JP2001248882A - Refrigeration cycle control device - Google Patents

Abstract

(57) [Summary] [PROBLEMS] To provide a refrigeration cycle control device capable of securing reliability for a plurality of types of flow path switching valves and reducing the cost of the refrigeration cycle. SOLUTION: A microcomputer 470 stores control programs for a plurality of types of flow path switching valves. IC [1] 40
6-1: Electromagnetic coil 10 in plural kinds of flow path switching valves
Drive 1-1. IC [1] 406-1 and IC [2] 40
In step 6-2, the stepping motor of a certain flow path switching valve is driven by bipolar driving of the electromagnetic coils 101-1 and 101-2. The microcomputer 470 has a jumper terminal C5-
1 (and C5-2). Jumper terminal C5-1
(Or jumper terminals C5-1 and C5-2) to select and determine the type of flow path switching valve. The microcomputer 470 controls switching of the selected and determined flow path switching valve by a control program corresponding to the selected and determined flow path switching valve.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration cycle control device, and more particularly, to a flow switching valve for switching a flow path of a refrigerant in a heat pump type air conditioner or the like. The present invention relates to a refrigeration cycle control device that switches and controls a flow path switching valve.

[0002]

2. Description of the Related Art Conventionally, in a refrigeration cycle such as a cooling / heating unit, the supply destination of high-pressure refrigerant from a compressor is switched from one of an indoor heat exchanger and an outdoor heat exchanger to the other, thereby cooling the indoor cooling system. And heating. A four-way valve is used as a flow path switching valve for switching the flow path of such a high-pressure refrigerant. As a technique related to such a refrigeration cycle, for example, Japanese Patent Publication No. 35
-12689, Japanese Utility Model Publication No. 55-53825,
Japanese Patent No. 2694032, JP-A-10-47812
JP, JP-A-11-37332, JP-A-11-337
No. 13919 and Japanese Patent Application Laid-Open No. 10-281321.

(Prior art-1) Japanese Patent Publication No. 35-12689
Japanese Patent Application Laid-Open No. 55-53825 and JP-A-55-53825 are slide type flow path switching valves in which a main body of the flow path switching valve is divided into a high pressure chamber and two pressure conversion chambers. A typical operating means is a drive circuit for turning on / off an electromagnetic coil of the pilot electromagnetic unit, and an AC-driven electromagnetic coil or a DC-driven electromagnetic coil is used. In the case of this DC-driven electromagnetic coil, energization is applied in one direction.

[0004] (Prior art-2) Japanese Patent No. 2694032 discloses that a main body of a flow path switching valve is divided into a high-pressure chamber and a pressure conversion chamber, and biased from the pressure conversion chamber to the high-pressure chamber. This is a slide type flow path switching valve provided with a biasing means (spring). A typical operating means is a drive circuit for turning on / off an electromagnetic coil of a pilot electromagnetic unit. Usually, the driving circuit is turned off during a heating operation, is turned on for a predetermined time during a cooling operation, and is turned on for a predetermined time. The pressure exceeds the force of the biasing means. As a result, even if the main valve is turned off, the main valve keeps its position. An AC-driven electromagnetic coil or a DC-driven electromagnetic coil is used. In the case of the DC-driven electromagnetic coil, current is applied in one direction, and these electromagnetic coils provide a certain energy saving effect.

(Prior art-3) JP-A-10-47812
Japanese Patent Application Laid-Open No. 11-37332 and JP-A-11-37332 are rotary type flow path switching valves provided with a communication stroke for communicating a high pressure side flow path and a low pressure side flow path. A typical operation means is to turn on / off the electromagnetic coil of the pilot electromagnetic unit for a predetermined time.
F is a drive circuit that switches the flow path by turning on / off the electromagnetic coil. Normally, bidirectional energization is applied by a DC coil, which brings about an energy saving effect as compared with the related art-2.

(Prior art-4) JP-A-11-13919
The publication discloses a rotary flow path switching valve that switches a flow path by using a driving force of a motor. A typical operation means is a drive circuit that turns on the coil of the motor for a predetermined time, and the flow path is switched by turning on the coil of the motor. Normally, bidirectional energization is applied by a DC coil, and the same energy saving effect as that of the prior art-2 is brought about.

(Prior art-5) JP-A-10-28132
No. 1 discloses a rotary flow path switching device that switches a flow path using a driving force of a stepping motor that drives an electric expansion valve and a flow path switching valve switching area other than a throttle control area of the electric expansion valve. It is a valve. A typical operation means is a drive circuit for driving a DC coil of a stepping motor, and a means for applying a current to the DC coil of the stepping motor.

[0008]

By the way, when the heat pump type refrigeration cycle is, for example, a room air conditioner, for example, 2.2 kW and 2.5 kW based on the cooling capacity.
W, 2.8 kW, 3.2 kW, 4.0 kW, 5.0 kW
Models such as are prepared. At this time, for example, 3.2
One flow path switching valve (small diameter) is used for a model of kW or less, and another flow path switching valve (large diameter) is used for a model exceeding 3.2 kW, for example. At this time, two (one, other) flow path switching valves having the same operation means and the same control step are not necessarily used. An example is shown below.

A case will be described in which the prior art-2 is used for one flow path switching valve and the conventional art-1 is used for another flow path switching valve. Here, it is assumed that a model having a small capacity requires more energy saving, and the conventional technology-2 of the energy saving type is used rather than the conventional technology-1. At this time, for example, assuming that an AC coil is used, it is OFF during the heating operation and O during the cooling operation.
The refrigerant pipe is connected to the flow path switching valve so as to be N. In order to standardize the connection pipes, for example, it is unified so that a conduit 7 described later is connected to an indoor heat exchanger and a conduit 8 described later is connected to an outdoor heat exchanger. Thus, the operating means (drive circuit)
Are the same, but a flow switching valve having a different control process is used. One of the flow path switching valves can maintain the position by energization (ON) for a predetermined time during the cooling operation, while the other flow path switching valve can energize (ON) for a long time during the cooling operation. Otherwise, the position cannot be maintained. Here, in the summer when cooling operation is required, the `` outside air temperature '' is high, and the temperature of the electromagnetic coil rises due to heat generation inside the electromagnetic coil due to the application of energization, and insulation deterioration of the coil occurs, There was a problem in the reliability of the flow path switching valve.

[0010] In addition, the above-mentioned prior art is used for one flow path switching valve.
3. A case where the above-mentioned conventional technology-1 is used for another flow path switching valve will be described. Here, it is assumed that a model having a small capacity requires more energy saving, and a conventional technology-3 of an energy saving type is used more than the conventional technology-2. At this time, for example, the prior art-1 uses an AC coil that applies commercial AC power, and is turned on during the heating operation and turned off during the cooling operation.
The refrigerant pipe is connected to the flow path switching valve so that On the other hand, prior art-3 is a bidirectional drive type of a DC coil,
In addition, since the position is held after the application of the electric current for a predetermined time, the application of the electric current is unnecessary, so that the latch type is used. Here, the prior art-1 is of an AC drive type, although the problem of the temperature rise of the electromagnetic coil has been solved.
Is a DC bidirectional drive type. That is, two operation means (drive circuits) and two control steps are required. Thus, a flow path switching valve having a different operation means (drive circuit) and a different control step has been used. At this time, the number of members does not increase because the control process can be performed only by using the memory of the microcomputer. However, two operation means (drive circuits) are required, and extra hardware (members) are required correspondingly, resulting in cost increase. There was a problem in that it polluted the global environment.

