JPH08159614A - Refrigeration cycle device - Google Patents

Abstract

PURPOSE: To make it possible to perform defrosting operation while continuing cooling and heating operations in a simple structure by providing a first valve body which switches over to cooling and heating operations and a second valve body which switches over to defrosting operation and a control means which controls supply voltage which maintains a switched over state of the first and second valve bodies. CONSTITUTION: Defrosting operation is carried out during heating operation and is controlled with the voltage applied to an electromagnet 51 of a magnetic force switch over unit 26. Both upper and lower stays 50 are magnetized where a magnet member and a second valve body 5 are turned. At that time, a first valve body 4 holds a state of a heating operation, and is not turned. A second through hole 35 of the first valve body 4 which interlocks with a defrosting port 17 is opened in a case 21 as opposed to a first through hole 43 of the second valve body 5. A first through hole 34 of the first valve body 4 is closed. A high temperature high pressure gas in the case is directly supplied to an outdoor heat exchanger by way of a bypass pipe and defrosted. In addition, the high temperature high pressure gas flows into a clearance between a valve base and the first valve body 4, thereby continuing the heating operation.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to, for example, a refrigeration cycle apparatus having a compressor having a switching valve for switching a flow path of a working gas.

[0002]

2. Description of the Related Art Generally, there is an air conditioner (refrigeration cycle device) capable of both cooling and heating. This air conditioner has a heat exchanger placed indoors and a heat exchanger placed outdoors, and switches the flow path of the working fluid to be circulated in these heat exchangers during cooling and heating. A flow path switching valve is provided.

Generally, as such a flow path switching valve,
Direct acting four-way switching valves are widely used. The four-way switching valve has a main body formed in a cylindrical shape, and a slide valve provided in the main body and capable of reciprocating along the axial direction of the main body. The four-way switching valve switches the flow path by linearly moving the sliding valve in the main body.

Further, this four-way switching valve is generally controlled via an electromagnetic valve, and by operating this electromagnetic valve, the pressure in the compressor is introduced into the switching valve through a capillary tube, and The sliding valve is driven by pressure.

By the way, as a fluid compressor with a built-in four-way valve in which such a four-way switching valve and a solenoid valve are built in a fluid compressor, the one disclosed in FIG. 4 of Japanese Utility Model Laid-Open No. 60-124595 has been disclosed. There is.

The present invention is a compressor of a type in which a high-pressure discharge gas discharged from the compressor section is filled in a hermetically sealed case that houses a compressor section and an electric motor section. Built-in switching valve and solenoid valve.

According to the present invention, by placing the four-way switching valve and the solenoid valve in a case filled with the high-pressure gas, a pipe for introducing high-pressure gas for connecting the compressor and the switching valve becomes unnecessary, and It is intended to effectively prevent damage to the capillary tube connecting the switching valve and the solenoid valve due to an external force.

[0008]

By the way, the four-way switching valve built in the compressor is a direct-acting type in which the flow path is switched by sliding the sliding valve in the main body. It is necessary to keep the sliding valve in close contact with the valve seat. For this reason, there is a problem that gas cannot be leaked from between the sliding valve and the valve seat at the time of stop, and the pressure balance in the refrigeration cycle pipe cannot be swiftly achieved. Therefore, it is considered that it is not possible to quickly restart after the stop or switch the operation between cooling and heating.

On the other hand, in the conventional refrigeration cycle apparatus, when frost is formed on the outdoor heat exchanger during the heating operation, the high-temperature high-pressure gas discharged from the compressor is passed through the bypass pipe to the outdoor heat exchanger. The heat is defrosted by directly supplying the heat exchanger to the heat exchanger. However, in this case, it is necessary to provide a switching valve for switching the high-temperature high-pressure gas in the bypass pipe in addition to the four-way switching valve.

However, if two switching valves are provided, the piping structure may be complicated. Further, if the switching valve for the bypass pipe is to be provided inside the case of the fluid compressor, the size of the fluid compressor becomes large.

Further, there arises a problem that the number of electric wires taken out from the case increases, a complicated control circuit is required to control them, and power consumption increases.

The present invention has been made in view of the above circumstances, and the gas pressure can be easily and quickly balanced when the operation is stopped, and the defrosting operation can be performed while continuing the heating operation with a simple structure. Moreover, it is an object of the present invention to provide a refrigeration cycle device with low power consumption.

[0013]

The first means of the present invention is a refrigeration cycle in which a compressor, a switching valve, an indoor heat exchanger, a pressure reducing device, and an outdoor heat exchanger are sequentially connected by piping, and this refrigeration cycle. In the refrigeration cycle apparatus having a control unit for controlling the above, the switching valve is an electromagnet whose magnetic poles can be switched, and a permanent magnet which is disposed so as to face the electromagnet and is rotationally driven by switching the magnetic poles of the electromagnet. And attached to this permanent magnet to switch to cooling / heating operation
And a second valve body that is attached to the permanent magnet and switches to the defrosting operation, and the control unit includes the first and second valve bodies.
A refrigeration cycle apparatus comprising: a control unit that controls a supply voltage for maintaining a switching state of a second valve body by controlling a voltage application to an electromagnet.

A second means is the refrigeration cycle apparatus of the first means, wherein the control means performs voltage application to the electromagnet by phase control.

A third means is the refrigeration cycle apparatus of the first means, wherein the control means applies the voltage to the electromagnet by wave number control.

A fourth means is the refrigeration cycle apparatus of the first means, characterized in that the control means performs voltage application to the electromagnet by DC chopper control.

A fifth means is the refrigeration cycle apparatus of the first means, wherein the switching valve is provided in a case filled with a high pressure discharge gas of the compressor. .

A sixth means is the refrigeration cycle apparatus according to the fifth means, wherein the switching valve is provided on the valve base attached to the case and the valve base, and the inside and outside surfaces of the case of the valve base. Open to the outdoor heat exchanger, the indoor heat exchanger and the three ports connected to the suction side of the compressor and the valve base, which is opened to the inside and outside of the case of the valve base, and is opened outdoors during heating. The defrosting port connected to a pipe connected to the refrigerant inlet of the heat exchanger and the surface of the first valve body facing the valve base are provided with the first valve body having a predetermined size. By pivoting at an angle, a communication groove that selectively communicates two of the three ports with each other and a communication groove that is provided in the first valve body and that communicates with another port and the defrosting port. Of the first and second through holes and the second valve body The second valve body is provided on a surface facing the first valve body, and the second valve body rotates by a predetermined angle with respect to the first valve body, so that the first valve body or the second valve body of the first valve body is rotated. And a closing means for selectively closing the through hole of the refrigeration cycle.

A seventh means is the refrigeration cycle apparatus according to the sixth means, wherein the driving torque by the electromagnet is based on a static frictional force generated between the first valve body and the valve base during the operation of the compressor. Is also smaller than the static frictional force generated between the first valve body and the second valve body.

[0020]

According to such means, the heating and cooling operations can be switched by driving by switching the magnetic poles of the permanent magnet and the electromagnet attached to the first and second valve bodies, and
The outdoor heat exchanger can be defrosted while continuing the heating operation. Then, by applying voltage to the electromagnet by phase control, wave number control, and DC chopper control, the power supplied to the electromagnet can be controlled.

