JP3377614B2 - Air conditioner - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner having a refrigeration cycle and equipped with a flow path switching valve for switching the flow path of a refrigerant.

[0002]

2. Description of the Related Art Generally, in an air conditioner that performs both cooling and heating, a flow path switching valve device that switches the flow of refrigerant flowing between an indoor heat exchanger and an outdoor heat exchanger during cooling and heating is provided. To have.

As such a flow path switching valve device, generally, a four-way switching valve device as shown by 1 in FIG. 16 is widely used. The four-way valve device 1 includes a valve main body 2, a high pressure gas introduction pipe 3 and a low pressure gas discharge pipe 4 connected to the valve main body 2, and a sliding valve provided in the valve main body 2. It is provided with first and second connecting pipes 6 and 7 which communicate with the low-pressure gas discharge pipe 4 or the high-pressure gas introduction pipe 3 by switching of 5.

The sliding valve 5 has first and second spaces R1 and R2 defined by the pistons 8 and 9 connected to the sliding valve 5 at both ends in the longitudinal direction of the valve body 2. It operates by the pressure difference.

As a device for introducing a pressure difference into the valve body 2 to operate the sliding valve 5, an electromagnetic valve device shown by 10 in the figure is used. The solenoid valve device 10 includes a first copper unit connected to the first and second spaces R1 and R2,
The second capillaries 11 and 12 are connected, and the same copper third capillaries 13 derived from the low-pressure gas discharge pipe 4 are connected between the first and second capillaries 11 and 12. There is.

The valve body 14 provided in the solenoid valve device 10 is shown by 15 in FIG.
By switching by the action of 6, the four-way valve device 1
The pressure (low pressure) in the low pressure gas discharge pipe 4 is introduced into the first or second space R1 or R2 in the valve body 2.

Although not shown, the pistons 8 and 9 provided in the four-way valve device are provided with fine through holes, respectively, and the valve main body is previously provided in the first and second spaces R1 and R2. The pressure (high pressure) in 2 is introduced. Therefore, when a low pressure is introduced into either of the first and second spaces R1 and R2, a pressure difference occurs between the two, and the sliding valve 5 is switched by the pressure difference. .

In the air conditioner, the four-way valve device 1 is used.
The high-pressure gas introduction pipe 3 is connected to the discharge pipe of the compressor indicated by 18 in the figure, and the low-pressure gas discharge pipe 4 is connected to the compressor 1
It is connected to eight suction pipes.

The first connecting pipe 6 is connected to the outdoor heat exchanger shown by 19 in the figure, and the second connecting pipe 7 is 2
It is connected to the indoor heat exchanger indicated by 0. Next, the operation of this air conditioner will be described.

When performing the heating operation, the sliding valve 5 is positioned at the position shown in FIG. 16 (the position on the left side in the main body 2) so that the second connecting pipe 7 and the high pressure gas introducing pipe are The first connection pipe 6 and the low-pressure gas discharge pipe 4 are communicated with each other.

As a result, the refrigerant (working fluid) flowing in the refrigerant pipe of the air conditioner changes its state, as shown by the arrows in the figure, and the compressor 18, the indoor heat exchanger 20, and the expansion valve 21. , The outdoor heat exchanger 19 and the compressor 18 flow in this order, and the air conditioner is caused to perform heating operation.

During cooling, the solenoid valve device 10 switches the slide valve 5 of the four-way valve device 1 to the right position in the main body 2 so that the first connecting pipe 6 and the high-pressure gas introducing pipe 3 And the second connection pipe 7 and the low pressure gas discharge pipe 4 are communicated with each other. As a result, the refrigerant circulates from the outdoor heat exchanger side 19 to the indoor heat exchanger 20 side, contrary to the case described above, and causes the air conditioner to perform the cooling operation.

[0013]

The air conditioner equipped with the above-mentioned four-way valve device has the following problems to be solved. That is, the four-way valve device 1 and the electromagnetic valve device 10 as described above are complicated in structure and large in size, and require a large number of parts as described above. Further, the piping is complicated, and in particular, since the high-pressure gas introduction pipe 3 is connected to the discharge pipe of the compressor 18, it is easy to transmit vibration, and therefore, it may be necessary to take vibration damping measures.

On the other hand, the first to third capillaries 11 to 13 connecting the valve body 2 and the electromagnetic valve device 10 are also deformed by a small impact, resulting in malfunction. As an invention made to solve such a problem, there is one disclosed in Japanese Patent Laid-Open No. 60-124595.

According to the present invention, as shown in FIG. 17, a hermetic case 24 for accommodating a compressor section 22 and an electric motor section 23 is provided.
It is a compressor of a type that is filled with the high-pressure discharge gas discharged from the compressor section 22 therein, and the four-way valve device 1 and the solenoid valve device 10 having the above-described configurations are built in the case 24, The high-pressure gas introduction pipe 4 is not required and the capillaries 11 to 13 are prevented from being damaged by an external force.

However, even with such a structure, the problem that the structure is complicated and large has not been solved. Furthermore, by incorporating such a four-way valve device 1 in the case 25, The compressor itself becomes large in size, which causes a new problem that the recent tendency toward downsizing of the compressor cannot be dealt with.

Further, since the four-way valve device 1 is constructed so as to be operated by a pressure difference, the sliding valve 5 must always be in close contact with the valve seat. For this reason, there is a problem in that it is difficult to balance the pressure when stopped.

That is, with such a structure, the pressure balance cannot be achieved in the four-way valve device 1.
The pressure is balanced from the other portion, for example, the portion such as the expansion valve 21. Therefore, it may take a long time to achieve pressure balance.

If pressure balance is not achieved, restarting after stoppage and operation switching between cooling and heating cannot be performed, so that these operations (restarting and operation switching) cannot be performed quickly. There is. In the conventional air conditioner, it has been necessary to wait, for example, 3 minutes after stopping the compressor in order to restart or switch the operation.

Further, during the heating operation, frost may be formed on the outdoor heat exchanger 19. Since the performance of the outdoor heat exchanger 19 deteriorates when frost is formed, it is necessary to defrost quickly.

Conventionally, in an air conditioner having a defrosting function, defrosting is performed by directly supplying the high temperature and high pressure refrigerant discharged from the compressor 18 to the outdoor heat exchanger 19 through a bypass pipe. In such a configuration, it is necessary to provide a switching valve for switching the refrigerant flow path from the compressor 18 separately from the four-way valve device 1.

However, according to this method, since two switching valves (and electromagnetic valve devices) are provided, the structure becomes complicated, and when the switching valve is provided outside the case 24, Since vibration from the compressor 18 is generated in the connecting pipe between the switching valve and the switching valve, it is necessary to take vibration damping measures.

When the defrosting switching valve is provided in the case 24, it is necessary to further increase the size of the case 24, and more wiring is taken out from the case 24. There is also a problem that the structure becomes complicated.

The present invention has been made in view of the above circumstances, and simplifies the piping configuration of an air conditioner that performs heating, cooling, and defrosting operations during heating.
It is an object of the present invention to provide an air conditioner that can perform defrosting while continuing heating operation with a simple configuration and that can quickly restart and switch operation between cooling and heating.

[0025]

[0026]

[0027]

The present invention has a refrigeration cycle in which a compressor, an indoor heat exchanger, a decompression device, and an outdoor heat exchanger are sequentially connected by piping, and a control section for controlling this refrigeration cycle. In the air conditioner, the refrigeration cycle includes an indoor heat exchanger-side connection pipe that connects the compressor and a pipe serving as a refrigerant inlet of the indoor heat exchanger during cooling operation, and the compressor and the outdoor heat exchanger during heating operation. The compressor has a pipe means having an outdoor heat exchanger-side connection pipe that connects with a pipe serving as a refrigerant inlet, and the compressor is a case filled with high-pressure refrigerant after compression.
And a rotary type five-way valve having a first valve element and a second valve element which are provided in the case and which switch the flow path of the refrigerant by rotating. By controlling the shape five-way valve and rotating the first and second valve bodies, heating,
In addition to switching to cooling and defrosting operation, switching to defrosting operation has means for supplying high-pressure refrigerant in the case to the outdoor heat exchanger side connection pipe while continuing heating operation .

Further , the piping means is provided in the indoor heat exchanger side connecting pipe, and is connected to the outdoor heat exchanger side connecting pipe and a first check valve for restricting the flow of the refrigerant toward the compressor. Second provided to restrict the flow of the refrigerant toward the compressor
The check unit further supplies the high-pressure refrigerant in the case to the outdoor heat exchanger side connection pipe when the heating operation is stopped, and stops the cooling operation during the cooling operation. having a means for supplying to the indoor heat exchanger-side connecting pipe pressure refrigerant
It

Further , when an error occurs in the switching to the cooling operation by the five-way switching valve, the control unit stops the compressor and at the same time connects the indoor heat exchanger-side connecting pipe with the cable. Supply high pressure refrigerant to the first and second
If there is a mistake in the means for switching to the cooling operation by rotating the valve body and the switching to the heating operation by the five-way switching valve, the compressor is stopped and the outdoor heat exchanger side connection is made. The high pressure refrigerant in the case is supplied to the pipe, and the means for switching to the heating operation by rotating the first and second valve bodies again .