Further, a case will be described in which the prior art-4 is used for one flow path switching valve and the conventional art-5 is used for another flow path switching valve. In the prior art-4, the flow path is switched by applying a current to the DC motor for a predetermined time, and the current is of a bidirectional drive type. Conventional technology-5
Is a composite valve using a stepping motor. The flow path is switched by being located in a “heating switching area” and a “cooling switching area” other than the throttle control area. Both of the two valves are rotary type flow switching valves. However, in the prior art-5, the four-way valve portion and the throttle valve portion are united, the refrigerant pipes are concentrated on the composite valve, and the pipe processing becomes complicated as compared with the prior art-4. There has been a problem that standardization of the piping configuration of the unit is hindered and causes a cost increase.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a refrigeration cycle control device which can ensure the reliability of a plurality (kinds) of flow path switching valves and reduce the cost of the refrigeration cycle.

[0013]

According to a first aspect of the present invention, there is provided a refrigeration cycle control apparatus for switching and controlling a flow path switching valve of a refrigeration cycle. And a control step corresponding to each of the plurality of flow path switching valves, wherein the selected flow path switching valve corresponds to the flow path switching valve. Switching control is performed in the control step.

According to a second aspect of the present invention, there is provided a refrigeration cycle control device comprising the configuration of the first aspect, wherein the plurality of flow path switching valves include an electrically driven valve electrically driven by operating means, and a non-electrically driven valve. A non-electrically driven valve to be driven, and a control step of switching and controlling the electrically driven valve by the operating means; and a control step of controlling and switching the non-electrically driven valve.

A third aspect of the present invention is directed to a refrigeration cycle control device, wherein the plurality of types of flow path switching valves include a plurality of non-electrically driven valves that are non-electrically driven. It is characterized by comprising a plurality of control steps for switching and controlling the plurality of non-electrically driven valves.

According to the refrigeration cycle control device of the first aspect, since there is provided a selection determining means for selecting and determining a control step corresponding to the plurality of flow path switching valves, a plurality of flow path switching valves having different control steps are provided. Can be selectively switched and controlled. Therefore, reliability can be ensured for the plurality of flow path switching valves, and the cost can be reduced.

According to the refrigeration cycle control device of the second aspect, the present invention is applied to a combination of an electrically driven valve electrically driven by the operating means and a non-electrically driven valve non-electrically driven. The same operation and effect as those of the first aspect can be obtained.

According to the refrigeration cycle control device of the third aspect, the same effect as that of the first aspect can be obtained by applying the present invention to a combination of a plurality of non-electrically driven valves that are non-electrically driven.

[0019]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, an embodiment of a refrigeration cycle control device according to the present invention will be described with reference to the drawings.

FIG. 10 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 figure) and an outdoor unit (in the dashed line in the figure). (Outside). In the figure, 4 is a compressor, 9A is an indoor heat exchanger mounted on an indoor unit, 9A
B is an outdoor heat exchanger mounted on the outdoor unit, 10A is a throttling device, 200 is an accumulator, and 100 is a rotary flow path switching valve constituting a four-way valve.

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

The compressor 4 compresses the refrigerant, and the compressed refrigerant flows into the flow path switching valve 100. As 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 expansion device 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 is supplied from the flow path switching valve 100 to the outdoor heat exchanger 9B, the expansion device 10A, and the indoor heat exchanger
A, 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 provided by a microcomputer or the like. The rotation control is performed via the driver 301 under the control of the configured indoor control unit 300. 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 92 for rotating the fan 91B.
The rotation of B is controlled via a driver 401 under the control of an outdoor control unit 400 composed of a microcomputer or the like. Thereby, the heat exchange capacity of the outdoor heat exchanger 9B is controlled. Further, the outside air temperature Ta ′ is
2, the temperature Tc ′ of the outdoor heat exchanger 9B is detected by the temperature sensor 403. Further, the outdoor control unit 400 controls the opening degree of the diaphragm of the diaphragm device 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 outdoor control section 400 outputs an operation mode control signal SDRV to a driver 406 as a drive source of the flow path switching valve, and the driver 406 outputs the operation mode control signal SDRV.
0 is controlled. In addition, the flow path switching valve 1
00 is provided with an electromagnetic coil for switching the flow path as described later, and switches the flow path in accordance with the power supply from the driver 406 based on the operation mode control signal SDRV.

In this example, a rotary type is shown as the flow path switching valve 100. However, the flow path switching valve 100 is, for example, disclosed in Japanese Patent Publication No. 35-12689 or Japanese Patent No. 2694032. A similar refrigeration cycle A is configured using a slide type flow path switching valve. In the case of such a slide type flow path switching valve 100, the electromagnetic coil of the pilot electromagnetic section is connected to the driver 406.
It is driven by. However, in the case of a pilot type electromagnetic section provided with an electromagnetic coil, or in the case of a rotary type flow path switching valve 100 using a motor or the like, in the case of a rotary type flow path switching valve 100 using a stepping motor, in the case of a slide type flow path switching valve 100, In each case, details of the drive control by the driver 406 are different from each other. Further, a flow path switching valve 10 whose flow path is switched by non-electric power described later.
In the case of 0, the driver 406 is not used.

FIG. 11 shows an indoor controller 300 and an outdoor controller 4.
00 is a block diagram mainly showing an electric system. The indoor control unit 300 includes a power relay 310 for turning on / off a main power supply.
And 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.
Note that an EEPROM 340 is connected to the microcomputer 330. The 100 V single-phase alternating current supplied via the power relay 310 is also supplied to the outdoor control unit 400 via the power supply line 200.

In the outdoor control unit 400, the supplied AC is applied to a noise filter 410, and then rectified by a converter 420 and smoothed by a smoothing capacitor 430 to generate a predetermined DC voltage. The generated DC current is supplied to the inverter module 450 via the shunt resistor 440.
Supplied to 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 the DC / DC converter 4
At 60, it is converted to a predetermined internal DC voltage and supplied to the microcomputer 470 and the like. Then, the microcomputer 470 controls the operation of the compressor 4 by outputting a drive signal to the inverter module 450. 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, between 15 Hz and 10 Hz, the pressure of the refrigerant is higher at 15 Hz than at 10 Hz.
The microcomputer 470 is connected to an EEPROM 480 and a voltage detector 490.
At 80, the position data of the position of the main valve body, which will be described later, corresponding to the switching position when the refrigeration cycle is stopped is stored.
Further, the microcomputer 470 performs serial communication with the microcomputer 330 of the indoor control unit 300 via the communication line 210 to exchange data.

FIG. 9 is a principle block diagram of an embodiment of a control device for a refrigeration cycle according to the present invention. Each element of the principle block diagram corresponds to each element in FIGS. 10 and 11 or a combination of each element. are doing. In the refrigeration cycle A, the same elements as those in FIG. 10 are denoted by the same reference numerals. 9 corresponds to the indoor control unit 300 and the outdoor control unit 400. The processing unit C1 of the control device C includes the microcomputer 330 of the indoor control unit 300 and the outdoor control unit 400. It corresponds to the microcomputer 470. The input unit C2 corresponds to the receiving unit 304 of the indoor unit or a manual switch (not shown), and the detecting unit C3 is a temperature sensor 302, 303, 402, 403, 405 or not shown, but a pressure detecting unit, a flow detecting unit. The semi-fixed storage unit C4 corresponds to the EEPROM 340 of the indoor control unit 300 and the outdoor control unit 40.
0 corresponds to the EEPROM 480.