Further, at the time of stop, by separating the first valve body from the valve base, the pressure in the pipe can be balanced through the gap. Further, in view of the fact that the static frictional force generated between the valve base and the second valve body due to the high-pressure refrigerant in the case is large during the compressor operation and is small during the stop, the first valve body and the second valve body are considered to be small. Since the relationship with the driving torque of the electromagnet that rotationally drives the second valve body is adjusted, only the second valve body is driven during the compressor operation to switch to the defrosting operation, and during the stop, Both the first and second valve bodies can be driven, and switching to cooling / heating operation can be performed.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. First, a first embodiment will be described. The refrigeration cycle apparatus of the first embodiment has the fluid compressor shown in FIG. This fluid compressor has a closed case 1
The case 1 includes a compression part 2 for compressing the low-pressure refrigerant sucked from the outside of the case 1 and discharging the compressed high-pressure refrigerant into the case 1, and two compression parts 2 attached to the upper wall part of the case. Case 1 by rotating the valve bodies 4 and 5
A rotary five-way switching valve 3 (which will be described in detail later) that switches the discharge flow path of the refrigerant to the outside and the suction flow path to the compression section is provided.

The compression section 2 is composed of a rotary type compression mechanism 6 provided in the lowermost part of the case 1 and an electric motor 7 provided in the middle of the case 1 for driving the compression mechanism 6. The compression mechanism 6 compresses the refrigerant by eccentrically rotating a roller-shaped piston 9 in two cylinders shown in FIG. 8, and the piston 9 is rotatably provided around a vertical axis. Held by a shaft 10.

On the other hand, the electric motor 7 is a DC brushless motor comprising a cylindrical stator 7a fixed to the case 1 and a rotor 7b provided in the stator 7a, and the rotor 7a is provided on the shaft 10. It is fixed to the upper end.

The power supply wiring 12 derived from the electric motor 7 is connected to the first sealed terminal 13 fixed to the upper wall of the case 1. Then, the electric motor 7
Operates when power is supplied from outside the case 1 through the sealed terminal 13, and rotationally drives the shaft 10. As a result, the compression mechanism 6 compresses the refrigerant sucked from the suction pipe shown in FIG. 20 in the cylinder 8 and discharges it into the case 1.

The five-way switching valve 3 has three ports 14 provided at 90 ° intervals in the circumferential direction as shown in FIG.
~ 16 and defrosting port 1 formed with a smaller diameter than this
And a valve base 18 having The three ports 14 to 16 are connected to the indoor heat exchanger 23, the compression mechanism 8 provided in the case 1 and the outdoor heat exchanger 22 by the pipes 19 to 21 in the figure, respectively, and the refrigeration cycle. Are configured. In addition, the defrosting port 17
Is connected to the outdoor heat exchanger 22 by a bypass pipe 24 to form a defrosting circuit.

The structure of the five-way switching valve 3 and its control will be described in more detail below. As shown in FIGS. 1 and 3B, the five-way switching valve 3 (hereinafter, referred to as switching valve) includes the valve base 18 fixed to the closed case 1,
The first valve element 4 (described above) that is rotatably provided on the lower surface of the valve base 18 and switches the flow path of the working gas;
Second valve body 5 (previously described) which is also rotatably provided on the lower surface of the valve body 4, and a magnet member 25 (permanent magnet) attached to the outer peripheral surfaces of the first and second valve bodies 4 and 5. The magnetic force is applied to the magnet member 25 to rotationally drive the first and second valve bodies 4 and 5 to cover the magnetic force switching unit 26 (electromagnet) for switching the flow path and the switching valve 3. And a holder 27.

As shown in FIG. 4, the valve base 18 has a circular shape in a plan view, and has a lower end portion with a flange portion 18a having a larger diameter than the upper end portion. As shown in FIG. 1, the valve base 18 is attached to the lid portion 1a that closes the upper end of the closed case 1.

That is, the upper wall of the lid portion 1a is shown in FIG.
A through hole shown by 8 is formed. The valve base 17 is attached to the lid 1a by inserting the upper end side into the through hole 28, and is fixed in a state where the through hole 28 is hermetically closed by welding, for example. Has become.

Further, as shown in FIG. 4, this valve base 1
8 is provided on the central axis L of the valve base 18,
The upper end of the central shaft 29, the lower end of which protrudes into the case 1, is fixed. And in this valve base 18,
The above-described three ports 14 to 16 penetrating the valve base 18 in the axial direction and the defrosting port 17 are provided.

The port 15 located at the center among the three ports 14 to 16 is a low pressure gas port connected to the suction pipe 20 extending from the compression mechanism 8 as shown in FIG. And this low pressure gas port 1
The other two ports 14 and 16 sandwiching 5 are the first and second connection ports connected to the indoor heat exchanger and the outdoor heat exchanger shown by 23 and 22 in FIGS. 1 and 2, respectively. Has become.

Further, the collar portion 18a of the valve base 18 is
The lower surface of the stopper is provided with a stopper indicated by 31 in FIG. As shown in FIG. 3B, the stopper 31 is attached by screwing and fixing the upper end portion to the valve base 18.

Next, the first valve body 4 will be described. As shown in FIG. 3 (b), the first valve body 4 is formed by inserting the central shaft 29 projecting from the valve base 18 into a central hole 4 a provided in the central portion thereof. The upper surface is brought into contact with the lower surface of the valve base 18 and is rotatably attached to the valve base 18.

On the upper surface of the first valve body 4, 33 in FIG.
The concave groove indicated by is provided in the circumferential direction over about 90 °. As shown in FIG. 5, the recessed groove 33 is a passage having an inner surface formed in a semicircular cross section, and when the first valve body 4 is rotated 90 °, the three ports 1 described above are provided.
Two adjacent ports of 4 to 16 at 90 ° intervals, that is, the low-pressure gas port 15 (shown by a chain line) and the first connection port 14 (shown by a chain line) as shown in FIG. 10A. Alternatively, as shown in FIG. 12A, the low pressure gas port 15 and the second connection port 16 (shown by the chain line) can be switched to communicate with each other.

Further, as shown in FIG. 5, the first valve body 4 has first and second through holes 34, 35 penetrating in the axial direction of the first valve body 4 in the circumferential direction. It is provided at 90 ° intervals. The first and second through holes 34 and 35 are formed to have a diameter smaller than the width of the recessed groove 33.

Then, the first and second through holes 34, 3
5, the first valve body 4 is 90 ° around the center hole 4a.
By being rotationally driven within the range of FIG.
(A), FIG. 11 (a), and FIG. 12 (a), the first and second connection ports 14, 16 of the valve base 18 are shown.
(Shown by a chain line) or the defrosting port 17 (shown by a chain line).

Further, when the first valve body 4 is attached to the valve base 18, the radially outer edge portion of the upper surface of the first valve body 4 is provided with a protrusion on the lower surface of the valve base 18. A guide groove 37 into which the above-mentioned stopper 31 is inserted is provided as a recess.

The guide groove 37 is provided over a range of 90 ° in the circumferential direction, and when the first valve body 4 is driven to rotate, one end of the guide groove 37 in the circumferential direction and the guide groove 37 are formed. By bringing the other end into contact with the stopper 31, as shown in FIGS. 10 to 12, the rotation range (maximum rotation angle) of the first valve body 4 is regulated to 90 °. There is.

As shown in FIG. 5A, the first
A seal member 33a is provided around the concave groove 33 on the upper surface of the valve body 4 in order to hermetically seal the communicating portion between the first valve body 4 and the valve base 18. 34
The seal member 34a is integrally formed around the second through hole 35, and the seal member 35a is integrally formed around the second through hole 35. Further, the seal member 37a formed around the guide groove 37 is for maintaining the gap between the valve base 18 and the first valve body 4 at a predetermined value.