Further , the rotary five-way switching valve is provided on the valve base attached to the case, and is provided on the valve base, and is open to the inside and outside surfaces of the case of the valve base. The three ports connected to the suction side of the outdoor heat exchanger, the indoor heat exchanger, and the compressor, the piping means ports connected to the piping means, and the valve base described above. A first valve body rotatably provided on the inner surface of the case where three ports and a port for piping means are opened, and the valve base of the first valve body.
And a communication groove provided on a surface facing the space for selectively communicating two of the three ports with each other by rotating the valve body by a predetermined angle, and provided on the first valve body. And a first through second hole for communicating the other one port and a port for piping means to the inside of the case, and rotatably provided with respect to the first valve body, A second valve body is provided which closes the first or second through hole of the first valve body by rotating the first valve body by a predetermined angle .

Further , the rotary five-way switching valve is provided on the first valve body and the valve base, and regulates the rotation angle of the first valve body with respect to the valve base. A first restricting means, a second valve provided on the first valve body and the second valve body, and restricting a relative rotation angle of the first valve body and the second valve body within a predetermined range.
Of the high pressure refrigerant from inside the case and low pressure refrigerant from the outside of the case by rotating the second valve element and operating the first or second restriction means. , An indoor heat exchanger, an outdoor heat exchanger, a suction side of the compressor, or a drive means for performing five-way switching to the piping means.
To do.

Further , the drive torque of the drive means is smaller than the static frictional force generated between the first valve body and the valve base during the operation of the compressor section, and the drive torque is smaller than the static frictional force. Graphics and the second Benbe - magnitude than the static friction force generated between the scan
Yes.

[0033]

According to this structure, the rotary five-way switching valve is provided in the case filled with the compressed high-pressure fluid, so that the outdoor heat exchanger can be defrosted while continuing the heating operation. It can be carried out.

When stopped, the high-pressure refrigerant in the case is supplied to the refrigerant inlet of the indoor heat exchanger or the refrigerant inlet of the outdoor heat exchanger to balance the pressure in the refrigeration cycle.

Further, in view of the fact that the static frictional force generated between the valve base and the first valve body by the high pressure refrigerant in the case is large during the operation of the compressor and is small during the stop, the above-mentioned first Since the drive torque of the drive means for rotationally driving the valve body and the second valve body is adjusted, only the second valve body can be driven during operation of the compressor, and the first and second valves can be operated during stoppage. Can drive both of the body,
Five-way switching can be performed.

[0036]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 shows an air conditioner of the present invention. However, in this figure, devices other than the fluid compressor 17 (indoor heat exchanger, outdoor heat exchanger, and expansion valve (pressure reducing device)) in the refrigeration cycle are schematically shown.

Hereinafter, the configuration of the air conditioner will be described centering on the configuration of the fluid compressor 17. Reference numeral 25 in FIG. 1 denotes a closed case of the fluid compressor 21. In the closed case 25, a compressor section 26 is provided at the lower end, a midway section and an upper end in the height direction, and an electric motor section 27 for driving the compressor section 26 to perform a compression operation. A switching valve portion 28, which is a main part of the invention, is provided.

The configuration of each part will be described below. The electric motor section 27 is a DC brushless motor composed of a stator 30 fixed to the inner surface of the hermetic case 25 and a rotor 31 arranged inside the stator 30. is there. The rotor 31 is shrink-fitted on the upper portion of the drive shaft shown by 32 in FIG.

The lower end of the drive shaft 32 is
It extends into the compressor section 26. At the lower end of the drive shaft 32, two crank portions 32a are formed which are vertically spaced apart from each other by a predetermined distance and are 180 ° out of phase with each other.

The compression mechanism section 26 is held by a partition member 33 fixed to the case 25, and two cylinders of a cylindrical shape connected in the vertical direction via an intermediate plate 34 shown in the drawing. 35, 35 are provided. The two crank portions 32a, 32a of the drive shaft 32 are located inside the two cylinders 35, 35, respectively.

The shaft 32 has a first bearing member 37 (main bearing) fixed to the partition member 33.
And a second bearing member 38 (sub-bearing) that closes the upper and lower ends of the two cylinders 35, 35 by the first bearing member 37, and is rotatably supported around the vertical axis.

The two crank portions 32a, 32a of the shaft 32 have cylindrical rollers 40, 4 respectively.
0 is fitted. This roller 40 is the cylinder 3
5 is eccentric to the cylinder 35 and a part of the outer peripheral surface is held in contact with the inner peripheral surface of the cylinder 35.

Therefore, a compression space 41 having a crescent cross section is defined between the inner peripheral surface of the cylinder 35 and the outer peripheral surface of the eccentric roller 40. A blade 42 for partitioning the compression space 41 into a high pressure side and a low pressure side is provided in the cylinder 35 (the upper cylinder 35 is not shown). This blade 4
2 is a roller 4 by means of a spring indicated by 43 in the figure.
It is urged toward the 0 side (the central direction of the cylinder 35) and moves in and out of a blade groove (not shown) provided in the cylinder 35 so that its tip always comes into contact with the outer peripheral surface of the roller 40. Has become.

Suction passages 44 for sucking the refrigerant gas into the compression space 41 and discharge ports for discharging the compressed refrigerant gas (discharge gas) are provided on both sides of the blade 35 of the cylinder 35. And a passage is formed. The suction passage 44 is shown only in the upper cylinder 35.

In the suction passage 44, 45 are respectively provided.
The suction pipe indicated by (4) is connected, and the suction pipe 45 is extended to the outside of the closed case 11 and is connected to the gas-liquid separator indicated by 46 in the figure.

On the other hand, the discharge passage is a first passage opened from the first discharge valve 47 provided on the flange portion of the first bearing member to the upper portion of the case 25 through the muffler 48. , The second discharge valve 49 provided on the flange portion of the second bearing member 38 communicates with the muffler 50. From the muffler 50, the cylinder 35, the intermediate plate 34, the first
And a second passage that penetrates through the bearing member 37 and also opens to the upper part of the case 25.

Therefore, the refrigerant in the refrigerant pipe is sucked into the cylinder 35 by the suction pipe 45, compressed by the rotation of the roller 40, and then discharged into the discharge passage consisting of the first and second passages. Through the case 25
It is designed to be discharged into the upper part of. That is, the inside of the case 25 is kept at a high pressure by the high pressure discharge gas.

Next, the switching valve portion 28 will be described with reference to FIGS. As shown in FIG. 1, the switching valve portion 28 includes a valve base 52 fixed to a hermetically sealed case 25.
A first valve body 53 rotatably provided on the lower surface of the valve base 52 to switch the flow path of the refrigerant; and a second valve body rotatably provided on the lower surface of the second valve body 53. Body 54
And a magnet member 55 attached to the outer peripheral surfaces of the first and second valve bodies 53 and 54, and rotating the first and second valve bodies 53 and 54 by applying a magnetic force to the magnet member 55. A magnetic force switching unit 56 that is dynamically driven to switch the flow path and a holder 57 that covers the switching valve unit 28 are provided.

As shown in FIG. 3, the valve base 52 has a circular shape in plan view, and has a lower end portion having a flange portion 52a having a diameter larger than that of the upper end portion. As shown in FIG. 1, the valve base 52 is attached to the lid portion 25a that closes the upper end of the hermetically sealed case 25.

That is, a through hole indicated by 58 in the figure is formed in the upper wall of the lid 25a. The valve base 52 is attached to the lid portion 25a by inserting the upper end side into the through hole 58, and is fixed, for example, by welding so as to hermetically close the through hole 58. It is like this.

Further, as shown in FIG. 3, this valve base 5
2 is provided on the central axis L of the valve base 52,
A central shaft 59 having a lower end protruding into the case 25 is fixed. Then, the valve base 52 is provided around the central axis 59 at 90 ° intervals in the circumferential direction.
Three ports 60 to 62 are provided that axially pass through 2.

The port 61 located at the center of the three ports 60 to 62 is a low pressure connected to a suction pipe 45 extending from the compressor section 26, as shown in FIG. The gas discharge port (corresponding to 4 in the conventional example (FIG. 11)) is provided. The other two ports 60 and 62 sandwiching the low pressure gas discharge port 61 are shown in FIGS. 1 and 9, respectively. To 6
First and second connection ports (corresponding to 6 and 7 in the conventional example) connected to the outdoor heat exchanger (64) and the indoor heat exchanger (63) shown by 4, 63.

As shown in FIG. 3, this valve base 5
2, 180 from the low pressure gas discharge port 60 in the circumferential direction.
A bypass pipe port 65, which has a smaller diameter than the other ports, is provided axially through the valve body 52 at positions separated from each other.

This bypass pipe port 65 is shown in FIG.
The bypass pipe indicated by 6 is connected, and this bypass pipe 66
Is a defrosting circuit indicated by 140 in the figure (the piping means of the present invention)
It is connected to the. The defrosting circuit 140 includes a first connecting pipe 141 (internal heat exchanger side connecting pipe) that connects the bypass pipe 66 to a pipe that connects the expansion valve 21 and the indoor heat exchanger 63, and the first connecting pipe 141. No. 1 check valve 142 provided in the connecting pipe 141 of No. 2 and the second connecting pipe 143 (outdoor heat exchange) for connecting the bypass pipe 66 to the pipe connecting the expansion valve 21 and the outdoor heat exchanger 64. Device side connection pipe) and a second check valve 144 provided on the second connection pipe 143.
Consists of.