Further, the selection determining means C5 is one feature of the present invention, and the selection determining means C5 is a jumper terminal and a jumper connected to the control unit 400. Then, according to the type of the flow path switching valve 100, the selection of the control step or the drive / non-drive of the flow path switching valve driving unit 406 described later is determined by the selection determining means C5.

The expansion device drive section C6, the use side heat exchanger drive section C7, the heat source side heat exchanger drive section C8, and the compressor drive section C9 are means that function by executing a control program described later. The flow path switching valve driving unit 406 corresponds to the driver 406.

The aperture device driving unit C6 includes an aperture device driving source 40.
A control signal is output to the aperture device 4 to control the aperture of the aperture of the aperture device 10A via the aperture device drive 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 driver of a fan motor) 301, and the use side heat exchanger drive source 301 responds to the control signal to generate a cross flow fan 91A. Drive, run or stop,
The heat exchange capacity of the indoor (use side) heat exchanger 9A is controlled by the number of revolutions. The heat source side heat exchanger drive unit C8 outputs a control signal to a heat source side heat exchanger drive source (for example, a driver of a fan motor) 401, and the heat source side heat exchanger drive source 401 drives the fan 91B according to the control signal. Then, the heat exchanger 9B is operated or stopped, and the outdoor (heat source side) heat exchanger 9B
Control the heat exchange capacity of the

The processing section C1 includes a flow path switching valve driving section 40.
6 (driver 406) to output a control signal (operation mode control signal SDRV), and the flow path switching valve driver 406 switches the flow path of the flow path switching valve 100 according to the control signal. Driving source (electromagnetic coil described later) 101
To supply power. Further, the compressor driving unit C9 is a compressor power source (for example, an inverter module and a motor).
A control signal is output to 450, the compressor power source 450 drives the compressor 4, and the compressor 4 is controlled such as forward rotation, reverse rotation, start, stop, and performance switching. It goes without saying that the compressor power source is not limited to a motor, but may be an engine.

Further, when a non-electrically driven flow path switching valve 100 (non-electrically driven valve) to be described later is selected, the forward rotation, reverse rotation, start, stop, and capacity switching of the compressor 4 are controlled. As a result, the pressure of the refrigerant in the refrigeration cycle A is controlled, whereby the flow path of the flow path switching valve 100 is switched without using the flow path switching valve driving unit 406 and the flow path switching valve driving source 101. Can be

The refrigerating cycle is not limited to the illustrated heat pump type air conditioner, but may include a heat pump type chiller unit, an engine driven type and a car air conditioner.

FIG. 1 is a block diagram of a main part of a control device for a refrigeration cycle according to the first embodiment. The microcomputer 470 of the outdoor control unit 400 includes an IC [1] 4 comprising a double arm circuit.
The electromagnetic coil 101-1 of the flow path switching valve is connected to the IC [1] 406-1. The microcomputer 470 is provided with a jumper terminal C5-1.

The electromagnetic coil 101-1 is formed by the conventional technology
1 (Japanese Patent Publication No. 35-126689 and Japanese Utility Model Publication No. 55-5)
3825) and the above-mentioned prior art-2 (Patent No. 2)
No. 694032), an electromagnetic coil of a slide type flow switching valve, or the above-mentioned prior art-3 (Japanese Unexamined Patent Publication No. Hei 10-47812 and Japanese Unexamined Patent Publication No. Hei 11-37332) or the above prior art-4. (Japanese Unexamined Patent Application Publication No. 11-1391
No. 9) and other electromagnetic coils of a rotary flow path switching valve. Then, energization / non-energization is controlled via the IC [1] 406-1 by a control signal from the microcomputer 470. Needless to say, in the case of a one-way energizing electromagnetic coil, one-way energization / non-energization control is performed via IC [1] 406-1. Alternatively, a dedicated drive unit may be separately provided to control energization / non-energization.

Further, the conventional technology-5 (Japanese Patent Laid-Open No. 10-2)
In the case of a rotary flow path switching valve using a stepping motor, such as that of JP-A-81321, the IC [2] 406-2 and the electromagnetic coil 10 as shown by the broken line in FIG.
1-2, I is controlled by a control signal from the microcomputer 470.
C [1] 406-1 and IC [2] 406-2 control the stepping motor by bipolar driving. Needless to say, in the case of the stepping motor of the unipolar drive type, the control of energization / de-energization in one direction is performed. Therefore, a dedicated drive unit is separately provided to control energization / de-energization.

The microcomputer 470 stores, for example, any two control programs of the above-mentioned various flow path switching valves, and switches the jumper terminal C5-1 to change the flow path switching valve to be controlled. The flow path switching valve is switched and controlled by the selected control program. In addition, 3
The control program for the type or four types of flow path switching valve is stored, and the jumper terminal C as shown by the broken line in FIG.
5-2 may be provided to select one flow path switching valve and its control program by two jumpers C5-1 and C5-2. Further, similarly, a desired one flow path switching valve can be selected from various kinds of flow path switching valves to perform switching control.

Next, in describing the refrigeration cycle control devices of the second and third embodiments, three types of rotary flow path switching valves 100 will be described as examples of control objects. The flow path switching valve 10 shown in FIGS.
0 corresponds to the following three kinds of flow path switching valves 100, but in order to distinguish the following three kinds of flow path switching valves 100, hyphens and numbers 1, 2 and 3 are added after the reference numeral 100. This will be additionally described. Here, the flow path switching valve 100-2 and the flow path switching valve 100-3, which are non-electrically driven valves,
The flow path switching valve drive section (driver) 406 and the flow path switching valve drive source (electromagnetic coil) 10 shown in FIGS.
Needless to say, 1 is unnecessary.

FIG. 12 is a cross-sectional view showing a first rotary type flow switching valve 100-1 for switching a flow path by energizing an electromagnetic coil of a pilot electromagnetic section.
-1 is the same flow path switching valve as that of Japanese Patent Application Laid-Open No. 10-47812. The flow path switching valve 100-1 is roughly divided into
The valve body 2 includes a main valve portion VM, a pilot valve portion (pilot electromagnetic portion) VP, and a magnetic circuit M. The valve body 2 is formed in a cylindrical shape, the upper end of which is inserted and fixed to the lower part of the casing 3, and the main valve seat 10 is fixed to the lower end thereof. A main valve element 48 supported by the shaft 13 erected at the center of the main valve seat 10 is rotatably provided inside the valve body 2.

The main valve seat 10 is formed with an outlet 11 communicating with the refrigerant suction port of the compressor 4 and the compressor 4
Is formed on the opposite side of the outlet 11 with respect to the shaft 13. Further, although not shown in the figure, the indoor heat exchanger 9A and the outdoor heat exchanger 9B are located on the circumference around the axis 13 at positions approximately 90 ° apart from the outlet 11 and the inlet 12, respectively. Are formed with two through holes, respectively. Here, one through hole is connected to the indoor heat exchanger 9A via a conduit 7 not shown in the figure, and the other through hole is connected to the outdoor heat exchanger 9B via a conduit 8. ing. The lower surface of the main valve body 48 (the surface on the side of the main valve seat 10) is formed in an arc shape so as to oppose on the circumference where the outlet 11, the inlet 12 and the two through holes of the main valve seat 10 are arranged. Contact groove 21
And a guide groove 22 are formed.