From the positional relationship between the recessed groove 33 and the first and second through holes 34 and 35, the second connection port 16 is located at the first through hole as shown in FIG. 10 (a). Three
4, the first connection port 14 and the low-pressure gas port 15 communicate with each other through the concave groove 33, and the defrosting port 17 includes the second defrosting port.
Of the through hole 35.

As shown in FIG. 12A, when the first connection port 14 communicates with the second through hole 35, the second connection port 16 and the low pressure gas port. 15 are connected to each other by the recessed groove 33, and the defrosting port 17 is provided in the first through hole 3
It is designed to communicate with 4.

Then, the first and second through holes 34, 3
The valve 5 communicates with the case 1 unless it is closed by the second valve element 5 described later. Further, as shown in FIG. 5, the upper end portion of the first valve body 4 is
The flange portion 4b has a flange shape that slightly protrudes outward in the radial direction of the first valve body 4. At a predetermined position along the circumferential direction of the outer surface on the lower end side of the flange portion 4b, a first positioning projection 39 that engages with the magnet member 25 is provided so as to project radially outward. The two first convex portions 39 are provided 180 ° apart in the circumferential direction.

Next, the second valve body 5 attached to the lower surface of the first valve body 4 will be described. This second valve body 5
6 is as shown in FIG. 6, in which a central hole 5a provided in the central portion of the valve base 18 to the first valve body 4 is provided.
By inserting the central shaft 29 that penetrates through and protrudes through, the upper surface of the central shaft 29 faces the lower surface of the first valve body 4 and is rotated with respect to the valve base 18 and the first valve body 4 ( It can be attached freely. (FIG. 3 (b)) On the upper surface of the second valve body 5, the first to the second valve bodies 40 to 42 shown in FIG.
A third circular seal member 120 is provided around the center hole 5a.
It is integrally formed with the second valve body 5 at intervals of °.

The first to third sealing members 40 to 42
Is formed to have a larger diameter than the first and second through holes 34 and 35 provided in the first valve body 4, and these can be closed as needed.

The second and third seal members 41,
Between 42, as shown in FIG. 6, first and axially penetrating the second valve body 5 located on the concentric circle where the second and third sealing members 41 and 42 are arranged, Second through hole 4
3, 44 are formed.

The first and second through holes 43 and 44 are the first and second through holes 3 which are opened in the lower surface of the first valve body 4.
The first and second through holes 34 and 35 are formed to have the same diameter as those of the first and second through holes 34 and 35 so as to communicate with each other in the case 1.

Further, as shown in FIG. 6, the positional relationship between the second seal member 41 and the second through hole 44 is set so as to form an angle of 90 ° with the center hole 5a as the center. , The third seal member 42 and the first through hole 43
The positional relationship of is also set so as to form 90 °.

Therefore, as shown in FIG.
When the second through hole 44 of the second valve body 5 faces (communicates with) the first through hole 34 provided in the first valve body 4, the second valve body 5 The second seal member 41 provided at the second seal member 41 is provided in the second through hole 35 of the first valve body 4.
Is to be closed.

Further, as shown in FIG. 12B, the first through hole 43 of the second valve body 5 is provided with the second through hole provided in the first valve body 4. When facing the hole 35, the third seal member 42 of the second valve body 5 is provided.
Closes the first through hole 35 of the first valve body 4.

That is, the second valve body 5 is the same as the first valve body.
Of the first and second through holes 34, 35 provided in the valve body 3, only one of them is allowed to communicate with the case 1, and the other one is closed.

On the outer peripheral surface of the second valve body 5, a second convex portion indicated by 45 in FIG. 16 is provided so as to project radially outward of the valve body 5. The second convex portion 45 engages with a slit 48 provided in the magnet member 25, which will be described later, so as to couple the second valve body 5 and the magnet member 25 such that they cannot rotate relative to each other. . This will be described in detail later.

As shown in the figure, the second convex portion 45 is 30 ° + α ° in the circumferential direction (α is the width of the first convex portion 39 provided on the first valve body 4). The width is formed by two pieces, and two pieces are provided so as to project at positions separated by 180 ° in the circumferential direction.

Next, the magnet member 25 attached to the outside of the first and second valve bodies 4, 5 will be described. As shown in FIGS. 7 and 8, the magnet member 25 includes a thin-walled cylindrical collar 46 that is externally inserted into the first and second valve bodies 4 and 5, and a permanent member fixed to the outer surface of the collar 46. Magnet 4
It consists of 7.

The upper end of the collar 46 is shown in FIG.
Is provided with a slit 48. The slits 48 are provided with a width of 30 ° + α ° (the same width as the second convex portion 82) in the circumferential direction, and two slits 48 are provided 180 ° apart from each other in the circumferential direction of the collar 46. ing.

The first and second valve bodies 4 and 5 have the first and second convex portions 39 and 45 provided on their outer peripheral surfaces so as to project.
As shown in FIG. 8, it is combined with the magnet member 25 in a state of being positioned in the slit 48.

As shown in FIG. 8, since the second convex portion 45 and the slit 48 of the second valve body 5 and the magnet member 25 are formed to have the same width, they cannot rotate relative to each other. Have been combined. Further, in the first valve body 4, since the width of the first convex portion 39 is narrower than that of the slit 48,
It is rotatable as shown by the arrow in the figure. Specifically, the first valve body 4 is rotatable in the range of 30 ° in the circumferential direction with respect to the magnet member 25 and the second valve body 5.

The permanent magnet 47 fixed to the outer peripheral surface of the collar 46 is divided into two parts at 180 ° intervals, each of which is composed of an N pole portion 47a and an S pole portion 47b. The magnet member 34 has a magnetic force switching unit 26 described below.
It is driven by magnetic force switching (suction and repulsion).

Next, the magnetic force switching section 26 will be described. As shown in FIGS. 3D and 9, the magnetic force switching unit 26 includes a pair of strip-plate-shaped iron stays 50 provided in parallel with each other and a base end portion (one end portion) of the stay 50. )
It is composed of an electromagnet 51 installed between them. This electromagnet 51
Is an iron core 52 having both ends fixed to the pair of stays 50,
The lead wire (coil) is wound around the iron core 52.

As shown in FIG. 3D, the stay 50 is
Is bent along the outer peripheral surface of the magnet member 25 (permanent magnet 47) fixed to the first and second valve bodies 4 and 5, and the bending radius of the inner surface is the magnet member. The outer diameter of the permanent magnet 47 is set to be larger than the outer diameter of the permanent magnet 47 so that there is a predetermined minute gap with the outer peripheral surface of the.

As shown in FIG. 9, the tips of the two stays 50 are set so as to be separated from each other at an angle of about 90 ° along the bending direction of the stays 50.

The magnetic force switching section 26 can magnetize the pair of stays 50 to different polarities (N pole or S pole) by applying a direct current to the lead wire of the electromagnet 51, and the magnetism thereof is obtained. By switching, the magnet member 25 and the first and second valve bodies 4 and 5 can be rotationally driven by attraction and repulsion with the permanent magnet.

Next, the holder 27 provided outside the tip of the stay 50 will be described with reference to FIG.
This holder 27 is a thin-walled cylindrical member, and is shown in FIG.
As shown in FIG. 3, the upper end portion is the collar portion 18 a of the valve base 18.
Is fixed to the lower surface of the outer edge of the. Also, this holder 27
As shown in FIGS. 3 (c) and 3 (d),
A notch portion 27 a is provided for taking out the base end side of the stay 50 of No. 6 from the holder 27. The holder 27 allows the magnetic force switching portion 2 to be formed by the notch portion 27a.
6 is positioned and rotation is prevented.