The flange 52a of the valve base 52 is also provided.
On the lower surface of the stopper, a stopper 67 is projected (indicated by a halftone dot in the figure). This stopper 67 is shown in FIG.
As shown in (b), the upper end portion is attached to the valve base 52 by screwing.

The first valve element 53 is attached to the lower surface of the valve base 52 thus formed, as shown in FIG. The upper surface of the first valve body 53 is formed by inserting the central shaft 59 projecting from the valve base 52 into a central hole 53a provided in the central portion of the first valve body 53. Of the valve base 52 and is rotatably attached to the valve base 52.

As shown in FIG. 5, on the upper surface of the first valve body 53, two adjacent ports (59, 60 or 90) out of the three ports 59 to 61 at 90 ° intervals. 6
0, 61) are provided with a recessed groove 68 that communicates with each other in the circumferential direction.

As shown in the drawing, the recessed groove 68 is a passage having an inner surface formed in a semicircular cross section, and when the first valve body 53 is rotated 90 °, the recessed groove 68 shown in FIG.
Alternatively, as shown in FIG. 12, adjacent ports, that is, the low-pressure gas discharge port 61 (shown by a chain line) and the first connection port 60 (shown by a chain line), or the low-pressure gas discharge port are connected. The port 61 and the second connection port 62 (shown by a chain line) can be switched so as to communicate with each other.

The first valve body 53 has the first
First and second through holes 6 penetrating in the axial direction of the valve body 53 of
9, 70 are provided at intervals of 90 ° in the circumferential direction. The first and second through holes 69 and 70 are formed to have a smaller diameter than the width of the concave groove 68.

Then, the first and second through holes 69, 7
0 means that the first valve body 53 is 9 around the center hole 53a.
By being rotationally driven in the range of 0 °, each of FIG.
As shown in FIGS. 11 (a), 11 (a) and 12 (a), the first and second connection ports 60, 62 of the valve base 52.
(Shown by a chain line) or the above-mentioned bypass pipe port 65
It is designed to communicate (indicated by the chain line).

When the first valve body 53 is attached to the valve base 52, the valve base 52 is attached to the radially outer edge of the upper surface of the first valve body 53. A guide groove 72 into which the stopper 67 protruding from the lower surface is inserted is provided as a recess.

The guide groove 72 is provided over the range of 90 ° in the circumferential direction, and when the first valve body 53 is rotationally driven, one end of the guide groove 72 in the circumferential direction and By bringing the other end into contact with the stopper 67, as shown in FIG.
As shown in (a), FIG. 11 (a), and FIG. 12 (a), the rotation range of the first valve body 53 is restricted to 90 °.

Therefore, the stopper 67 and the guide groove 7
2 and 1 constitute the first restricting means of the present invention. In addition,
From the positional relationship between the recessed groove 68 and the first and second through holes 69 and 70, as shown in FIG. 10A, the second connection port 62 is connected to the first through hole 69. When they are communicated with each other, the first connection port 60 and the low-pressure gas discharge port 61 are communicated with each other through the concave groove 68, and the bypass pipe port 65 is provided with the second through hole. It is designed to communicate with 70.

As shown in FIG. 12 (a), when the first connection port 60 communicates with the second through hole 70, the second connection port 62 and the second connection port 62 are connected. The low-pressure gas discharge port 61 is connected to each other by the concave groove 68, and the bypass pipe port 65 communicates with the first connection port 69.

Then, the first and second through holes 69, 7
0 is communicated with the case 25 unless it is closed by the second valve body 54 described later. As shown in FIG. 5, on the upper surface of the first valve body 53, in order to hermetically seal the communicating portion between the first valve body 53 and the valve base 52, A seal member 68a is provided around the concave groove 68, and a seal member is provided around the first through hole 69.
The sealing member 69a and the sealing member 7 around the second through hole 70.
0a is integrally formed. The guide groove 72
A seal member 72a formed around the valve base 5 is the valve base 5 described above.
This is for maintaining a gap between the second valve body 53 and the first valve body 53.

Further, as shown in FIG. 5, the upper end portion of the valve body 53 is a flange-like flange portion 53b protruding slightly outward in the radial direction of the valve body 53. At a predetermined position along the circumferential direction of the outer surface on the lower end side of the flange portion 53b, a first convex portion 73 for positioning that engages with the magnet member 55.
Are projected outward in the radial direction.

The first convex portion 73 has a circumferential angle of 180 °.
Two are provided separately. Next, this first valve body 5
The second valve body 54 attached to the lower surface of No. 3 will be described.

The second valve body 54 is as shown in FIG. 6, and the first valve body 53 is penetrated from the valve base 52 into a central hole 54a provided in the central portion thereof. By inserting the central shaft 59 protruding from the valve base 53, the upper surface of the central shaft 59 faces the lower surface of the first valve body 53, and the valve base 52 and the first valve body 53 are rotated. It can be attached freely. (See FIG. 2B) On the upper surface of the second valve body 54, first to third circular seal members denoted by 76 to 78 in FIG. 6 are spaced 120 ° around the central hole 54a. And is integrally formed with the second valve body 54.

The first to third seal members 76 to 78
Is the first and second through holes 69, 7 of the first valve body 53.
The diameter is formed to be larger than 0, and these can be closed as needed.

The second valve body 54 is axially penetrated between the second and third seal members 77 and 78 on a concentric circle in which the seal members 77 and 78 are arranged. First, second
Through holes 79 and 80 are formed.

The first and second through-holes 79 and 80 are the first and second through-holes 6 which are opened in the lower surface of the first valve body 53.
The first and second through holes 69 and 70 are formed to have substantially the same diameter as those of the first and second through holes 69 and 70 so as to communicate with each other in the case 25.

Further, as shown in FIG.
The positional relationship between the seal member 78 and the first through hole 79 is set so as to form an angle of 90 ° with the center hole 54a, and the first seal member 77 and the second through hole 79 are formed. Hole 8
The positional relationship of 0 is also set to form 90 °.

Therefore, as shown in FIG.
When the second through hole 80 of the second valve body 54 faces the first through hole 69 of the first valve body 53, the second through hole 80 of the second valve body 54 is provided. The second seal member 77 closes the second through hole 70 of the first valve body 53.

Further, as shown in FIG. 11 (b), the first through hole 79 of the second valve body 54 is formed in the first valve body 53.
When facing the second through hole 70 of
The third seal member 78 of the valve body 54 of FIG.
The first through hole 69 of No. 3 is closed.

On the outer peripheral surface of the second valve body 54,
A second convex portion denoted by 82 in FIG. 6 is provided so as to project radially outward of the valve body. The second convex portion 82 engages with a slit provided in the magnet member 56, which will be described later, to couple the second valve body 54 and the magnet member 56 so that they cannot rotate relative to each other.

The second convex portion 82 is, as shown in the figure, 30 ° + α ° in the circumferential direction (α is the first valve body 53).
The width of the first convex portion 73 provided on the first projection 73 is formed, and two projections are provided at positions separated from each other by 180 ° in the circumferential direction.

Further, as shown in FIG. 2B, the magnet member 55 is attached to the outer peripheral surfaces of the first and second valve bodies 53 and 54. As shown in FIG. 7 and FIG. 7, the magnet member 55 includes the first and second valve bodies 53,
It is composed of a thin-walled cylindrical collar 84 that is directly inserted onto the outer peripheral surface 54, and a permanent magnet 85 fixed to the outer surface of the collar 84.

In addition, at the upper end of the color 84, as shown in FIG.
Is provided with a slit 87. The slit 87 is provided with a width of 30 ° + α ° (the same width as the second convex portion 82 provided on the second valve body 54) in the circumferential direction. Are provided 180 degrees apart from each other.

The first and second valve bodies 53 and 54 have first and second convex portions 73 and 82 provided on their outer peripheral surfaces so as to project.
Is positioned in the slit 87 as shown in FIG. 8 and is combined with the magnet member 55.

Therefore, the second valve body 54 and the magnet member 55 are provided so as not to rotate relative to each other, and the first valve body 53 surrounds the magnet member 55 as indicated by an arrow in the figure. It is rotatable in the direction of 30 °.

Therefore, the first and second convex portions 73,
82 and the slit 87 form the second restricting means of the present invention. The permanent magnet 85 fixed to the outer peripheral surface of the collar 84 is divided into two at 180 ° intervals.
Each is composed of an N pole portion 85a and an S pole portion 85b,
It is driven by the magnetic force from the magnetic force switching unit 56.

As shown in FIGS. 2 (d) and 4, the magnetic force switching section 56 includes a pair of strip-shaped iron-made stations 88 (magnetic pieces of the present invention) provided in parallel and spaced apart from each other. An iron core 89 is installed between the base ends of the station 88, and an electromagnet 90 is formed by winding a coil winding on the iron core 89.

The tip portion of the step 88 is bent along the outer peripheral surface of the permanent magnet 85 attached to the first and second valve bodies 53, 54, and the bending radius is the inner surface. Is set to be slightly larger than the outer diameter of the permanent magnet 85 so that there is a predetermined minute gap with the outer peripheral surface of the permanent magnet 85.

The tip ends of the two stations 88 are approximately 90 ° to each other along the bending direction of the station 88.
It is set so as to be separated at an angle of. The magnetic force switching unit 56 can magnetize the tip portion of the station 88 to a predetermined polarity by applying a direct current to the electromagnet 90, and by switching the magnetism, the magnetic force switching unit 56 and the permanent magnet 85 can be magnetized. The valve body 53 is rotationally driven by generating a suction / repulsion force on the.

The driving torque applied to the magnet member 56 by the magnetic force switching unit 56 is generated by the pressure difference between the high pressure refrigerant and the low pressure refrigerant during the heating and cooling operations described later, and the first valve body 53 and the valve base. It is set to be smaller than the static frictional force with respect to the sleeve 52.

The drive torque of the magnetic force switching section 56 is set to be larger than the static frictional force between the first valve body 53 and the second valve body 54 during the same operation. . Therefore, during operation of heating and cooling, the magnetic force switching unit 56 can drive only the second valve body 54, and when operation is stopped, the first and second valve bodies 53,
Both 54 can be driven.

Further, a holder shown by 57 in FIGS. 2 (b) to 2 (e) is provided on the outside of the tip portion of the step 88. The holder 57 is a thin-walled cylindrical member, and its upper end is fixed to the lower surface of the outer edge of the flange 52a of the valve base 52.

In this holder 57, (c) in FIG.
As shown in (d), a notch 57a is provided for taking out the base end side (electromagnet 90 side) of the above-mentioned step 88 to the outside of the holder 57. The holder 57 is configured to position and prevent rotation of the magnetic force switching portion 56 by the cut portion 57a.

On the other hand, the lower end of the holder 57 and the lower end of the central shaft 59 extending downward from the valve base 52 through the first and second valve bodies 53 and 54 are shown in FIG. Two
The pressing member indicated by 92 in FIGS. 2B and 2E is fixed.

The pressing member 92 is formed in the shape of a strip plate, and its longitudinal end portions are fixed to the lower end of the holder 57 by welding, and the central portion is fixed to the lower end of the central shaft 59.

A spring 93 shown in the drawing is inserted between the central portion of the pressing member 92 and the lower surface of the second valve body 54 in a state of being compressed in the axial direction.
The second valve bodies 53 and 54 are pressed against the lower surface of the valve base 52.

Further, the urging force of the spring 93 is the same as the first and second when the compressor is not operating, that is, when the high / low pressure difference of the refrigerant is not acting on the switching valve portion 28. Due to the weight of the valve bodies 53 and 54, the first
The strength is adjusted to allow a minute gap to be formed between the upper surface of the valve body 53 and the lower surface of the valve base 52.

Next, the assembly of the switching valve portion 28 will be described. First, the holder 57 is attached to the valve base 52.
To fix. On the other hand, as described above, the first and second valve bodies 53 and 54 and the magnet member 55 have the slits 87 of the collar 84 provided in the magnet member 55 in the first and second valves. First and second convex portions 73, 7 of the bodies 53, 54
4 are inserted (state shown in FIG. 8) and held in a state of being combined with each other.

In this state, between the lower surface of the first valve body 53 and the upper surface of the second valve body 54, as shown in FIG. A gap corresponding to the thickness of the seal members 76 to 78 is defined.

Next, the upper end portion of the valve base 52 is provided with the insertion hole 5 provided in the lid portion 25a of the hermetic case 25.
Insert into No. 8 and weld and fix. Thereafter, the combination of the first and second valve bodies 53 and 54 and the magnet member 55 is attached to the central axis 59 of the valve base 52, and the magnetic force switching section 56 is attached. Finally, the pressing member 92 is compressed by the spring 93 while the central shaft 59 is compressed.
And it is fixed to the lower end of the holder 57.

On the other hand, in the lid portion 25a, as shown in FIG. 1, second and third through holes 9 are formed on the side of the switching valve portion 28.
4a and 95b are provided, and the second and third through holes 94a and 94b are provided with the first and second sealed terminals (terminal block of the present invention) shown by 95a and 95b in the figure, respectively. The second and third through holes 94a and 94b are attached in an airtight manner.

The first hermetically sealed terminal 95a is for taking out the wiring for supplying power to the electric motor section 27 to the outside of the case 25, and the three first protruding terminals projecting inside the case 25. -Third inner terminals 96 to 98 and three first to first terminals connected to the respective terminals and projecting outside the case 25
And third outer terminals 100-102.

The second hermetically sealed terminal 95 is for taking out the wiring for feeding the magnetic force switching portion 56 of the switching valve portion 28 to the outside of the case 25, and projecting to the inside of the case 25. A pair of inner terminals 99, 99 and a pair of outer terminals 10 connected to both terminals and protruding outside the case 25.
3 and 103 are provided.

The first to third inner terminals 96 to 98 of the first sealed terminal 95a are the three leads taken out from the three-phase winding of the electric motor section 27 (DC brushless motor). To the wire via a pair of first connectors 104, and the pair of inner terminals 9 of the second sealed terminal 95b.
Reference numerals 9 and 99 are respectively connected to the two lead wires taken out from the switching valve section 28 through a pair of second connectors 105.

That is, when assembling this compressor, the switching valve portion 28 and the first and second sealed terminals 95a and 95b are assembled to the lid portion 25a, and the pair of the second sealed terminals 95b are assembled. The second extended from the inner terminal 99
The connector 105 and the second connector 105 extending from the switching valve portion 28 are connected to each other.

Then, the lid 25a is attached to the case 25.
The first to the first sealed terminal 95a
The first connector 104 derived from the third inner terminals 96 to 98 and the second connector 104 derived from the electric motor unit 27 are also provided.
The connector 104 is connected.

On the other hand, the outer terminals 100 to 103 of the respective sealed terminals 95a and 95b are connected to the control section 106 shown in the figure. The control unit 106 has the first sealed terminal 95.
a general inverter circuit (not shown) to which the outer terminals 100 to 102 of a are connected, and the second sealed terminal 95b.
And a control circuit 111 to which the pair of outer terminals 103, 103 are connected.

The control circuit 111 is constructed, for example, as shown in FIG. That is, the energization from the AC power supply 110 to the electromagnet 90 provided in the magnetic force switching unit 56 is
It is designed to be performed via a phototriac 112 that performs half-wave control. At this time, the micro computer
The data 113 and the phototransistor 114 that detects the AC 0V (zero cross) timing determine whether or not to energize the phototriac 112 at the zero cross point, and output the result.

As a result, the magnetic force switching section 56 can switch the magnetism of the pair of stations 88 between the N pole and the S pole (FIGS. 10 to 13) and also stop the generation of the magnetic force. it can.

Next, the control (operation) of the air conditioner described above will be described. The operation described below is
This is performed according to a command from the control unit 106. First,
The state at the time of stop will be described.

At the time of stop, although not shown, the first and second valve bodies 53 and 54 are urged by their own weight to cause the spring 93 to move.
A slight amount of downward force is exerted against the urging force of the first valve body 53, and a slight amount of clearance is formed between the upper surface of the first valve body 53 and the lower surface of the valve base 52.

In this case, the first and second connection ports 60, 62, the low pressure gas discharge port 61 and the bypass pipe port 65 are all in communication through this gap. Therefore, the pressure in the piping of this air conditioner is balanced (pressure balance).

Next, the control when the heating operation is performed from this state will be described. When the heating operation is performed, the control circuit 111 controls the voltage applied to the electromagnet of the switching valve unit 28 as shown in the waveform diagram of FIG. As a result, the STE 88 (magnetic piece) located on the upper side in the figure is magnetized to the S pole, and the STE 88 located on the lower side is N
Magnetized to poles.

Therefore, the N pole portion 8 of the magnet member 85 is
5a is attracted to the station 88 located on the upper side in the figure, and the S pole portion 85b is attracted to the station 88 located on the lower side, whereby the magnet member 85 rotates clockwise.

As described above, the second valve body 54 is combined with the magnet member 85 such that it cannot rotate relative to the magnet member 85. Further, the first valve body 53 is the second valve body 54
Supported by. Therefore, the first and second
The valve bodies 53 and 54 rotate together with the magnet member 85.

Then, as shown in FIG. 10A, if the stopper 67 projecting from the valve base 52 comes into contact with one end of the guide groove 72 of the first valve body 53 in the circumferential direction. If
Only the first valve body 53 stops rotating.

As a result, as shown in FIG.
The connection port 60 and the low-pressure gas discharge port 61 are communicated with each other by the recessed groove 68 provided in the first valve body 53. The second connection port 62 faces the first through hole 69 provided in the first valve body 53, and the bypass pipe port 65 is provided in the second through hole 7.
Oppose 0.

Further, the second valve body 54 is rotated, and FIG.
As shown in (b), if the first convex portion 73 provided on the first valve body 53 comes into contact with one end in the circumferential direction of the slit 87 provided on the collar 84 of the magnet member 56. The rotation of the magnet member 56 and the second valve body 54 is stopped.

As a result, as shown in FIG.
The second through hole 70 that opens in the valve body 53 is closed by a second seal member 77 provided in the second valve body 54.

On the other hand, the first through hole 69 of the first valve body 53 is the second through hole 8 provided in the second valve body 54.
It will face 0. As a result, the first
Only the second connection port 62 facing the first through hole 69 of the valve body 53 is opened in the case 25.