A cylindrical magnetic conductive yoke 33 is provided on the upper part of the main valve element 48, and four permanent magnet pieces 14 (the other two are not shown in the figure) are provided on the outer periphery of the magnetic conductive yoke 33. ) Are attached, and the four permanent magnet pieces 14 are arranged such that the polarity (S-pole / N-pole) on the outer peripheral side is different for every other one. The lower open end of the casing 3 seals the periphery of the vicinity of the upper end of the valve body 2, but around the permanent magnet piece 14, the two tongues facing each other at 180 ° on the circumference Shaped portions 3A and 3B.
Thereby, by energizing the electromagnetic coil 101,
The main valve body 48 is rotated according to the polarities of the tongue portions 3A and 3B and the four permanent magnet sides 14, and the flow path is switched.

On the other hand, the magnetic circuit M is composed of the attraction element 16, the casing 3, the magnetic conductive yoke 33 provided on the main valve body 48, the permanent magnet piece 14, and the plunger 15, and the main valve section V
Used to drive both the M and pilot valve parts VP.

A plunger tube 18 is attached to the lower end of the suction element 16, and an electromagnetic coil 101 is arranged around the plunger tube 18 and the suction element 16. The plunger 15 is slidably disposed in the plunger tube 18 with a compression coil spring 20 disposed between the plunger 15 and the suction element 16. The compression coil spring 20 connects the plunger 15 to the pilot valve seat 48 a. Direction, that is, in the valve closing direction. At the center of the lower surface of the plunger 15, a pilot valve body 15a protrudes, while at the center of the upper part of the main valve body 48, a pilot port 47 is bored, and this pilot port 47 communicates with the communication groove 21. ing. An end of the pilot port 47 constitutes a pilot valve seat 48a, and the pilot valve body 15a of the plunger 15 that slides up and down and the pilot valve seat 48a.
a constitutes a pilot valve.

The outlet 11 is provided with a suction pipe 6 communicating with the refrigerant suction port of the compressor 4 of the refrigeration cycle, and the introduction port 12 is provided with the discharge pipe 5 communicating with the refrigerant outlet of the compressor 4. And the pipeline having the inlet 12 is
It protrudes into the guide groove 22 and functions as a stopper in the direction of rotation of the main valve element 48 that rotates.

With the above configuration, the flow path switching valve 100-1
Works as follows. FIG. 12 shows a non-energized state of the electromagnetic coil 101 in the cooling operation mode (a state in which the flow path is held).
This state corresponds to the compressor 4 of the refrigeration cycle.
Inlet 12 and outdoor heat exchanger 9 connected to the discharge port of
B is communicated with the through hole via the guide groove 22, and the outlet 11 connected to the inlet of the compressor 4 and the outlet connected to the outlet of the indoor heat exchanger 9A. The holes are in communication with each other via the communication groove 21. Note that, for convenience described later, the position of the main valve body 48 of the flow path switching valve 100-1 in the cooling operation mode is a second position.

As a result, the refrigerant flows through the path of the compressor 4 → the flow path switching valve 100-1 → the outdoor heat exchanger 9B → the throttle 10A → the indoor heat exchanger 9A → the flow path switching valve 100-1 → the compressor 4. It will circulate. At this time, the high-temperature, high-pressure refrigerant discharged from the discharge port of the compressor 4 is applied to the upper and lower parts of the main valve body 48 through the inlet 12 at the same pressure. That is, since the pilot valve seat 48a is in the closed state, the pressure in the space 25 on the plunger 15 side is high. In this state,
If it is instructed to switch to the heating operation mode, the operation mode control signal SDRV is output to excite the electromagnetic coil 101 so that the casing 3 has, for example, the N pole.

As a result, the magnetic circuit M first causes the suction element 16 to suck the plunger 15 and the pilot valve seat 48
a is opened. In this state, the refrigerant flows out of the pilot port 47 into the space 25, so that the pressure at the upper part of the main valve body becomes lower than the pressure at the lower part of the main valve body, and the main valve body 48
Rises away from the main valve seat 10. As a result, the main valve body 4
8, the upper pressure and the lower pressure of the main valve element become equal, that is, a low pressure outlet 11 communicating with a refrigerant suction port of the compressor 4 and a high pressure inlet 12 communicating with a refrigerant discharge port of the compressor 4. The pressure of the refrigerant in the holes is forcibly set to substantially the same pressure.
When the main valve body 48 is raised, the refrigerant and oil discharged from the compressor 4 pass through the space 26 from the high-pressure inlet 12,
It returns directly to the low pressure outlet 11 and does not flow out to the indoor heat exchanger 9A or the outdoor heat exchanger 9B.

At this time, the pair of opposed permanent magnet sides 14 receives a repulsive action from the casings 3A and 3B, and the other pair of permanent magnet sides 14 receives an attraction action from the casings 3A and 3B. Will rotate. Thereby, the inlet 12 connected to the discharge port of the compressor 4 of the refrigeration cycle communicates with the through hole connected to the indoor heat exchanger 9A via the guide groove 22. The outlet port 11 connected to the suction port and the through hole connected to the outlet port of the outdoor heat exchanger 9B are in communication with each other via the communication groove 21. As a result, the refrigerant circulates in the path of the compressor 4 → the flow path switching valve 100-1 → the indoor heat exchanger 9A → the throttle 10A → the outdoor heat exchanger 9B → the flow path switching valve 100-1 → the compressor 4; The refrigeration cycle is switched to the heating operation mode. In addition, the position of the main valve body 48 of the flow path switching valve 100-1 in the heating operation mode will be referred to as a first location for convenience described later.

In addition, while operating in the heating operation mode, the operation mode control signal SDRV is output to
When the power supply to the first coil 1 is stopped and the electromagnetic coil 101 is de-energized, the plunger 1
5 and the main valve element 48 descend again, and the main valve element 48 and the main valve seat 1
0 contacts, and the pilot valve seat 48a of the main valve body 48 is closed. At this time, there is no magnetic force in the casing, and the main valve body 48 and the main valve seat 10 remain switched, and this state is maintained.

When switching from the heating operation mode to the cooling operation mode, the dehumidification operation mode or the defrosting operation mode, the electromagnetic coil 101 is set so that the casing 3 has the opposite polarity to the polarity when switching to the heating operation mode. Energize. As a result, the plunger 15 is sucked by the suction element 16, the pilot valve seat 48a is opened, the main valve body 48 rises, the main valve body 48 is rotated in the opposite direction, and the flow path is switched.

FIG. 13 is a cross-sectional view of a second rotary type flow path switching valve 100-2 whose flow path can be switched by non-electric power. A substantially cylindrical main body is provided inside a cylindrical valve housing 53. The valve body 55 is rotatably and movably accommodated in the direction of the rotation axis, and the open end of the valve housing 53 is closed by a valve seat 57.
And biases the main valve body 55 inside the valve housing 53 so as to separate the main valve body 55 from the valve seat 57.
A second coil spring 73 is housed between the upper closed end of the outer housing 53a and the main valve body 55 for urging the main valve body 55 toward the valve seat 57. It is configured.

More specifically, the valve housing 53 includes an outer housing 53a and two upper and lower inner housings 53a.
The outer housing 53a is formed in a cylindrical shape with one end opened and the other end closed, and the discharge pipe 5 is connected to the other end of the outer housing 53a. ing.

The upper and lower inner housings 53b, 5
Reference numeral 3c denotes a cylindrical shape having an outer diameter that can be accommodated in the outer housing 53a, and the lower side of the upper inner housing 53b is shaped such that the peaks and valleys are continuous at 90 ° cycles. The upper side of 53c is shaped such that the peaks and valleys are continuous at 90 ° intervals along the shape of the lower side of the upper inner housing 53b. Thus, the valve housing 5 facing the periphery of the main valve body 55
The cam groove 53j of the spiral lock which goes up and down every 90 degrees in the inner peripheral surface of No. 3
Are formed.