On the other hand, as shown in FIGS. 3B and 3E, it extends downward from the lower end of the holder 27 and the valve base 18 through the first and second valve bodies 4 and 5. A pressing member indicated by 55 in FIG. 3 is fixed to the lower end of the ejected central shaft 29.

That is, the pressing member 55 is formed in the shape of a strip plate, and both ends in the longitudinal direction are fixed to the lower end of the holder 27 by welding. Also, this pressing member 2
The central portion of 7 is fixed to the lower end of the central shaft 29 by screwing.

Further, between the central portion of the pressing member 55 and the lower surface of the second valve body 5, a spring shown by 56 in FIG. 3 is inserted in a state of being compressed in the axial direction, and The second valve bodies 4 and 5 and the magnet member 25 are urged in a direction of pressing the lower surface of the valve base 18.

The urging force of the spring 56 is such that the compressor 1 is not in operation, that is, the case 1 has no high pressure, and the high and low pressure difference between the high pressure gas and the low pressure gas inside and outside the switching valve 3. Is not acting, the first valve body 4 is owing to the weight of the first and second valve bodies 4 and 5.
Is adjusted to a strength that allows a minute gap to be formed between the upper surface of the valve base 18 and the lower surface of the valve base 18.

Since the inside of the case 1 is maintained at a high pressure during operation of the compressor, the first valve body 4 is provided with the biasing force of the spring 56 and the first valve body 4. The force generated by the pressure difference between the low-pressure gas in the concave groove 33 and the high-pressure gas in the case 1 is pressed (adhered) to the valve base 18.

On the other hand, the second valve body 5 is pressed against the lower surface of the first valve body 4 by a force obtained by subtracting the weight of the first valve body 4 from the urging force of the spring 56. . Therefore, during operation, the pressing force of the first valve body 4 against the valve base 18 is larger than the pressing force of the second valve body 5 against the first valve body 4.

The driving torque applied to the magnet member 25 by the magnetic force switching unit 26 is the static friction force F1 (biasing force of the spring 56) generated between the first valve body 4 and the valve base 18 during this operation. (Corresponding to the above only) and is larger than the static friction force F2 (F2 <F1) generated between the first valve body 4 and the second valve body 5.

Therefore, during the heating and cooling operations, the magnetic force switching section 26 can drive only the second valve body 5, and after the operation is stopped, the first and second valve bodies 5 are driven. Both 4 and 5 can be driven.

Next, the control system of this refrigeration cycle apparatus will be described. The power supply wiring led out from the electromagnet 51 of the magnetic force generator 26 of the switching valve 3 is connected to the second sealed terminal 59 provided on the lid 1a of the case 1 as shown in FIG. . As shown in FIG. 2, the second sealed terminal 59 is provided on the side of the first sealed terminal 13 connected to the electric motor 7 described above.

That is, as shown in FIGS. 1 and 2, the lid portion 25a has second and third through holes 60a, 60a, which are located laterally of the first through hole 28 in which the switching valve 3 is attached. 6
0b is provided, and the first and second sealed terminals 1 are provided.
3, 59 are the second and third through holes 60a,
It is attached in a state of hermetically closing 60b.

On the other hand, the first and second sealed terminals 13 and 5 are
Each external terminal of 9 is connected to the control part shown by 62 in the drawing. The control unit 62 uses the electric motor 7 (compression mechanism 6).
The inverter circuit 63 for driving the switching valve 3 and the control circuit 64 for driving the switching valve 3.

The inverter circuit 63 is connected to the wirings derived from the external terminals of the first hermetically sealed terminal 13. Further, the control circuit 64 is connected to the wiring led from the second sealed terminal 59. The control circuit 64 is configured as shown in FIG. 10, for example.

That is, the energization of the electromagnet 51 of the magnetic force switching section 26 from the AC power source 65 is carried out via a phototriac shown by 66 in the figure. A microcomputer (CPU) 67 is shown in FIG.
Is configured to determine whether or not to energize the phototriac 66 with respect to the AC 0V (zero cross) timing detected by the phototransistor 68, and output it. Therefore, the voltage applied to the coil of the electromagnet 51 is half-wave controlled as shown in FIGS. 10 (c) and 12 (c).

That is, the control circuit 65 is responsive to the command from the microcomputer 66 to generate the electromagnet 51.
A positive current or a negative current can be selectively applied to. Further, the application of current can be stopped as shown in FIGS. 10 (d) and 12 (d).

By switching the positive / negative of the current applied to the electromagnet 51 in this manner, the magnetic force switching section 26 is switched.
As shown in FIGS. 10 to 12, the magnetism of the pair of stays 50 can be switched between N pole and S pole.
It is also possible to stop the generation of magnetic force.

The microcomputer 67 is
Based on the zero-cross point detected as described above, an energization signal is sent to the phototriac 66 to perform half-wave control, but in the defrosting operation described later, FIG.
As shown in (d), it has a function of emitting an energization signal with a certain time delay from the zero-cross point and controlling the phase of the half-wave rectified voltage. This will be described later together with the operation.

Next, the control (operation) of the refrigeration cycle having the above-described compressor will be described. First, the state at the time of stop will be described.

Although not shown, at the time of stop, the first and second valve elements 4 and 5 are slightly moved against the biasing force of the spring 56 by the own weight of the first and second valve elements 4 and 5. As it descends, the upper surface of the first valve body 4 and the lower surface of the valve base 18 are slightly separated from each other.

In this case, the first and second valve bodies 4 and 18 are separated from each other through the gap formed between them.
The connection ports 14 and 16, the low pressure gas port 15 and the defrosting port 17 are all in communication with each other. Therefore, the pressure in the piping of this refrigeration cycle is balanced.

Next, the control when the heating operation is performed from this state will be described with reference to FIGS. 10 (a) to 10 (d).
When performing the heating operation, the voltage applied to the electromagnet 51 of the magnetic force switching valve section 26 is controlled by the control circuit 64 as shown in FIG.
Control is performed as shown in the waveform chart of 0 (c). With this,
The stay 50 (magnetic piece) located on the upper side in the figure is magnetized to the S pole, and the stay 50 located on the lower side is magnetized to the N pole.

Therefore, the stay 50 in which the N pole portion 47a of the magnet member 25 (permanent magnet 47) is located on the upper side in the figure.
And the S pole portion 47b is attracted to the stay 50 located on the lower side, whereby the magnet member 25
Rotates clockwise.

As described above, the second valve body 5 is combined with the magnet member 25 such that the second valve body 5 cannot rotate relative to the magnet member 25. The first valve body 4 is supported by the second valve body 5. Therefore, the first and second valve bodies 4 and 5 rotate together with the magnet member 25.

Then, as shown in FIG. 10 (a), a stopper 31 protruding downward from the lower surface of the valve base 18 is provided.
However, if it comes into contact with one end of the guide groove 37 of the first valve body 4 in the circumferential direction, only the first valve body 4 stops rotating.

As a result, as shown in FIG.
The connection port 14 and the low-pressure gas port 15 of the
The valve body 4 is communicated with the concave groove 33 provided in the valve body 4. The second connection port 16 is connected to the first valve body 4
The first defrosting port 17 faces the first through hole 34 and the defrosting port 17 faces the second through hole 35.

Further, as shown in FIG. 10B, the first convex portion 39 provided on the first valve body 4 has one end in the circumferential direction of the slit 48 provided on the collar 46 of the magnet member 25. When it comes into contact with, the rotation of the magnet member 25 and the second valve body 5 is stopped.

As a result, as shown in FIG.
The second through hole 35 opening in the valve body 4 of
It is closed by the second seal member 41 provided on the valve body 5.

On the other hand, the first through hole 3 of the first valve body 4
4 is opposed to the second through hole 44 provided in the second valve body 5. As a result, the second connection port 16 provided on the valve base 18 has the first through hole 34 of the first valve body 4 and the second through hole 44 of the second valve body 5 connected thereto. It will communicate with the inside of the said case 1 through.

In this state, the electric motor 7 shown in FIG. 1 is operated. When the electric motor 7 operates, the compression mechanism 6 operates, and the low-pressure gas sucked from the suction pipe 20 is compressed. The high pressure gas after being compressed is the case 1 above.
Is discharged inside. The high-pressure gas filled in the closed case 1 is the second valve provided in the second valve body 5.
Through the through hole 44 and the gap between the first valve body 4 and the second valve body 5 (the gap corresponding to the thickness of the seal members 40 to 41) and the first penetration provided in the first valve body 4. It passes through the hole 34 and is guided to the second connection port 16.

The above-mentioned high-pressure gas is used in this second connection port 1
6 is discharged to the outside of the case 1 and passes through the indoor heat exchanger 23, the pressure reducing device 30, and the outdoor heat exchanger 22 while sequentially changing the state to heat the room (see FIG. 2).

The low-pressure gas which has passed through the outdoor heat exchanger 22 and has a low pressure flows into the first connection port 14,
The compression mechanism in the case 1 is guided to the low pressure gas port 15 through the recessed groove 33 provided in the first valve body 4 and from the low pressure gas port 15 through the suction pipe 20 of the compressor. Introduced (returned) to 6.

The low-pressure gas introduced into the compression mechanism 6 is again compressed by the compression mechanism 6 to become a high-pressure gas and is discharged into the case 1. Then, it is again introduced into the indoor heat exchanger 23 from the second connection port 16 via the second through hole 44 of the second valve body 5 and the first through hole 34 of the first valve body 4. Circulate in the piping of this refrigeration cycle.

During this period, the control circuit 64, FIG.
The control is performed as shown in the waveform diagram of FIG. That is, the voltage applied to the electromagnet 51 of the magnetic force switching unit 26 is controlled to 0, and the pair of stays 50 is not magnetized.

Even in such a state, the stay 5
Since 0 is made of iron (magnetic piece), the attraction force generated between the magnet member 25 and the magnet member 25 causes the above-mentioned FIG. 10 (a) and FIG. 10 (b).
The state shown in can be maintained.

At this time, the second through hole 35 of the first valve body 4 which communicates with the defrosting port 15 has the second through hole 35.
Is closed by a second seal member 41 provided on the valve body 5. As a result, no gas flows through the bypass pipe 24 shown in FIGS. 1 and 2.

The timing chart shown in FIG. 13A shows the control described above with the passage of time. It should be noted that FIG. 13 (a) is similar to FIG.
Compared with the graph shown in, the time axis is much larger.

As shown in this figure, the voltage application (control shown in FIG. 10A) for switching the first and second valve bodies is performed for about 1 second, and thereafter, as described above. No voltage is applied (corresponding to FIG. 10D). The operation of the compression unit 2 is started after switching the first and second valve bodies 4, 5.

As described above, this refrigeration cycle performs heating operation, but if it is operated for a long time,
Frost may occur on the refrigerant distribution pipe and the heat radiation fins of the outdoor heat exchanger 22. When frost is formed, the heat exchange efficiency of the outdoor heat exchanger 22 is reduced and the performance of the refrigeration cycle is reduced. Therefore, it is necessary to perform the defrosting operation regularly. Next, this defrosting operation will be described.

This defrosting operation is performed during the heating operation (during operation of the compression section 2) as shown in FIG. 13 (b). That is,
From the state shown in FIG. 10, as shown in the waveform diagram of FIG. 11C, the voltage applied to the electromagnet 51 of the magnetic force switching unit 26 is controlled. As a result, contrary to the case shown in FIG. 20A, the stay 50 located on the upper side in the figure is magnetized to the N pole, and the stay 50 located on the lower side is magnetized to the S pole.

As a result, a repulsion occurs between the permanent magnet 47 and the stay 50, and the magnet member 25 and the second valve body 5 fixed to the magnet member 25 are indicated by arrows in FIG. 10 (b). Rotate in the counterclockwise direction shown.

At this time, the first valve element 4 maintains the state during the heating operation and does not rotate. This is because in the heating operation, the recessed groove 33 of the first valve body 4 is filled with low-pressure gas, and is filled with high-pressure gas.
The pressure is lower than that of the inside of the valve. Therefore, due to this pressure difference, the first valve body 4 and the valve base 18 are in close contact with each other in an airtight manner. This is because the static friction force F1 is generated.

On the other hand, the first valve body 4 and the second valve body 5 are not pressed by the pressure difference between the high pressure gas and the low pressure gas, and the second valve body 5 is pressed by the spring 56. Is only pressed against the first valve body 4.

Therefore, the static frictional force F2 generated between them is considerably smaller than the static frictional force F1 generated between the first valve body 4 and the second valve base 18, and this The force F2 is smaller than the drive torque of the magnetic force switching unit 26.

Therefore, only the second valve body 5 rotates together with the magnet member 25 independently of the first valve body 4. The magnet member 25 and the second valve body 5 rotate integrally, and as shown in FIG. 11 (b), the first convex portion 39 provided on the first valve body 4 is the magnet member. 25 colors 4
When the other end of the slit 48 provided in 6 in the circumferential direction is brought into contact with the slit 48, the second valve body 5 and the magnet member 25 stop rotating.

As described above, the drive torque of the magnetic force switching portion 25 is set to be smaller than the static friction force F1 generated between the first valve body 4 and the valve base 5 during the heating operation. The second valve body 5 and the magnet member 25 do not rotate any more.

As a result, as shown in FIG. 11B, the first valve element 4 communicating with the defrosting port 17 is communicated.
The second through hole 35 faces the first through hole 43 provided in the second valve body 5 and is opened in the case 1. Also,
The first through hole 34 of the first valve body 4 communicating with the second connection port 16 is closed by the third seal member 42.

As a result, the high-temperature high-pressure gas filled in the case 1 flows into the bypass pipe 24 through the first through hole 43, the second through hole 35 and the defrosting port 17. , Will be directly supplied to the outdoor heat exchanger 22. Therefore, the outdoor heat exchanger 22 is defrosted.

On the other hand, a gap of a predetermined size is formed between the valve base 18 and the first valve body 4 by the seal members 33a to 35a and 37a which are integrally formed with the first valve body 4. Since there is, the second
The high-temperature high-pressure gas in the case 1 also flows into the connection port 16 of the above. Therefore, the heating operation is continued.

Therefore, the defrosting operation of the outdoor heat exchanger 23 can be performed while continuing the heating operation. During the defrosting operation, the control during the heating operation (FIG. 10 (d))
Unlike the above, as shown in the waveform diagram of FIG. 11D, the power supply to the electromagnet 51 of the magnetic force switching unit 26 is continued.

This is different from the second operation, which is different from the heating operation.
This is because the valve body 5 is unstable in the rotation direction. That is,
Although not explained before, during heating operation, as shown in FIG.
As shown in (b), the bypass pipe 2 connected to the low pressure side
The second through hole 35 of the first valve body communicating with the second seal member 4 formed integrally with the second valve body.
Since it is closed at 1, the differential pressure from the high pressure in the case 1 causes the spring 56 to move against the second valve body 5.
In addition to the urging force of, the force in the direction of close contact works. This force is considerably smaller than the adhesion force of the first valve body 4 to the valve base 18 because the contact area between the second seal member 41 and the first valve body 4 is very small.
However, as shown in FIG. 11 (b), such a force does not work during the defrosting operation, and the second valve body 5 is correspondingly operated.
Is unstable in the direction of rotation.

