JP2001221538A - Controller for refrigeration cycle, driver for fluid control valve and fluid control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a simple structure of refrigeration cycle by controlling the switching of a channel selector valve (four-way valve) through a pilot valve acting in response to flow control of a fluid control valve (motor expansion valve) and eliminating heat conduction loss of a transfer unit thereby eliminating mechanical transfer unit. SOLUTION: A motor expansion valve 10A is provided with a pilot valve 210 being switched depending on the valve opening and alternative switching of 'interconnection/closing' is made among the interconnecting pipes 212a, 213a and 214a of S, E and C ports at a pilot valve 210. In a channel selector valve 43, a high pressure chamber R1 and a pressure conversion chamber R2 are interconnected constantly through a through hole 121 made in a piston cylinder 12. The high pressure chamber R1 and a second pressure conversion chamber R5 are interconnected constantly through a second through hole 121' made in a second piston cylinder 12'. Interconnection of a suction pipe 6 is switched between the pressure conversion chamber R2 and the second pressure conversion chamber R5 using the pilot valve 210.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid control valve such as a throttle device for adjusting a flow rate of a refrigerant in a refrigeration cycle, and a flow path switching valve such as a four-way valve for switching a flow path of the refrigerant in a refrigeration cycle. The present invention relates to a refrigeration cycle control device that controls a fluid control valve and a flow path switching valve, a drive device for the fluid control valve, and a fluid control valve.

[0002]

2. Description of the Related Art Conventionally, in a heat pump refrigeration cycle, a refrigerant flows through a compressor, a heat source side heat exchanger, a throttle device, and a use side heat exchanger during a cooling mode operation. The refrigerant recirculates in the refrigeration cycle so that the refrigerant flows through the compressor, the use-side heat exchanger, the expansion device, and the heat-source-side heat exchanger during the heating mode operation. Let me. like this,
There is a so-called four-way valve as a flow path switching valve used to reverse the circulation path of the refrigerant in the heat pump refrigeration cycle.

On the other hand, there is a so-called expansion valve as a throttle device used for adjusting the flow rate of the circulating refrigerant. In recent years, an electric expansion valve (electric valve) has been frequently used as the expansion valve.

(Background Art-2) Conventional four-way valves are disclosed, for example, in Japanese Patent Publication No. 35-12689 and Japanese Utility Model Publication No. 55-53.
As disclosed in Japanese Patent Application Laid-Open No. 825, the center valve in which the valve element is disposed among the three valve chambers inside the valve body by energizing the electromagnetic coil of the electromagnetic pilot valve provided outside the valve body. One of the two valve chambers disposed on both sides of the chamber is selectively depressurized, and the valve body is moved in the valve body by a differential pressure generated between the depressurized valve chamber and the central valve chamber. (Sliding or sliding). Incidentally, Japanese Patent Publication No. 35-12689 and Japanese Utility Model Publication No. 55-53
In the drawing of Japanese Patent Publication No. 825, the valve body and the pilot valve are illustrated as separate bodies, but they are actually combined and used.

(Prior Art-1) The control valve disclosed in Japanese Patent No. 2711516 has an electric valve and a four-way switching valve (flow path switching valve), and uses a transmission device for transmitting the rotation of the electric valve. The opening and closing of the valve opening of the motor-operated valve and the switching of the flow path by the rotation of the valve body of the four-way switching valve are performed in conjunction with each other by utilizing the rotational force of the rotor. That is, it is a control valve, that is, a composite valve that uses a driving force of an electric valve (throttle device) to rotate a four-way switching valve (flow path switching valve) by a transmission device.

(Prior art-2) JP-A-10-30741
The control valve disclosed in the above publication is a composite valve including an electric valve, a four-way valve, and a two-way valve (bypass valve). The two-way valve is provided adjacent to the four-way valve and is used for opening and closing a hot gas defrost type bypass circuit. This Japanese Patent Laid-Open No. 10-3
In the case of Japanese Patent Publication No. 0741, similarly to Japanese Patent No. 2711516, a four-way valve (flow path switching valve) is rotated by a transmission device using the driving force of an electric valve (throttle device).

(Prior art-3) JP-A-10-28132
The control valve disclosed in Japanese Patent Publication No. 1 is a composite valve having a motor-operated valve, a four-way valve, and a bypass circuit provided in the four-way valve. The four-way valve (flow path switching valve) is rotated by the device.

(Prior art-4) JP-A-9-189456
Japanese Patent Application Laid-Open No. 10-30741 discloses a control valve disclosed in Japanese Patent No.
Japanese Patent Application Laid-Open No. 81321 discloses an invention related to opening / closing control of a composite valve which can be applied to a control valve and the like. In Japanese Patent Application Laid-Open No. 9-189456, the opening degree is 0 to 24.
(Heating four-way valve), opening degree 24-356 (expansion valve), opening degree 3
56 to 380 (cooling four-way valve) function according to the opening degrees classified into three ranges. An EEPROM is provided as storage means for storing the opening.

(Prior Art-5) Japanese Patent Application Laid-Open No. 7-63446 discloses that, when controlling an electric expansion valve of an air conditioner, an intermittent oscillation occurs when a switching transformer is in a light load state. There is disclosed a technique of turning off an electric expansion valve and controlling energization so that a motor of the electric expansion valve does not rotate.

[0010]

Patent No. 2711516
JP-A-10-30741, and JP-A-10-281321.
Utilizing the driving force of the electric expansion valve (throttle device), the four-way valve (flow path switching valve) is rotated (operated) by the transmission device. In each case, one motor (power supply means)
By using both the drive unit of the motor-operated valve and the drive unit of the flow path switching valve, there is a certain effect in that the consumption of electricity (electric power) is reduced.

However, by combining two or three control valves and combining them, there is a problem that the arrangement of various parts in the refrigeration cycle, the connection of refrigerant pipes, and the like are remarkably restricted, and the usability is poor.

In addition, since it is a direct drive type using an electromechanical force using a stepping motor, an increase in torque is required, and there is a problem that the structure is correspondingly complicated.

Further, the high-temperature gas refrigerant and the low-temperature gas refrigerant of the four-way valve and the high-pressure liquid refrigerant and the low-pressure liquid refrigerant of the solenoid valve (throttle device) concentrate on the composite valve, thereby impairing the heat shut-off property.
There is a problem that energy loss occurs.

In Japanese Unexamined Patent Publication No. 9-189456, the opening degree of the expansion valve of the composite valve is controlled in controlling the cooling / heating cycle.
At the time, after 50 seconds, the compressor is fully opened, and during heating, the compressor is started with the four-way valve heated from full open to fully closed. During cooling, the compressor is fully closed from full open once, and then fully closed to fully open again. Is set to the cooling state and the compressor is started. That is, the method disclosed in Japanese Patent Application Laid-Open No. 9-189456 has a problem that the control process is complicated.

Japanese Patent Application Laid-Open No. 9-189456 discloses that the operation flow updates the opening data of the EEPROM at the same frequency as the frequency of updating the opening data of the RAM. The EEPROM has no limitation on the life of reading data, but has a limitation on the number of times data can be stored. As described in Japanese Patent Application Laid-Open No. 9-189456, it is difficult to update data frequently.
There were problems with the life and reliability of the OM.

Japanese Unexamined Patent Application Publication No. 7-63446 uses an electric expansion valve as a pseudo load for a switching transistor.
There is a problem that power consumption is only replaced by the electric expansion valve, and if the attention is paid to the entire control circuit of the air conditioner, much effect cannot be obtained. In addition, since the electromagnetic coil is energized while the electric expansion valve is stopped, there is a problem in energy saving.

According to the present invention, a combined valve in which a four-way valve and an electric expansion valve are combined is inconvenient in terms of piping connection, and this problem is solved. It is an object of the present invention to realize a simple structure by eliminating a mechanical transmission device while enabling a flow path switching valve (four-way valve) and a fluid control valve (electric expansion valve) to be disposed separately.

Another object is to simplify the control process.

Further, since the writing durability of the EEPROM is limited in the number of times, it is an object to configure the EEPROM so that writing is not frequently performed.

It is still another object of the present invention to configure a drive circuit by using a semiconductor having a small remaining voltage at the time of ON to save energy.

[0021]

According to a first aspect of the present invention, there is provided a refrigeration cycle control apparatus for controlling a flow path switching valve of a refrigeration cycle by controlling a flow rate of fluid in the refrigeration cycle. A drive signal is output to the fluid control valve, and the flow path switching valve is driven by the non-electric power generated by the fluid that is communicated / closed by the pilot means that operates according to the flow control of the fluid control valve. Switching is controlled.

A control device for a refrigeration cycle according to a second aspect has the configuration according to the first aspect, wherein the pilot means communicates the fluid with the fluid control valve in accordance with a fully open state or a fully closed state of the degree of opening of the fluid control valve. The fluid control valve is configured to be closed to control the opening degree of the fluid control valve to be in a fully open state or a fully closed state when it is determined that the flow path switching valve is to be switched or when it is determined not to be switched. And

According to a third aspect of the present invention, there is provided a driving device for a fluid control valve, comprising: a driving portion for driving a fluid control valve for controlling a flow rate of a fluid; and a positive electrode side of a power supply for supplying non-AC power to the driving portion. And a control unit for controlling the conduction / non-conduction means, the control unit controlling the conduction / non-conduction means, and providing the conduction / non-conduction means for conducting or non-conduction between the drive unit and the positive electrode side.
A control terminal connected to the non-conducting means is short-circuited / opened to the negative side of the power supply,
Non-conduction is controlled.

According to a fourth aspect of the present invention, there is provided a fluid control valve driving device according to the third aspect, wherein the control terminal is a collector or a drain of a transistor having an open output type.

According to a fifth aspect of the present invention, there is provided a fluid control valve driving device having the configuration of the third or fourth aspect, wherein the conducting / non-conducting means comprises:
It is a PNP transistor or a P-channel MOS-FET.

A fluid control valve according to a sixth aspect of the present invention is a fluid control valve for controlling a flow rate of a fluid in a refrigeration cycle, and includes a pilot means for communicating / closing a fluid operated in accordance with the flow rate control of the fluid control valve. It is characterized by having.

A fluid control valve according to a seventh aspect of the present invention includes the configuration of the sixth aspect, wherein an opening control area of the fluid control valve for controlling the flow rate is separated by the flow rate control area and a switching area of the pilot means. It is characterized by the following.

An eighth aspect of the present invention provides the fluid control valve according to the sixth or seventh aspect, wherein the fluid control valve comprises an eccentric valve portion formed on a shaft portion rotated by electric power, and the valve portion comprises: A valve port portion communicated with the disposed closed space, and the flow rate control is performed by changing a gap formed between the valve port portion and a peripheral surface of the valve portion opposed to the valve port portion by rotation of the shaft portion. The pilot means,
It operates according to the rotation of the shaft.

A fluid control valve according to a ninth aspect has the configuration according to the sixth, seventh or eighth aspect, wherein the pilot means generates non-electric power for switching the flow path switching valve of the refrigeration cycle in a passive manner. And communicating / closing the fluid.

The fluid control valve according to claim 10 is the same as in claim 6,
It has a configuration of 7, 8 or 9, wherein the flow path switching valve has a sliding type switching valve element which is moved by the non-electric power.

An eleventh aspect of the present invention provides the fluid control valve having the configuration of the tenth aspect, wherein the flow path switching valve biases the sliding type valve element to generate a part of the non-electric power. Means are provided.

The fluid control valve according to claim 12 is the same as
It has a structure of 7, 8 or 9, and the flow path switching valve has a rotary switching valve body which is rotated and moved by the non-electric power.

According to the refrigeration cycle control device of the first aspect, the pilot means communicates / closes the fluid that operates according to the flow control of the fluid control valve, and generates non-electrical fluid such as pressure generated by the fluid. The switching of the flow path switching valve is controlled by motive power. Therefore, a fluid control valve such as an electric expansion valve and a flow path switching valve such as a four-way valve can be arranged separately, and a non-electric power generated by a fluid is used. And a simple structure can be achieved.