In the valve seat 57, a first switching port 57a to which the conduit 7 is connected from the bottom side and a second switching port 57b to which the conduit 8 is connected from the bottom side sandwich the center of the valve seat 57. Are provided at positions facing each other. Although not shown in the figure, two low pressure side ports are provided at positions where the phases are shifted by 90 ° in the circumferential direction of the valve seat 57 from the first and second switching ports 57a and 57b. The suction pipe 6 is bifurcated from the bottom side of the valve seat 57 and connected to these two low-pressure ports.

The main valve body 55 has a semicircular low-pressure side communication groove 55a so as to oppose the switching ports 57a and 57b of the valve seat 57 and the two low-pressure side ports.
And a high-pressure side communication passage 55b having a hole that can communicate with one of the switching ports 57a or 57b.

When the main valve body 55 is in contact with the valve seat 57, the first rotation position of the main valve body 55
The switching port 57a and the two low pressure side ports are connected to each other by a low pressure side communication groove 55a, and the main valve body 5
5, the second switching port 57b
And the two low-pressure ports are connected to each other by a low-pressure communication groove 55a.

The high-pressure side communication passage 55b is opened on the end face of the main valve body 55 on the valve seat 57 side, avoiding the low-pressure side communication groove 55a, and passes through a hollow chamber 55d formed in the upper part of the main valve body 55. It is connected to the valve port 55c. In addition, the main valve body 55
The operating rod 55f is inserted through the center of the shaft so as to be movable in the axial direction. When the main valve body 55 is separated from the valve seat 57, the auxiliary valve body 55g attached to the operating rod 55f is connected to the valve port 55g. When the high-pressure side communication passage 55b is closed and the main valve body 55 is seated on the valve seat 57, the distal end of the operating rod 55f abuts on the valve seat 57 so that the auxiliary valve body 55g is closed. 55c to open the high-pressure side communication passage 55b.
Are open to the upper space in the valve housing 53.

Note that two guide pins (not shown) project from the peripheral surface of the main valve body 55, which are shifted in phase by 180 ° in the circumferential direction, and these guide pins are formed in the cam grooves 53j. Each is inserted.

With the above configuration, the flow path switching valve 100-2
Works as follows. First, when the compressor 4 is stopped, as shown in FIG. 13, the main valve element 55 applies the urging force of the coil spring 59 and the second coil spring 7.
Due to the balance with the urging force of No. 3, it is located at an intermediate position in the movement range in the direction of approaching and separating from the valve seat 57. The valve port 55c is closed by the auxiliary valve body 55g.

In this state, when the compressor 4 starts operating, the auxiliary valve body 55g closes the valve port 55c.
The high-pressure refrigerant that has flowed into the inside acts to move the main valve body 55 to the valve seat 57 side against the urging force of the coil spring 59, and the guide pin located at the intermediate position of the cam groove 53j And the cam groove 53j is located at a position closest to the valve seat 57 (hereinafter referred to as a lower end).

That is, the main valve body 55 is
The main valve body 55 is seated on the valve seat 57 and reaches the second position when the main valve body 55 is rotated by approximately 45 ° from the intermediate position of the cam groove 53j while rotating inside the cam groove 53j. As a result, the tip of the operating rod 55f contacts the valve seat 57, and the auxiliary valve body 55g opens the valve port 55c. In this state, the low pressure side communication groove 55a faces the first switching port 57a and the two low pressure side ports, and the high pressure side communication passage 55b faces the second switching port 57b. For this reason, the discharge pipe 5 is connected via the high pressure side communication passage 55b and the second switching port 57b.
Communicates with the conduit 8, and the suction pipe 6 communicates with the conduit 7 via the first switching port 57a, the low-pressure communication groove 55a, and the two low-pressure ports.

Therefore, the high-pressure refrigerant from the compressor 4 is
Through the discharge pipe 5, the high-pressure communication path 55b, and the second switching port 57b, the air flows from the conduit 8 into the outdoor heat exchanger 9B,
From the conduit 7 via the throttle 10 and the indoor heat exchanger 9A, the first
After returning to the suction port of the compressor 4 from the suction pipe 6 via the switching port 57a, the low-pressure communication groove 55a, and the two low-pressure ports, the refrigeration cycle A enters the cooling operation mode. Note that, for convenience, the position of the main valve body 55 of the flow path switching valve 100-2 in the cooling operation mode is defined as a second location.

Thereafter, when the operation of the compressor 4 is stopped,
Since the pressure of the refrigerant flowing into the valve housing 53 decreases, the urging force of the coil spring 59 is reduced by the main valve body 55.
Acts in a direction away from the valve seat 57, and the guide pin located at the lower end of the cam groove 53j is
Returning to the halfway point (the state in FIG. 13) where the urging force of the coil spring 59 and the urging force of the second coil spring 73 are balanced, the operating rod 55f whose tip is separated from the valve seat 57
The valve port 55c is closed by the auxiliary valve body 55g.

Thereafter, when the compressor 4 is operated again, the main valve body 55 returns to the second position by the same operation as described above, and the refrigeration cycle A enters the cooling operation mode.

On the other hand, when the compressor 4 is operated in reverse rotation,
The refrigerant pressure in the space between the closed end of the outer housing 53a and the main valve body 55 is reduced, and the second coil spring 7
The main valve body 55 moves in a direction away from the valve seat 57 against the urging force of No. 3. As a result, the guide pin located at an intermediate position of the cam groove 53j moves following the cam groove 53j and is located at a position of the cam groove 53j farthest from the valve seat 57 (hereinafter, referred to as an upper end). become.

Thereafter, when the operation of the compressor 4 is stopped,
Since the pressure of the refrigerant in the space between the closed end of the outer housing 53a and the main valve body 55 is not reduced, the main valve body 55 moves in the direction approaching the valve seat 57 by the urging force of the second coil spring 73. . The shape of the upper end position and the lower end position of the cam groove 53j is such that when the guide pin moves away from the upper end position or the lower end position, the guide pin moves in one circumferential direction in the upper inner housing 53b and the lower inner housing 53C. It is formed in such a shape.

Therefore, the guide pin located at the upper end of the cam groove 53j moves following the cam groove 53j, and the main valve body 55 further rotates by about 90 ° from the state shown in FIG. Reach different midway points.

Thereafter, when the compressor 4 is operated again, the auxiliary valve element 55g closes the valve port 55c.
The high-pressure refrigerant flowing from the compressor 4 into the valve housing 53 is compressed by the main valve body 5 against the urging force of the coil spring 59.
5 to move to the valve seat 57 side.
The guide pin located at an intermediate position of j
j at the lower end of the valve seat 5 when the main valve body 55 is rotated by 180 ° from the position in the cooling operation mode.
7 and reaches the first location, whereby the refrigeration cycle A enters the heating operation mode. Note that, for convenience, the position of the main valve body 55 of the flow path switching valve 100-2 in the heating operation mode is defined as a first position.

Thereafter, when the operation of the compressor 4 is stopped,
The main valve element 55 moves in the direction away from the valve seat 57 by the urging force of the coil spring 59 acting on the main valve element 55 due to the pressure drop of the refrigerant flowing into the valve housing 53, and the lower end of the cam groove 53j. The located guide pin moves following the cam groove 53j and reaches a halfway point rotated by approximately 90 ° from the state shown in FIG.

