JP3354783B2 - Fluid compressor and heat pump refrigeration cycle - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid compressor having a switching valve for switching a flow path of a working fluid, an air conditioner having the fluid compressor, and a heat pump type refrigeration cycle.

[0002]

2. Description of the Related Art Generally, there is an air conditioner capable of performing both cooling and heating. This air conditioner has a fluid compressor that compresses and discharges a working fluid, an indoor heat exchanger, and an outdoor heat exchanger. In addition, the flow of the working fluid flowing through these heat exchangers during cooling and heating is performed. A flow path switching valve for switching a path is provided.

As such a flow path switching valve, a direct acting four-way switching valve has been widely used. The four-way switching valve has a main body formed in a cylindrical shape, and a slide valve provided in the main body and held so as to be able to reciprocate along the axial direction of the main body. The four-way switching valve switches the flow path by moving the sliding valve linearly in the main body.

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

By the way, the four-way switching valve described above is
It is common to incorporate a four-way switching valve and a solenoid valve into a fluid compressor. There is one disclosed in FIG. 4 of Japanese Patent Application Laid-Open No. 60-124595.

This invention is a compressor of a type in which a high-pressure discharge gas discharged from the compressor section is filled in a sealed case accommodating a compressor section and an electric motor section. Built-in dynamic four-way switching valve and solenoid valve.

This invention eliminates the need for a high-pressure gas introduction pipe connecting the compressor and the switching valve by placing the four-way switching valve and the solenoid valve in a case filled with the high-pressure gas. An object of the present invention is to effectively prevent the capillary connecting the four-way switching valve and the solenoid valve from being damaged by an external force.

[0008]

The four-way switching valve built in the compressor has a solenoid valve for switching a sliding valve, and this solenoid valve is also built in the case of the compressor. I have. For this reason, there is a problem that the compressor becomes large.

Further, since the slide valve is a direct-acting type in which the flow path is switched by sliding the slide valve in the main body, it is necessary to keep the slide valve in close contact with the valve seat. . Therefore, a considerable driving force is required to drive this sliding valve. Therefore, the mechanism (electromagnetic valve) for driving the sliding valve must be large, and the valve device itself including the electromagnetic valve may be enlarged accordingly.

Further, a piping structure for connecting the four-way switching valve and the solenoid valve is complicated, and it is necessary to secure a considerable space in the case to route the piping. For this reason, the whole of the fluid compressor may be increased in size.

The present invention has been made in view of such circumstances, and a fluid compressor with a built-in switching valve has the following features.
An object of the present invention is to provide a compact fluid compressor with a built-in switching valve and an air conditioner having the fluid compressor, by miniaturizing and simplifying the driving means of the switching valve.

[0012]

The present invention comprises a case,
Compression mechanism housed in this case and this compression mechanism
In the fluid compressor having an electric motor for driving, the Ke
3 ports that are attached to the case and lead out of the case
Valve base formed and three ports of this valve base
Are held slidably in contact with the opening surfaces of the three
Do not connect two adjacent ports of the
A valve body having a communication passage for moving the valve body.
As a result, the discharge passage outside the case and the suction
A switching valve for switching the inlet flow path, and a switching valve connected to the switching valve.
And a second magnetic generator connected to the rotor of the electric motor.
The motor's driving force by rotatably facing the magnetic
And magnetic coupling means for transmitting to the switching valve, set to the switching valve
Pressure that guides the high-pressure fluid compressed by the compression mechanism.
A force operating chamber and a compartment for dividing the pressure operating chamber into two rooms.
The cutting means is held rotatably,
Selectively in one or the other chamber of the pressure working chamber
Introduce low pressure and move valve body by pressure difference generated between rooms
Magnetic coupling means comprising pressure introduction switching means for freely driving
Valve body driving means for transmitting the driving force of the stage to the valve body, and the valve body
It is provided in the drive means, and when the motor rotates forward,
When the drive force from the motor to the valve body is regulated and the motor rotates
Drive power control to transmit the drive power from the motor to the valve
Means and the driving force control means, and the electric motor
In the case of rotation, the drive of the pressure introduction switching means is regulated and
When the machine rotates in reverse, drive the pressure introduction switching means.
A rotation restricting mechanism for switching a fluid flow path.