According to the refrigeration cycle control device of the second aspect, the same operation and effect as those of the first aspect can be obtained, and only by controlling the opening degree of the fluid control valve to the fully open state or the fully closed state. Since the flow path switching valve is switched, the control process can be significantly simplified. Also, EEP
The configuration can be such that writing is not frequently performed on the ROM.

According to the fluid control valve driving device of the third aspect, the conduction provided between the positive electrode side of the power supply for supplying the non-AC power and the driving unit such as the electromagnetic coil for driving the fluid control valve. / Since the control unit controls the non-conducting means, a drive with a small remaining voltage can be performed at the time of conducting by a simple (circuit) configuration.
A power saving effect is obtained.

According to the fluid control valve driving device of the fourth aspect, the same effect as that of the third aspect can be obtained by the transistor configured in the open output type.

According to a fifth aspect of the present invention, a PNP transistor or a P-channel MOS-FE is provided.
By T, the same function and effect as in claim 3 can be obtained.

According to the fluid control valve of claim 6, claim 1 is provided.
Similarly to the above, a fluid control valve such as an electric expansion valve and a control valve such as a flow path switching valve can be arranged separately, and a simple structure can be achieved without a mechanical transmission device.

According to the fluid control valve of claim 7, claim 6 is provided.
The same operation and effect as those described above can be obtained, and the control process can be simplified since the opening control region of the fluid control valve for controlling the flow rate is separated by the flow control region and the switching region of the pilot means.

[0040] According to the fluid control valve of claim 8, according to claim 6 of the present invention.
Or the same operation and effect as those of 7 can be obtained, and a control valve such as a flow path switching valve can be switched by a pilot means. Therefore, for example, any type of flow path of a double-sided slide valve, a cantilever slide valve, and a rotary valve It can also be used as a switching valve, greatly improving usability.

According to the fluid control valve of the ninth aspect, the same operation and effect as those of the sixth, seventh or eighth aspect can be obtained.
Since the non-electric power generated by the fluid is supplied to a control valve such as a flow path switching valve through a valve port portion, for example, any type of flow path switching valve such as a double-sided slide valve, a cantilevered slide valve, and a rotary valve Can be used, and the usability is significantly improved.

According to the fluid control valve of the tenth aspect, the same operation and effect as those of the sixth, seventh, eighth or ninth aspects can be obtained, and the fluid control valve has a sliding type switching valve body, for example, a cantilever type or a double-sided type. Apply to holding slide type flow path switching valve,
The usability is significantly improved.

According to the fluid control valve of the eleventh aspect, for example, when applied to a cantilever slide type flow path switching valve, the same operation and effect as the tenth aspect can be obtained.

According to the fluid control valve of the twelfth aspect, the same operation and effect as those of the sixth, seventh, eighth, or ninth aspect can be obtained, and when applied to a flow path switching valve having a rotary switching valve body, The usability is significantly improved.

[0045]

Next, embodiments of the present invention will be described with reference to the drawings.

FIG. 2 is a block diagram showing an example of a refrigeration cycle according to an embodiment of the present invention. The refrigeration cycle of this embodiment includes an indoor unit (inside the dashed line in the drawing) and an outdoor unit (in the dashed line in the drawing). (Outside). 4 is a compressor in the figure,
9A is an indoor heat exchanger mounted on the indoor unit, 9B is an outdoor heat exchanger mounted on the outdoor unit, 10A is an electric expansion valve as a fluid control valve, 200 is an accumulator,
100 is a flow path switching valve. In the following embodiments, the fluid control valve will be described as an electric expansion valve 10A in terms of the structure, and the control will be described as a throttle device representing the function of the electric expansion valve 10A. It is needless to say that the fluid control valve is not limited to the electric expansion valve and may have another configuration.

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. The flow path switching valve 100 is connected to the indoor heat exchanger 9A through a heat exchanger conduit.
The electric expansion valve 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 electric expansion valve 10A constitute a refrigeration cycle A. In the refrigeration cycle A according to this embodiment, the flow path switching valve 100 is a flow path switching valve according to a first example and a second example described later.

The compressor 4 compresses the refrigerant, and the compressed refrigerant flows into the flow path switching valve 100. As will be described later, the flow path of the flow path switching valve 100 is switched 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.
Or, it flows into the outdoor heat exchanger 9B. That is, in the heating operation mode, the compressed refrigerant flows into the indoor heat exchanger 9A from the flow path switching valve 100 as shown by the solid arrow in the figure, and the indoor heat exchanger 9A functions as a condenser. The refrigerant liquid flowing out of the indoor heat exchanger 9A flows into the outdoor heat exchanger 9B via the electric expansion valve 10A, and the outdoor heat exchanger 9B functions as an evaporator. Then, the refrigerant evaporated in the outdoor heat exchanger 9B flows into the compressor 4 via the flow path switching valve 100 and the accumulator 200.
On the other hand, in the cooling operation mode, the refrigerant compressed by the compressor 4 flows from the flow path switching valve 100 to the outdoor heat exchanger 9B, the electric expansion valve 10A, the indoor heat exchanger 9A, The flow path switching valve 100, the accumulator 200, and the compressor 4 are circulated in this order, the outdoor heat exchanger 9B functions as a condenser, and the indoor heat exchanger 9A functions as an evaporator.

The indoor unit is provided with a cross flow fan 91A for blowing air passing through the indoor heat exchanger 9A. A heat exchanger motor 92A for rotating the cross flow fan 91A is controlled by a microcomputer or the like. The driver 3 is controlled by the configured indoor control unit 300.
Rotation control is performed via 01. Thereby, the heat exchange capacity of the indoor heat exchanger 9A is controlled. The indoor temperature Ta 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 a signal from the remote controller 500 such as an infrared type by the receiving unit 304, switching and setting of operation of the indoor control unit 300 can be performed by remote control operation.

The outdoor unit is provided with a fan 91B for blowing air passing through the outdoor heat exchanger 9B, and a heat exchanger motor 92B for rotating the fan 91B.
Is an outdoor control unit 4 composed of a microcomputer or the like.
Under the control of 00, rotation control is performed via the driver 401. Thereby, the heat exchange capacity of the outdoor heat exchanger 9B is controlled. The outside air temperature Ta ′ is determined by the temperature sensor 402.
The temperature Tc ′ of the outdoor heat exchanger 9B is detected by the temperature sensor 403. The outdoor controller 400 controls the opening degree of the throttle of the electric expansion valve 10A via the driver 404. Further, the outdoor control section 400 detects the discharge section temperature Td of the compressor 4 with the temperature sensor 405, and controls the drive of the compressor 4 with three-phase power from an inverter module described later.

The indoor heat exchanger 9A is provided with a pressure sensor Pc. The detected pressure is input to the indoor control unit 300, and the outdoor heat exchanger 9B is provided with a pressure sensor Pc '. The detected pressure is input to the outdoor control unit 400. Then, each pressure is detected, and the flow path switching valve 100 is detected.
Of the moving member described later (ie, the flow path switching valve 1)
00 current state).

The electric expansion valve 10A has a pilot valve 210. Here, in FIG. 2, the pilot valve 210 is illustrated as corresponding to each embodiment described later,
The pilot valve 210 has two ports of an S port 212 and an E port 213 in the case of a flow path switching valve according to a first embodiment described later, and has a port in the case of the flow path switching valve according to the second embodiment. It has three ports: an S port 212, an E port 213, and a C port 214. Each port is connected to the flow path switching valve 100 by a communication pipe. FIG. 2 illustrates a flow path switching valve according to a first embodiment described later.

FIG. 3 shows an indoor controller 300 and an outdoor controller 40.
0 is a block diagram mainly showing an electric system. The indoor control unit 300 has a built-in power relay 310 for turning on / off a main power supply. For example, a 100 V single-phase alternating current is supplied to the AC / DC converter 320 through the power relay 310.
, And converted into various predetermined DC voltages by an AC / DC converter 320, and supplied to the microcomputer 330 and the like.
An EEPROM that saves various data in the microcomputer 330
340 are connected. The 100 V single-phase alternating current supplied via the power relay 310 is connected to the power supply line 35.
0 is also supplied to the outdoor control unit 400.

In the outdoor control unit 400, after the supplied alternating current is applied to the noise filter 410, the alternating current is rectified by, for example, the voltage doubler rectifier circuit 420 and smoothed by the smoothing capacitor 430.
A predetermined DC voltage is generated. The generated DC current is supplied to the inverter module 450 via the shunt resistor 440. Then, three-phase power is generated by the inverter module 450 and supplied to the compressor 4. On the other hand, the output of the smoothing capacitor 430 is DC / DC
The converter 460 converts the voltage into a predetermined internal DC voltage and supplies the DC voltage to the microcomputer 470 and the like. An EEPROM 480 and a voltage detector 490 are connected to the microcomputer 470, and when a voltage drop is detected by the voltage detector 490, an interrupt process is performed, and the opening degree data and position data of the RAM are saved in the EEPROM 480.

The microcomputer 470 includes the inverter module 4
The operation of the compressor 4 is controlled by outputting a drive signal to 50. The ability of the compressor 4 to compress the refrigerant is controlled by the frequency (Hz) of the drive signal, and the higher the frequency (Hz), the higher the compression capacity. For example, 30
If Hz is the first predetermined capacity and 10 Hz is the second predetermined capacity, the pressure of the refrigerant is higher at the first predetermined capacity than at the second predetermined capacity. The microcomputer 470 is connected to the microcomputer 330 of the indoor control unit 300 via the communication line 360.
To perform data communication by performing serial communication with

The degree of opening of the electric expansion valve (throttle device) 10A is controlled by the control of the microcomputer 470, and the flow path switching valve 100 is switched by the pilot means 210 which operates according to the flow control of the electric expansion valve 10A. Controlled.

FIG. 1 is a principle block diagram of an embodiment of a control device for a refrigeration cycle according to the present invention. Each element of this principle block diagram corresponds to each element in FIGS. 2 and 3 or a combination of each element. are doing. In addition, in the refrigerating cycle A, FIG.
The same elements as those described above are denoted by the same reference numerals. The control device C indicated by a dashed line in FIG. 1 corresponds to the indoor control unit 300 and the outdoor control unit 400, and the processing unit C1 of the control device C
Is the microcomputer 330 of the indoor control unit 300 and the outdoor control unit 4
00 corresponds to the microcomputer 470. Also, the input unit C
Reference numeral 2 corresponds to the receiving unit 304 of the indoor unit or a manual switch (not shown), and the detecting unit C3 corresponds to the temperature sensors 302, 303, 402, 403, 405, the pressure sensors PC, PC ', and the like. Further, the power failure detection unit C4 corresponds to the voltage detector 490, and the semi-fixed storage unit C5
Corresponds to the EEPROMs 340 and 480. The expansion device drive unit C6, the use-side heat exchanger drive unit C7, the heat source-side heat exchanger drive unit C8, and the compressor drive unit C9 are units that function by executing a control program of each embodiment described later. Note that each of the driving units is the driver shown in FIG.

The diaphragm driving unit C6 outputs a control signal to a diaphragm driving source (for example, a stepping motor) 404, and controls the aperture of the diaphragm 10A via the diaphragm driving source 404. The use side heat exchanger drive unit C7 outputs a control signal to a use side heat exchanger drive source (for example, a fan motor) 301, and the use side heat exchanger drive source 301 drives the cross flow fan 91A according to the control signal. Then, the operation or stop is performed, and the heat exchange capacity of the use-side heat exchanger (indoor heat exchanger) 9A is controlled based on the rotation speed. The heat source side heat exchanger driving unit C8 outputs a control signal to a heat source side heat exchanger driving source (for example, a fan motor) 401, and the heat source side heat exchanger driving source 401 drives the fan 91B according to the control signal, While operating or stopping, the heat exchange capacity of the heat source side heat exchanger (outdoor heat exchanger) 9B is controlled by the rotation speed.
Further, the compressor driving unit C9 outputs a control signal to a compressor power source (for example, an inverter module and a motor) 450, and the compressor power source 450 drives the compressor 4, and the compressor 4 rotates forward and reverse. Rotation, start, stop, capacity switching, etc. are controlled. It goes without saying that the compressor power source is not limited to a motor, but may be an engine.