In this state, the motor section 27 shown in FIG.
Operate. When the electric motor section 27 operates, the compression mechanism section 28 operates, and the refrigerant (working fluid) is compressed. The high temperature high pressure refrigerant after being compressed is discharged into the closed case 25. The high-pressure refrigerant filled in the closed case 25 is filled with the second through hole 80 provided in the second valve body 54 and the gap between the first valve body 53 and the second valve body 54. From (the gap corresponding to the thickness of the seal members 76 to 78), through the first through hole 69 provided in the first valve body 53, and flows into the second connection port 62, The indoor heat exchanger 63, the expansion valve 21, and the outdoor heat exchanger 64 are sequentially passed through while changing the state to heat the room (see FIG. 9).

The refrigerant passing through the outdoor heat exchanger 64 is
It becomes a low-temperature low-pressure refrigerant, flows into the first connection port 60, flows through the recessed groove 68 provided in the upper valve body 53 to the low-pressure gas discharge port 61, and this low-pressure gas discharge port
From the casing 61 through the suction pipe 45 of the compressor to the case 25
It is introduced into the compressor section 26 inside.

The refrigerant introduced into the compressor section 26 is again compressed by the compressor section 26 and discharged into the case 25. Then, again the second valve 54
Is introduced into the indoor heat exchanger 63 from the second connection port 62 through the through hole 80 and the first through hole 69 of the first valve body, and circulates in the pipe of the air conditioner.

During this time, the control circuit 111 is controlled as shown in the waveform diagram of FIG. 10 (d). That is, the applied voltage is controlled to 0, and the pair of stations 88 are not magnetized.

Even in such a state, the above step 8
Since 8 is made of iron (magnetic piece), the state shown in FIG. 10 can be maintained by the attraction force with the magnet member 55.

At this time, since the pressure inside the concave groove 68 of the first valve body 53 is lower than that inside the case 25, the pressure in the case 25 causes the pressure in the first valve body 53 to rise. Body 53
The valve base 52 and the valve base 52 are hermetically adhered to each other, and the magnetic force switching portion 56 is provided.
A static frictional force exceeding the drive torque of is generated.

At this time, the second through hole 70 of the first valve body 53 communicating with the bypass pipe port 65 is closed by the second seal member 77 of the second valve body 54. As a result, the refrigerant in the case 25 does not flow into the bypass pipe indicated by 66 in FIGS. 1 and 9.

In this way, the air conditioner performs the heating operation. However, when it is operated for a long time, frost is formed on the refrigerant distribution pipes and the radiating fins of the outdoor heat exchanger 64 through which the low temperature refrigerant flows. May occur. When frost forms, the heat exchange efficiency of the outdoor heat exchanger 64 decreases and the performance of the air conditioner deteriorates. Therefore, it is necessary to perform the defrosting operation. Next, this defrosting operation will be described.

This defrosting operation is performed during the heating operation. That is, the voltage applied to the electromagnet 90 of the magnetic force switching unit 56 is controlled from the state shown in FIG. 10 as shown in the waveform chart of FIG. 11C. As a result, contrary to the case shown in FIG. 10A, the stay 88 located on the upper side in the figure is magnetized to the N pole, and the stay 88 located on the lower side is magnetized to the S pole.

As a result, repulsion occurs between the permanent magnet 85 and the stage 88, and the magnet member 54 and the second valve body rotate counterclockwise as shown by the arrow in FIG. 10 (b).
At this time, the first valve body 53 maintains the state during the heating operation and does not rotate. That is, during the heating operation, the inside of the recessed groove 68 formed on the upper surface of the first valve body 53 has a negative pressure, and the inside of the case 25 has a high pressure. This is because the valve body 53 strongly adheres to the lower surface of the valve base 52, and the static frictional force generated therebetween is equal to or larger than the drive torque of the magnetic force switching portion 56.

On the other hand, as described above, the first valve body 5 is
3 and the second valve body 54, the static frictional force generated between
A force corresponding to the opening area of the first and second through holes 69, 70 of the first valve body 53 and the pressure applied to the seal members 76, 77 of the second valve body 54 for closing these through holes. Therefore, it is smaller than the drive torque of the magnetic force switching portion 56, and therefore only the second valve body 54 is provided with the first valve body 53.
Independently of, the magnetic member 55 and the magnet member 55 rotate together.

Therefore, as shown in FIG.
If the first convex portion 73 provided on the first valve body 53 comes into contact with the other end portion in the circumferential direction of the slit 87 provided on the collar 76 of the magnet member 55, the second valve The body 54 and the magnet member 55 stop rotating.

As described above, the driving force (driving torque) of the magnet member 55 by the magnetic force switching section 56 is the static friction between the first valve body 53 and the valve base 52 during the heating operation. Since the force is set smaller than the force, the second valve body 54 and the magnet member 55 do not rotate any more.

As a result, as shown in FIG. 11B, the second through hole 70 of the first valve body communicating with the bypass pipe port 65 is provided in the second valve body 54. Facing the first through hole 79 provided, opened into the case 25,
The first through hole 69 of the first valve body 53 communicating with the second connection port 62 is closed by the third seal member 78.

As a result, the high-temperature and high-pressure refrigerant in the case 25 flows into the bypass pipe 66 through the first through hole 79, the second through hole 70 and the bypass pipe port 65, and defrosts. Since the air flows directly to the outdoor heat exchanger 65 via the second connection pipe 143 of the circuit 140 (see FIG. 9), the outdoor heat exchanger 65 is defrosted.

At the same time, a predetermined gap is formed between the valve base 52 and the first valve body 53 by the seal members 68a to 70a and 72a integrally formed on the first valve body 53. Since it is formed, the high-temperature high-pressure refrigerant in the case 25 also flows into the second connection port 62 from this gap and flows into the indoor heat exchanger 63, so that the heating operation is continued. .

Therefore, the defrosting operation of the outdoor heat exchanger 64 can be performed while continuing the heating operation. At this time, the high-temperature high-pressure refrigerant from the bypass pipe 66 flows into the first connecting pipe 141 of the defrosting circuit 140 in a slight amount, but there is a throttle (expansion valve 21) between the compressor 24 and the first connecting pipe 141. So it can be ignored and there is no problem.

During the defrosting operation, the power supply to the magnetic force switching section 56 is maintained as shown in the waveform chart of FIG. 11 (c). Then, after a lapse of a predetermined time, the outdoor heat exchanger 6
When the defrosting of No. 4 is completed, the power supply to the magnetic force switching unit 56 is stopped. By stopping the power supply in this way, the above-mentioned step 88 (magnetic body) and the above-mentioned magnet member 55 (permanent magnet) are provided.
The second valve body 54 returns to the original heating operation (FIGS. 10 (a) and 10 (b)) position by the suction force of. And
Heating operation is continued in this state.

On the other hand, when the heating operation is stopped, the electric motor section 27 (compressor section 26) is stopped.
Then, almost simultaneously with stopping the electric motor section 27, the switching valve section 28 is caused to perform the pressure balancing operation described below.

When the pressure balance operation is performed when the heating operation is stopped (the pressure balance operation when the cooling operation is stopped will be described later), the operation when switching to the defrosting operation described above. Is exactly the same as.

That is, the control circuit shown in FIG.
As shown in the waveform diagram of FIG. 11C from the state shown in FIG. 11, the voltage applied to the electromagnet 90 of the magnetic force switching unit 56 is controlled. As a result, the second valve body is rotated counterclockwise and, as shown in FIGS. 11 (a) and 11 (b), the valve base is rotated.
The bypass pipe port 65 provided in the space 52 is attached to the first
Through the second through hole 70 of the valve body and the first through hole 79 provided in the second valve body 54.

Since a detailed description of this operation has already been given in the above-mentioned defrosting operation, it will be omitted here. By such an operation, the high temperature high pressure refrigerant in the case 25 is
It flows into the bypass pipe 66 through the first through hole 79, the second through hole 70 and the bypass pipe port 65, and then flows into the outdoor heat exchanger 65 through the second connection pipe 143 of the defrosting circuit 140. It will be distributed directly. (See FIG. 9) On the other hand, when the electric motor unit 27 is completely stopped, unlike the above-described defrosting operation, the supply of the low-temperature low-pressure refrigerant to the outdoor heat exchanger 64 is stopped. 64
Low pressure refrigerant inside and the bypass pipe 66 (defrost circuit 140)
The pressure is rapidly balanced with the high-pressure refrigerant supplied from. As a result, the pressure of the refrigerant in the pipe of the air conditioner converges to a constant value (balance pressure) within an extremely short time.

This pressure balancing operation is performed by the electric motor unit 2 described above.
It is performed at substantially the same time as 7 and is continued for a predetermined time (for example, 30 seconds to 1 minute). That is, immediately after the electric motor section 27 is stopped, the pressure in the case 25 is rising, so that only the second valve body 54 is rotated, and the first valve body 53 is the valve base. It does not rotate due to the static frictional force with the sleeve 52.

After a lapse of a predetermined time, the bypass pipe 66 and the defrosting circuit 140 work to balance the pressure. Then, as described above, the static frictional force between the first valve body 53 and the valve base 52 becomes smaller than the drive torque of the magnetic force switching section 56, so that the first valve body 53. Can be easily driven. Therefore, it is possible to easily switch to the cooling operation described later.

By such a pressure balance operation, the pressure in the refrigeration cycle is quickly balanced, so that the waiting time when the air conditioner is restarted or when the air conditioner is switched to the cooling operation described below is significantly shortened. be able to.