[0013]

[0014] Incidentally, the second magnetism generating means may also serve the permanent magnets disposed on the rotor of the motor.

[0015] Incidentally, the suction force or repulsive force between the first magnetic generating means and the second magnetic generator, the rotation axis of the second magnetic generator and connected to the electric motor to the magnetic generating means and It may be set to a value smaller than the total mass with the rotor .
No.

[0016] Incidentally, the first magnetism generating means has an outer diameter is set smaller than the inner circumferential diameter of the coil end of the stator of the motor, and be disposed to penetrate inside of the coil end Good .

[0017]

[0018]

[0019] Incidentally, the valve body drive means is provided at both ends along the driving direction of the valve body of the pressure operation chamber, introducing a high pressure within the case in a room with low pressure the pressure operation chamber is not introduced May be provided.

[0020] Incidentally, the pressure operation chamber is provided in the valve body, the partition means is immovably held in the driving direction of the valve body
You may .

[0021] Incidentally, the partition means may the pressure introducing member that is inserted into the pressure operating chamber.

[0022] Incidentally, the switching valve, and ports for low pressure fluid pipe connected to the compression mechanism, and a low-pressure introduction hole for introducing the low pressure fluid flowing to the low pressure fluid port to the pressure introduction switching means takes out a low pressure May be provided.

[0023]

[0024] Note that the switching valve is intended to switch the flow path of the ports formed in the valve base by the rotation of the valve body
You may .

[0025] Note that the switching valve be switched to the flow path of the ports formed in the valve base by the reciprocating movement of the valve body
No.

[0026] Incidentally, the valve base and the metal material, the valve body abuts on the valve base may be a synthetic resin material.

[0027] Incidentally, by forming a synthetic resin material to one surface either of said valve base or said valve body is in sliding contact with each other
Is also good .

[0028]

[0029]

The present invention is driven by an electric motor.
Has a compression mechanism to suck in and compress fluid and discharge compressed fluid
A fluid compressor, a first heat exchanger for performing heat exchange of the fluid, and
In a heat pump refrigeration cycle having a second heat exchanger
In addition , the above-mentioned fluid compressor has a case and
A stored compression mechanism and an electric motor for driving the compression mechanism
And three ports attached to the case and connected to the outside of the case.
Valve base formed with a base and three of this valve base
Slidably held in sliding contact with the port opening surface
Two adjacent ports among three ports communicate with each other
A valve having a communication passage formed by moving the valve.
To move the discharge channel and compressor out of the case
Switching valve for switching the suction flow path to the structure and connected to the above switching valve
Connected to the rotor of the electric motor.
The second magnetic generating means rotatably opposed to the
And magnetic coupling means for transmitting the driving force to the switching valve, the switching
High-pressure fluid provided in the switching valve and compressed by the compression mechanism
And a pressure working chamber that guides
Partitioning means, and rotatably held and rotated
Therefore, one of the pressure operation chambers or the other is selected.
Low pressure is introduced selectively, and the valve is actuated by the pressure difference generated between the rooms.
Pressure introducing switching means for movably driving the body,
Valve body driving means for transmitting the driving force of the pneumatic coupling means to the valve body
Stage and the valve body driving means, and the electric motor rotates forward.
The drive force from the motor to the valve
When the motor rotates in reverse, the driving force is transmitted from the motor to the valve
Driving force control means, and the driving force control means
When the motor rotates forward, the pressure introduction switching means is driven.
Operation is regulated, and pressure is switched when the motor rotates in the reverse direction.
Rotation control mechanism that drives the means and switches the fluid flow path
And with.

[0031]

According to the present invention , since the electric motor for driving the compression mechanism is used as the drive source for the switching operation of the switching valve, there is no need to provide an electromagnetic valve for driving the switching valve, and the compressor is compact. Can be configured.

According to the present invention , the driving force of the electric motor is transmitted by the magnetic coupling means without directly coupling the switching valve and the electric motor, so that the transmission mechanism is simplified.

Since the second magnetism generating means connected to the electric motor also serves as the permanent magnet provided on the rotor of the electric motor, a simple structure can be obtained.

[0035] Incidentally, a suction force or repulsive force generated between the first and second magnetic generator, a second magnetic generator,
Since the value is set to a value smaller than the total mass of the rotating shaft of the electric motor and the rotor, it is possible to prevent the rotating shaft from being lifted during the operation of the compressor and to prevent abnormal noise or vibration.

Since the outer diameter of the first magnetism generating means is inserted inside the coil end of the stator of the electric motor, the compressor can be made compact.

Further, according to the present invention , since the valve element is driven by utilizing the pressure difference generated between the two chambers divided by the two pressures, the valve element can be reliably driven. .

Further, according to the present invention , since the pressure introduction switching means for introducing the pressure into the pressure operation chamber is rotated, the valve body can be driven quickly.

It should be noted, the introduction of high pressure within the case in a room that is not the introduction of low pressure operation chamber, can be generated efficiently pressure difference for driving the valve body,
The drive of the valve body can be performed quickly.

[0040] Incidentally, the pressure operation chamber is provided in the valve body, the partition means because it is immovably held in the driving direction of the valve element, can move freely drive the valve body in opposite directions.

Since the pressure introducing member is used as the partitioning means, the constituent members can be simplified.

It should be noted, removed low pressure from the low pressure fluid flowing into the compression mechanism, the low pressure can be introduced into the pressure operating chamber of the valve body through the pressure introduction switching means.

Further, according to the present invention , of the three ports communicating to the outside, two ports adjacent in the driving direction of the valve element are connected to each other, and the other port is connected to the case where the high-pressure gas is discharged. Can be communicated with. And
According to such a configuration, a port located at the center of the three ports can be connected to the compression mechanism, and ports on both sides can be connected to the heat exchanger, respectively, to form a heat pump refrigeration cycle.

Since the flow paths of the ports are switched by the rotation of the valve body, the three ports can be provided on the circumference.

Since the flow paths of the ports are switched by the reciprocating motion of the valve body, three ports can be provided on a straight line.

In addition , it is possible to improve the conformability of the valve body with the valve base with which the valve body slides, suppress the amount of leakage from the valve body, and reduce the loss.

Further, according to the present invention , the valve body can be driven by reversing the electric motor driven forward when performing the normal compression operation. Therefore, after the compressor is once stopped, Switching of the switching valve using the driving force of the electric motor can be easily performed.

It is to be noted that the present invention is a heat pump type refrigeration cycle including the above-mentioned switching valve built-in type fluid compressor.

[0049] Since the case is switching valve if you are filled with high-pressure fluid is disposed within the high pressure, reducing the amount of leakage from the valve body, it is possible to reduce the loss. When the case is filled with the low-pressure fluid, the accumulator can be omitted.

[0050]

An embodiment of the present invention will be described below with reference to the drawings.

First, the first embodiment is shown in FIGS.
This will be described with reference to FIG.

As shown in FIG. 1, the fluid compressor has a case 1. The case 1 is a pressure vessel which is opened upward, and the upper end opening of the case 1 is closed by a lid shown in FIG.

In the case 1, a rotary compression mechanism 2 for compressing the low-pressure refrigerant sucked from outside the case 1 and discharging the compressed high-pressure refrigerant into the case 1 is provided in a middle part of the case 1. An electric motor 7 for driving the compression mechanism 2 and the lid 1a (upper part of the case 1) are attached to the lid 1a. By rotating a valve element 24 shown in FIG. A rotary four-way switching valve 3 for switching a suction flow path to the mechanism 2 is provided.

First, the compression mechanism 2 and the electric motor 7 will be described.

The compression mechanism 2 compresses the refrigerant by eccentrically rotating a roller-shaped piston 9 in two cylinders indicated by 8 in the figure. The piston 9 is rotatable about a vertical axis. Drive shaft 10 provided in
Is held by

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

Therefore, when the electric motor 7 is operated, the shaft 10 is driven to rotate, and the piston 9 is eccentrically rotated in the cylinder 8. Thus, the compression mechanism 2 compresses the refrigerant sucked from the two suction pipes indicated by 11 in FIG. 2 in each of the cylinders 8 and discharges the refrigerant into the case 1.

Power is supplied to the electric motor 7 through a sealed terminal 12 fixed to the lid 1a. The external electrode of the sealing terminal 12 is connected to a control unit indicated by 13 in FIG.
Is controlled by the

Next, the four-way switching valve 3 will be described.

As shown in FIG. 2, the four-way switching valve 3 has three ports 15 to 17 provided at 55 ° intervals in the circumferential direction.
Is formed. The three ports 15 to 17 are respectively connected to the outdoor heat exchanger 22, the compression mechanism 2 provided in the case 1, and the indoor heat exchanger 23 by pipes indicated by 19 to 21 in FIG.
To form an air conditioner (refrigeration cycle). In addition, what is shown by 24 in FIGS. 1 and 2 is an accumulator (gas-liquid separator).

That is, the four-way switching valve 3 is
The air conditioner performs a cooling operation by switching a flow path (shown by a dotted line in the figure) of a discharge gas (high-pressure high-temperature gas) filled therein to the outdoor heat exchanger 23 (pipe 17) side,
A heating operation is performed by switching to the indoor heat exchanger 22 (pipe 15) side.

Hereinafter, the structure and control of the four-way switching valve 3 will be described in more detail with reference to FIGS.

FIG. 3 is a front view (side view) showing the four-way switching valve 3 in an enlarged manner.

The switching valve 3 is roughly divided into the valve base 14 fixed to the lid 1a of the case 1 and the lower surface of the valve base 14 so as to be rotatable. A valve element 24 for switching a flow path;
And a pressure introduction shaft 25 which is inserted into the lower surface side of the valve base 14 and penetrates the valve body 24 to introduce pressure for driving the valve body 24 to the valve body 24 side.
And a shaft drive mechanism 26 for driving the pressure introduction shaft 25 by magnetically connecting the pressure introduction shaft 25 to the drive shaft 10 of the electric motor 7.

A collar 28 for covering the outer surface of the valve element 24 is attached to the lower surface of the valve base 14, and a lower plate 29 for supporting the lower surface of the valve element 24 is fixed to the collar 28. ing.

The drive mechanism 26 is connected to the lower plate 2.
9 and the pressure introducing shaft 25.

Hereinafter, each component constituting the switching valve 3 will be described in detail with reference to an assembly diagram shown in FIG.

First, the valve base 14 will be described with reference to FIG.

As shown in FIG. 5, the valve base 14 has a circular shape in a plan view, and has a flange 14a formed at a lower end with a diameter larger than that at an upper end. As a specific material of the valve base 14, since it is welded to the lid 1a of the case 1, carbon steel, stainless steel, and other non-ferrous metals are employed.

The valve base 14 has the above-mentioned 3
Two ports 15 to 17 are provided to penetrate from the upper surface to the lower surface of the valve base 14. These three ports 15
17 are provided around the central axis L of the valve base 14 at circumferential intervals of, for example, about 55 °.

As shown in FIGS. 1 and 2, the port 16 located at the center of the three ports 15 to 17 is connected to the suction pipe 21 (11) connected to the compression mechanism 2 as shown in FIG. The other two ports 15 and 17 sandwiching the low-pressure gas port 16 are the indoor heat exchanger 22 and the outdoor heat exchanger 2 respectively.
3 are the first and second connection ports.

Further, in the valve base 14, FIG.
(B) is provided with a first pressure introduction hole (low pressure introduction hole) indicated by 31. The first pressure introduction hole 31 is diametrically formed from the outer peripheral surface at a position shifted by 180 ° from the position where the low-pressure gas port 16 is provided. Is in communication with

Further, at the center of the lower surface of the valve base 14, a holding hole 33 into which a pin shaft (indicated by 32 in FIG. 4) serving as a rotation center axis of the valve body 24 is inserted is opened. A low-pressure gas hole 34 through which the low-pressure gas is introduced from the low-pressure gas port 16 through the first pressure introducing hole 31 is opened on the lower surface at a position shifted by 180 ° from the gas port. The first pressure introduction hole 31
The other end is closed with a stopper shown in FIG. 35 so that the low-pressure gas does not leak from the low-pressure gas hole 34.

As shown in FIG. 4, the pressure introducing shaft 25 is inserted into the low-pressure gas hole 34 from the lower surface side of the valve base 14. As shown in FIG. 5, a fine hole 36 for introducing a high-pressure gas for urging the pressure introducing shaft 25 downward is provided at the upper end of the valve base 14. are doing.

Next, the pressure introduction shaft 25 will be described with reference to FIGS.

As shown in FIG. 3, the pressure introducing shaft 25 has a second pressure introducing hole 38 (low pressure introducing hole) communicating with the first pressure introducing hole 31 provided in the valve base 14. Have. As shown in FIG. 6, the second pressure introducing hole 38 has a first lateral hole 38a which penetrates the pressure introducing shaft 25 in the diametrical direction, and a first lateral hole 38a intersecting with the first lateral hole 38a. 25 to the valve element 24
And a vertical hole 38b provided at a depth up to
8b comprises a second lateral hole 38c provided at the lower end. Unlike the first horizontal hole 38a, the second horizontal hole 38c does not penetrate the shaft 25, but extends in the radial direction from the center and opens to the outer peripheral surface of the shaft 25. The opening height of the second lateral hole 38c is immediately below the lower surface of the valve base 14, as shown in FIG.

Next, the valve element 24 will be described with reference to FIG.

The valve element 24 has a disk shape and is rotatably attached to the lower surface of the valve base 14 via the center pin 32 as shown in FIG. As shown in FIG. 3, a notch groove 32a is provided on the outer peripheral surface of the upper part of the center pin 32 over the entire length in the circumferential direction.
Thereby, the first pressure introducing hole 31 is configured to communicate left and right.

On the other hand, the upper surface of the valve
The communication passage indicated by 0 is open. This communication passage 40
Has a substantially semicircular cross-sectional shape as shown in FIG. 7B, and has three ports 15 to 17 provided in the valve base 14 as shown in FIG. (Shown), two adjacent ports are provided over a range corresponding to an interval (55 ° in the circumferential direction) between the two adjacent ports so that the two ports can communicate with each other.

The valve 24 is provided with the communication passage 4.
The first and second through holes 4 are respectively provided on both sides sandwiching
1, 42 are provided. As shown in FIG. 9A or FIG. 9C, the through holes 41 and 42 are in a state where two of the three ports 15 to 17 communicate with each other through the communication passage 40. Each of them communicates with one other port 15 or 17.
Further, as shown in FIG.
Is bent in an L-shape in the middle part and is opened on the outer peripheral surface of the valve body 24.

FIG. 8 shows the collar 28 (see FIG. 3) which covers the outer surface of the valve body 24. The collar 28 has the valve body having a 55 ° angle as shown in FIG. First and second through-holes 43a and 43b are formed to release the first or second through-holes 41 and 42 into the inside of the case 1 when driven to rotate in the range.

On the other hand, as shown in FIG. 7A, the communication passage 40 and the central axis L of the valve
The pressure operation chamber 44 is formed in a point symmetrical shape with the pressure operation chamber 44 therebetween. The pressure operation chamber 44 is provided with the communication passage 4 in plan view.
Although the shape is substantially similar to 0, unlike the communication passage 40, the valve element 24 is provided so as to penetrate from the upper surface to the lower surface as shown in FIG.

Further, the pressure operation chamber 44 is provided in FIG.
As shown in (d), the pressure introduction shaft 25 is inserted through the pressure operation chamber 44, and the pressure operation chamber 44 is partitioned into two chambers 44a and 44b by the shaft 25. As described above, the shaft 25 has the second pressure introducing hole 38 for introducing the low-pressure gas from the low-pressure gas port 16.
By being driven to rotate by 0 °, the pressure introducing hole 38 communicates with one of the two rooms.

As shown in FIGS. 7A and 7B, both ends of the pressure operation chamber 44 are provided with 45 and 46 in FIG.
The first and second high-pressure preliminary chambers 47 and 48 into which the high-pressure gas in the case 1 is introduced by the first and second high-pressure holes shown by.
Is provided. These high pressure reserve chambers 47 and 48 are
As shown in (b), a crescent-shaped room is provided in the middle of the valve body 24 in the thickness direction so as to go under the inner surface of the pressure operation chamber 44.

Therefore, if a low pressure is introduced into one of the two chambers 44a and 44b by the pressure introducing shaft 25, a pressure difference is generated between the two chambers 44a and 44b. The body 24 is driven to rotate in a direction to eliminate the room into which the low pressure is introduced.
That is, in FIG. 7D, the rotary drive is performed in the direction indicated by the arrow in FIG.

The rotation of the valve body 24 is performed as shown in FIG.
As shown in (a), the shaft 25 stops when it comes into contact with one end surface of the pressure operation chamber 44 in the circumferential direction. As described above, since the pressure operation chamber 44 and the communication passage 40 are provided at point-symmetric positions, at this time, two ports 16 and 1 of the three ports 15 to 17 are used.
7 is communicated by the communication passage 40, and the other port 15 is connected to the first through hole 41 of the first and second through holes 41 and 42 provided in the valve body 24, It will communicate with the inside of the case 1 through the first through hole 43a provided in the collar 28.

The high-pressure reserve chambers 47 and 48 are provided in FIG.
As shown in the figure, the pressure introduction shaft 25 is provided at a height vertically shifted from the opening of the second pressure introduction hole 38 (shown by 38c in the drawing).
8 and the second pressure introducing hole 38 do not directly communicate with each other. When the pressure introduction shaft 25 comes into contact with one end of the pressure operation chamber 44 as shown in FIG. 9A, the second pressure introduction hole 38 is closed by the inner surface of the pressure operation chamber 44. Therefore, the high-pressure gas is prevented from flowing back through the pressure introducing hole 38, and
The state of FIG. 9A is maintained.

The material of the valve body 24 is a resin material such as PPS or porcelain (ceramics) for the purpose of improving abrasion resistance between the valve body 24 and the valve base 14.

Next, the driving means 26 for driving the pressure introducing shaft 25 will be described.

The driving means 26, as shown in FIG.
A magnetic coupling 50 for magnetically connecting the drive shaft 10 of the electric motor 7 and the shaft 25 to rotate the shaft 25, and a magnetic coupling 50 fixed to the lower end of the shaft 25 A driving plate 51 for transmitting the driving force applied to the shaft 25 to the shaft 25, and a rotation angle of the driving plate 51 provided on the lower surface of the lower plate 29 to 1
And a regulating mechanism 52 for regulating the angle within a range of 80 °.

The magnetic coupling 50 is connected to the motor-side rotor 5 fixed to the upper end of the drive shaft 10 of the motor 7.
4 and a valve-side rotor 55 rotatably provided at the lower end of the shaft 25.
55 are arranged facing each other in a non-contact state with a predetermined gap.

The two rotors 54, 55 have substantially the same structure, and are fixed to the holding members 56, 57 attached to the drive shaft 10 or the shaft 25, and to the holding members 55, 57. Yoke 58, 59 and permanent magnets 60, 61 sandwiched between the holding members 55, 57 and the yokes 58, 59.

FIG. 10 shows the valve-side rotor 55. As shown in FIG. 10C, the permanent magnet 61
Are arranged in a ring shape, and have different polarities alternately magnetized at a pitch of 45 °. The motor-side rotor 54 has the same configuration, but is not shown.

The driving force transmission performance of the magnetic coupling 50 depends on the magnetic force of the permanent magnets 60 and 61,
The pitch is determined by the pitch of 0 and 61 (45 ° in this embodiment), the interval between the rotors 54 and 55, and the like. Further, in the present invention, the magnetic coupling 50 only needs to have a driving force transmitting force sufficient to rotationally drive the pressure introducing shaft 25, and does not directly rotate the valve body 4. Therefore, it is not necessary to have such a large transmission performance.

Here, as shown in FIG. 4, the valve-side rotor 55 is configured such that the upper end of the holding member 59 is rotatably externally inserted into the lower end of the shaft 25, and rings 63 and 64 shown in FIG. Thus, the shaft 25 is held so as not to fall off. The valve-side rotor 55 is rotatably attached to the shaft 25.

The driving force transmitted to the valve rotor 55 is applied to the drive plate 5 fixed to the shaft 25.
1 is transmitted to the shaft 25 by driving via an engagement protrusion indicated by 65 in FIG.

Next, the driving plate 51 will be described with reference to FIG.

The drive plate 51 includes a base plate 67 and engagement pins 68 projecting downward from the lower surface of the base plate 67. The base plate 67 has a shape such that two semicircular plates are coupled with their central axes shifted, and the first and second steps 6 are located at positions shifted by 180 ° in the circumferential direction.
9, 70 are provided.