As described above, in the refrigeration cycle A, the flow rate of the refrigerant and the rate of change of the flow rate in the refrigeration cycle A are controlled by controlling the opening degree of the throttle of the expansion device (electric expansion valve) 10A. Further, by controlling the driving, stopping, and heat exchange capacity of the indoor heat exchanger 9A and the outdoor heat exchanger 9B, the pressure of the refrigerant in the indoor heat exchanger 9A, the outdoor heat exchanger 9B, and the refrigeration cycle A is controlled. You. Also,
By controlling the normal rotation, the reverse rotation, the start, the stop, and the performance switching of the compressor 4, the pressure and the pressure change rate of the refrigerant in the refrigeration cycle A, and the flow rate and the flow rate change rate of the refrigerant are controlled.

Then, by communicating or closing the pilot means 210 of the expansion device (electric expansion valve) 10A, the pressure, differential pressure, etc., inside the flow path switching valve 100 are controlled via the communication means (communication pipe). Thereby, in each embodiment of the flow path switching valve 100 described later, the non-electric power called the pressure is generated, and the flow path of the flow path switching valve 100 is switched. The refrigerating cycle is not limited to the illustrated heat pump type air conditioner, and it is needless to say that a heat pump type chiller unit, an engine driven type, a car air conditioner and the like are also included.

FIG. 4 is a diagram showing a signal and an operation flow of an embodiment of the refrigeration cycle control apparatus according to the present invention, in which a remote controller 500 or the like instructs a heating operation, a cooling operation, or the like, or switches an operation mode. As a result, the flow path switching valve 100
Is input to the control device C. Then, as a first step, the control device C performs “control of the aperture device”.
Output a signal for As a second step, a signal for "control of the compressor" or "control of the heat exchanger" is output. Next, as a result of the various controls, in a third step, physical quantities such as a refrigeration cycle pressure and a differential pressure necessary for operating the flow path switching valve are confirmed. Next, as a fourth step, a drive signal is output to the expansion device for “switching operation of the flow path switching valve”, and the switching operation is performed in the flow path switching valve 100 of each embodiment described later. Next, the fifth
In step (3), “flow control” is performed to control the flow rate.

Next, the electric expansion valve 10 as a fluid control valve
The embodiment A will be described. 5A is a cross-sectional view of the electric expansion valve 10A, FIG. 5B is a bottom view, and FIG. 5A is a cross-sectional view taken along the line AA of FIG. 5B. FIG. 6 is an enlarged sectional view of a main part of the electric expansion valve 10A. The motor-operated expansion valve 10 </ b> A has a rotor formed by a valve body 101, a shaft part 102 rotatably supported by a guide part 101-1 on the upper part of the valve body 101, and a permanent magnet 103 fixed around the upper part of the shaft part 102. Is configured.

A valve chamber 101A (see FIG. 7A) which forms a cylindrical space is formed in the center of the valve main body 101. The valve chamber 101A has a valve port 101a-1 and a valve port 101b-. 1 is opened, and the valve port portion 101a-1 is opened.
The primary port 101a communicated with the valve port 101b-
A fluid such as a refrigerant flows in or out of the secondary port 101b communicated with 1.

The shaft portion 102 is formed by covering a central shaft 102a made of stainless steel or the like with a synthetic resin such as nylon or PPS (polyphenylene sulfide), and a lower portion of the shaft portion 102 has a valve portion 102A (see FIG. 6 and FIG. 6). 7 (see FIG. 7) is disposed in the valve chamber 101A. The valve portion 102A is adjacent to the valve port portion 101a-1 communicating with the primary port 101a and the valve port portion 101b-1 communicating with the secondary port 101b. The cross-sectional shape of the valve portion 102A is constant in the axial direction, and a specific example of this shape is a cross-sectional view taken along the line BB in FIG.
(A). The flow characteristics when each of the cross-sectional shapes shown in these figures is adopted will be described later.

A lower cover 105 is fixed to the outer periphery of the guide portion 101-1 of the valve body 101 by brazing.
The closed case 106 of the stepping motor is fixed on the upper side. In addition, the electromagnetic coil 1
07 is provided,
In the case 106, the rotor constituted by the shaft portion 102 and the permanent magnet 103 is rotatably provided on the valve main body 101 as described above.

As shown in FIG. 5A, a step 103a is formed at a part of the lower end of the permanent magnet 103.
a functions as a stopper. On the other hand, a projection 105a is provided on the lower lid 105, and the projection 105a is
It functions as a stopper on the main body side provided integrally with the camera.

In the above configuration, when the electromagnetic coil 107 of the stator 108 is energized, the permanent magnet 103 rotates,
The shaft 102 also rotates according to the rotation of the permanent magnet 103.
When the shaft portion 102 rotates, the valve port portions 101a-1 and 101b- of the valve portion 102A according to the rotation angle of the shaft portion 102.
1 changes, and the valve port portions 101a-1 and 101a-1 change.
01b-1 and the valve port portions 101a-1, 101b-
The gap D (see FIG. 7) formed between the valve member 102 and the opposing peripheral surface of the valve portion 102A is changed by the rotation of the shaft portion 102 according to the cross-sectional shape perpendicular to the axis of the shaft portion 102 of the valve portion 102A. Therefore, the flow rate of a fluid such as a refrigerant can be controlled. For example, as shown in FIG.
If there is a gap D between the first port 101a and the valve section 102A, the primary port 101a and the secondary port 101b communicate with each other, and the refrigerant flows according to the width of the gap D. Also, as shown in FIG. 6, the valve port portions 101a-1 and 101b-1 and the valve portion 102
If there is no gap between the primary port 101a and the secondary port 10
1b is closed and no refrigerant flows.

A pilot valve 210 as pilot means is formed below the valve chamber 101A. The pilot valve 210 has a cylindrical valve body 211 aligned with the inner periphery of the valve chamber 101A, an S port 212 opened at the lower end of the valve chamber 101A, and a valve chamber 1 facing the periphery of the valve body 211A.
E port 213 and C port 21 formed in 01A
4, S port 212, E port 213, C port 21
4, the communication pipes 212a, 213a,
14a. In the flow path switching valve of the first and third embodiments described later, the C port 214 is used.
And a communication pipe 214a or a motor-operated expansion valve in which these are sealed, that is, a 2-port pilot valve is used. In the second embodiment, the S port 212 and the E port 21 are used.
3, C port 214, communication pipes 212a, 213a, 21
Since a three-port pilot valve provided with 4a is used, the description of this electric expansion valve will be made as a three-port configuration.

FIG. 8 is a top view (FIG. 8A) and a side view (FIG. 8B) of the valve body 211. The valve body 211 has a vertical hole 211a formed along the axis of a cylinder. At the same time, a valve body groove 211b communicating with the vertical hole 211a is formed on the side surface. A projection 211c is formed on the upper surface of the valve body 211 so as to be located above the valve body groove 211b.

As shown in FIG. 6, a pin 102a-1 projecting at right angles to the central axis 102a is formed at the lower end of the central axis 102a of the shaft 102. Also, the central axis 1
The lower end of 02a is fitted in the vertical hole 211a of the valve body 211. As a result, the valve body 211 is rotatably held below the valve chamber 101A. When the shaft 102 rotates, the pin 102a-1 moves the valve body 211 in accordance with the rotation position and the rotation position of the valve body 211. 6 abuts on the projection 211c (not shown in FIG. 6), and the valve body 211 is rotated.
And, depending on the rotation position of this valve body 211, the vertical hole 21
1a and S port 212 and E via valve body groove 211b.
The port 213 is in communication with the S port 212 and the C port 21 via the vertical hole 211a and the valve body groove 211b.
4 is selectively switched.

FIG. 9 is a view for explaining the relationship between the valve opening degree of the electric expansion valve 10A, that is, the rotation angle of the valve portion 102A, the rotation position of the valve body 211, and the communication / closed state of each port. FIG. 9A shows a change in the section BB in FIG. 5A, FIG. 9B shows a change in the section DD in FIG.
FIG. 9C shows a change in the EE section of FIG. Note that the numerical data (-8 ps, 0 ps, etc.) shown above the rotation angle (-36, 0 ps, etc.)
3 and the number of drive pulses from the reference position of the stepping motor constituted by the electromagnetic coil 107. Also, -3
The start-side stopper position at 6 ° and the end-side stopper position at 279 ° correspond to the step 10 of the permanent magnet 103 shown in FIG.
3a and the position regulated by the protrusion 105a of the lower lid 105.

First, at the position of -36 °, the primary port 101
a and each valve port portion (main port) 101 of the secondary port 101b
a-1 and 101b-1 are closed by the valve portion 102A,
The pin 102a-1 of the central shaft 102a pushes the projection 211c of the valve body 211 toward the E port 213, and the S port 212 and the E port 213 are connected via the valve body groove 211b of the valve body 211 and the vertical hole 211a. Communicated. Then C
Port 214 is closed. At the 0 ° position, the pin 102a-1 is rotated while the valve port portions 101a-1 and 101b-1 remain closed, but the valve body 211 is not rotated, and the S port 212 and the E port 213 are not rotated. Communication with the
The closed state of the C port 214 is maintained. This -36 °
In the range from 0 ° to 0 °, the E port 213 is connected.

Further, at the position where the angle becomes 243 ° from 0 ° through 135 °, the valve port portions 101a-1 and 101b-1
Are communicated with each other in accordance with the distance from the valve portion 102A, and the pins 102
a-1 is rotated, but the valve body 211 is not rotated,
The communication state between the port 212 and the E port 213 and the closed state of the C port 214 are maintained. That is, the range from 0 ° to 243 ° is a flow rate control range. The flow characteristics in this flow control region are as shown in FIG.

Between the position 243 ° and 9 ° (corresponding to 2 ps) and 279 °, the valve port 10
1a-1 and 101b-1 are almost fully opened, and pin 1
02a-1 pushes the projection 211c toward the C port 214, and the valve body groove 211b of the valve body 211 and the vertical hole 211
The S port 212 and the C port 214 are communicated via a. At this time, the E port 213 is closed. That is, the connection state of the C port 214 is in the range from 243 ° to 279 °.

FIG. 27 is a block diagram of a drive circuit for driving a stepping motor of the electric expansion valve 10A according to the embodiment, and FIGS. 28 to 30 are views showing examples of the drive circuit.
Although the stepping motor has a plurality of coils, FIGS. 27 to 30 do not show the circuit for one coil. Actually, as many drive circuits as shown in the figure other than the control unit or the microcomputer are provided corresponding to the coils.

The drive circuit of FIG. 27 corresponds to the drive device of the fluid control valve according to the third aspect. The control unit 400 controls the conduction / non-conduction means via the control terminal T1 by the internal control element 400a, and the electromagnetic coil 107 is energized by a DC power supply of + 12V or + 24V, for example.

The drive circuit shown in FIG. 28 includes a PNP transistor 61 as conduction / non-conduction means.
The base of the transistor 61 is connected to the output terminal T2 of the open collector (open output type) of the driver circuit 62. The driver circuit 62 is an open drain (open output type) of the control unit 400 such as a microcomputer.
Is connected to the output terminal T3. Then, conduction / non-conduction of the PNP transistor 61 is switched by a control signal (voltage signal) of the control unit 400, and conduction / non-conduction to the electromagnetic coil 107 is controlled.

The drive circuit shown in FIG. 29 uses the base of the PNP transistor 61 as the conducting / non-conducting means,
0 is connected to the terminal T4 of the open collector (open output type) of the NPN transistor 400b. Then, conduction / non-conduction of the PNP transistor 61 is switched by a control signal (current signal) from the NPN transistor 400b of the control unit 400, and conduction / non-conduction to the electromagnetic coil 107 is controlled.

The drive circuit of FIG. 30 includes a P-channel MOS-FET 63 as conduction / non-conduction means. The gate of the P-channel MOS-FET 63 is connected to an open drain (open output type) of the microcomputer (control unit) 400. Is connected to the output terminal T5 (output port).
The output terminal T5 is a drain terminal of the N-channel MOS-FET 400c of the microcomputer 400. Then, conduction / non-conduction of the P-channel MOS-FET 63 is switched by a control signal (voltage signal) of the microcomputer 400, and conduction / non-conduction to the electromagnetic coil 107 is controlled.

The above drive circuit is provided with the electric expansion valve 10.
The step A is for controlling the energization of the electromagnetic coil 107 of the stepping motor. For example, although different from the present invention, an electromagnetic coil having a conventional flow path switching valve provided in the flow path switching valve is widely used. The present invention can also be applied to a case where the energization / non-energization of the electromagnetic coil of the solenoid valve, the other electromagnetic coil, or the electromagnetic coil of another drive device is controlled.

Next, each embodiment of the flow path switching valve 100 and a specific control operation corresponding thereto will be described.

FIG. 11 is a view showing the flow path switching valve of the first example according to the embodiment together with the main part of the refrigeration cycle A, and FIG. 11 is a sectional view showing the operation state in the heating operation mode. . The flow path switching valve of the first embodiment has a cylindrical reversing valve main body 1 and plugs 2 and 3 are fixed to both ends thereof by welding. A discharge pipe 5 communicating with a discharge port of the compressor 4, a suction pipe 6 communicating with a suction port of the compressor 4, and two pipes 2 disposed on both sides of the suction pipe 6 on the peripheral surface of the reversing valve body 1. Are connected to each other,
Reference numeral 8 is connected to the two heat exchangers 9A and 9B.

The suction pipe 6 and the inner ends of the conduits 7 and 8 are connected to the three through holes 1 of the switching valve seat 11 fixed in the reversing valve body 1.
1a, 11b and 11c, a series of smooth surfaces 11d is formed inside the valve seat 11. Between the valve seat 11 and the plug 3 piston cylinder 12 (corresponding to the moving member) is provided to divide the reversing valve body 1 into a pressure transducer chamber R ₂ and the high pressure chamber R _1. The piston cylinder 12 is always biased to the high pressure chamber R ₁ direction by a compression spring 13.

A slide valve 27 having a communication lumen 27 a is provided on the valve seat 11, and the slide valve 27 is connected to the piston cylinder 12 by a connecting rod 28. The sheet 11 slides on the smooth surface 11d. Thereby, the piston cylinder 12
As shown in FIG. 12, the flow path switching valve in the cooling operation mode is shown in cross section, and the second portion where the piston cylinder 12 abuts on the plug 3 and, as shown in FIG. It is possible to move between the first position abutting the body 2.

Then, the first portion of the piston cylinder 12 (FIG. 1)
The slide valve 27 in 1), a suction pipe 6 communicates with the conduit 8 through the closed space S1 defining a high pressure chamber R ₁ by the smooth surface 11d of the lumen 27a and the valve seat 11,
In this state, the conduit 7, through the high pressure space S2 that is defined in the high pressure chamber R ₁ by the slide valve 27, the discharge pipe 5
Communicate with Further, a second portion of the piston cylinder 12 (FIG. 1)
In 2), the slide valve 27 allows the suction pipe 6 to communicate with the conduit 7 via the closed space S1, and in this state, the conduit 8 communicates with the discharge pipe 5 via the high-pressure space S2.

Although not shown, for example, the piston cylinder 12
In order to detect the position of the piston cylinder 12 and the connecting rod 28,
A permanent magnet is provided at the connecting portion with the magnet, and magnetic detecting means (for example, a Hall element) for detecting magnetism when the piston cylinder 12 moves to the second position (cooling) is provided on the other peripheral surface of the reversing valve main body 1. It is provided on the side. Here, when the piston cylinder 12 is at the first position (heating), no magnetism is detected. Thereby, the control device C can detect the position of the piston cylinder 12 (moving member), and the control device C can store the position data.

The aforementioned electric expansion valve 10A is connected between the two heat exchangers 9A and 9B. Note that the pilot valve 210 of the electric expansion valve 10A in the first embodiment is used.
Is a pilot two-way valve having no C port as described above. The communication pipe 212a of the S port 212 of the electric expansion valve 10A is connected by a pipe 15 to the suction pipe 6 of the flow path switching valve. On the other hand, the E of the electric expansion valve 10A
The communication pipe 213 a of the port 213 is connected to the plug 3 of the flow path switching valve by a pipe 14. With this configuration, when the opening of the electric expansion valve 10A is further opened by eight pulses from the fully open position, that is, 54 pulses, the pulse becomes 62 pulses, and the S port 212 and the E port 213 as shown in FIG.
Means "closed". When the opening degree of the electric expansion valve 10A is further closed by 8 pulses from the fully closed position, that is, 0 pulse, the pulse becomes -8 pulses, and the S port 212 and the E port 213 are "communicated" as shown in FIG. 9C. Becomes

Next, the operation (operation) of the flow path switching valve of the first embodiment having the above-described configuration will be described.

First, when the compressor 4 is stopped,
As shown in FIG. 11, the piston cylinder 12 urged by the compression spring 13 is located at the first position, and the suction pipe 6 and the conduit 8 communicate with each other, and the discharge pipe 5 and the conduit 7 communicate with each other. .

[0090] Here, the force applied from the pressure transducer chamber R ₂ side to the piston cylinder 12 and F1 (hereinafter this product is referred to as "F1"), a force applied from the high pressure chamber R ₁ side to the piston cylinder 12 F2 (hereinafter This is abbreviated as “F2”, the urging force of the compression spring 13 is Fs (hereinafter, abbreviated as “Fs”), and the static friction force between the smooth surface 11d of the valve seat 11 and the slide valve 27 is Ff. (Hereinafter abbreviated as “Ff”). Therefore, the piston cylinder 12 is
If the respective forces are balanced in the state of being located at the position, F2 = F1 + Fs + Ff holds. Where F
In order to discuss about 1, the following is transformed to F1 = F2-Fs-Ff.

When heating is started from the heating stopped state,
It is sufficient that F1> F2-Fs-Ff is satisfied. Therefore, the control device C sets the electric expansion valve 10A to a fully opened state or more by a predetermined procedure and sets the S port 212 and the E port 2
13 is closed. When the compressor 4 is started, the compressor 4 tries to suck the refrigerant through the suction pipe 6, while the refrigerant discharged from the compressor 4 flows through the discharge pipe 5 to the high pressure chamber R _1.
Flows into. In this state, the pressure of the pressure transducer chamber R ₂ is because it is cut off from the pressure in the suction pipe 6, F1 is not smaller, F1 ≒ F2 next, F1> F2-Fs-F
f eventually becomes 0> − (Fs + Ff). Therefore, the piston cylinder 12 continues to be located at the first position (FIG. 11) due to the resultant force of the urging force Fs of the compression spring 13 and the static friction force Ff. As a result, the refrigeration cycle A operates in the heating mode. At this time, the electric expansion valve 10A
Is controlled by the control device C to return to a predetermined opening degree which is a "flow rate control range" and to control the flow rate of the refrigerant.

Next, when the operation of the refrigeration cycle is completed,
The piston cylinder 12 remains at the first position due to the resultant force of the urging force Fs of the compression spring 13 and the static friction force Ff. When the operation of the refrigeration cycle A is restarted after a predetermined time, the heating mode is repeated.

When starting the cooling from the heating stop state,
It suffices if F1 <F2-Fs-Ff is satisfied. Therefore, the control device C sets the electric expansion valve 10A to a fully closed state or less by a predetermined procedure and sets the S port 212 and the E port 2
13 is "communicated". When the compressor 4 is started, the compressor 4 tries to suck the refrigerant through the suction pipe 6, while the refrigerant discharged from the compressor 4 flows through the discharge pipe 5 to the high pressure chamber R _1.
Flows into. In this state, the pressure of the pressure transducer chamber R ₂ is conducting the pressure in the suction pipe 6, F1 becomes small at the low pressure side, F2 is large in the high pressure side, F1«F
2 to obtain F1 <F2-Fs-Ff. Therefore, the piston cylinder 12 moves against the resultant force of the urging force Fs of the compression spring 13 and the static friction force Ff, and moves to the second position (FIG. 1).
2). As a result, the refrigeration cycle A
Will operate in the cooling mode. At this time,
The electric expansion valve 10A is returned by the control device C to a predetermined opening degree which is a "flow rate control range", and controls the flow rate of the refrigerant.

Next, when the operation of the refrigeration cycle is completed,
High pressure and low pressure are equalized to F1 ≒ F2, and piston cylinder 1
In No. 2, since the urging force Fs of the compression spring 13 is larger than the static friction force Ff, it moves from the second location to the first location. At this time, since the static friction force Ff also acts in the opposite direction, it is sufficient that F1> F2−Fs + Ff is satisfied.
Thereby, Fs> Ff is obtained. Then, when the operation of the refrigeration cycle is restarted after a predetermined time, the cooling mode is repeated.

When the heating is started after the cooling is stopped, the piston column 12 has already moved to the first position as described above, so that the column "0091" is used. When the cooling is started after the cooling is stopped, the operation is the same as the column “0093”. Since the flow path switching valve of this embodiment is a cantilever slide valve, it basically operates in two ways. When the refrigerating cycle is stopped, the flow path switching valve is always located at the first position by the urging force Fs of the compression spring 13. I have.

As described above, the heating operation mode in which the refrigerant discharged from the compressor 4 is supplied to the indoor heat exchanger 9A via the conduit 7 and the cooling operation mode in which the refrigerant discharged to the outdoor heat exchanger 9B via the conduit 8 are provided. Can be switched by controlling the opening degree of the electric expansion valve without using a power source such as an electromagnetic solenoid (electromagnetic coil) dedicated to the flow path switching valve, and the switching state can be maintained.

Next, the control operation of the control device C for performing the switching control of the flow path switching valve of the first embodiment will be described with reference to a flowchart. The processing unit C1 of the control device C controls the microcomputer 330 of the indoor control unit 300 and the microcomputer 470 of the outdoor control unit 400. These microcomputers 330 and 470 exchange data by serial communication. The control corresponding to each of the following flowcharts is jointly performed.

FIG. 21 is a flowchart of the main routine, which is common to the flow path switching valves of the first to third embodiments. This main routine is first started by a power-on reset of a first priority level, and is executed in step S11.
To perform "initialization processing-1" such as all clearing of the RAM, and then proceed to step S13. Also, the second operation is performed by resetting the watchdog timer or releasing the wait state (Wait).
At the priority level, a second start is performed. In step S12, "initialization process-2" such as partial clearing of the RAM is performed, and the flow advances to step S13.

In step S13, an initial setting process of the control device shown in FIG. 22 is performed. In step S14, an operation command input process for inputting an operation signal from the remote controller 500 or a switch is performed. Perform input processing for inputting physical quantities such as pressure, temperature, flow rate, voltage, current, electric frequency, or mechanical frequency involved. In step S16, input signal calculation, comparison, determination processing, and refrigeration cycle control conditions are performed. Overall processing such as determination is performed, and the process proceeds to step S17.

In step S17, it is determined whether or not the data is normal as a result of the processing. If the data is abnormal, it is determined in step S18 whether the degree of abnormality is such that the standby state (Wait) is required. If necessary, the standby state (Wai
t). If not necessary, the operation of the refrigeration cycle is stopped in step S19, and in step S101, the process waits for a predetermined time until restarting, and returns to step S14.