After that, when the compressor 4 is operated again, the high pressure refrigerant flowing into the valve housing 53 causes the main valve body 55 to oppose the urging force of the coil spring 59 to the valve seat 5.
7, the guide pin located at the middle position of the cam groove 53j is located at the lower end of the cam groove 53j, the main valve body 55 returns to the first position, and the refrigeration cycle A is in the heating operation mode. Becomes

In this state, when the compressor 4 is operated in the reverse rotation, the compressor 4 is stopped, and the compressor 4 is further operated in the normal rotation, the cooling operation mode is changed to the heating operation mode. The same operation as the switching is performed, and the refrigeration cycle A is switched from the heating operation mode to the cooling operation mode. After that, when the operation of the compressor 4 is stopped,
The main valve element 55 returns to the halfway point shown in FIG.

As described above, according to the flow path switching valve 100-2, the differential pressure generated by the refrigerant flow of the compressor 4 and the pressure of the coil spring 59 interposed between the main valve body 55 and the valve seat 57 are increased. The urging force and the reverse rotation of the compressor 4 cause the main valve body 5
5 is moved in a direction to approach and separate from the valve seat 57, and the guide pin is moved along the cam groove 53j.
The main valve element 55 is rotated with respect to the valve housing 53 to move the main valve element 55 between the first position and the second position.

Therefore, the start and stop of the operation of the compressor 4 without using a dedicated drive source such as an electromagnetic solenoid or the like causes the discharge pipe 5 and the suction pipe 5 to be communicated by the low-pressure communication groove 55a and the high-pressure communication passage 55b. The communication destination of the pipe 6 is switched between the first and second switching ports 57a and 57b of the valve seat 57, and the refrigerant discharged from the discharge pipe 5 is supplied to the indoor heat exchanger 9A via the conduit 7. The refrigeration cycle A can be switched between the heating operation mode and the cooling operation mode supplied to the outdoor heat exchanger 9B via the conduit 8, and the switching state can be maintained.

Further, according to the second rotary type flow path switching valve 100-2, switching of the communication destination of the discharge pipe 5 and the suction pipe 6 in the flow path switching valve 100-2 starts the operation of the compressor 4. In addition, since the driving is performed by the stop and the stop, not only the drive source for the electric drive is not required, but also the control by the electric signal for switching the flow path can be unnecessary.

FIG. 14 is a cross-sectional view of a third rotary flow path switching valve 100-3 whose flow path can be switched by non-electric power. In FIG. 14, the second flow path switching valve 100-3 of FIG. The same members and portions as in FIG. 2 are denoted by the same reference numerals as those in FIG.

Then, the third flow path switching valve 100-3
Is different from the second flow path switching valve 100-2 shown in FIG. 13 in that the second flow path switching valve 100-2 does not include the second coil spring 73. The points are configured similarly to the second flow path switching valve 100-2.

The third flow path switching valve 1 configured as described above
00-3 operates as follows. First, when the compressor 4 is stopped, the main valve element 55 is separated from the valve seat 57 by the urging force of the coil spring 59, and the auxiliary valve element 5
The valve port 55c is closed by 5g, and the two guide pins 55h of the main valve body 55 are located at the positions of the cam groove 53j farthest from the valve seat 57 (hereinafter, referred to as the upper end).

Then, assuming that the operation of the compressor 4 is stopped from the state where the refrigeration cycle A is in the heating operation mode and the guide pin 55h is located at the upper end of the cam groove 53j,
The low-pressure side communication groove 55a of the main valve body 55 faces the first and second switching ports 57a and 57b of the valve seat 57.

In this state, when the compressor 4 starts operating, the auxiliary valve body 55g closes the valve port 55c.
The high-pressure refrigerant flowing into the inside of the cam groove acts to move the main valve body 55 to the valve seat 57 side against the urging force of the coil spring 59, and guide pins 55h respectively located at the upper end of the cam groove 53j. Are located at positions of the cam groove 53j closest to the valve seat 57 (hereinafter, referred to as a lower end).

That is, the main valve body 55 is
The main valve body 55 moves to the valve seat 57 side while rotating in the inside, and when rotated by 90 °, the main valve body 55 sits on the valve seat 57 and reaches the second position. As a result, the tip of the operating rod 55f contacts the valve seat 57, and the auxiliary valve body 55g opens the valve port 55c. In this state, the low-pressure side communication groove 55a faces the first switching port 57a and two low-pressure side ports not shown in the drawing, and the high-pressure side communication passage 55b is connected to the second switching port 5a.
7b. For this reason, the high-pressure side communication passage 55b
The discharge pipe 5 communicates with the conduit 8 via the second switching port 57b and the suction pipe 6 via the first switching port 57a, the low-pressure communication groove 55a, and the two low-pressure ports.
Communicates with the conduit 7.

Therefore, the high-pressure refrigerant from the compressor 4 is
Through the discharge pipe 5, the high-pressure communication path 55b, and the second switching port 57b, the air flows from the conduit 8 into the outdoor heat exchanger 9B,
From the conduit 7 via the throttle 10 and the indoor heat exchanger 9A, the first
After returning to the suction port of the compressor 4 from the suction pipe 6 via the switching port 57a, the low-pressure communication groove 55a, and the two low-pressure ports, the refrigeration cycle A enters the cooling operation mode. Note that, for convenience, the position of the main valve body 55 of the flow path switching valve 100-3 in the cooling operation mode is a second position.

Thereafter, when the operation of the compressor 4 is stopped,
Since the pressure of the refrigerant flowing into the valve housing 53 decreases, the urging force of the coil spring 59 is reduced by the main valve body 55.
And the guide pin 55 located at the lower end of the cam groove 53j.
h moves along the cam groove 53j and comes to the upper end.

That is, the main valve body 55 is
When it is rotated to 90 ° by rotating toward the discharge pipe 5 side while rotating within, the state shown in FIG.
The main valve body 55 reaches the first intermediate point farthest away from the valve seat 57 in the opposite direction by 0 °, whereby the valve port 55c is moved by the auxiliary valve body 55g of the operating rod 55f whose tip is separated from the valve seat 57. Closed. In this state, the low-pressure side communication groove 55a is connected to the first and second switching ports 57a, 57a.
b.

When the compressor 4 starts operating in this state, the guide pins 55h located at the upper ends of the cam grooves 53j move to the lower ends of the cam grooves 53j, and the main valve body 55 is moved to the valve housing 53j. While rotating inside the valve seat 57
The main valve element 55
Is seated on the valve seat 57 and reaches the first location. As a result, the distal end of the operating rod 55f contacts the valve seat 57 and the auxiliary valve element 5
5g opens the valve port 55c.

In this state, the low-pressure side communication groove 55a is
The high-pressure side communication passage 55b faces the first switching port 57a while the switching port 57b faces the two low-pressure ports. For this reason, the discharge pipe 5 communicates with the conduit 7 via the high-pressure communication path 55b and the first switching port 57a, and the second switching port 57b, the low-pressure communication groove 55a,
And the suction pipe 6 is connected to the conduit 8 via the two low pressure ports.
Communicate with

Therefore, the high-pressure refrigerant from the compressor 4 is
Through the discharge pipe 5, the high pressure side communication passage 55b, and the first switching port 57a, the refrigerant flows into the indoor heat exchanger 9A from the conduit 7,
From the conduit 8 via the throttle 10 and the outdoor heat exchanger 9B, the second
Through the switching port 57b, the low-pressure communication groove 55a, and the two low-pressure ports, the air returns from the suction pipe 6 to the suction port of the compressor 4, and the refrigeration cycle A enters the heating operation mode. Note that, for convenience, the position of the main valve body 55 of the flow path switching valve 100-3 in the heating operation mode is defined as a first location.