Next, the control and operation during the cooling operation will be described. During cooling operation, pressure is balanced in the refrigeration cycle (first valve can be driven)
Then, as shown in the waveform diagram of FIG. 12C, the voltage applied to the electromagnet 90 of the switching valve portion 28 is controlled. As a result, contrary to the case of the heating operation shown in FIG. 10, the stay 88 located on the upper side in the figure is magnetized to the N pole, and the stay 88 located on the lower side is magnetized to the S pole.

As a result, the S pole portion 8 of the magnet member 55 is
5b is attracted to the station 88 located on the upper side in the figure, and the N pole portion 85a is attracted to the station 88 located on the lower side, whereby the magnet member 55 rotates.

The second valve body 54 has the magnet member 55.
Since the first valve body 53 is engaged with the slit 87 of the collar 84 provided on the magnet member 55, the first and second valve bodies 53, 54 are Rotate with the magnet member.

At this time, since the air conditioner is not in operation, there is no difference between high and low pressures, the first valve body 53 and the valve base 52 are not in close contact with each other, and an excessive static friction force is generated. Therefore, even if the torque applied to the magnet member 55 by the electromagnet 90 is low, the first valve body 53 is easily driven to rotate.

A stopper 67 projecting from the valve base 52 is provided with a guide groove 7 provided in the first valve body 53.
When it abuts on the other end in the circumferential direction of 2, the first valve body 53 stops rotating, as shown in FIG.

As a result, the second connection port 62 and the low-pressure gas discharge port 61 communicate with each other through the recessed groove 68, as opposed to during heating. Then, the first connection port
The port 60 faces the second through hole 70 provided in the first valve body 53, and also the bypass pipe port 65.
Faces the second through hole 69.

Further, as shown in FIG. 12 (b), the first convex portion 73 provided on the first valve body 53 is provided around the slit 87 provided on the collar 84 of the magnet member 55. If it abuts on the other end face in the direction, the rotation of the second valve body 54 and the magnet member 55 is stopped.

As a result, the second through hole 70 of the first valve body 53 facing the first connection port 60 has the first through hole provided in the second valve body 54. The case 25 is opened so as to face the hole 79. Further, the first through hole 69 of the first valve body 53 facing the bypass pipe port 65 is closed by a third seal member 78 provided in the second valve body 54. It

When the operation of the electric motor section 27 is started in this state, the high pressure refrigerant is filled in the case 25 by the operation of the compressor section 26, and this pressure and the inside of the concave groove 68 are Due to the pressure difference, the first valve body 53 is brought into close contact with the lower surface of the valve base 52.

The high pressure refrigerant in the case 25 is
The first through hole 79 and the seal member 76 of the second valve body 54.
Through the gap between the first valve body 53 and the second valve body 54, the second through hole 70 of the first valve body 53 is formed.
Through the first connection port 60. Also,
At the same time, the seal members 68a to 68a of the first valve body 53
The high-temperature high-pressure refrigerant in the case 25 also flows into the first connection port 60 through the gap between the valve base 52 and the first valve body 53 formed by 70a and 72a.

Then, the air is circulated from the first connection port 60 to the outdoor heat exchanger 64, the expansion valve 21 (pressure reducing device), and the indoor heat exchanger 63 while sequentially changing their states to cool the room. .

The refrigerant having passed through the indoor heat exchanger 63 flows into the second connection port 62, passes through the concave groove 68, and flows from the low pressure gas discharge port 61 to the case. It is introduced into the compressor section 26 in the space 25.

During the cooling operation, the applied voltage to the electromagnet 90 is controlled to 0 as in the heating operation (FIG. 12 (d)). However, even in such a state, since the above-mentioned station 88 is made of iron (magnetic piece), the attraction force with the magnet member 55 causes the above-mentioned FIGS. 12 (a) and 12 (c).
The state of can be maintained. At this time, since the pressure inside the recessed groove 68 is lower than that inside the case 25, the pressure inside the case 25 causes the first valve body 53 and the valve base 52 to be separated from each other. It adheres airtightly and cannot be easily moved.

On the other hand, when stopping the cooling operation, the electric motor section 27 (compressor section 26) is stopped.
Then, almost simultaneously with stopping the electric motor section 27, the switching valve section 28 is caused to perform the pressure balancing operation described below.

That is, from the state shown in FIG.
As shown in the waveform diagram of (c), the voltage applied to the electromagnet 90 of the magnetic force switching unit 56 is controlled. In this way,
Contrary to the case shown in FIG. 2 (a), the stay 88 located on the upper side in the figure is magnetized to the N pole, and the stay 88 located on the lower side is magnetized to the S pole.

As a result, a repulsion occurs between the permanent magnet 85 and the stage 88, and the magnet member 54 and the second valve body rotate clockwise as shown by the arrow in FIG. 12 (b). At this time, the first valve body 53 maintains the state during the cooling operation and does not rotate. That is, immediately before or immediately after stopping the electric motor section 27 (compressor section 26), as in the cooling operation, the inside of the concave groove 68 formed in the upper surface of the first valve body 53 is kept at a negative pressure, Since the inside of the case 25 is kept at a high pressure, the pressure difference causes the first valve body 53 to come into close contact with the lower surface of the valve base 52, and the static frictional force generated therebetween causes the magnetic force switching. This is because the driving torque of the portion 56 is equal to or higher than the driving torque.

On the other hand, as described above, the first valve body 5 is
3 and the second valve body 54, the static frictional force generated between
As described above, it is smaller than the drive torque of the magnetic force switching unit 56. Therefore, only the second valve body 54 rotates together with the magnet member 55 independently of the first valve body 53.

Therefore, as shown in FIG.
If the first convex portion 73 provided on the first valve body 53 comes into contact with one circumferential end of the slit 87 provided on the collar 76 of the magnet member 55, the second valve body is formed. 54 and the magnet member 55 stop rotating.

As described above, the driving force (driving torque) of the magnet member 55 by the magnetic force switching section 56 is the static friction between the first valve body 53 and the valve base 52 during the heating operation. Since the force is set smaller than the force, the second valve body 54 and the magnet member 55 do not rotate any more.

As a result, as shown in FIG. 13B, the first through hole 69 of the first valve body communicating with the bypass pipe port 65 is provided in the second valve body 54. Facing the second through hole 80 formed, opened into the case 25,
The second through hole 70 of the first valve body 53 communicating with the first connection port 60 is the second through hole provided in the second valve body 54.
It is closed by the seal member 77.

By such an operation, the high-temperature high-pressure refrigerant filled in the case 25 is bypassed through the second through hole 80, the first through hole 69 and the bypass pipe port 65. It flows into the pipe 66 and directly flows into the indoor heat exchanger 63 via the first connection pipe 141 of the defrosting circuit 140. (See FIG. 9) On the other hand, when the electric motor unit 27 is completely stopped, the supply of the low-temperature low-pressure refrigerant to the indoor heat exchanger 63 is stopped, so that the low-pressure refrigerant in the indoor heat exchanger 64 and the bypass pipe are The pressure is rapidly balanced with the high-pressure refrigerant supplied from 66 (defrosting circuit 140). As a result, the pressure of the refrigerant in the pipe of the air conditioner converges to a constant value (balance pressure) within an extremely short time.

This pressure balancing operation is performed by the electric motor section 2 described above.
It is performed at substantially the same time as 7 and is continued for a predetermined time (for example, 30 seconds to 1 minute). That is, immediately after the electric motor section 27 is stopped, the pressure in the case 25 is rising, so that only the second valve body 54 is rotated, and the first valve body 53 is the valve base. It does not rotate due to the static frictional force with the sleeve 52.

After a lapse of a predetermined time, the pressure balance is achieved by the action of the bypass pipe 66 and the defrosting circuit 140. Then, as described above, the static frictional force between the first valve body 53 and the valve base 52 becomes smaller than the drive torque of the magnetic force switching section 56, so that the first valve body 53. Can be easily driven. Therefore, switching to the heating operation can be easily performed.

Since the pressure balancing is performed quickly by such a pressure balancing operation, the waiting time when the air conditioner is restarted or when the cooling operation is switched to the heating operation can be significantly shortened.

Next, the operation when the switching between the cooling operation and the heating operation fails will be described. When the switching fails, the switching is performed in a state where the pressure is not balanced for some reason, and the first valve body 53 is switched to the normal position (shown in FIGS. 10 and 12) during cooling or heating. If not.

Therefore, it becomes difficult for the refrigerant to circulate, and normal cooling or heating operation cannot be performed. This state is eliminated by the switching error elimination operation described below.

This switching error elimination operation is substantially the same as the pressure balance operation described above. That is, if a switching error occurs when switching to heating operation (FIG. 10),
Almost at the same time when the electric motor unit 27 (compressor unit 26) is stopped, the voltage applied to the electromagnet 90 of the magnetic force switching unit 56 is controlled as shown in the waveform diagram of FIG. 11 (c).

As a result, as described above, only the second valve body 54 rotates, and as shown in FIG. 11B, the second through hole 70 of the first valve body 53 is formed. And the first through hole 79 of the second valve body communicate with each other. When the heating operation is performed for a while, the second through hole 70 of the first valve body 53 is provided with the bypass pipe port 6 of the valve base 52.
5, the port 65 enables rapid pressure balance in the piping using the bypass pipe 66 and the defrosting circuit 140.

Therefore, thereafter, the voltage applied to the electromagnet 90 of the magnetic force switching section 56 is controlled again as shown in the waveform diagram of FIG. 10C, and the heating shown in FIGS. 10A and 10B is performed again. The first and second valve bodies 5 are placed in the operating position.
Switch between 3 and 54.

By such an operation, even if there is a switching error, the state can be quickly eliminated and the heating operation can be restarted. It should be noted that, if a switching mistake is made when switching to the cooling operation (FIG. 12), the motor unit 27
And the electromagnet 9 of the magnetic force switching unit 56 is stopped.
The voltage applied to 0 is controlled as shown in the waveform diagram of FIG.

As a result, the bypass pipe 66 and the defrosting circuit 1 are operated in the same manner as the switching error eliminating operation during the cooling operation described above.
By using 40, the pressure balance in the pipe can be rapidly achieved.

Therefore, even if there is a switching error,
The state can be quickly eliminated and the cooling operation can be restarted. Since the magnetic force switching unit 56 always generates a driving torque sufficient to drive the second valve body 54, the second valve body 54 is always driven reliably.

The structure described above has the following effects. First, there is an effect that a pressure balance operation can be performed when cooling or heating is stopped, and this pressure balance can be easily and quickly performed.

That is, in the case of the conventional reciprocating type sliding valve, in order to prevent the compressed gas leakage, the sliding valve must be in close contact with the valve seat at all times. The pressure cannot be balanced in a portion, and the pressure can be balanced only through the mechanical portion of the compressor section 26 or the expansion valve 21 having a large flow resistance. Therefore, there is a case where it is necessary to wait for a long time (for example, 3 minutes or more) as shown by the alternate long and short dash line in FIG. 14 from the stop of the compressor to the pressure balance.

On the other hand, if it is possible to switch between cooling and heating without this pressure balance being established, if such switching is attempted, the sliding valve must be driven with an excessive force. However, the switching load becomes considerably large. In order to withstand such a switching load, not only the rigidity of the valve body and the sliding valve must be increased, but also the driving force of the solenoid valve device must be increased. It has the drawback of becoming

However, in the case of the present invention, the switching valve is of the case built-in type and of the rotating type so that the five-way switching can be performed by utilizing the pressure difference in the case. . As a result, the bypass pipe 66 can be communicated with the case to perform the pressure balance operation.

As a result, a bypass pipe and a defrosting circuit having a small flow resistance are added unlike the mechanical portion of the compressor unit 26 and the portion having a large flow resistance such as the expansion valve 21. As shown by, the operation from the operation stop to the pressure balance can be rapidly performed, and there is an effect that the restart and the operation switching can be performed quickly. Further, there is an effect that the injection of the refrigerant or the like can be performed quickly without waiting for a long time for pressure balance.

Further, since the pressure balance operation can be performed under the same switching load as usual, it is not necessary to increase the size of the switching valve section or the electromagnetic switching section to increase the driving force, and the pressure balancing operation can be performed. Since the vinegar driving means for suffices to use a magnetic force switching section for performing a heating / cooling switching operation, the device can be made compact.

Even when such pressure balance operation is not performed, when the operation of the electric motor unit 27 is stopped, the pressure in the case is lowered and the first and second valve bodies are slightly moved by their own weight. It goes down and the gap with the valve base 52 is enlarged. Therefore, since all the ports 60 to 62 provided on the valve base 52 communicate with each other through the gap formed between the ports 60 and 62 and the upper surface of the valve body 53, the pressure as shown by the dotted line in FIG. The balance can be done rather quickly.

However, since it is necessary to wait until the pressure in the case decreases, the time until pressure balance becomes longer than that in the case of performing the pressure balance operation of the present invention.
Even with the configuration as described above, the pressure in the case 25 causes the first valve body 53 to operate during operation.
Since it is pressed against the valve base 52 and comes into close contact with it,
There is no leakage of compressed gas, and it is held so as not to easily move in the rotation direction.

Secondly, there is an effect that the defrosting of the outdoor heat exchanger can be performed quickly without stopping the heating operation with a simple structure. That is, in the configuration of the conventional example, when frost is formed on the outdoor heat exchanger 64, in order to melt the frost,
It is necessary to temporarily switch the heating cycle to the cooling cycle and send the high-temperature high-pressure refrigerant to the outdoor heat exchanger.

However, this causes a problem that the room temperature is lowered. Further, as described above, in the configuration of the conventional example, it may not be possible to quickly defrost because switching between cooling and heating cannot be performed quickly.

In order to eliminate such a defect,
It is conceivable to provide a switching valve different from the above four-way valve and directly supply the high temperature and high pressure refrigerant from the compressor to the outdoor heat exchanger in the frosted state to perform defrosting.

However, according to this method, since two switching valves are provided, the structure becomes complicated, and when the switching valve is provided outside the case 25, vibration from the compressor is generated. Is generated in the connecting pipe between the switching valve and the switching valve, it is necessary to take vibration damping measures.

Further, when the other switching valve is provided in the case 25, it is necessary to upsize the case 25, and more wiring is taken out from the case 25, which results in a wiring structure. There is also the problem of complication.

However, in the present invention, the switching valve portion 28 is
Is a rotary type 5 having first and second two valve bodies 53, 54.
This was housed in the case 25 as a one-way valve. As a result, it is possible to obtain a compressor that can quickly perform the defrosting operation with a simple configuration without stopping the heating operation.

[0187] Further, the above-mentioned first condition during the cooling or heating operation.
The first and second valve bodies 53, 54 are utilized by utilizing the increase in static frictional force due to the close contact state between the valve body 53 and the valve base 52.
Can be driven separately by one magnetic force switching unit 56. Therefore, the wiring need only be two wirings for supplying power to the electromagnet 90 provided in the magnetic force switching unit 56, and the wiring structure can be simplified. effective.

If it is attempted to switch among the four operating states (FIG. 10 to FIG. 13) of cooling, heating, pressure balance operation and defrosting without using the above-mentioned structure, at least two electromagnets are required. Therefore, the size of the structure becomes large and the wiring and the structure become complicated.

Further, according to the present invention, the bypass pipe 66 and the defrosting circuit 140 used for defrosting can be used for the above-mentioned pressure balancing operation, so that an effective operation can be performed with a small piping structure. is there.

Thirdly, even if a switching error to the heating / cooling operation occurs, this state can be quickly resolved by the switching error elimination operation, and the heating / cooling operation can be restarted quickly.

That is, when there is a switching error, the motor unit 27 is stopped and at the same time the magnetic force switching unit 56 is operated.
By operating, like the pressure balance operation,
The first or second through hole 79, 8 of the second valve body 54.
0 can be communicated with the bypass pipe port 65 of the valve base 52, and the pressure balance in the pipe can be rapidly achieved by utilizing the bypass pipe 66 and the defrosting circuit 140.

Therefore, again, the first and second valve bodies 5
There is an effect that the cooling or heating operation can be restarted quickly by re-driving Nos. 3 and 54. Fourthly, there is an effect that the piping of the air conditioner can be simplified.

That is, the first provided on the valve base.
Alternatively, the second connection port is connected to the first and second valve bodies 5 described above.
Since it can be opened directly into the case 25 through 3, 54, a high pressure gas pipe is not required. Also,
As a result, the anti-vibration measures that were conventionally required for high-pressure gas piping are no longer required.

Further, unlike the conventional example, the switching valve portion 28 does not use the electromagnetic valve device, and therefore the capillary tube required for the conventional switching valve (11 to 12 shown in FIGS. 16 and 17). Becomes unnecessary.

Therefore, the compressor can be easily assembled, and an air conditioner with a simple structure and less vibration can be obtained. Fifthly, the compressor can be downsized.

That is, the switching valve portion 28 incorporated in the case 25 of this compressor is of a rotary type unlike the conventional example, and since it does not have an electromagnetic valve device, its total length is reduced. be able to.

Moreover, as described above, since the mechanism for performing the defrosting operation and the pressure balancing operation can be integrally incorporated, the case 25 does not have to be made large and the switching valve portion 28 is not required.
Can be incorporated in the case 25 of the compressor, and there is an effect that it is possible to sufficiently cope with the recent tendency of downsizing of the compressor.

Further, as a result of this, the total length of the connecting portion between the through hole 58 of the lid 25a of the case 25 and the valve base 52 is reduced, so that the welded portion itself is also reduced and the gas leak is prevented. Reliability and workability of welding work are also improved.

Sixth, there is an effect that the electric power for controlling the switching valve portion 28 can be reduced. That is, since the stay 88 is made of iron (magnetic piece), the stay 88 is magnetized by the attraction force between the stay 88 and the magnet member 54 even when the stay 88 is not magnetized except when the valve 52 is driven. , The switching position can be maintained.

Therefore, unlike the conventional example in which the position of the sliding valve is maintained by the spring and the electromagnet, it is not necessary to apply a voltage to the magnetic force switching section 56 during operation, so that power consumption can be reduced. .

The present invention is not limited to the above-described embodiment, but can be variously modified without changing the gist of the invention. In the above embodiment, the bypass pipe is connected to the first and second connecting pipes and the check valve as a defrosting circuit. However, as shown in FIG. 15, only the second connecting pipe is used. Is also good.

According to this structure, since the first connecting pipe does not exist, the pressure balance operation when the cooling operation is stopped cannot be performed, but the pressure balance operation when the heating operation is stopped and the defrosting operation during the heating operation are performed. Can be performed through the second connecting pipe.

However, even if the pressure balancing operation is not performed when the cooling operation is stopped, the first valve body descends when the pressure in the case lowers.
The pressure can be balanced at the speed indicated by the dotted line in FIG.

In consideration of this, the configuration of FIG. 15 eliminates the need for the first connecting pipe and the first and second check valves, as compared with the above-described embodiment, so that the piping configuration of this air conditioner is eliminated. There is an effect that can be greatly simplified.

Further, even when the switching from the cooling operation to the heating operation is missed, the high pressure refrigerant is directly supplied to the outdoor heat exchanger through the bypass circuit and the second connecting pipe to rapidly balance the pressure. As a result, it is possible to quickly eliminate the switching error condition.

Further, in the above embodiment, the fluid compressor is a twin rotary compressor having two cylinders 35 and rollers 40, but the invention is not limited to this. For example, a single rotary compressor having only one roller 40 may be used.

In addition, the swirl scroll blade and the non-swirl scroll
It may be a scroll type compressor which forms a compression space by combining with a wing and swirls the swirl scroll with respect to the non-swirl scroll to compress the fluid in the compression space. . The point is that the case can be filled with the compressed high pressure refrigerant.

Further, in the above embodiment, not only the compressor section 28 but also the electric motor section 27 is provided in the case 25. However, only the compressor section 27 and the switching valve section 28 are provided in the case 25.
The electric motor part 27 may be housed inside and provided outside the case 25.

Further, in the above-mentioned one embodiment, the first valve body 53 and the second valve body 54 are driven by one magnetic force switching section 56, but the present invention is not limited to this. .
For example, the first valve body 53 is driven by a servo motor,
The second valve body 54 may be driven by a crank mechanism connected to the electromagnetic switching valve.

Even in this case, as described above, the first,
Since the second valve body does not require a large driving force, it is not necessary to upsize the driving mechanism, and the switching valve itself can be downsized.

[0211]

According to the structure as described above, the outdoor five-way switching valve is provided while the heating operation is continued by providing the rotary five-way switching valve in the case filled with the compressed high-pressure fluid. Can be defrosted.

Further, at the time of stop, the high pressure refrigerant in the case is supplied to the refrigerant inlet of the indoor heat exchanger or the refrigerant inlet of the outdoor heat exchanger, so that the pressure balance in the refrigeration cycle can be rapidly achieved. Therefore, there is an effect that the restart or the operation switching between cooling and heating can be quickly performed.

Further, in view of the fact that the static frictional force generated between the valve base and the first valve body by the high pressure refrigerant in the case is large during the operation of the compressor and is small during the stop, the above-mentioned first Since the drive torque of the drive means for rotationally driving the valve body and the second valve body is adjusted, only the second valve body can be driven during operation of the compressor, and the first and second valves can be operated during stoppage. Can drive both of the body,
Five-way switching can be performed.

Therefore, even when the switching valve is incorporated in the case, the case does not become large, and the piping configuration can be simplified, so that a compact air conditioner can be obtained. be able to.

[Brief description of drawings]

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

FIG. 2 is a plan view, a front view, a side view, a cross sectional view, and a vertical sectional view showing a switching valve portion.

FIG. 3 is a plan view, a side view, and a bottom view showing a valve base of the switching valve portion.

FIG. 4 is a plan view, a side view, and a front view showing a magnetic force switching unit.

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 first 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 likewise a top view of the compressor.

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

FIG. 11 is an operation diagram and a waveform diagram showing the switching operation of the switching valve portion during the defrosting operation (pressure balance operation).

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

FIG. 13 is an operation diagram and a waveform diagram showing a pressure balance operation.

FIG. 14 is a graph showing a time until pressure balance.

FIG. 15 is a vertical cross-sectional view showing the main parts of another embodiment.

FIG. 16 is a vertical cross-sectional view showing a conventional four-way valve.

FIG. 17 is a vertical sectional view showing a compressor of the same.

[Explanation of symbols]

17 ... Compressor, 21 ... Expansion valve (pressure reducing device), 25 ... Case
26 ... Compressor section, 28 ... Switching valve section (rotary five-way switching valve), 52 ... Valve base, 53 ... First valve body, 54 ... Second
Valve member, 55 ... Magnet member, 56 ... Magnetic force switching section (driving means), 60 ... First connection port, 61 ... Low-pressure gas discharge port, 62 ... Second connection port, 63 ... Indoor heat exchanger,
64 ... Outdoor heat exchanger, 65 ... Bypass pipe port (piping means port), 66 ... Bypass pipe, 68 ... Concave groove (communication groove), 69 ... First through hole, 70 ... Second Through hole, 106 ... Control unit, 140 ... Defrost circuit (piping means),
141 ... First connecting pipe (indoor heat exchanger-side connecting pipe), 14
2 ... 1st check valve, 143 ... 2nd connection pipe (outdoor heat exchanger side connection pipe), 144 ... 2nd check valve.

Front page continuation (58) Fields surveyed (Int.Cl. ⁷ , DB name) F25B 41/04 F04B 39/00 F16K 11/074

Claims (6)

(57) [Claims] 1. An air conditioner comprising a refrigeration cycle in which a compressor, an indoor heat exchanger, a decompression device, and an outdoor heat exchanger are sequentially connected by piping, and a control section for controlling the refrigeration cycle. Is an indoor heat exchanger-side connection pipe that connects the compressor to a pipe that serves as a refrigerant inlet of the indoor heat exchanger during cooling operation, and connects a compressor and a pipe that serves as a refrigerant inlet of the outdoor heat exchanger during heating operation. And a pipe means having an outdoor heat exchanger-side connecting pipe, and the compressor is provided with a case filled with high-pressure refrigerant after compression, and the compressor is provided in the case and is rotated by the above. The rotary type five-way valve having first and second valve bodies for switching the flow path of the refrigerant is provided, and the control unit controls the rotary type five-way valve.
By rotating the second valve element, the heating, cooling and defrosting operations are switched, and the switching to the defrosting operation is performed by continuing the heating operation to transfer the high pressure refrigerant in the case to the outdoor heat exchanger. An air conditioner having means for performing the operation by supplying to the side connecting pipe. 2. The air conditioner according to claim 1, wherein the piping means is provided in the indoor heat exchanger-side connecting pipe and regulates the flow of the refrigerant toward the compressor. And a second check valve provided in the outdoor heat exchanger-side connection pipe and for restricting the flow of the refrigerant in the compressor direction. The controller further stops the heating operation and the case. Air having a means for supplying the high-pressure refrigerant in the outdoor heat exchanger-side connection pipe to supply the high-pressure refrigerant in the case to the indoor heat-exchanger-side connection pipe when the cooling operation is stopped. Harmony machine. 3. The air conditioner according to claim 1, wherein the control unit further stops the compressor and, at the same time, stops the compressor when an error occurs in switching to the cooling operation by the five-way switching valve. A means for switching the cooling operation by supplying the high-pressure refrigerant in the case to the indoor heat exchanger-side connecting pipe and rotating the first and second valve bodies again, and the heating operation by the five-way switching valve. If there is an error in switching to, the compressor is stopped and the high-pressure refrigerant in the case is supplied to the outdoor heat exchanger-side connecting pipe, and the first,
An air conditioner having a means for switching to a heating operation by rotating the second valve body. 4. The air conditioner according to claim 1, wherein the rotary type five-way switching valve is provided on a valve base attached to the case, and the valve base is provided on the valve base. -Three ports connected to the suction side of the outdoor heat exchanger, the indoor heat exchanger and the compressor, respectively, and the piping means ports connected to the piping means, which are open to the inside and outside surfaces of the case. Port, the three ports of the valve base, and the port for piping means.
First rotatably mounted on the inner surface of the case where the door opens
And a valve body of the first valve body which is provided on a surface of the first valve body facing the valve base.
A communication groove for selectively communicating two of the ports with each other, and another one of the port provided in the first valve body and the port for piping means are communicated with the inside of the case. First, second
Of the first valve body and the through hole of the first valve body.
Air having a second valve body that closes the first or second through hole of the first valve body by rotating the first valve body by a predetermined angle. Harmony machine. 5. The air conditioner according to claim 4, wherein the rotary five-way switching valve is provided on the first valve body and the valve base, and the first five-way switching valve is provided on the first valve body and the valve base.
For regulating the rotation angle of the valve body of the above with respect to the valve base
Of the first valve body and the second valve body, the second regulating means for regulating the relative rotation angle of the first valve body and the second valve body within a predetermined range, and the second valve body. It is driven to rotate, and the first or second
The high pressure refrigerant from inside the case and the low pressure refrigerant from outside the case are actuated by the regulating means of No. 5 to the indoor heat exchanger, the outdoor heat exchanger, the suction side of the compressor, or the piping means. An air conditioner comprising: a drive unit for switching between directions. 6. The air conditioner according to claim 5, wherein the drive torque of the drive means is based on a static friction force generated between the first valve body and the valve base during operation of the compressor section. The air conditioner is also small and larger than the static frictional force generated between the first valve base and the second valve base.