On the other hand, if the data is normal in step S17, it is determined in step S102 whether or not to start the refrigeration cycle. If not, the process returns to step S14, and if so, the process proceeds to step S103. In step S103, by each subroutine described later,
Functional component drive processing for driving compressors, electric expansion valves, heat exchanger motors, and the like according to each embodiment, and a flow path switching valve for detecting the position of a moving member (for example, a piston cylinder 12) of the flow path switching valve. Perform position detection processing. This step S
By the processing of the subroutine 103, the switching control of the flow path switching valve in each embodiment is performed.

Next, in step S104, it is determined whether or not the position data of the moving member of the flow path switching valve matches the command data. If not, the process proceeds to step S19. If not, the process proceeds to step S105. Various output processes such as display are performed, and the process proceeds to step S106. Step S106
Then, it is determined whether or not to continue the operation of the refrigeration cycle,
If it does not continue, the process proceeds to step S19, and if it does continue, it is determined in step S117 whether or not the command is a command to "switch the flow path". If the flow path is not switched, the process returns to step S14. If the flow path is switched, the compressor operation / stop processing is performed in step S108 according to each embodiment, and the process returns to step S14.

FIG. 22 is a flowchart of a subroutine of step S13. In step S21, EEPRO
The M valve opening data and position data are stored in RAM,
In step S22, the opening is “255” (FF in hexadecimal)
h), and if YES, the step S
In step 23, the valve is driven in the opening direction by 80 pulses, and step S24 is performed.
The valve is driven 70 pulses in the closing direction in step S25, the valve is driven eight pulses in the opening direction in step S25, and the opening degree data of the valve is stored in the RAM as 0 pulse in step S26. Then, in step S27, the valve opening data is read from the RAM to the EEPROM.
And the process proceeds to step S202. This control is executed at the time of the first power-on.

On the other hand, if the decision is NO in step S22, the flow advances to step S28 to determine whether or not the position data is the second location. If it is not the second location, the mode is the heating mode, so that the valve opening is set to fully open or more in step S29, and the process proceeds to step S202. If it is not the second location, the mode is set to the fully closed or less in step S201 because the cooling mode is set. Proceed to S202. Then, in step S202, other initialization processing of the control device is performed, and the process returns to the main routine.

FIG. 23 is a flowchart of an interrupt routine due to a voltage drop. When a voltage drop is detected and interrupt processing is started, at step S10, an RA is executed.
The M valve opening data and the position data are stored in the EEPROM, and the operation of the refrigeration cycle is stopped in step S20.
It is set to a standby state (Wait).

FIG. 24 is a flowchart of a subroutine (step S103 of the main routine) relating to the flow path switching valve of the first embodiment. First, in step S31, it is determined whether or not the command is a command to "switch the flow path". I do.
If it is not "switch the flow path", it is determined in step S32 whether or not the position data is the second position. If it is not the second position, the process proceeds to step S34. If it is the second position, the flow proceeds to step S33. The opening degree is set to be equal to or more than the full opening, and the process proceeds to step S34. In step S34, the compressor 4 is set to the second
Starting with a predetermined capacity (for example, 10 Hz), step S37
Proceed to. On the other hand, "switch the flow path" in step S31.
If so, in step S35, the opening degree of the expansion device 10A is set to be not more than fully closed, and in step S36, the compressor 4 is started at the first predetermined capacity (for example, 30 Hz), and the process proceeds to step S37. In step S37, the heat exchanger motor drive processing (normal processing) is performed. In step S38, the throttle device is returned to the predetermined opening after a predetermined time, and in step S39, the flow path switching valve position detection processing is performed. Return to.

FIG. 13 is an explanatory view showing a schematic configuration of a refrigeration cycle A to which the flow path switching valve of the second example according to the embodiment is applied. In FIG. 13, the flow path according to the first example of FIG. The same members and portions as the switching valve will be described with the same reference numerals as those given in FIG. The flow path switching valve of the second embodiment is a slide type four-way valve 43. As described above, the pilot valve 210 of the electric expansion valve 10A is a pilot three-way valve having an S port 212, an E port 213, and a C port 214. It is.

[0108] Of this, sliding the four-way valve 43, the second piston cylinder 12 'that defines a second pressure transducer chamber R ₅ facing the pressure transducer chamber R ₂ across the high pressure chamber R _1, the reversing valve body The slide valve 27 and the second piston cylinder 12 'are connected by a second connection rod 28' between the valve seat 11 and the plug body 2 in the inside 1. The second embodiment differs from the second embodiment in that the compression spring 13 for urging the piston cylinder 12 from the second position toward the first position is omitted.
The configuration is largely different from the flow path switching valve of the first embodiment shown in FIG.

In this slide type four-way valve 43,
Through hole 12 of stone tube 12₁Second through hole 12 similar to₁But
The second through-hole formed in the second piston cylinder 12 ′
12 ₁′, The high pressure chamber R₁And the second pressure conversion chamber R_FiveWhen
Is always in communication.

The suction pipe 6 connected to the suction port of the compressor 4 is connected to one end of a pipe 14s, the plug 2 is connected to one end of a pipe 14c from outside, and the plug 3 is connected to outside from the outside. One end of a pipe 14e is connected, and the other end of each of the pipes is
Communication pipe 212a of S port 212 of electric expansion valve 10A,
The communication pipe 213a of the E port 213 and the communication pipe 214a of the C port 214 are connected to each other. The electric expansion valve 10A is connected to two heat exchangers 9A and 9B via a primary port 101a and a secondary port 101b.

FIG. 13 shows the piston cylinder 12.
At the first position of the piston cylinder 12, the valve seat 3a of the plug 3
Conduit 14e and pressure conversion chamber R_TwoVice to communicate with
Valve 12_TwoIs provided on the second piston cylinder 12 ′.
Is a plug at a first position of the piston cylinder 12 shown in FIG.
The conduit 14c and the second pressure conversion chamber R are seated on the valve seat 2a of the body 2.
_FiveSecond valve 12 that shuts off_Two'Is provided.

At the second position of the piston cylinder 12 where the suction pipe 6 and the conduit 7 communicate with each other via the closed space S1 and the discharge pipe 5 and the conduit 8 communicate with each other via the high-pressure space S2, the auxiliary valve 12 is provided. ₂ is seated on the valve seat 3a of the plug 3 and the conduit 1
Blocking 4e and the pressure transducer chamber R _2, a second sub valve 12 ₂ 'communicates the conduit 14G and the second pressure transducer chamber R ₅ separated from the valve seat 2a of the stopper 2.

A permanent magnet M is disposed on the inner bottom of the second piston cylinder 12 ′, and a conduit 8 of the reversing valve main body 1 is provided.
A magnetic detecting means H (for example, a Hall element or the like) H is disposed at the outer peripheral bottom in the vicinity of. And the piston cylinder 12
When the second piston cylinder 12 '(moving member) is located at the first position, the magnetic field by the permanent magnet M is not detected by the magnetic detection means H, and the piston cylinder 12 and the second piston cylinder 12 are not detected.
Is located at the second position, the magnetic field from the permanent magnet M is detected by the magnetic detection means H. Thereby, the control device C can detect the positions of the piston cylinder 12 and the second piston cylinder 12 ', and the control device C can store the position data.

Next, the operation (operation) of the flow path switching valve of the second embodiment having the above-described configuration will be described.

Here, as described above, when the control device C drives the electric expansion valve 10A, and the opening degree of the valve is further opened by 8 pulses from the fully opened position 54 pulses, the pulse becomes 62 pulses.
As shown in (c), the S port 212 and the C port 214
And “communication” with S port 212 and E port 21
3 is "closed". When the valve opening is further closed by 8 pulses from the fully closed position 0 pulse, the pulse becomes -8 pulses, and the S port 212 and the E port 213 "communicate" as shown in FIG. The S port 212 and the C port 214 are in a “closed” state.

When heating is to be started after heating is stopped, first, when the compressor 4 is stopped, the piston cylinder 12 and the second piston cylinder 12 'of the slide type four-way valve 43 are
The position at the time of operation of the compressor 4 immediately before is maintained as it is, and if it is at the first position during operation, it is maintained at the first position, and if it is at the second position, it is maintained at the second position. This is the same also when performing cooling start from cooling stop.

Here, as shown in FIG. 13, when the compressor 4 stops operating while the refrigerating cycle A is in the heating mode, the piston cylinder 12 of the slide type four-way valve 43 is
3 does not move while being located at the first position. Also, the valve body 211 of the pilot valve 210 does not move unless the electric expansion valve 10A is set to an opening degree of not more than fully closed (0 to -8 pulse range). The pilot valve 210 communicates with the plug 2 via the suction pipe 6 via the pipes 14s and 14c, and
The plug 4s and the plug 3 via the pipe 14e are closed. In this state, the valve seat 2a of the plug body 2 side is closed by the auxiliary valve 12 ₂ ', the valve seat 3a of the stopper 3 is opened by the auxiliary valve 12 _2.

In this state, when the compressor 4 starts operating,
The high-pressure refrigerant from the compressor 4 flows into the high-pressure space S2 of the slide-type four-way valve 43 via the discharge pipe 5, and further flows into the indoor heat exchanger 9A from the conduit 7, and the refrigerant flows into the electric expansion valve 10A and the outdoor The refrigerant flows into the closed space S1 from the conduit 8 via the heat exchanger 9B, and returns to the suction port of the compressor 4 via the suction pipe 6, so that the refrigeration cycle A is in the heating mode.

At this time, since the pressure conversion chamber R ₂ is shut off from the low pressure side and the vicinity of the plug 2 side of the second pressure conversion chamber R ₅ is on the low pressure side, the piston cylinder 12 and the second piston cylinder 12 are closed. 'Continues to be located at the first location. Then, predetermined control (operation) of the refrigeration cycle A is performed.

Here, when the compressor 4 is stopped, the operation becomes the same as described above (column “0117”). Then, the above heating mode state is repeated according to the operation command.

When starting the cooling from the stop of the heating, first, when the compressor 4 is stopped, the piston cylinder 12 and the second piston cylinder 12 'of the slide type four-way valve 43 are
Since the position at the time of the operation of the compressor 4 immediately before is maintained as it is, it is at the first position. Here, before the compressor 4 is started, the opening degree of the electric expansion valve 10A is further closed by 8 pulses from the fully closed position 0 pulse for 8 pulses, resulting in -8 pulses, so that the S port 212 and the E port 213 "communicate", S port 2
12 and the C port 214 are in the “closed” state. Here, as long as the valve body 211 of the pilot valve 210 does not open the electric expansion valve 10A more than fully open (54 to 62 pulse range),
Do not move.

The pilot valve 210 is connected to the suction pipe 6
The pipe 3 communicates with the plug 3 via the pipe 14s and the pipe 14e, and the plug 2 via the pipe 14s and the pipe 14c is closed. In this state, the valve seat 2a on the plug 2 side is still in the auxiliary valve 12a.
Is closed by ₂ ', the valve seat 3a of the stopper 3 is opened by the auxiliary valve 12 _2.

When the compressor 4 starts operating in this state,
Pressure transducer chamber R ₂ decreases the pressure in communication with the low pressure side,
The second pressure transducer chamber R ₅ the pressure increases because it is cut off from the low pressure side. Thus, the high-pressure space S2 and the pressure conversion chamber R ₂
And the piston cylinder 12 and the second piston cylinder 12 'move from the first location to the second location. Thereafter, the opening of the electric expansion valve 10A is returned to the predetermined opening, and the predetermined control is performed.

As a result, the high-pressure refrigerant from the compressor 4 flows through the discharge pipe 5 into the high-pressure space S2 of the slide type four-way valve 43, and further flows from the conduit 8 into the outdoor heat exchanger 9B. The refrigerant flows into the closed space S1 from the conduit 7 via the electric expansion valve 10A and the indoor heat exchanger 9A, and returns to the suction port of the compressor 4 via the suction pipe 6, so that the refrigeration cycle A is in the cooling mode.

The case where the cooling start is performed from the cooling stop is the same as the case where the heating start is performed from the heating stop. The case where the heating start is performed from the cooling stop is the case where the cooling start is performed from the heating stop. Is the same as In these cases, it goes without saying that the respective members and portions of the slide type four-way valve 43 and the port of the pilot valve 210 correspond to each other in reverse.

As described above, according to the second embodiment, the refrigerant in the high-pressure space S2 and the pressure conversion chamber R ₂ or the second pressure conversion chamber R
_The sliding four-way valve 43 for switching the piston cylinder 12 and the second piston cylinder 12 ′ between the first position and the second position by the pressure difference between the refrigerant in the suction pipe 5 and the suction pipe while the compressor 4 is stopped. It has a structure for switching operation of the 6 communicating destination using a pilot valve 210 for switching between the pressure transducer chamber R ₂ and the second pressure transducer chamber R _5.

Therefore, the heating mode in which the refrigerant discharged from the compressor 4 is supplied to the indoor heat exchanger 9A via the conduit 7;
Controlling the cooling mode supplied to the outdoor heat exchanger 9B via the conduit 8 by controlling the pilot port of the electric expansion valve 10A without using a drive source dedicated to the flow path switching valve such as an electromagnetic solenoid (electromagnetic coil). Thus, the flow path switching valve can be switched, and the switching state can be maintained.

The slide type four-way valve of the second embodiment is described.
An operation equation applied to 43 will be described. Pressure conversion
Room R_TwoThe force applied to the piston cylinder 12 from the side is F1,
Pressure chamber R₁The force applied to the piston cylinder 12 from the side is F2
You. Similarly, the second pressure conversion chamber R _FiveThe second piston cylinder from the side
The force applied to 12 ′ is F1 ′ and the high pressure chamber R₁Second from the side
The force applied to the piston cylinder 12 'is defined as F2'. And
The smooth surface 11d (see FIG. 13) of the valve seat 11 and the slide
The static friction force between the drive valves 27 is defined as Ff.

When moving from the first location (heating) to the second location (cooling), it is sufficient that F1 '+ F2>F2' + F1 + Ff is satisfied. F1 <F
1'-F2 '+ F2-Ff. When starting the compressor 4, 'by the action of, F1' hole 12 ₁ since a = F2 ', the F1 <F2-Ff. Here, the high pressure chamber R ₁ is high, the pressure transducer chamber R ₂ becomes because the low pressure F1 <F2, also because it is F2»Ff, so that the move to the second location. When the move is completed, the sub valve 12 ₂ is closed, but the F1 = F2, continuously positioned in the second location by static friction.

Stop at the second location and start again at the second location
When the through hole 12₁And through hole 12 ₁By the action of ´
Since F1 '= F2' and F1 = F2, F1 <F1 '
-F2 '+ F2-(-Ff), that is, 0 <Ff
Therefore, the position at the second position is maintained by the static friction force.
You.

When moving from the second location to the first location,
It is sufficient that F2 '+ F1>F1' + F2 + Ff is satisfied.
When F1 'is rearranged, F1'<F2'+ F1-F
2-Ff. When starting the compressor 4, by the action of the hole 12 _1, since the F1 = F2, F1 '<F2'-
Ff. Here, the high pressure chamber R ₁ is a high pressure, the second pressure transducer chamber R ₅ becomes because the low pressure F1 '<F2', also F
Since 2′≫Ff, it moves to the first location. When the movement is completed, the auxiliary valve 12 ₂ ′ is closed,
Although F1 '= F2', the static friction force acts in the opposite direction, so that (-Ff). Therefore, F1 ′ <F2′−
(−Ff), that is, 0 <Ff, and the piston cylinder 12 and the second piston cylinder 12 ′ continue to be located at the first position by the static friction force.

Stop at the first location and start again at the first location
When the through hole 12₁And through hole 12 ₁By the action of ´
Since F1 ′ = F2 ′ and F1 = F2, F1 ′ <F
2 '+ F1-F2-(-Ff), that is, 0 <Ff
Therefore, to maintain the position at the first place by the static friction force
Become.

FIG. 25 is a flowchart of a subroutine (step S103 of the main routine) relating to the flow path switching valve of the second embodiment, and FIG. 21 shows the main routine. First, in step S41, it is determined whether or not the command is a command to “switch the flow path”. If it is not "switch the flow path", it is determined in step S42 whether or not the position data is the second location.
The flow proceeds to 44, and if it is the second position, the opening degree of the expansion device 10A is set to the full opening or more in step S43, and the flow proceeds to step S48. In step S44, the compressor 4 is started at the fourth predetermined capacity (for example, 10 Hz), and in step S45, a drive process (normal process) of the heat exchanger motor is performed.
Go to 02.

On the other hand, if "switch the flow path" in step S41, it is determined in step S46 whether or not the position data is the first location.
The process proceeds to step S44, and if it is the first position, the opening degree of the expansion device 10A is set to the fully closed position or less in step S47, and the process proceeds to step S48. In step S48, the compressor 4 is started at the third predetermined capacity (for example, 30 Hz), and in step S49, a driving process (normal process) of the heat exchanger motor is performed.
In step S402, the opening degree is returned to a predetermined degree after a predetermined time, and step S402 is performed.
Proceed to. In step S402, drive processing of the expansion device 10A is performed, and in step S403, position detection processing of the flow path switching valve is performed, and the process returns to the main routine.

The flow path switching valve of the first and second embodiments is a slide type four-way valve. Next, a rotary type switching operation for switching the flow path by rotation of a main valve body inside the housing. A third embodiment in which the present invention is applied to a flow path switching valve will be described.

First, as shown in FIG. 1, a refrigeration cycle A is constituted by a rotary type flow switching valve (four-way valve) in the same manner as a slide type flow switching valve (four-way valve). As shown in FIGS. 2, 3, and 13, pressure detecting means, current detecting means, temperature detecting means, magnetic detecting means, and the like are used as means for detecting the switching position of the flow path switching valve. In a refrigeration cycle A to which the flow path switching valve of the embodiment is applied, an example in which a pressure detecting means is used will be described.

FIG. 14 is an explanatory view schematically showing a refrigeration cycle A to which the flow path switching valve of the third example according to the embodiment is applied. In the refrigeration cycle A, the same elements as those in FIG. I have. In FIG. 14, the indoor heat exchanger 9
A and a pressure sensor Pc ′ between the outdoor heat exchanger 9B and the flow path switching valve 50.
Is interposed.

In FIG. 14, the refrigeration cycle A in which the flow path in the heating mode is indicated by a solid line and the flow path in the cooling mode is indicated by a broken line is a refrigeration cycle A in which the high-pressure refrigerant discharged from the compressor 4 is introduced and the accumulator 200. And the introduction source of the refrigerant sucked into the compressor 4 through the rotary four-way valve 50.
Is configured to switch from one of the indoor heat exchanger 9A and the outdoor heat exchanger 9B to the other, and the electric expansion valve 10A is interposed between the indoor heat exchanger 9A and the indoor heat exchanger 9B. Has been established. The pilot valve 210 of the electric expansion valve 10A is connected to the rotary four-way valve 50. The electric expansion valve 10A in the third embodiment.
Is a pilot two-way valve not provided with a C port as described above.

In the following description, the rotary four-way valve 5
0, the conduit (discharge pipe viewed from the compressor 4 side) connected to the discharge port (high pressure side) of the compressor 4 is connected to the “D joint pipe 110”.
D ”, the conduit (the suction pipe viewed from the compressor 4 side) connected to the accumulator 200 (the low pressure side) is connected to the“ S joint pipe 110 ”.
S ”, the conduit connected to the indoor heat exchanger 9A is“ E joint pipe 110E ”, and the conduit connected to the outdoor heat exchanger 9B is“ C
Joint pipe 110C ".

FIG. 15 is a sectional view of the rotary four-way valve 50 and the pilot valve 210 according to the third embodiment, and FIG. 16 is a sectional view showing a state where the main valve body 112 of the rotary four-way valve 50 is raised. Note that, in FIGS. 15 and 16 and the following drawings, hatched lines indicating cross sections are omitted as appropriate for easy understanding. The rotary four-way valve 50 includes a cylindrical valve housing 111, a substantially cylindrical main valve body 112, a housing upper lid 113 covering an upper part of the valve housing 111, a main valve seat 114 attached to a lower part of the valve housing 111, A central shaft 115 erected at the center of the valve seat 114, the D-joint tube 1 described with reference to FIG.
10D, S fitting pipe 110S, E fitting pipe 110E and C
The joint pipe 110C is configured as a main part. 15 and 16 are cross-sectional views as viewed from the C joint pipe 110C side.
C has not appeared.

The main valve body 112 is housed in the valve housing 111, the space between the valve housing 111 and the housing upper lid 113 is sealed through a packing 111a, and the space between the valve housing 111 and the main valve seat 114 is through a packing 111b. And sealed. The main valve body 112 is rotatably supported on the center shaft 115 by a through hole 112a at the center of the main valve 112A, whereby the main valve body 112 is rotatable around the center shaft 115 inside the valve housing 111, It is movable in the direction of the rotation axis (vertical direction in FIG. 15). further,
A main valve body spring 116 fitted on the central shaft 115 is disposed between the housing upper cover 113 and the main valve body 112, and the main valve body 112 is moved by the main valve body spring 116. 113. A piston ring 11 for sealing between the upper outer periphery of the main valve body 112 and the inner peripheral surface of the housing 111 is provided.
2b is provided.

FIG. 18 is an enlarged sectional view of the main valve body 112 and the central shaft 115 and a partial plan sectional view thereof. FIG. 18B is a sectional view taken along the line CC of FIG. 18A. The figure shows a state in which the main valve body 112 has risen. Central axis 115
The portion where the main valve body 112 slides is a grooved rod 115R. Further, four balls 112 are provided at positions 90 ° apart around the rotation axis in the through hole 112a of the main valve 112A.
The ball 112c is disposed in the guide groove 115a of the grooved rod 115R. The ball 112c is attached by a retainer 112d fixed to the upper end of the main valve 112A, and the ball 112c is moved with respect to the main valve 112A and the retainer 112d in the rotation direction and the vertical direction of the main valve body 112. Although fixed, the ball 112c itself is rotatable.

FIG. 19 is an exploded view of the outer peripheral side surface of the grooved rod 115R. The guide groove 115a is located at a position separated by 90 ° in the circumferential direction of the center shaft 115 (the main valve seat 114R).
Side) has a concave vertical groove 115b. Above each vertical groove 115b, there is a stopper 115c which is depressed upward at a position separated by 90 ° in the circumferential direction. Here, the position of the vertical groove 115b is changed to “0 °, 90 °, 180 °”.
°, 270 °, 360 ° (= 0 °) ”(that is, when the position of the stopper 115c is“ 45 °, 135 °, 225 °,
315 ° ”), 0 ° → 90 ° → 180 ° → 270 °
→ The direction of 360 ° (= 0 °) is called “rotation direction”. The adjacent stopper portions 115c, 115c are connected to each other by a first guide slope 115d that is inclined upward in the rotation direction. In addition, the upper ends of the adjacent vertical grooves 115b, 115b are connected by a second guide slope 115e inclined downward in the rotation direction.

With the above configuration, when the main valve body 112 is seated on the main valve seat 114, the ball 112c is
15b, the main valve body 112 rotates 90 ° in the rotation direction by moving up and down with respect to the central axis 115. That is, as shown in FIG.
c is located at the position (a) in the vertical groove 115b, and the main valve body 11
When the ball 2c moves upward, the ball 112c separates from the vertical groove 115b and comes into contact with the first guide slope 115d at the position (b), and the ball 112c exerts a reaction force from the first guide slope 115d by a force moving further upward. As a result, the ball 112c is moved to the first guide slope 115d by its rotation direction component.
And reaches the position (c) of the stopper 115c. Thereby, the main valve body 112 is prevented from moving upward, and the main valve body 112 is at the top dead center position. During this time, the main valve body 112 is rotated by 45 °.

Next, when the main valve body 112 moves downward,
The ball 112c reaches the position (d) of the second guide slope 115e from the stopper portion 115c, and is further guided by the second guide slope 115e by a force moving downward, so that the ball 112c is moved to the position (e) of the vertical groove 115b. Reach the position. As a result, the main valve body 112 is seated on the main valve seat 114. During this time, the main valve body 112 is further rotated by 45 °, and is rotated 90 ° by one vertical movement. Thus, the main valve body 11
2 is a rotation angle of 0 °, 90 °, 180 °, 270 °
The main valve seat 114 is seated at the rotational position. The rotation positions at the rotation angles of 0 ° and 180 ° are the first rotation position, and the rotation positions at the rotation angles of 90 ° and 270 ° are the second rotation position.

FIG. 17 is a plan sectional view and a longitudinal sectional view for explaining a change in the rotational position of the main valve body 112.
17 (A) and FIG. 17 (B) are sectional views taken along the line AA of FIG.
FIG. 17 (C) is a sectional view taken along the line BB of FIG. 16. FIG.
17D is a sectional view taken along the line DD in FIG. 17C, and FIG. 17E is a sectional view taken along the line EE in FIG. 17C. Note that FIG.
(A), (B) and (C) correspond to the rotational positions of 0 °, 90 ° and 45 °, respectively, but the rotational positions are 180 ° and 270 °.
And 225 °, the same figure is used.
The rotation positions of 270 ° and 225 ° are indicated by reference numerals in parentheses.

As shown in FIG. 17, the main valve seat 114 has the first switching port 12 to which the E joint pipe 110E is connected.
0e (in FIG. 15 and FIG. 16, not visible behind the central shaft 115), and the second switching port 120c to which the C joint pipe 110C is connected (in FIG. 15 and FIG. (Not visible) are respectively provided at positions facing each other across the center of the main valve seat 114. Further, the low pressure side port 12 to which the S-joint pipe 110S is connected at a position shifted by 90 ° in the circumferential direction of the main valve seat 114 from the first and second switching ports 120e and 120c.
0s, high pressure side port 12 to which D joint pipe 110D is connected
0d are respectively provided.

On the end face of the main valve 112A on the side of the main valve seat 114, two substantially semi-circular connecting grooves 112e and 112f are formed independently of each other. At 180 ° (or 180 °), as shown in FIG. 17A, the communication groove 112e (or 112f) connects the high-pressure side port 120d and the first switching port 120e with each other, and the communication groove 112f (or 112
e), the low pressure side port 120s and the second switching port 12
0c is communicatively connected. Thereby, a circulation path in the heating operation mode is formed.

On the other hand, the second rotation position 90 of the main valve body 112
At (° or 270 °), as shown in FIG. 17B, the communication groove 112e (or 112f) connects the high pressure side port 120d and the second switching port 120c with each other, and the communication groove 112f (or 112e) connects the low pressure side port 120s and the first switching port 120e in communication. Thereby, a circulation path in the cooling operation mode is formed.

Note that, as shown in FIG.
A partition plate 112g is provided between the communication grooves 112e and 112f of A.
Is built in, and the partition plate 112g is provided with a spring 11 for the partition plate.
2h (FIGS. 17 (D) and 17 (E)), it is urged toward the main valve seat 114 side. As a result, the main valve body 112 is
4, the partition plate 112g is in contact with the main valve seat 114 like the main valve body 112 by the urging force of the partition plate spring 112h. Is lifted from the main valve seat 114, the partition plate spring 112h is extended, and the partition plate 112g is moved from the main valve seat 114.
Will remain in contact. Thereby, even when the main valve body 112 is lifted, the two communication grooves 11 of the main valve 112A are provided.
2e and 112f are partitioned from each other. The elastic force of the partition plate spring 112h is negligible compared to the elastic force of the main valve body spring 116.
The effect of 12h on the vertical movement of the main valve body 112 can be ignored.

The relative positional relationship between the main valve seat 114 and the central shaft 115 in the rotational direction is determined by the first switching port 120e, the second switching port 120c, the low pressure side port 120s, and the high pressure side port 120d and the guide groove 115a. Vertical groove 115b
However, as shown in FIG. 18, the positioning is performed at the time of assembling by the rotary positioning ball 114a disposed at the contact point between the center shaft 115 and the main valve seat 114, as shown in FIG. You.

[0152] As shown in FIG.
3, the pilot valve 210 of the electric expansion valve 10A
A pipe 130e connected to the E port 213 of the pilot valve extends through the pipe 130e, and a pipe 130s connected to the S port 212 of the pilot valve 210 extends through the S joint pipe 110S.

Then, by driving the electric expansion valve 10A,
E port 213 and S port 212 of pilot valve 210
Is in the "communication" state, in the rotary four-way valve 50, the space R1 surrounded by the valve housing 111, the housing upper lid 113, and the main valve body 112 communicates with the S joint pipe 110S connected to the low pressure side.

Next, the operation of the rotary four-way valve 50 of the third embodiment will be described.

In the stopped state, first, when the compressor 4 is stopped, the main valve body 112 is brought into contact with the main valve seat 114 by the urging force of the main valve body spring 116 as shown in FIG. I have. At this time, the rotation angle of the grooved rod 115R of the central shaft 115 is 0 ° (or 180 °), and the main valve body 112
And the main valve seat 114 are in the position in the heating operation mode.

When the heating is started from the stop state, the E port 213 and the S port 212 of the pilot valve 210 are in a "closed" state (hereinafter, the pilot valve 210 is in a closed state). When the operation of the compressor 4 is started, D
High-pressure refrigerant is supplied from the joint pipe 110D into the communication groove 112e of the main valve 112A via the high-pressure port 120d.
Here, a narrow groove through which a small amount of high-pressure refrigerant passes is formed at a contact portion between the main valve 112A and the main valve seat 114, and the high-pressure refrigerant in the communication groove 112e is supplied to the main valve 112A.
A small amount flows into the space R1 from the gap between the valve shaft 111 and the gap between the main valve 112A and the valve housing 111. Since the pilot valve 210 is in a closed state, the pressure in the space R1 becomes high, and the main valve body 112 is seated on the main valve seat 114 with a force that is combined with the urging force of the main valve body spring 116. Thus, the refrigeration cycle enters the heating operation mode.

When the cooling is started from the stop state, the E port 213 and the S port 212 of the pilot valve 210 are set in the "communication" state (hereinafter, the pilot valve 210 is in the communication state). When the operation of the compressor 4 is started, D
High-pressure refrigerant is supplied from the joint pipe 110D into the communication groove 112e of the main valve body 112 via the high-pressure side port 120d, and this high-pressure refrigerant flows into the space R1 although slightly, as described above. However, the pilot valve 210 is in a communicating state,
Since the space R1 communicates with the S-joint pipe 110S on the low pressure side, the pressure in the space R1 is low. Thereby, the main valve body 1
Numeral 12 floats up against the urging force of the main valve body spring 116, and the ball 112c of the main valve body 112 moves as shown in (a) → (b) → (c) of FIG.
The position becomes the position of 15c, and becomes the position of the top dead center rotated by 45 ° as shown in FIGS. 16 and 17C.

Here, the pilot valve 210 is closed. As a result, the high-pressure refrigerant in the communication groove 112e flows into the space R1 although slightly in the same manner as described above, so that the pressure in the space R1 becomes high, and the main valve is pressed by the force combined with the urging force of the main valve element spring 116. The body 112 is moved toward the main valve seat 114. At this time, the ball 112c of the main valve body 112 moves as shown in FIG. 20 (c) → (d) → (e), and the main valve body 112 is rotated by 90 ° to the main valve seat 114.
To sit down. As a result, the refrigeration cycle enters the cooling operation mode.

In any of the heating operation mode and the cooling operation mode, the pilot valve 210 is in operation.
Is in a closed state. Therefore, the pilot valve 2
The operation mode can be switched while the compressor 4 is operating while the compressor 4 is operating, by setting the state 10 to the communication state and then setting the state to the closed state.

Further, in the third embodiment, the differential pressure generated by the refrigerant flow by the compressor 4 and the communication / closure of the pilot valve 210 and the main valve body interposed between the housing upper lid 113 and the main valve body 112 The main valve body 112 is moved in the direction of approaching / separating from the main valve seat 114 by using the biasing force of the spring 116 for use, and the plurality of balls 112c of the main valve body 112 follow the grooved rod 115R. By moving the main valve body 112 with respect to the main valve seat 114, the main valve body 112 is moved between a first rotation position (heating) and a second rotation position (cooling). It has a configuration.

Therefore, the flow path of the refrigeration cycle can be switched without using an electromagnetic solenoid (electromagnetic coil) for directly driving the main valve body, and the switching state can be maintained.

The rotary four-way valve 50 according to the third embodiment described above has a hole in the center of the main valve body 112 and a grooved rod 115R provided with a central shaft 115 to form the main valve body 112.
The guide valve is provided on the inner peripheral surface of the valve housing 111 so that the main valve body 11 can be rotated.
Needless to say, a ball or the like may be provided on the outer peripheral surface of 2 and the ball may be moved along the guide groove to rotate the main valve body 112.

Incidentally, the rotary four-way valve 5 of the third embodiment is described.
An operation equation applied to 0 will be described. Upper lid 113
The force applied to the main valve body 112 from the side is defined as F1 and the valve seat 114
The force applied to the main valve body 112 from the side is F2. The biasing force of the main valve body spring 116 is Fs, and the static friction force between the main valve body 112 and the inner peripheral surface of the valve housing 111 and the static friction force between the ball 112c and the grooved rod 115R. Are synthesized and considered as Ff.

When moving from the first location (heating) to the second location (cooling), first, F1 <F2-Fs-Ff may be satisfied in order to raise the main valve body 112. When the compressor 4 is started, since the pilot valve 210 is in communication,
The pressure in the space R1 becomes low, F1≪F2, and the main valve body 1
12 moves to the top dead center (45 °) of the grooved rod 115R. Here, assuming that the area of the main valve body 112 is α, (F1−F2) = α × ΔP (negative differential pressure of Pd and Ps) is much smaller than − (Fs + Ff), so that it is located at the top dead center. I do.

Next, consider a case where the pilot valve 210 is closed after a predetermined time and the main valve body 112 is seated. In this case, it is sufficient that F1 + Fs> F2 + Ff is satisfied. F1
Becomes larger, F1 = F2, and Fs> Ff, so that the main valve body 112 is seated on the valve seat 114. And it continues to be in the cooling mode.

To stop at the second location and restart at the second location, start the compressor 4 and the pilot valve 210
Is closed, F1> F2-Fs-Ff may be satisfied. Since the pressure in the space R1 becomes high and F1 = F2, eventually, 0> − (Fs + Ff), and the space R1 cannot move. In this way, the main valve body 112 continues to be located at the second position.

When moving from the second location to the first location,
Except that the rotation angle has moved by 90 °, it is the same as the movement from the first location to the second location. When stopping at the first location and restarting at the first location, the rotation angle is 90 °
Apart from moving, it is the same as stopping at the second location and starting again at the second location.

FIG. 26 is a flowchart of a subroutine (step S103 of the main routine) relating to the flow path switching valve of the third embodiment, and FIG. 21 shows the main routine. First, in step S51, it is determined whether or not the command is a command to “switch the flow path”. If it is not "switch the flow path", it is determined in step S52 whether or not the position data is the second location.
In step S53, the compressor 4 is started at a fifth predetermined capacity (for example, 30 Hz) at step S53, the opening degree of the expansion device 10A is set to be not more than fully closed at step S54, and the heat exchanger motor is set at step S55. Is performed (normal processing), and the process proceeds to step S56. In step S56, the opening degree of the expansion device 10A is set to the full opening or more after the first predetermined time, and in step S57, the expansion device 10A is
The opening of A is returned to a predetermined opening. Then, step S58
To move the position data from the second location to the first location, or
Rewrite from the first location to the second location, and proceed to step S503.

On the other hand, if "switch the flow path" in step S51, if the position data is the first location in step S59, the process proceeds to step S53 because the previous time was heating, and if not, the process proceeds to step S53. Since the air conditioner has been cooled, the process proceeds to step S501. In step S501, the compressor 4 is started at the sixth predetermined capacity (for example, 10 Hz), and
At step 502, a heat exchanger motor driving process (normal process) is performed, and the process proceeds to step S503. Then, step S50
In S3, a driving process of the aperture device 10A is performed, and in step S5
At 04, the position of the flow path switching valve is detected, and the process returns to the main routine.

[0170]

According to the refrigeration cycle control device of the first aspect, the fluid control valve such as the electric expansion valve and the control valve such as the flow path switching valve can be arranged separately, and the fluid can be controlled. Since the generated non-electric power is used, a simple structure can be achieved without a mechanical transmission device.

According to the refrigeration cycle control device of the second aspect, the same effect as that of the first aspect can be obtained, and only by controlling the opening degree of the fluid control valve to the fully open state or the fully closed state, Since the flow path switching valve is switched, the control process can be significantly simplified. Also, EEPRO
M can be configured so that writing is not performed frequently.

According to the third aspect of the present invention, there is provided a fluid control valve driving device, wherein a positive electrode of a power supply for supplying non-AC power and a driving unit such as an electromagnetic coil for driving the fluid control valve are provided. / Since the control unit controls the non-conducting means, a drive with a small remaining voltage can be performed at the time of conducting by a simple (circuit) configuration.
A power saving effect is obtained.

According to the fluid control valve driving device of the fourth aspect, the same operation and effect as those of the third aspect can be obtained by the transistor configured as the open output type.

According to a fifth aspect of the present invention, a PNP transistor or a P-channel MOS-FE is provided.
By T, the same function and effect as in claim 3 can be obtained.

According to the fluid control valve of the sixth aspect, the first aspect is provided.
Similarly to the above, a fluid control valve such as an electric expansion valve and a control valve such as a flow path switching valve can be arranged separately, and a simple structure can be achieved without a mechanical transmission device.

According to the fluid control valve of claim 7, claim 6
In addition to the same effects as described above, the opening control range of the fluid control valve for controlling the flow rate is separated by the flow control range and the switching range of the pilot means, so that the control process can be simplified.

According to the fluid control valve of claim 8, claim 6 is provided.
Or 7 and the control valve such as the flow path switching valve can be switched by the pilot means. Therefore, for example, any type of flow path switching, such as a double-sided slide valve, a cantilever slide valve, or a rotary valve, is provided. It can also be used for valves, greatly improving usability.

According to the fluid control valve of the ninth aspect, the same effect as that of the sixth, seventh or eighth aspect is obtained, and the non-electric power generated by the fluid is supplied to the flow path switching valve via the valve port. And so on, and can be used for any type of flow path switching valve, for example, a double-sided slide valve, a cantilevered slide valve, or a rotary valve, and the usability is remarkably improved.

According to the fluid control valve of the tenth aspect, the same effect as that of the sixth, seventh, eighth or ninth aspect can be obtained.
When the present invention is applied to, for example, a cantilever slide type or double-sided slide type flow path switching valve having a sliding type switching valve body, the usability is remarkably improved.

According to the fluid control valve of the eleventh aspect, the same effect as that of the tenth aspect can be obtained by applying the invention to a cantilever slide type flow path switching valve, for example.

According to the fluid control valve of the twelfth aspect, the same effect as that of the sixth, seventh, eighth or ninth aspect can be obtained.
When applied to a flow path switching valve having a rotary switching valve body, the usability is significantly improved.

[Brief description of the drawings]

FIG. 1 is a principle block diagram of an embodiment of a refrigeration cycle control device of the present invention.

FIG. 2 is a block diagram illustrating an example of a refrigeration cycle according to the embodiment of the present invention.

FIG. 3 is a block diagram mainly showing an electric system of an indoor control unit and an outdoor control unit in the embodiment.

FIG. 4 is a diagram showing a signal and an operation flow of an embodiment of the refrigeration cycle control device of the present invention.

FIG. 5 is a cross-sectional view and a bottom view of the electric expansion valve according to the embodiment of the present invention.

FIG. 6 is an enlarged sectional view of a main part of the electric expansion valve according to the embodiment of the present invention.

FIG. 7 is a sectional view of a valve body and a shaft of the electric expansion valve according to the embodiment of the present invention.

FIG. 8 is a top view and a side view of a valve body of the pilot valve according to the embodiment of the present invention.

FIG. 9 is a diagram illustrating a relationship among a valve opening degree, a rotation position of a valve body, and a communication / closed state of each port in the electric expansion valve according to the embodiment of the present invention.

FIG. 10 is a diagram showing a flow rate characteristic in a flow rate control range of the electric expansion valve according to the embodiment of the present invention.

FIG. 11 is a diagram showing a flow path switching valve of a first example according to an embodiment of the present invention, together with a main part of a refrigeration cycle.

FIG. 12 is an explanatory diagram of a refrigeration cycle showing a cross-section of the flow path switching valve of FIG. 11 in a cooling mode.

FIG. 13 is an explanatory diagram illustrating a schematic configuration of a refrigeration cycle A to which the flow path switching valve of the second example according to the embodiment of the present invention is applied.

FIG. 14 is an explanatory diagram illustrating a schematic configuration of a refrigeration cycle A to which the flow path switching valve of the third example according to the embodiment of the present invention is applied.

FIG. 15 is a sectional view of a rotary four-way valve and a pilot valve according to a third embodiment.

FIG. 16 is a cross-sectional view showing a state where a main valve body of a rotary four-way valve according to a third embodiment is raised.

17A and 17B are a plan sectional view and a longitudinal sectional view illustrating a change in the rotational position of the main valve element of the rotary four-way valve according to the third embodiment.

FIG. 18 is an enlarged sectional view of a main valve body and a central axis of a rotary four-way valve according to a third embodiment, and a partial plan sectional view thereof.

FIG. 19 is a development view of the outer peripheral side surface of the grooved rod of the rotary four-way valve according to the third embodiment.

FIG. 20 is a view showing a relationship between balls and guide grooves of a rotary four-way valve according to a third embodiment.

FIG. 21 is a flowchart of a main routine in the embodiment.

FIG. 22 is a flowchart of a subroutine in the embodiment.

FIG. 23 is a flowchart of an interrupt routine in the embodiment.

FIG. 24 is a flowchart of a subroutine relating to a flow path switching valve of the first embodiment.

FIG. 25 is a flowchart of a subroutine relating to a flow path switching valve of the second embodiment.

FIG. 26 is a flowchart of a subroutine relating to a flow path switching valve of the third embodiment.

FIG. 27 is a block diagram of a drive circuit in the embodiment.

FIG. 28 is a diagram illustrating an example in which a PNP transistor of the drive circuit according to the embodiment is connected to a driver circuit.

FIG. 29 is a diagram illustrating an example in which the PNP transistor of the drive circuit according to the embodiment is connected to the open collector of the control unit.

FIG. 30 is a diagram illustrating a P-channel MO of a driving circuit according to an embodiment.
FIG. 3 is a diagram illustrating an example in which an S-FET is connected to an open drain of a microcomputer.

[Explanation of symbols]

 Reference Signs List 4 Compressor 5 Discharge pipe 6 Suction pipe 7 Conduit 8 Conduit 9A Indoor heat exchanger (use side heat exchanger) 9B Outdoor heat exchanger (heat source side heat exchanger) 10A Electric expansion valve (throttle device) 11 Valve seat 12 Piston Cylinder (moving member) 12 'Second piston cylinder (moving member) 50, 100 Flow path switching valve 210 Pilot valve (pilot means) 300 Indoor control unit 301 Driver (use side heat exchanger drive source) 400 Outdoor control unit 401 Driver (Heat source side heat exchanger drive source) 404 Driver (Throttle device drive source) 450 Inverter module (Compressor power source) A Refrigeration cycle C Controller

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Nobuyuki Kiuchi 535 Sasai, Sayama-shi, Saitama Prefecture Sagimiya Manufacturing Co., Ltd. 72) Inventor Seiichi Nakahara 535 Sasai, Sayama-shi, Saitama F-term in Sayama Works, Sayama Works 3H062 AA15 CC02 HH04 HH09 3H067 AA15 CC32 DD05 DD33 EA15 EA16 FF17 GG02 GG24 3H106 DA26 DA35 DB02 DB28 DB08 DC18 GB02 HH05 KK23

Claims (12)

[Claims] 1. A refrigeration cycle control device for switching and controlling a flow path switching valve of a refrigeration cycle, comprising: outputting a drive signal to a fluid control valve for controlling a flow rate of a fluid of the refrigeration cycle; A control device for a refrigeration cycle, wherein the flow path switching valve is controlled to be switched by non-electric power generated by a fluid that is communicated / closed by a pilot means that operates according to flow rate control. 2. The system according to claim 1, wherein the pilot means is configured to communicate / close the fluid in accordance with a fully open state or a fully closed state of the degree of opening of the fluid control valve, and determines that the flow path switching valve is switched. 2. The refrigeration cycle control device according to claim 1, wherein the controller controls the opening degree of the fluid control valve to a fully open state or a fully closed state when it is determined that the fluid control valve is not to be switched. 3. A drive unit for driving a fluid control valve for controlling a flow rate of a fluid, and a positive electrode side of a power supply for supplying non-AC power to the drive unit. And a control unit for controlling the conduction / non-conduction means, wherein a control terminal connected to the conduction / non-conduction means is connected to the power supply by the control unit. Short-circuited / opened to the negative electrode side,
A fluid control valve driving device, wherein conduction / non-conduction of the conduction / non-conduction means is controlled. 4. The drive device for a fluid control valve according to claim 3, wherein the control terminal is a collector or a drain of a transistor configured in an open output format. 5. The fluid control valve driving device according to claim 3, wherein the conduction / non-conduction means is a PNP transistor or a P-channel MOS-FET. 6. A fluid control valve for controlling a flow rate of a fluid in a refrigeration cycle, comprising a pilot means for communicating / closing a fluid operated in accordance with the flow rate control of the fluid control valve. Control valve. 7. The fluid control valve according to claim 6, wherein an opening degree control area of the fluid control valve for performing the flow rate control is separated by the flow rate control area and a switching area of the pilot means. 8. The fluid control valve includes an eccentric valve portion formed on a shaft portion that is rotated by electric power, and a valve port portion that communicates with a sealed space in which the valve portion is disposed. An electric expansion valve that performs the flow rate control by changing a gap formed between a valve port portion and a peripheral surface of the valve portion facing the valve portion by rotation of the shaft portion. 8. The fluid control valve according to claim 6, wherein the fluid control valve operates according to rotation. 9. The fluid control system according to claim 6, wherein the pilot means communicates / closes the fluid to generate non-electric power for switching the flow path switching valve of the refrigeration cycle in a driven manner. 9. The fluid control valve according to claim 8. 10. The fluid control valve according to claim 6, wherein the flow path switching valve has a sliding switching valve body that is moved by the non-electric power. 11. The fluid according to claim 10, wherein the flow path switching valve includes an urging means for generating a part of the non-electric power to the sliding valve element. Control valve. 12. The fluid control valve according to claim 6, wherein the flow path switching valve has a rotary switching valve body that is rotated and moved by the non-electric power. .