At the center of the base plate 67, an external insertion hole 71 to be inserted into the shaft 25 is formed. The outer insertion hole 71 is partially provided with a straight portion 71a,
When the drive plate 51 is extrapolated to the shaft 25, the drive plate 51 is engaged with a notch 72 of the shaft 25 shown in FIG. Thus, the drive plate 51 and the shaft 25 are connected to each other so as not to rotate relatively.

On the other hand, the engagement pin 68 is provided so as to be circumferentially engageable with an engagement protrusion 65 provided on the valve-side rotor 55.
8, the driving force of the electric motor 7 transmitted by the magnetic coupling 50 is transmitted to the shaft 25.

Next, the regulating mechanism 52 for regulating the rotation of the shaft 25 will be described.

This regulating mechanism 52, as shown in FIG.
A cover 73 attached to the lower surface of the lower plate 29, and a spring 74 disposed between the cover 73 and the lower plate 29;
Consists of

The spring 74 has a U-shape as shown in FIG. 12 (a), and has both ends 74a, 74b.
Is bent downward in an L-shape as shown in FIG. On the other hand, the cover 73 is as shown in FIG. 13, and a projection 75 for catching the U-shaped bent portion of the spring 74 and both ends 74 a and 74 b of the spring 74 are located below the cover 73 (the Extending holes 76a and 76b for extending to the driving plate 51 side) are provided. Reference numeral 77 in the drawing denotes an insertion hole through which the shaft 25 is inserted.

As shown in FIG. 4, the cover 73 holds the lower plate 2 with the spring 74 housed therein.
9. Note that this cover 7
At the time of attaching 3, a ring indicated by 79 in FIG. 4 is attached in the middle of the shaft 25, and the ring 79 is brought into contact with the upper surface of the cover 73 to prevent the shaft from falling out.

Further, both ends 74a and 74b of the spring extending below the cover 73 are shown in FIG.
As shown in (a), the outer peripheral surface of the driving plate 51 comes into contact with the driving plate 51. The two ends 74 a and 74 b of the spring 74 are pressed against the outer peripheral surface of the drive plate 51 by the restoring force of the spring 74,
Further, by engaging with the first and second step portions 69 and 70, a function as a rotation stop (rotation restriction) of the drive plate 51 is achieved.

Next, the operation of the shaft driving mechanism 26 will be described with reference to FIG. 14 together with FIG. Note that FIG.
Is a view of only the drive mechanism 26 taken out and viewed from above, and the reference numeral 57 in the figure denotes the upper end of the holding member 57 of the valve-side rotor 55.

Hereinafter, the operation of switching the operation of the air conditioner from the heating operation to the defrosting operation, and then to the heating operation again will be described as an example.

An arrow shown in FIG. 14A indicates a drive shaft 10 of the electric motor 7 when the air conditioner performs a normal cooling operation.
The rotation direction (forward rotation) (not shown in this figure) is shown.

The driving force of the drive shaft 10 is transmitted to the holding member 57 of the valve-side rotor 55 via the magnetic coupling 50. The transmitted driving force is applied to the engaging projection 65 provided on the holding member 57 and the driving plate 5.
1 through the protruding pins 68 formed on the driving plate 51.
The drive plate 51 divides the first and second steps 69, 70 into both ends 74 of the spring 74.
a, 74b, and rotation in this direction is regulated. Therefore, in this state, the pressure introduction shaft 2
5 does not rotate.

Therefore, during normal operation, the flow path is not switched by the switching valve 3, and the valve body 24
The compression operation is continued while being held at the position shown in FIG. In this position, the valve 24
The communication passage 40 communicates the low-pressure gas port 16 provided in the valve base 14 with the second connection port 17 (shown by a dotted line in the figure). Further, the first connection port 15 of the valve base 14 is connected to the first through hole 4 of the valve body 24.
1 and the first through hole 43a of the collar 28 to open into the case 1.

Therefore, the high-pressure gas discharged from the compression mechanism 2 into the case 1 is introduced into the switching valve 3 through the first through hole 43a and the first through hole 41, and is connected to the first connection port. