flow path switching means so that the fluid flows in the order of the second heat exchanger, the second expansion device includes an electromagnetic coil that seats the valve body on the valve seat by energization. The valve body is configured to be seated on the valve seat by a differential pressure generated by the fluid flowing in the same direction in the second expansion device, and the valve coil is kept closed by interrupting the energization of the electromagnetic coil. Special to do To.

An air conditioner according to a fourth aspect of the present invention is provided at the connecting portion between the outdoor unit and the indoor unit, and the flow directions of the fluids flowing through the indoor heat exchanger in the cooling mode and the heating mode are the same. The first heat exchanger and the second throttle device of the indoor heat exchanger that constitute the indoor unit during the dehumidifying operation are provided with the flow passage switching means for switching the flow passages as described above and the second throttle device provided in the indoor unit. , And a second heat exchanger, in the air conditioner for switching and controlling the flow path switching means so that the fluid flows, the second expansion device is generated by the fluid flowing in the same direction in the second expansion device. A main valve body that is seated on a valve seat by a pressure difference between the main valve body and a control valve provided on the main valve body, and maintains the valve closed state of the main valve body by the differential pressure of the fluid. The second throttle device is controlled by controlling a control valve. And controlling the flow rate of the fluid flowing through the.

According to the control device for an air conditioner of the first aspect, since the flow path of the fluid (refrigerant) of the indoor heat exchanger is switched by the flow path switching means, the flow of the fluid flowing through the indoor heat exchanger is in the same direction. And, due to the throttling action of the second throttling device,
In both heating and dehumidifying operation and dehumidifying operation in cooling, it is possible to control so that dehumidifying action → reheat action is performed, and the reheating ability and dehumidifying efficiency are improved. Further, since the valve body is seated on the valve seat by the differential pressure generated by flowing in the same direction in the second expansion device, even if the electromagnetic coil is de-energized, the seated state of the valve body is maintained by the differential pressure to perform the dehumidifying operation. You can do it. Therefore, power consumption can be reduced.

According to the control device of the air conditioner of the second aspect, similarly to the first aspect, it is possible to perform control so that the dehumidifying action → reheat action is performed during both the heating dehumidifying operation and the cooling dehumidifying operation, and the reheating ability And the dehumidification efficiency is improved. Furthermore, cooling operation and heating operation are performed with the main valve element in the seated state, and heating dehumidification operation or cooling dehumidification operation is performed with the main valve element seated, and the flow rate of the fluid (refrigerant) is controlled by the control valve during this dehumidification operation. You can control. Then, the main valve body is seated on the valve seat by the differential pressure generated by flowing in the same direction in the second expansion device, so that the main valve body can be separated by opening the control valve, and the compressor is stopped. Without this, it is possible to switch between the heating dehumidifying operation and the heating operation, or to switch between the cooling dehumidifying operation and the cooling operation.

According to the air conditioner of claim 3, claim 1
The same action and effect can be obtained.

According to the air conditioner of claim 4, claim 2
The same action and effect can be obtained.

The second aspect of the present invention is as follows.
The diaphragm device can be more specifically configured as follows. That is, this second expansion device is provided between the first heat exchanger and the second heat exchanger that form the indoor heat exchanger, and is a valve provided in the valve chamber that communicates with the first heat exchanger. The body is seated on / separated from the valve seat of the valve port interposed between the valve chamber and the second heat exchanger, and is formed by the valve body and the valve seat when the valve body is in the seated state. An electromagnetic coil for allowing a dehumidifying operation to be performed in the air conditioner by causing a fluid to flow out from the valve chamber to the valve port via the restricted throttle portion, and the valve body is seated on the valve seat by energization. And valve body urging means for urging the valve body so as to separate the valve body from the valve seat, the valve body urging means is configured such that the electromagnetic coil is in a non-energized state and the valve is Set so that the valve element does not separate from the valve seat when the pressure difference between the room and the valve port is a specified value or more. It is characterized in that is.

In this case, the valve element urging means does not separate the valve element from the valve seat when the electromagnetic coil is in the non-driving state and the pressure difference between the valve chamber and the valve port is a predetermined value or more. Since it operates, the valve body is seated on the valve seat by the electromagnetic coil when the heating dehumidifying operation or the cooling dehumidifying operation is started, and the differential pressure between the valve chamber and the valve port becomes a predetermined value or more by the operation control of the air conditioner. After that, even if the electromagnetic coil is not energized, the seated state of the valve element can be maintained by the above-mentioned differential pressure to perform the heating dehumidifying operation or the cooling dehumidifying operation. Therefore, power consumption can be reduced.

The second aspect of the present invention is the second aspect of the invention.
The diaphragm device can be more specifically configured as follows. That is, the second expansion device is provided between the first heat exchanger and the second heat exchanger that form the indoor heat exchanger, and is inside the valve chamber in which the first port and the second port are formed. Seated on the main valve seat of the 2nd port.
A main valve body which is separated from the main valve body, a main valve body urging means which urges the main valve body to be separated from the main valve seat, and the main valve body against the urging force of the main valve body urging means Main valve body driving means for seating the vehicle on the second port, a conduction means for conducting the main valve body chamber formed on the opposite side of the main valve body from the second port, and the first port, A control valve provided in the valve body for controlling the flow rate of the fluid from the main valve body chamber to the second port, wherein the main port is conducted to the first port when the flow rate is controlled by the control valve. The seated state of the main valve body is maintained against the biasing force of the main valve body biasing means by the pressure difference between the valve body chamber and the second port, and the main valve body is opened by opening the control valve. Reduce the differential pressure between the chamber and the second port,
It is characterized in that the main valve body is separated from the seat by the urging force of the main valve body urging means.

In this case, the main valve body drive means causes the main valve body to be seated in the second port against the biasing force of the main valve body biasing means.
This isolates the valve chamber from the second port. The flow rate is controlled by the control valve while maintaining the seated state of the main valve body by the differential pressure between the main valve body chamber that is connected to the first port and the second port. Further, the pressure difference between the main valve body chamber and the second port is reduced by opening the control valve, and the main valve body is separated by the urging force of the main valve body urging means. 2 ports are conducting. Therefore, the first port is connected to the high-pressure side and the second port is connected to the low-pressure side to perform cooling operation, heating operation, etc. with the main valve element in the seated state, and heating dehumidification operation or cooling dehumidification operation with the main valve element in the seated state. The flow rate of the fluid (refrigerant) can be controlled by the control valve during the heating dehumidifying operation or the cooling dehumidifying operation. Then, since the main valve body can be seated by the main valve body drive means and can be separated by opening the control valve, switching between the heating dehumidifying operation and the heating operation without stopping the compressor, Alternatively,
It is possible to switch between the cooling / dehumidifying operation and the cooling operation.

[0022]

BEST MODE FOR CARRYING OUT THE INVENTION Next, an embodiment of a control device for an air conditioner and an air conditioner according to the present invention will be described with reference to the drawings.

FIG. 2 is a block diagram showing an example of an air conditioner according to an embodiment to which the present invention is applied. The air conditioner of this embodiment has an indoor unit (inside the one-dot chain line in the figure) and an outdoor unit (FIG. Outside the one-dot chain line) and a heat pump type refrigeration cycle. 4 in the figure
Is a compressor, 9A to be described later is an indoor heat exchanger mounted in an indoor unit, 9B is an outdoor heat exchanger mounted in an outdoor unit, 10A is a first throttle device, 200 is an accumulator, and 100 is a four-way valve. For example, it is a rotary type flow path switching valve.

The discharge port of the compressor 4 is connected to the flow path switching valve 100, and the suction port of the compressor 4 is connected to the flow path switching valve 100 via the accumulator 200. In addition, the flow path switching valve 100 is connected to the indoor heat exchanger 9A via the heat exchanger conduit.
And the outdoor heat exchanger 9B, and the first expansion device 10A
Is interposed between the indoor heat exchanger 9A and the outdoor heat exchanger 9B. Thereby, the compressor 4, the flow path switching valve 100,
The accumulator 200, the indoor heat exchanger 9A, the outdoor heat exchanger 9B, and the expansion device 10A constitute a heat pump type refrigeration cycle A.

Incidentally, the "flow path switching means" in the present invention,
The “first heat exchanger”, the “second expansion device”, and the “second heat exchanger” are provided in the indoor heat exchanger 9A as described later.

The flow path of the refrigeration cycle A is the flow path switching valve 100.
The flow passage mode of the flow passage switching valve 100 is set to the “cooling mode” and the “heating mode”, although the flow passage mode can be switched to two kinds of flow passages according to the flow passage mode. In the cooling mode, cooling operation, cooling dehumidifying operation, and defrosting operation are performed, and in heating mode, heating operation and heating dehumidifying operation are performed.

The compressor 4 compresses the refrigerant, and the compressed refrigerant (fluid) flows into the flow path switching valve 100. The flow path switching valve 100 switches the flow path mode according to the operation mode. The refrigerant from the compressor 4 is supplied to the indoor heat exchanger 9A according to the flow path selectively switched by the flow path switching valve 100.
Alternatively, it is introduced into the outdoor heat exchanger 9B.

That is, in the heating mode, as shown by the solid arrow in the figure, the compressed refrigerant causes the flow path switching valve 100 to flow.
The refrigerant liquid flowing into the indoor heat exchanger 9A from the indoor heat exchanger 9A and flowing out from the indoor heat exchanger 9A flows into the outdoor heat exchanger 9B via the first expansion device 10A. And the outdoor heat exchanger 9B
The refrigerant that has flowed out of is flowed into the compressor 4 via the flow path switching valve 100 and the accumulator 200. On the other hand, in the cooling mode, as shown by the broken line arrow in the figure, the compressor 4
The refrigerant compressed by the flow passage switching valve 100, the outdoor heat exchanger 9B, the first expansion device 10A, the indoor heat exchanger 9A, the flow passage switching valve 100, the accumulator 200, and the compressor 4
Are circulated in the order of.

Since the heating operation, the cooling operation, and the defrosting operation may be conventionally known controls, the heating dehumidifying operation and the cooling dehumidifying operation will be mainly described below.

The indoor unit is provided with a cross flow fan 91A for blowing the air passing through the indoor heat exchanger 9A, and the heat exchanger motor 301 rotating this cross flow fan 91A is a microcomputer or the like. The driver C is controlled by the configured indoor control unit 300.
Rotation control is performed via 7. As a result, the heat exchange capacity of the indoor heat exchanger 9A is controlled. Also, the room temperature T
The temperature a is detected by the temperature sensor 302, and the temperature Tc of the indoor heat exchanger 9A is detected by the temperature sensor 303. By receiving the signal from the infrared remote controller 500 at the receiver 304, the operation of the indoor controller 300 can be switched or set by operating the remote controller.

Further, the indoor control section 300 is provided with a driver C1.
The control signal is output to 1. Here, FIG. 2 is shown as a block diagram common to the first and second embodiments of the second diaphragm device described later, and in the case of the second diaphragm device of the first embodiment, the driver C11 is The circuit that drives the electromagnetic coil 11, and in the case of the second diaphragm device of the second embodiment, the driver C11 is a circuit that supplies a pulse signal to the stepping motor 311. Then, in the first embodiment, the electromagnetic coil 11 is driven by the drive current from the driver C11, and the valve opening state and the valve closing state of the second throttle device are switched. Further, in the second embodiment, the rotation angle of the stepping motor 311 is controlled according to the pulse signal from the driver C11, the switching control between the fully open state and the closed state of the second expansion device, and the flow rate control of the refrigerant are performed. In addition, the indoor control unit 30
0 outputs a control signal to the driver C12, the driver C12 controls the flow path switching means drive source 312, and drives the flow path switching means in the indoor heat exchanger 9A.

The outdoor unit is provided with a fan 91B for blowing air passing through the outdoor heat exchanger 9B, and a heat exchanger motor 401 for rotating the fan 91B.
Is an outdoor control unit 4 including a microcomputer or the like.
By the control of 00, the rotation control is performed via the driver C8. As a result, the heat exchange capacity of the outdoor heat exchanger 9B is controlled. Further, the outside air temperature Ta ′ is detected by the temperature sensor 402, and the temperature Tc ′ of the outdoor heat exchanger 9B is detected by the temperature sensor 403. In addition, the outdoor control unit 4
00 is a stepping motor 404 via a driver C6
Is controlled to control the opening of the diaphragm of the first diaphragm device 10A. Further, the outdoor control unit 400 detects the discharge part temperature Td of the compressor 4 with the temperature sensor 405, drives the compressor motor 450 by the three-phase power from the inverter module C9, and controls the operation of the compressor 4.

Further, the outdoor control section 400 has a driver C1.
A control signal is output to 0 to control the power supplied from the driver C10 to the electromagnetic coil 101 of the flow path switching valve 100. The flow path switching valve 100 switches the flow path according to the electric power supplied to the electromagnetic coil 101.

FIG. 1 is a principle block diagram of an embodiment of a control device for an air conditioner of the present invention. Each element of this principle block diagram corresponds to each element of FIG. 2 and a combination of each element. There is. In the refrigeration cycle A, the same elements as those in FIG. 2 are designated by the same reference numerals. The control device C shown by the alternate long and short dash line in FIG. 1 corresponds to the indoor control unit 300 and the outdoor control unit 400, and the processing unit (control unit) C1 of this control device C is shown.
Is the microcomputer 330 of the indoor control unit 300 and the outdoor control unit 4
It corresponds to the microcomputer 470 of 00. Also, the input section C
2 corresponds to the receiving unit 304 of the indoor unit or a manual switch (not shown), and the detecting unit C3 includes temperature sensors 302, 303, 402, 403, 405, or pressure detecting means, flow rate detecting means, and frequency detecting means (not shown). It corresponds to means. Further, the power failure detection unit C4 corresponds to the voltage detector 490 of the outdoor control unit 400, and the semi-fixed storage unit C5 corresponds to the EEPROM 340 of the indoor control unit 300 and the EEPROM 480 of the outdoor control unit 400.

The first diaphragm drive unit C6 is a driver C6, and the first diaphragm drive source 404 is a stepping motor 404. The flow path switching means drive unit C12 is the driver C12 that drives the flow path switching means drive source 312.
The second diaphragm device driving unit C11 is a driver C11, and the second diaphragm device driving source 311 is a stepping motor 311. The indoor fan drive unit C7 is a driver C7, and the indoor fan drive source 301 is a heat exchanger motor 301.
The outdoor fan drive unit C8 is a driver C8, and the outdoor fan drive source 401 is a heat exchanger motor 401. The flow path switching valve drive unit C10 is a driver C10, and the flow path switching valve drive source 101 is an electromagnetic coil 101. The compressor drive unit C9 is an inverter module C9, and the compressor power source 450 is a compressor motor. In addition, the column [003
However, in some embodiments, the second diaphragm drive source (311/11) may be the electromagnetic coil 11.

FIG. 9 is a block diagram of the indoor heat exchanger 9A. The indoor heat exchanger 9A includes a flow path switching means 91, a first heat exchanger 9A1, a second heat exchanger 9A2, and a second expansion device 9A3, and the second expansion device 9A3 has the first heat. It is interposed between the exchanger 9A1 and the second heat exchanger 9A2. The second expansion device 9A3 is fully opened in the operation modes other than the heating dehumidifying operation mode and the cooling dehumidifying operation mode, and the first heat exchanger 9A1 and the second heat exchanger 9A2 are substantially integrated into the room. Performs the function of the heat exchanger 9A. Thus, in the heating mode, the indoor heat exchanger 9A functions as a condenser, the outdoor heat exchanger 9B functions as an evaporator, and the room is heated. In the cooling mode, the outdoor heat exchanger 9B functions as a condenser, the indoor heat exchanger 9A functions as an evaporator, and the room is cooled.

On the other hand, in the heating dehumidifying operation mode and the cooling dehumidifying operation mode, the second expansion device 9A3 is in the valve closed state, and the cut groove formed in the valve seat described later (first embodiment).
Alternatively, the control valve (second embodiment) functions to throttle the refrigerant. Then, in both the heating dehumidifying operation mode and the cooling dehumidifying operation mode, the flow passage is switched by the flow passage switching means 91 so that the refrigerant is the first heat exchanger 9A1 → the second expansion device 9A3 → the second heat exchanger. 9A2 flow in the same direction, the first heat exchanger 9A1 functions as a condenser,
The heat exchanger 9A2 functions as an evaporator. That is, the heating by the condenser and the cooling / dehumidification by the evaporator both dehumidify the heating dehumidifying operation and the cooling dehumidifying operation.
Since it reburns, reheat capacity and dehumidification efficiency are improved.

FIG. 10 is a block diagram showing a first example of the flow path switching means 91, and this example uses one four-way valve 91a. In the heating and dehumidifying operation mode indicated by the solid arrow, the four-way valve 91a is switched to the flow path illustrated by the solid line, and in the cooling and dehumidifying operation mode indicated by the broken arrow, the four-way valve 91a.
The flow path is switched to the flow path indicated by the broken line in a. In the heating operation mode, the second heat exchanger 9A2 → second
It is also possible to flow the refrigerant like the expansion device 9A3 → first heat exchanger 9A1.

FIG. 11 is a block diagram showing a second example of the flow path switching means 91, and this example shows two two-way valves 91b, 91.
c and two check valves 91d and 91e are used.
In the heating dehumidifying operation mode, the first two-way valve 91b is OF
F (closed), and the second two-way valve 91c is turned on (open). In the cooling / dehumidifying operation mode, the first two-way valve 91b is turned on (open) and the second two-way valve 91c is OF.
F (closed). The check valve 91e acts to conduct the refrigerant flowing out from the second heat exchanger 9A2 in the cooling / dehumidifying operation mode, but the pressure of the refrigerant flowing out from the second heat exchanger 9A2 in the heating / dehumidifying operation mode is outside the room. Since it is lower than the pressure of the refrigerant discharged from the unit side, the refrigerant flowing from the second heat exchanger 9A2 acts so as not to be conducted. The action of such a check valve is the same in the check valve described later.

FIG. 12 is a block diagram showing a third example of the flow path switching means 91. In this example, four two-way valves 91f, 91 are used.
g, 91h, 91i are used. In the heating / dehumidifying operation mode, the first two-way valve 91f is turned off (closed), the second two-way valve 91g is turned on (open), and the third two-way valve 91h is turned on (open). The fourth two-way valve 91i is turned off (closed). In the cooling / dehumidifying operation mode, the first two-way valve 91f is turned on (open), the second two-way valve 91g is turned off (closed), and the third two-way valve 91h.
Is turned off (closed), and the fourth two-way valve 91i is turned on.
It is opened.

FIG. 13 is a block diagram showing a fourth example of the flow path switching means 91, and this example uses one three-way valve 91j and two check valves 91k, 91m. In the heating / dehumidifying operation mode, the three-way valve 91j is OFF, that is, the pipeline A-1 and the pipeline A-3 are open and the pipeline A-2 is closed.
In the cooling / dehumidifying operation mode, the three-way valve 91j is set to O.
N, that is, pipeline A-1 and pipeline A-2 are open and pipeline A-3
Is closed.

FIG. 14 is a block diagram showing a fifth example of the flow path switching means 91, and this example shows two three-way valves 91n, 91.
p is used. In the heating dehumidifying operation mode, the three-way valve 91n is OFF, that is, the pipeline A-1 and the pipeline A-3.
Is opened to close the conduit A-2, and the three-way valve 91p is turned on, that is, the conduits A-4 and A-5 are opened and the conduit A-6 is closed. In the cooling / dehumidifying operation mode, the three-way valve 91
n is ON, that is, pipeline A-1 and pipeline A-2 are open and pipeline A-3 is closed, and three-way valve 91p is OFF, that is pipeline A-4 and pipeline A-6 are open. Line A-5 is closed.

Next, the second diaphragm device 9A in the embodiment.
The structure and specific operation of each of the third embodiments will be described.

3 and 4 are sectional views of the first embodiment of the second diaphragm device 9A3. An electromagnetic coil 11 that is energized via a conductive wire 11a is provided on the outer periphery of a cylindrical portion 17a formed in the upper portion of the valve housing 17. Further, the tubular portion 17 a is provided with a guide 12 on the inner upper side thereof and also with a suction element 16 on the lower inner side thereof. Between the guide 12 and the suction element 16, the valve element 14 is provided.
Plunger 13 connected to the upper part of is arranged.
The plunger 13 has a tubular shape, and this tubular portion is arranged between the protruding portion of the guide 12 and the tubular portion 17a.

The plunger 13 is moved upward by the spring 15 fixed to the suction element 16, that is, the guide 12
Is urged to approach. Also, the plunger 1
A cushioning material 13a is provided inside the guide 3, and the guide 1
The lower end of 2 functions as a stopper that restricts the movement of the plunger 13 by the urging force of the spring 15 by contacting the cushioning material 13a. The valve housing 17
(And the cylindrical portion 17a), the guide 12, and the valve body 14 are made of a non-magnetic material, and the suction element 16 and the plunger 13 are made of a magnetic conductive material.

A valve chamber 19 is provided inside the valve housing 17, and the valve chamber 19 has a first heat exchanger 9A1.
The pipe 21 connected to is connected to the second heat exchanger 9A2, and the pipe 22 connected to the second heat exchanger 9A2 is connected to the second heat exchanger 9A2 via the valve port 20. Further, a tip end portion of the valve body 14 connected to the plunger 13 is arranged in the valve chamber 19, and an end portion of the valve port 20 on the valve body 14 side faces the tip end portion of the valve body 14. A valve seat 18 is formed. A tapered surface 14a is formed on the outer periphery of the tip of the valve body 14, and a tapered surface 18a is formed on the inner peripheral surface of the upper end of the valve seat 18 so as to be aligned with the tapered surface 14a of the valve body 14. There is.

With the above structure, when the electromagnetic coil 11 is energized, an electromagnetic force is generated between the suction element 16 and the plunger 13 in a direction to lower the plunger 13 against the biasing force of the spring 15. . Therefore, when the plunger 13 is lowered by this electromagnetic force, the valve body 14 is also lowered,
Tapered surface 14a of valve body 14 and tapered surface 1 of valve seat 18
The valve body 14 is seated on the valve seat 18. As a result, the valve is closed.

Here, a part of the tapered surface 18a of the valve seat 18 is formed with a plurality of cut grooves 18b as shown in FIG. 5, and the valve chamber 19 and the valve port 20 are formed even when the valve is closed. Are communicated with each other by the cut groove 18b. On the other hand, since the pipe 21 is connected to the first heat exchanger 9A1 and the pipe 22 is connected to the second heat exchanger 9A2, the refrigerant flows from the valve chamber 19 to the valve port 20 via the cut groove 18b. . In this configuration, since the cut groove 18b serves as a throttle, the pressure inside the valve chamber 19 becomes higher than the pressure inside the valve port 20, and a differential pressure is generated.

FIG. 6 is a diagram showing the differential pressure vs. applied power characteristic of the second expansion device 9A3, and the straight line in the figure indicates the valve element 14 with the valve seat 1
8 shows the threshold value of the applied electric power required for seating at No. 8. For example, the differential pressure ΔP between the valve chamber 19 and the valve port 20
Is 0.0 MPa, the rated power of 6.5 W or more is applied to the electromagnetic coil 11 to change the valve from the open state (state of FIG. 3) to the closed state (state of FIG. 4). The body 14 sits on a valve seat 18. Then, the cut groove 18b acts as a throttle, the pressure inside the valve chamber 19 becomes higher than the pressure inside the valve port 20, and when the pressure difference between them becomes 0.08 MPa (third predetermined pressure difference) or more, the electromagnetic Even when the coil 11 is de-energized, the valve closed state can be maintained. When the differential pressure ΔP is 0.005 MPa (first predetermined differential pressure), the valve open state is closed by applying a power of approximately 6.1 W (first predetermined power) or more to the electromagnetic coil 11. And the differential pressure ΔP is 0.015 MPa
Approximately 5.3 W (second predetermined power) when (second predetermined differential pressure)
By applying the above electric power to the electromagnetic coil 11, the valve open state can be changed to the valve close state.

Further, the differential pressure ΔP is 0.08 MPa (3rd
If the pressure is equal to or higher than a predetermined differential pressure, the valve opening state can be changed to the valve closing state without applying electric power to the electromagnetic coil 11. That is, according to claim 1, the urging force of the spring 15 as the valve urging means is such that the electromagnetic coil 11 is in the non-energized state (energized state) and the valve chamber 1
The differential pressure ΔP between 9 and the valve port 20 is 0.08 MPa
The valve body 14 is set so as not to be separated from the valve seat 18 when (the third predetermined differential pressure) or more. This differential pressure Δ
P mainly changes depending on the control (driving, stopping, etc.) of the operating capacity of the compressor 4, but in the dehumidifying operation mode, the differential pressure ΔP is 0.08 MPa (third predetermined differential pressure) or more. The air conditioner is operated. Also, the differential pressure ΔP
Becomes gradually (gradually), the biasing force of the spring 15 acts to separate the valve body 14 from the valve seat 18, and when the differential pressure ΔP is reduced to 0.015 MPa (second predetermined differential pressure), The valve body 14 is set so as to be reliably separated from the valve seat 18.

7 and 8 show the second diaphragm 9A3 of the second diaphragm device 9A3.
It is sectional drawing of embodiment, FIG. 7 has shown the open state and FIG. 8 has shown the closed state. This fluid control valve includes a valve body 31, and a valve chamber 31a is formed in the valve body 31. Valve chamber 31a
Has a first port 31b opening on its side surface and a second port 31c opening on its lower surface, and a main valve seat 31d is formed at the end of the second port 31c on the valve chamber 31a side.
The primary joint 21 is connected to the first port 31b, the secondary joint 22 is connected to the second port 31c, the primary joint 21 is connected to the first heat exchanger 9A1, and the secondary joint 2 is connected.
2 is connected to the second heat exchanger 9A2.

A cylinder 31e, which opens from the valve chamber 31a to the upper end, is formed on the opposite side of the valve body 31 from the second port 31c, and the main valve body 32 and the piston 33 are slidable in the cylinder 31e. It is installed in.

The main valve body 32 has a cylindrical shape, and has a partition wall projecting from the lower end to the piston 33 side in the shape of a truncated cone, and a control valve seat 32a is formed at the upper end portion of this partition wall. There is. Further, a taper surface 32b is provided on the lower end of the main valve body 32.
Is formed, and the tapered surface 32b contacts the main valve seat 31d. Further, a bleed hole 32c is formed on the side surface of the main valve body 32 so as to communicate with the main valve body chamber 32d therein.

The needle valve 3 is provided at the center of the lower end of the piston 33.
4, the needle valve 34 has a tip having a diameter smaller than the inner circumference of the control valve seat 32a of the main valve body 32 and a root side having a diameter larger than the inner circumference of the control valve seat 32a. A coil spring 35 is provided on the outer circumference of the needle valve 34. The upper end of the coil spring 35 is fixed to the lower end of the piston 33, and the lower end of the coil spring 35 is fixed to the inner bottom of the main valve body 2. There is. This allows
The main valve body 32 is biased toward the piston 33 side.

A case 36 made of a thin plate cylindrical body is attached above the valve body 32, and a lower opening portion of the case 36 and the valve body 31 are closed by a lid 37. Inside the case 36, the rotor 3 made of magnet is used.
8, shaft 39 having male screw 39a, spring receiver 4
0, a coil spring 41 is provided. The rotor 38 is attached to a shaft 39, and the upper end of the shaft 39 is slidably supported by a spring receiver 40.
A coil spring 41 is interposed between the upper part of the and the spring receiver 40.

The spring receiver 40 is rotatably supported at its tip protruding portion in a recess 36a formed by protruding the center of the top wall portion of the case 36 to the outside, and the lower end of the shaft 39 is at the upper end portion of the valve body 31. It is pivotally supported by the formed bearing 31f. As a result, the rotor 38 and the shaft 39 can rotate within the case 36. The coil spring 41 absorbs the vibration of the shaft 39. A coil 42a is wound around the stator 42 fixed to the outer periphery of the case 36. The coil 42a, the rotor 38, and the shaft 3 are provided.
9 constitutes a stepping motor 311.
The stator 42 and the coil 42a are partially omitted in the drawing.

The piston 33 has a columnar shape having a hollow portion, and a female screw 33a which is screwed into the male screw 39a of the shaft 39 is attached above the hollow portion.
A guide part 31 is provided at the upper end of the cylinder 31e for guiding the piston 33 so as to reciprocate in the axial direction (axial direction of the shaft 34) while stopping the rotation of the piston 33.
g is provided. A leaf spring 31h with which the upper end of the needle valve 34 abuts is arranged at the lower end of the bearing 31f. Then, in the state of FIG. 7, the stepping motor 31
When 1 is rotated normally, the piston 33 descends to the state shown in FIG. 8, and when the stepping motor 311 is rotated reversely in the state shown in FIG. 8, the piston 33 rises to the state shown in FIG. 7.

With the above construction, the second diaphragm device 9A3 of the second embodiment operates as follows. First, in the state shown in FIG. 7, the needle valve 34 is connected to the bearing 31 through the leaf spring 31h.
It is stopped at the first location using f as a stopper. At this time, the main valve body 32 is integrated with the piston 33 by the pulling force (biasing force) of the coil spring 35. That is, the main valve body 32 is separated from the main valve seat 31d, and the second throttle device 9 is separated.
A3 is fully opened and is in an operation mode other than the dehumidification operation mode.

Next, when switching to the dehumidifying operation mode, the stepping motor 311 is rotated in the normal direction, so that the piston 33 and the main valve body 32 descend and stop at the second position in FIG. At this time, the first port 31b is on the high pressure side and the second port 31c is on the low pressure side. Therefore, when the main valve body 32 contacts (or approaches) the main valve seat 31d as shown in FIG. 8, the refrigerant in the first port 31b is bleedhole 3.
It flows into the main valve body chamber 32d above the main valve body 32 via 2c, and a differential pressure is generated between the main valve body chamber 32d and the second port 31c. Therefore, the main valve body 32 is pressed against the main valve seat 31d and seated.

The force pressing the main valve body 32 is the main valve body chamber 32d (substantially the first port 31b) and the second port 31.
It is determined by the pressure difference between the control valve seat 32a of the main valve body 32 and the needle valve 34, and the pressing force (differential pressure) becomes smaller as the sectional area of the gap between the control valve seat 32a of the main valve body 32 and the needle valve 34 is smaller than the sectional area of the bleed hole 32c. growing. In addition, the coil spring 35 is set such that the force pressing the main valve body 32 is larger than the biasing force (pulling force) of the coil spring 35.
Strength and needle shape are set.

As described above, since the main valve body 32 maintains the state of being seated on the main valve seat 31d due to the differential pressure, the stepping motor 311 moves the piston 33 (that is, the needle valve 34) up and down to control the valve seat. The opening degree of the control valve composed of 32a and the needle valve 34 changes, and the flow rate of the refrigerant in the dehumidifying operation mode can be controlled.

Next, when switching from the dehumidifying operation mode to the cooling operation mode or the heating operation mode, the stepping motor 311 is rotated in the reverse direction (full rotation) and the piston 33 is rotated.
Is moved to the first position in FIG. As a result, the needle valve 34 opens the control valve seat 32a, so that the main valve body chamber 32d
7 and the pressure at the second port 31c decrease, and the force due to the pressure difference becomes smaller than the biasing force of the coil spring 35, the main valve body 32 is separated from the main valve seat 31d and the state shown in FIG. Become. That is, the first port 31b and the second port 31
When c is completely conducted, the refrigeration cycle A enters the cooling mode (or the heating mode or the like).

As described above, even when the refrigerant is circulated in the refrigeration cycle A, the switching control of the second expansion device 9A3 can be performed by driving the stepping motor 311, so that it is not necessary to stop the compressor 4. . Further, even in the dehumidifying operation mode, the flow rate of the refrigerant can be controlled by the control valve including the control valve seat 32a and the needle valve 34.

[0064]

According to the controller of the air conditioner of the first aspect of the present invention, the reheat capacity and the dehumidifying efficiency are improved, and the valve body is seated by the differential pressure generated by flowing in the same direction in the second expansion device. Since the seat is seated on the valve, even if the electromagnetic coil is de-energized, the seated state of the valve element can be maintained by the differential pressure, and the dehumidifying operation can be performed, thus reducing the power consumption.

According to the control device of the air conditioner of the second aspect, the reheat capacity and the dehumidifying efficiency are improved similarly to the first aspect, and the flow rate of the fluid (refrigerant) can be controlled by the control valve during the dehumidifying operation. Further, since the main valve body is seated on the valve seat due to the differential pressure generated by flowing in the same direction in the second expansion device, the main valve body can be separated by opening the control valve, and the compressor can be stopped. Instead, the heating / dehumidifying operation and the heating operation can be switched, or the cooling / dehumidifying operation and the cooling operation can be switched, and power consumption can be reduced.

According to the air conditioner of claim 3, claim 1
The same effect as can be obtained.

According to the air conditioner of claim 4, claim 2
The same effect as can be obtained.

[Brief description of drawings]

FIG. 1 is a principle block diagram of an embodiment of a control device for an air conditioner of the present invention.

FIG. 2 is a block diagram showing an example of an air conditioner according to an embodiment to which the present invention is applied.

FIG. 3 is a sectional view of a second diaphragm device of the first example of the embodiment in an open state.

FIG. 4 is a cross-sectional view of a second diaphragm device of the first example of the embodiment in a closed state.

FIG. 5 is a diagram illustrating a cut groove of the second diaphragm device according to the first example of the embodiment.

FIG. 6 is a diagram showing a differential pressure vs. applied power characteristic of the second diaphragm device of the first example of the embodiment.

FIG. 7 is a cross-sectional view of a second diaphragm device of a second example of the embodiment in an open state.

FIG. 8 is a cross-sectional view of a second diaphragm device of a second example of the embodiment in a closed state.

FIG. 9 is a block diagram of the indoor heat exchanger in the embodiment.

FIG. 10 is a block diagram showing a first example of flow path switching means in the embodiment.

FIG. 11 is a block diagram showing a second example of the flow path switching means in the embodiment.

FIG. 12 is a block diagram showing a third example of the flow path switching means in the embodiment.

FIG. 13 is a block diagram showing a fourth example of the flow path switching means in the embodiment.

FIG. 14 is a block diagram showing a fifth example of flow path switching means in the embodiment.

[Explanation of symbols]

9A indoor heat exchanger 9B outdoor heat exchanger 9A1 First heat exchanger 9A2 Second heat exchanger 9A3 Second diaphragm device 91 flow path switching means 10A First diaphragm device 100 flow path switching valve 200 accumulator 300 Indoor control unit 312 Flow path switching means drive source 400 Outdoor control unit A refrigeration cycle

Claims (4)

[Claims] 1. A flow path switching means, which is provided at a connecting portion between an outdoor unit and an indoor unit, and switches the flow paths so that the flow directions of fluids flowing through the indoor heat exchanger in the cooling mode and the heating mode are the same. And a second expansion device provided in the indoor unit to control the air conditioner, and during the dehumidifying operation, the first heat exchanger of the indoor heat exchanger forming the indoor unit, the second expansion device, and the second expansion device. In the control device of the air conditioner for switching and controlling the flow path switching means so that the fluid flows in the order of two heat exchangers, the second expansion device includes an electromagnetic coil for seating the valve body on the valve seat by energization. The valve body is configured to be seated on the valve seat by a differential pressure generated by the fluid flowing in the second throttle device in the same direction, and the valve coil is kept closed by interrupting the energization of the electromagnetic coil. Special to do Control device for an air conditioner to. 2. A flow path switching means, which is provided at a connecting portion between the outdoor unit and the indoor unit, and switches the flow paths so that the flow directions of the fluids flowing through the indoor heat exchanger in the cooling mode and the heating mode are the same direction. And a second expansion device provided in the indoor unit to control the air conditioner, and during the dehumidifying operation, the first heat exchanger of the indoor heat exchanger forming the indoor unit, the second expansion device, and the second expansion device. In a control device of an air conditioner that controls switching of the flow path switching means so that a fluid flows in the order of two heat exchangers, the second expansion device is generated by the fluid flowing in the same direction in the second expansion device. A main valve body that is seated on a valve seat by a pressure difference, and a control valve that is provided on the main valve body. While maintaining the valve closed state of the main valve body by the pressure difference of the fluid, The second throttle device is controlled by controlling a control valve. Control device for an air conditioner and controlling the flow rate of the fluid flowing through the. 3. A flow path switching means which is provided at a connecting portion between the outdoor unit and the indoor unit and switches the flow paths so that the flow directions of the fluids flowing through the indoor heat exchanger in the cooling mode and the heating mode are the same. And a second expansion device provided in the indoor unit, the first heat exchanger of the indoor heat exchanger constituting the indoor unit, the second expansion device, during the dehumidifying operation,
And an air conditioner that switches and controls the flow path switching means so that the fluid flows in the order of the second heat exchanger, the second expansion device includes an electromagnetic coil that seats the valve body on the valve seat by energization, The valve body is configured to sit on the valve seat due to a differential pressure generated by the fluid flowing in the same direction in the second throttle device, and the valve coil is kept closed by interrupting the energization of the electromagnetic coil. An air conditioner characterized by that. 4. A flow path switching means which is provided at a connecting portion between the outdoor unit and the indoor unit, and which switches the flow paths so that the flow directions of the fluids flowing through the indoor heat exchanger in the cooling mode and the heating mode are the same direction. And a second expansion device provided in the indoor unit, the first heat exchanger of the indoor heat exchanger constituting the indoor unit, the second expansion device, during the dehumidifying operation,
And an air conditioner that controls switching of the flow path switching means so that the fluid flows in the order of the second heat exchanger, wherein the second expansion device is generated by the fluid flowing in the same direction in the second expansion device. A main valve body seated on the valve seat by a differential pressure; and a control valve provided on the main valve body. The main valve body is kept closed by the differential pressure of the fluid, and the control is performed. An air conditioner characterized by controlling a valve to control a flow rate of a fluid flowing through the second throttle device.