Thereafter, when the operation of the compressor 4 is stopped,
The guide pin 55h located at the lower end of the cam groove 53j moves along the cam groove 53j due to the urging force of the coil spring 59 acting on the main valve body 55 as the pressure of the refrigerant flowing into the valve housing 53 decreases. The main valve element 55 is moved to the upper end,
The main valve body 55 reaches the second intermediate position furthest away from the valve seat 57 as shown in FIG. The valve port 55c is closed by the auxiliary valve body 55g of the operating rod 55f whose tip is separated from the valve seat 57. Thereby, the low pressure side communication groove 55a returns to the first state facing the first and second switching ports 57a and 57b. The outer housing 53a, the upper and lower inner housings 53b and 53c, and the hollow chamber 55d shown in FIG.
Are the same as those of the second flow path switching valve 100-2 shown in FIG.

The flow path switching valve 100-
3, the same effect as that of the flow path switching valve 100-2 can be obtained.

Next, second and third embodiments of the control device of the refrigeration cycle will be described.

FIG. 2 is a block diagram of a main part of a control device for a refrigeration cycle according to a second embodiment. In the second embodiment, the first rotary type flow path switching valve 100-1 and the second rotary type This is applicable to the flow path switching valve 100-2.

The microcomputer 470 of the outdoor control unit 400 includes:
The IC [1] 406-1 composed of a double arm circuit is connected, and the electromagnetic coil 101 of the first rotary flow path switching valve 100-1 is connected to the IC [1] 406-1. The microcomputer 470 has a jumper terminal C5-.
1 is provided. Then, the microcomputer 470 controls the switching of the first rotary type flow path switching valve 100-1 or the second rotary type flow path switching valve 100-2 according to the selected state by the jumper terminal C5-1. IC [1] 40 when switching control of the first rotary flow path switching valve 100-1 is performed.
The direction of energization to the electromagnetic coil 101 is switched and controlled through 6-1. Also, the second rotary type flow path switching valve 100-2
Is controlled, the operation of the compressor 4 is controlled.

The microcomputer 470 stores a control program of the main routine of FIG. 3, a control program of a subroutine shown in FIG. 4, and a control program of a subroutine shown in FIG. The subroutine of FIG. 4 is for controlling the first rotary flow path switching valve 100-1, and the subroutine of FIG. 5 is for controlling the second rotary flow path switching valve 100-2. is there. Then, when the flow path switching valve to be controlled is selected by the jumper terminal C5-1, the flow path switching valve is switched and controlled by a corresponding control program.

When the processing of the main routine of FIG. 3 is started by turning on the power or the like, an initialization process is performed in step S1, and it is determined in step S2 whether or not the jumper terminal C5-1 has a jumper. If there is a jumper, the drive routine of the first rotary flow path switching valve 100-1 in FIG. 4 is executed in step S3, the refrigeration cycle is operated in step S5, and the process returns to step S2. If there is no jumper, the driving routine of the second rotary flow path switching valve 100-2 in FIG.
To operate the refrigeration cycle and return to step S2.

In the driving routine of the first rotary flow path switching valve shown in FIG. 4, it is determined in step S11 whether or not the requested operation mode is the cooling mode. 4 is started with the first predetermined ability, and it is determined in step S13 whether or not the position data is the first position. If it is not the first location, the process returns to the original routine. First
If it is a place, the second step is to the electromagnetic coil 101 in step S14.
The flow direction switching valve 100-1 is driven in the direction of the second position by energizing in the direction of the position, the driving in the direction of the second position is turned off after a predetermined time in step S15, and the routine returns to the original routine.

On the other hand, if the requested operation mode is heating, the compressor 4 is started with the first predetermined capacity in step S16, and it is determined in step S17 whether the position data is the second location. If it is not the second location, the process returns to the original routine. If it is the second location, in step S18 the electromagnetic coil 1
01 to the flow path switching valve 100-
1 is driven in the direction of the first location, the driving in the direction of the first location is turned off after a predetermined time in step S19, and the routine returns to the original routine. In this manner, the switching control for the first rotary flow path switching valve 100-1 selected by the jumper terminal C5-1 is performed.

In the driving routine of the second rotary flow path switching valve shown in FIG. 5, it is determined in step S21 whether the requested operation mode is cooling or not. If the cooling mode is requested, step S22 is performed. The following processes are performed, and if the heating mode is requested, the processes after step S28 are performed.

In step S22, it is determined whether or not the position data is the first position. If the position data is not the first position, the process proceeds to step S27. If the position data is the first position, the compressor 4 is rotated in the reverse direction in step S23. After starting, the position data is updated to the second location after a first predetermined time (approximately 10 seconds) in step S24. Next, the operation of the refrigeration cycle is stopped in step S25, the operation is waited for a third predetermined time (approximately 30 seconds) in step S26, and the process proceeds to step S27. In step S27, the compressor 4 is started at the first predetermined capacity (for example, 30 Hz), and returns to the original routine.

On the other hand, if the heating mode is requested in step S21, it is determined in step S28 whether or not the position data is the second location.
27, if it is the second location, the compressor 4 is started in the reverse rotation direction in step S29, and the position data is updated to the first location after a first predetermined time (approximately 10 seconds) in step S201. Next, the operation of the refrigeration cycle is stopped in step S202, and the operation is on standby for a third predetermined time (approximately 30 seconds) in step S203. Then, in step S27, the compressor 4
Is started at the first predetermined capability (for example, 30 Hz), and the process returns to the original routine. In this way, switching control is performed on the second rotary flow path switching valve 100-2 selected by the jumper terminal C5-1.

FIG. 6 is a block diagram of a main part of a control device for a refrigeration cycle according to a third embodiment. In the third embodiment, a second rotary type flow path switching valve 100-2 and the third rotary type This is applicable to the flow path switching valve 100-3.

The microcomputer 470 of the outdoor control section 400 is provided with a jumper terminal C5-1. Then, the microcomputer 470 controls the switching of the second rotary flow path switching valve 100-2 or the third rotary flow path switching valve 100-3 according to the selection state by the jumper terminal C5-1. The operation of the compressor 4 is controlled both when switching control of the second rotary flow path switching valve 100-2 and when switching control of the third rotary flow path switching valve 100-3.

The microcomputer 470 stores a main routine control program shown in FIG. 7, a subroutine control program shown in FIG. 5 of the second embodiment, and a subroutine control program shown in FIG. The subroutine of FIG. 5 is similar to the above-described second rotary type flow path switching valve 100-.
The subroutine in FIG. 8 is for controlling the third rotary flow path switching valve 100-3. Then, when the flow path switching valve to be controlled is selected by the jumper terminal C5-1, the flow path switching valve is switched and controlled by a corresponding control program.

When the power is turned on or the like, the processing of the main routine shown in FIG. 7 is started, an initialization process is performed in step S1 ', and in step S2', the presence or absence of a jumper of the jumper terminal C5-1 is determined. If there is a jumper, step S
At 3 ', the drive routine process of the second rotary flow path switching valve 100-2 in FIG. 5 is executed, and at step S5', the refrigeration cycle is operated and the process returns to step S2 '. If there is no jumper, the drive routine of the third rotary flow path switching valve 100-3 shown in FIG. 8 is executed in step S4 ', the refrigeration cycle is operated in step S5', and the process returns to step S2 '.