Since the defrosting operation is continued for a maximum of 10 minutes, as shown in FIG. 13 (b), the power supply to the coil must be continued for a maximum of about 10 minutes. However, if the same current value as that required for switching is applied for 10 minutes, the coil temperature rises due to an increase in power consumption, and this electromagnet 51
(Coil) may be damaged.

Therefore, as shown in FIG. 13 (b), the average applied voltage is lowered and supplied in the range shown by B in the figure than the average voltage at the time of switching (range shown by A in the figure). By lowering the power, damage to the electromagnet 51 is prevented. Therefore, the following control is performed during this defrosting operation.

That is, as shown in FIG. 11D, when the CPU 67 detects the zero-cross point, it does not immediately issue a voltage application signal to the phototransistor 66, but rather changes the phase by, for example, 1/4. Only the cycle is delayed and applied.

As a result, the integrated value of the applied voltage (power consumption) is shown in FIG. 11 (c) as indicated by the diagonal lines in FIG. 11 (d).
It can be made smaller than the integrated value of the applied voltage at the time of switching. As a result, the average value of the applied current values is shown in FIG.
As indicated by B in (b), the power consumption can be reduced to about half that in (A) during switching, and power consumption can be suppressed.

It should be noted that the phase to be shifted may be such that the average applied voltage value is sufficient to hold the second valve body 5 in the state shown in FIG. When the defrosting of the outdoor heat exchanger 22 is completed as described above, the voltage applied to the magnetic force switching section 26 is changed to the voltage shown in FIG.
The switching is performed as shown in the waveform diagram of (c) to return to the original heating operation state (see FIGS. 10A, 10B, and 13B).

On the other hand, when stopping the heating operation, the electric motor 7 is stopped. As a result, the pressure in the case 1 is reduced, so that the adhesive force between the first valve body 4 and the valve base 18 is eliminated.

Further, since the weight of the first valve body 4 is added to the second valve body 5, the spring 56 is slightly compressed by the weight of the first and second valve bodies 4 and 5, A minute gap is generated between the first valve body 4 and the valve base 18. As a result, the first and second connection ports 14,
16 and the low-pressure gas port 15 communicate with each other, and the pressure in the refrigeration cycle pipe is balanced (gas balance).

As described above, since the gas balance is performed quickly, the waiting time for restarting the fluid compressor can be shortened. Next, the control and operation during the cooling operation will be described.

During the cooling operation, the voltage applied to the electromagnet 51 of the magnetic force switching section 26 is controlled as shown in the waveform chart of FIG. 12 (c). As a result, contrary to the heating operation shown in FIGS. 10A and 10B, the stay 50 located on the upper side in FIG. 12 is magnetized to the N pole, and the stay 5 located on the lower side.
0 is magnetized to the south pole.

As a result, the S pole portion 47b of the permanent magnet 47 of the magnet member 25 is attracted to the stay 50 located on the upper side in the figure, and the N pole portion 47a is attracted to the stay 50 located on the lower side. As a result, the magnet member 25 rotates counterclockwise.

The second valve body 5 is held non-rotatably with the magnet member 25, and the first valve body 4 is engaged with the slit 48 of the collar 46 provided on the magnet member 25. Therefore, the first and second valve bodies 4 and 5 rotate together with the magnet member 25.

At this time, since the electric motor 7 has not been operated yet, the case 1 is not filled with high-pressure gas. Therefore, the first valve body 3 and the valve base 18
Are not in close contact with each other and an excessive static frictional force is not generated. Therefore, even if the torque applied from the magnetic force switching unit 26 to the magnet member 25 is low, the first valve body 4 does not have the magnet member 25. And it will be easily rotationally driven with the 2nd valve body 5.

The stopper 31 projecting from the valve base 18 is provided with the guide groove 37 provided in the first valve body 4.
If it abuts on the other end in the circumferential direction, the first valve body 4 stops rotating, as shown in FIG.

As a result, the second connection port 16 and the low-pressure gas port 15 communicate with each other through the recessed groove 33, as opposed to during heating. Then, the first connection port 14 has the second through hole 3 provided in the first valve body 4.
5 and the defrosting port 17 faces the first through hole 34.

On the other hand, the magnet member 25 and the second valve body 5 continue to rotate, and the first valve body 4 provided with the first valve body 4 is rotated.
12B, if the convex portion 39 comes into contact with the other end surface in the circumferential direction of the slit 48 provided in the collar 46 of the magnet member 25, as shown in FIG. 12B, the second valve body 5 and the magnet member. The rotation of 25 is stopped.

As a result, the second through hole 35 of the first valve body 4 facing the first connection port 14 has the first through hole 43 provided in the second valve body 5. And communicates with the inside of the case 1.

Further, the first through hole 134 of the first valve body 4 facing the defrosting port 17 is closed by the third seal member 42 provided in the second valve body 5. It

When the operation of the electric motor 7 is started in this state, the compression mechanism 6 operates to fill the high pressure gas in the case 1, and the pressure and the concave groove 33 are filled.
The first valve body 4 is brought into close contact with the lower surface of the valve base 18 by the pressure difference with the low pressure gas inside.

Then, the high-pressure gas in the case 1 flows into the first through hole 43 of the second valve body 5, and the above-mentioned high pressure gas is introduced between the first valve body 4 and the second valve body 5. Seal members 33a-35
It flows into the 2nd through-hole 35 of the 1st valve body 4, and the 1st connection port 14 through the clearance gap formed by a and 37a.

Further, the seal members 33a to 35 of the first valve body 4 are provided between the valve base 18 and the first valve body 4.
a through the gap formed by a and 37a
High-pressure gas therein flows into the first connection port 14.

The high-pressure gas that has passed through the first connection port 14 circulates to the outdoor heat exchanger 22, the decompression device 30, and the indoor heat exchanger 23 while sequentially changing their states to cool the room.

The low-pressure gas (low-pressure gas) that has passed through the indoor heat exchanger 23 flows into the second connection port 16, passes through the recessed groove 33, and the low-pressure gas port 15 Be led to. The low pressure gas that has passed through the low pressure gas port 15 is introduced into the compression mechanism 6 provided in the case 1 through the suction pipe 20.

During the cooling operation, as shown in FIG. 12 (d), as in the heating operation, the magnetic force generator 26 is operated.
The applied voltage to the electromagnet 51 is controlled to zero. However, even in such a state, since the stay 72 is made of iron (a magnetic piece), the state shown in FIGS. 12A and 12B is maintained by the attraction force generated between the magnet members 25. Is able to.

At this time, since the pressure inside the recessed groove 33 is lower than that inside the case 1, the pressure difference causes the first valve body 4 to adhere to the valve base 18 in an airtight manner. , Cannot be moved easily.

The control during the cooling operation described above is
Similar to the control during the heating operation, it is shown in the timing chart of FIG. According to the configuration described above, there are the effects described below.

First, when the cooling operation or the heating operation is stopped, there is an effect that the pressure balance in the pipes constituting the refrigeration cycle can be easily and quickly performed. That is, according to the configuration described above, when the operation of the electric motor 7 is stopped, the pressure in the case 1 is reduced, so that the first and second valve bodies 4 and 5 are slightly lowered due to their own weight, and the valve base 18 is
Expand the gap between and. As a result, all the ports 14 to 17 provided on the valve base communicate with each other through the gap, so that pressure balance in the pipe can be quickly performed.

As a result, it becomes possible to restart after a stop and quickly switch between heating and cooling. Second
In addition, the defrosting of the outdoor heat exchanger 23 can be quickly performed without stopping the heating operation.

That is, in the conventional configuration, when defrosting the outdoor heat exchanger 23, it was necessary to temporarily switch the heating operation to the cooling operation and send the high-temperature refrigerant to the outdoor heat exchanger 23. . Therefore, there is a fear that the temperature in the room may be lowered.

On the other hand, there is also a method of performing the defrosting operation while continuing the heating operation by separately providing a switching valve for the defrosting operation. In such a method, it is necessary to provide two switching valves. Therefore, the configuration may be complicated.

However, in the above-mentioned invention, the five-way switching valve 3 having the first and second valve bodies 4 and 5 is housed in the case 1. Further, the first and second valve bodies can be separately driven by one driving device (magnetic force switching unit 26) by utilizing the pressure difference between the inside of the case 1 and the suction side. This has the effect of performing the defrosting operation while continuing the heating operation with a simple configuration.

Thirdly, the electric power for controlling the switching valve 3 can be reduced and the damage of the electromagnet 51 can be effectively prevented. That is, since the stay 50 of the magnetic force switching unit 26 is made of iron (a magnetic piece), the stay 50 and the magnet member 25 (permanent magnet) may be magnetized without magnetizing the stay 50 except when the valve bodies 4 and 5 are driven. 47) and the suction force works. The first valve body 4 is in close contact with the valve base 18 and cannot be easily moved. As a result, after switching, there is an effect that the switching state (FIGS. 10 and 12) can be maintained without applying a voltage.

Therefore, unlike the conventional case where the position of the sliding valve is held by the spring and the electromagnet, during operation,
Since it is not necessary to apply a voltage to the switching valve 3, power consumption can be reduced.

On the other hand, during the defrosting operation, as described above,
The second valve body 5 described above than during the heating operation or the cooling operation.
There is a case where the adhesion of the first valve body 4 to the first valve body 4 is small. Therefore, it is necessary to continue applying the voltage in order to maintain the switching position of the second valve body, unlike the case where only the heating operation is performed. However, if the voltage at the time of switching is continuously applied, the temperature of the coil rises and the electromagnet 51 may be damaged.

However, according to the present invention, as shown in FIG. 11 (d), the phase of the half-wave rectified voltage is controlled so that the electromagnet during defrosting operation is controlled as shown in FIG. 13 (b). The average applied current value is set to about half of that at the time of switching. As a result, power consumption can be reduced.

From the above, it is expected that the power consumption required for controlling the switching valve 3 can be reduced throughout the entire operation of the refrigeration cycle, which is economically advantageous.

In addition, since it is possible to prevent the high voltage from being continuously applied to the electromagnet 51 of the magnetic force switching section 26, the temperature of the coil (electromagnet 51) abnormally rises during operation, and the electromagnet 51 is prevented. Can be effectively prevented from being damaged.

Therefore, there is an effect that more reliable operation can be performed. Next, a second embodiment of the present invention will be described. The second embodiment relates to the control during the defrosting operation, and the configuration itself is the same as that of the first embodiment. Therefore, the description of the configuration is omitted.

FIG. 14 (a) is a waveform diagram showing the waveform of the power supply voltage, and FIG. 14 (b) is a waveform diagram showing the control during the defrosting operation in the first embodiment. That is, in the first embodiment, the CPU 67 controls the phase of the half-wave rectified voltage for the given AC voltage (FIG. 14A) as shown in FIG. 14B. As a result, the integrated value (the hatched area in the figure) of the applied voltage value during the defrosting operation is reduced.

On the other hand, the second embodiment is shown in FIG.
4 (c) or 4 (d), the wave number control of the half-wave rectified voltage is performed to reduce the integrated value of the applied current value in the same manner as in the first embodiment.

That is, the CPU 67 controls the number of supplied half-wave rectified voltages. In FIG. 14 (c), the half-rectified voltage is intermittently supplied,
In (d), it is supplied every predetermined time.

Even with such a configuration, the integrated value of the applied voltage value, that is, the supplied power can be reduced as compared with the case where all the half-wave rectified voltages are supplied. Therefore, the same effect as that of the first embodiment can be obtained.

Next, the third embodiment will be described. The control circuit 64 provided in the control unit 62 of the third embodiment is composed of a DC chopper circuit 64 'shown in the figure.

That is, the AC power supply 70 includes the rectifier circuit 7
1 is connected, and two capacitors 72 (smoothing circuits) are provided in series between the output terminals of this rectifying circuit. Each capacitor 72 is connected to the coil forming the electromagnet 51 via the first and second transistors 73 and 74, respectively.

Then, the first and second transistors 7
3, 74 are connected to the CPU shown at 75 in the figure, and this C
It is adapted to be activated by an activation signal from the PU 75.

According to the DC chopper circuit 64 ', the supplied AC current can be converted into a DC current by the chopper, and the CPU 75 selectively operates one of the first and second transistors 73 and 74. By turning on and turning the other off, the direction of the current applied to the electromagnet 51 (coil) can be changed. As a result, the magnetic poles of the pair of stays 50 of the magnetic force switching section 26 can be switched.

Specifically, as shown in the timing chart of FIG. 16A, the first transistor 73 is turned on.
By setting N and turning off the second transistor 74, it is possible to apply a current in the direction indicated by the solid arrow in the figure to the electromagnet 51 (coil).

As a result, as shown in FIGS. 10A and 10B, the stay 50 located on the upper side in the figure is magnetized to the N pole, and the stay 50 located on the lower side is magnetized to the S pole. Therefore, the first and second valve bodies 4 and 5 can be switched to the heating position.

The application of this current is performed for about 1 second only when the first and second valve bodies 4 and 5 are switched over, as in the first and second embodiments, and the compressor 7 is operated. It is not performed inside (see FIG. 13 (a)).

Further, as shown in the timing chart of FIG. 16B, the second transistor 74 is turned on and the first transistor 73 is turned off, so that the electromagnet 51 (coil) is turned on. A current in the direction indicated by the dashed-dotted arrow can be applied to.

As a result, the magnetism of the magnetic force supply section 26 can be switched to the state shown in FIGS. 12 (a) and 12 (b), and the first and second valve bodies 4 and 5 are set to the cooling position. It can be switched.

Even in this cooling operation, the application of current is
Similar to the first and second embodiments, it is performed for about 1 second only when switching the first and second valve bodies 4 and 5, and is not performed while the compressor 7 is operating (Fig. 13 (c)). reference).

Further, the defrosting of the outdoor heat exchanger 23 is performed during the heating operation as in the first and second embodiments. That is, during the compressor operation, the second transistor 74 is turned on and the first transistor 73 is turned off, as in the cooling operation shown in FIG. 16B.

As a result, only the second valve body 5 is rotated, and the switching valve 3 is switched to the defrosting position shown in FIGS. 11 (a) and 11 (b). Next, the control during the defrosting operation will be described.

The CPU 75 is constructed so as to be able to perform so-called DUTY ratio control for changing the ON / OFF ratio (DUTY ratio) to the second capacitor 74. For example, at the time of switching the defrosting operation shown in FIG. 16B, the ON / OFF (time) ratio of the second transistor 74 is t1: t2.

On the other hand, the CPU 75 once switches the switching valve 3 to the defrosting operation position, and then the DUT
The Y ratio (t1: t2) is changed so as to be as shown in FIG. That is, the ON ratio was higher than the OFF ratio at the time of switching shown in FIG. 16B, but the OFF ratio is increased during the defrosting operation. Then, in this state, the outdoor heat exchanger 23 is defrosted by continuing the operation for a maximum of 10 minutes.

In this way, the integrated value of the applied voltage value to the electromagnet 51 (coil) (corresponding to the shaded area in the figure) can be made smaller than that at the time of switching shown in FIG. 16 (a). Therefore, the power consumption of the switching valve 3 can be reduced as in the first and second embodiments.

The DUTY ratio indicates the rotational state of the second valve body 5 by the driving force obtained thereby.
It should be determined so that the state shown in can be maintained.

According to the structure as described above, the same effect as that of the first embodiment can be obtained. The present invention is not limited to the above first to third embodiments, and can be variously modified without changing the gist of the invention.

For example, in the above-mentioned one embodiment, the compression mechanism 6 is a rotary type in which the roller-shaped piston 9 is eccentrically rotated in the cylinder 8, but the invention is not limited to this. For example, a scroll-type compression mechanism that forms a compression space by combining an orbiting scroll blade and a non-orbiting scroll blade, and compresses the fluid in the compression space by orbiting the orbiting scroll with respect to the non-orbiting scroll, Is also good. The point is that the case 1 may be of a type in which the high pressure gas after compression is filled.

Further, in the above embodiment, not only the compression mechanism 6 but also the electric motor 7 is provided in the case 1. However, only the compression mechanism 8 and the switching valve 3 are accommodated in the case 1, and the electric motor is It may be provided outside the case 1.

Further, in the above-mentioned one embodiment, the switching valve 3
Was provided in the compressor, but is not limited to this, and may be provided in a case filled with another high-pressure gas.

[0173]

According to the structure described above, the compact structure in which the rotary switching valve is provided in the case of the fluid compressor enables the cooling / heating operation and the defrosting operation while continuing the heating operation. I chose

As a result, the piping structure of the refrigeration cycle apparatus can be simplified, and the situation where the temperature inside the room drops during the heating operation can be effectively prevented. Also,
By controlling the voltage applied to the electromagnet for maintaining the rotation of the second valve body by phase control, fraction control or DC chopper control, the power consumption of the refrigeration cycle apparatus can be saved. Therefore, the temperature rise of the electromagnet can be suppressed, and the damage of the electromagnet can be prevented. As a result, there is an effect that a comfortable and reliable cooling / heating operation and defrosting operation can be performed with low power consumption.

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing a first embodiment of the present invention.

FIG. 2 is a top view of the same.

FIG. 3 is a plan view, a front view, a side view, a lateral cross-sectional view, and a vertical cross-sectional view showing the switching valve.

FIG. 4 is a plan view, a side view, and a bottom view showing the valve base of the switching valve.

FIG. 5 is a plan view, a side view, and a bottom view of the first valve body.

FIG. 6 is a plan view, a side view, and a bottom view of the second valve body.

FIG. 7 is a plan view and a vertical sectional view showing a magnet member.

FIG. 8 is a perspective view showing a combined state of the magnet member and the first and second valve bodies.

FIG. 9 is a plan view, a side view, and a front view showing the magnetic force switching unit.

FIG. 10 is an operation diagram and a waveform diagram showing the switching operation of the switching valve during the heating operation.

FIG. 11 is an operation diagram and a waveform diagram showing the switching operation of the switching valve during the defrosting operation.

FIG. 12 is an operation diagram and a waveform diagram showing the switching operation of the switching valve during the cooling operation.

FIG. 13 is a timing chart showing the switching timing of the switching valve.

FIG. 14 is a waveform diagram showing a second embodiment of the present invention.

FIG. 15 is a circuit diagram showing a control system of a third embodiment of the present invention.

FIG. 16 is a timing chart of the same.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Case, 2 ... Compression part, 3 ... Switching valve, 4 ... 1st valve body, 5 ... 2nd valve body, 18 ... Valve base, 25 ... Magnet member (permanent magnet), 26 ... Magnetic force switching part ( Electromagnet), 14 ... First connection port, 15 ... Low-pressure gas port, 16 ... Second
Connection port, 17 ... defrosting port, 22 ... indoor heat exchanger, 23 ... outdoor heat exchanger, 24 ... bypass pipe, 33 ... concave groove (communication groove), 34 ... first through hole, 35 ... first 2 through-holes, 47 ... permanent magnets, 51 ... electromagnets, 62 ... control unit,
64 ... Control circuit.

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Yoshitaka Yoshina 336 Tatehara, Fuji City, Shizuoka Prefecture, Toshiba Corporation Fuji Factory (72) Inventor Sohiro Kobayashi 336 Tatehara, Fuji City, Shizuoka Toshiba A ・ V ・ E Co. Ltd. In the company

Claims (7)

[Claims] 1. A refrigeration cycle apparatus having a refrigeration cycle in which a compressor, a switching valve, an indoor heat exchanger, a pressure reducing device, and an outdoor heat exchanger are sequentially connected by piping, and a control unit for controlling the refrigeration cycle, The switching valve includes an electromagnet whose magnetic poles can be switched, a permanent magnet which is arranged so as to face the electromagnet, and is driven to rotate by switching the magnetic poles of the electromagnet, and the permanent magnet is attached to the permanent magnet to start the heating and cooling operation. And a second valve body that is attached to the permanent magnet and that switches to the defrosting operation.
And a control means for controlling the supply voltage for maintaining the switching state of the first and second valve bodies by controlling the voltage application to the electromagnet. Refrigeration cycle device characterized by. 2. The refrigeration cycle apparatus according to claim 1, wherein the control means performs voltage application to the electromagnet by phase control. 3. The refrigeration cycle apparatus according to claim 1, wherein the control means applies a voltage to the electromagnet by wave number control. 4. The refrigeration cycle apparatus according to claim 1, wherein the control means applies a voltage to the electromagnet by DC chopper control. 5. The refrigeration cycle apparatus according to claim 1, wherein the switching valve is provided in a case filled with high-pressure discharge gas of the compressor. 6. The refrigeration cycle apparatus according to claim 5, wherein the switching valve is provided on the valve base attached to the case, the switching base is provided on the valve base, and is opened to the inside and outside surfaces of the case of the valve base. Three ports connected to the suction side of the outdoor heat exchanger, the indoor heat exchanger, and the compressor, and provided on the valve base, open to the inside and outside of the case of the valve base, and when heating the outdoor heat exchanger A defrosting port connected to a pipe connected to a portion serving as a refrigerant inlet and a surface provided on a surface of the first valve body facing the valve base, and the first valve body rotates by a predetermined angle. Therefore, the above 3
Communication groove that selectively communicates two of the two ports with each other, and first and second through holes that are provided in the first valve body and that communicate with the other one port and the defrosting port. And the second valve body is provided on a surface of the second valve body facing the first valve body, and the second valve body is rotated by a predetermined angle with respect to the first valve body, whereby the first valve body is rotated. A refrigeration cycle apparatus comprising: a closing unit that selectively closes the first or second through hole of the valve body. 7. The refrigeration cycle apparatus according to claim 6, wherein the driving torque by the electromagnet is smaller than the static friction force generated between the first valve body and the valve base during the operation of the compressor, A refrigeration cycle device characterized in that it is larger than a static frictional force generated between the first valve body and the second valve body.