The driving routine of the second rotary type flow path switching valve shown in FIG. 5 is the same as that of the second embodiment.
Second rotary flow path switching valve 100 selected in 5-1
The switching control for -2 is performed.

In the driving routine of the third rotary flow path switching valve shown in FIG. 8, it is determined in step S31 whether the requested operation mode is cooling or not. If the heating mode is requested, step S32 is performed. The following processing is performed, and if the cooling mode is requested, the processing from step S38 is performed.

In step S32, it is determined whether or not the position data is the first location.
Proceeding to 37, if it is the first location, the compressor 4 is started at the first predetermined capacity (for example, 30 Hz) in step S33, and the position data is updated to the second location after the first predetermined time (about 10 seconds) in step S34. I do. Next, the operation of the refrigeration cycle is stopped in step S35, the operation is waited for a third predetermined time (approximately 30 seconds) in step S36, and the process proceeds to step S37. In step S37, the compressor 4 is started at the second predetermined capacity (for example, 10 Hz), and returns to the original routine.

On the other hand, in step S38, it is determined whether or not the position data is the second position. If the position data is not the second position, the process proceeds to step S304.
To start the compressor 4 at the second predetermined capacity (for example, 10 Hz), and in step S301, after the first predetermined time (approximately 10 seconds), the position data is updated to the first location. Next, step S3
02, the operation of the refrigeration cycle is stopped, and step S303 is performed.
Waits for a third predetermined time (approximately 30 seconds). Then, in step S304, the compressor 4 is started at the first predetermined capacity (for example, 30 Hz), and returns to the original routine. In this manner, the switching control for the third rotary flow path switching valve 100-3 selected by the jumper terminal C5-1 is performed.

FIG. 15 is a circuit diagram showing an example of the flow path switching valve driving section. This circuit is controlled by the control section C1 via the signal conversion section 70, and performs full-wave rectification of, for example, commercial AC power. The smoothed DC power is applied to the first to fourth transistors TR1, TR2, TR3, TR4 to switch between conduction and non-conduction. Thereby, via the positive power line BL + and the negative power line BL−,
The flow path switching valve drive source 101, that is, the electromagnetic coil 101 is configured to flow in one of a forward direction indicated by a solid arrow in FIG. 15 and a reverse direction indicated by a dotted arrow in FIG. .

Then, the control unit C1 sets the flow path switching valve 100
When performing the valve switching operation, two types of command signals corresponding to the switching direction are output, and the command signals are converted to a signal conversion unit 70.
(For example, a photocoupler and a driver circuit), and in response to the command signal, among the first to fourth transistors TR1, TR2, TR3, and TR4, the transistors TR1, TR2, and TR2 corresponding to the type of the command signal. TR3
By causing the signal converter 70 to output a bias signal to the base of the TR 4, the above-described energization or non-energization of the electromagnetic coil 101 in the forward or reverse direction is performed.

Although three types of rotary flow path switching valves 100 have been described as controlled objects, the flow path switching valves 10
Needless to say, the present invention performs suitable control even if 0 is a slide type or another type. For example, the present invention can also be applied to a slide type four-way valve having a latch type electromagnetic pilot unit driven by a DC bidirectional drive using a permanent magnet disclosed in Japanese Patent Application Laid-Open No. 9-72633. Further, in the case of the electric drive valve, the driver IC has been described as an example of the flow path switching valve drive unit 406. However, it is possible that energization / non-energization may be performed by a contact such as a relay which is widely used. Needless to say.

[0112]

As described above, according to the refrigeration cycle control apparatus of the first aspect, since the selection step determining means for selecting and determining the control steps corresponding to the plurality of flow path switching valves is provided, A plurality of different flow path switching valves can be selectively switched and controlled. Therefore, reliability can be ensured for the plurality of flow path switching valves, and the cost can be reduced.

According to the refrigeration cycle control device of the second aspect, the present invention is applied to a combination of an electrically driven valve electrically driven by the operating means and a non-electrically driven valve non-electrically driven. The same operation and effect as those of the first aspect can be obtained.

According to the refrigeration cycle control device of the third aspect, the same effect as that of the first aspect can be obtained by applying the present invention to a combination of a plurality of non-electrically driven valves that are non-electrically driven.

[Brief description of the drawings]

FIG. 1 is a main block diagram of a control device for a refrigeration cycle according to a first embodiment of the present invention.

FIG. 2 is a main block diagram of a control device for a refrigeration cycle according to a second embodiment of the present invention.

FIG. 3 is a flowchart of a main routine according to a second embodiment of the present invention.

FIG. 4 is a flowchart of a subroutine for controlling a first rotary flow path switching valve according to the embodiment of the present invention.

FIG. 5 is a flowchart of a subroutine for controlling a second rotary flow path switching valve according to the embodiment of the present invention.

FIG. 6 is a main block diagram of a control device for a refrigeration cycle according to a third embodiment of the present invention.

FIG. 7 is a flowchart of a main routine according to a third embodiment of the present invention.

FIG. 8 is a flowchart of a subroutine for controlling a third rotary flow path switching valve according to the embodiment of the present invention.

FIG. 9 is a principle block diagram of an embodiment of a control device for a refrigeration cycle of the present invention.

FIG. 10 is a block diagram illustrating an example of a refrigeration cycle according to the embodiment of the present invention.

FIG. 11 is a block diagram mainly showing an electric system of an indoor control unit and an outdoor control unit according to the embodiment of the present invention.

FIG. 12 is a cross-sectional view showing a first rotary flow path switching valve according to the embodiment of the present invention.

FIG. 13 is a cross-sectional view showing a second rotary flow path switching valve according to the embodiment of the present invention.

FIG. 14 is a sectional view showing a third rotary flow path switching valve according to the embodiment of the present invention.

FIG. 15 is a circuit diagram illustrating an example of a flow path switching valve drive unit according to the embodiment of the present invention.

[Explanation of symbols]

 Reference Signs List 4 compressor 5 discharge pipe 6 suction pipe 7, 8 conduit 9A indoor heat exchanger 9B outdoor heat exchanger 53 valve housing 53j cam groove 55 main valve body 57 valve seat 100 flow switching valve 101 electromagnetic coil 200 accumulator 300 indoor control unit 400 Outdoor controller 470 Microcomputer C Controller C5-1, C5-2 Jumper terminal A Refrigeration cycle

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Seiichi Nakahara 535 Sasai, Sayama-shi, Saitama Prefecture Sagimiya Manufacturing Co., Ltd. Terms (Reference) 3L060 AA08 CC02 CC03 CC04 CC19 DD02 EE02 EE05 EE06 EE09 3L092 AA02 BA26 DA19 EA20 FA22

Claims (3)

[Claims] 1. A refrigeration cycle control device for switching and controlling a flow path switching valve of a refrigeration cycle, comprising: a selection determination means for selecting and determining one flow path switching valve from a plurality of flow path switching valves; A control step corresponding to each of the flow path switching valves, wherein the selected and determined flow path switching valve is switched and controlled in a control step corresponding to the flow path switching valve. apparatus. 2. The plurality of flow path switching valves include an electrically driven valve electrically driven by an operation means, and a non-electrically driven valve non-electrically driven. 2. The control device for a refrigeration cycle according to claim 1, further comprising: a control step of switching control of a dynamic drive valve; and a control step of switching control of the non-electrically driven valve. 3. 3. The plurality of types of flow path switching valves include a plurality of non-electrically driven valves that are non-electrically driven, and include a plurality of control steps for switching and controlling the plurality of non-electrically driven valves. The control device for a refrigeration cycle according to claim 1, wherein: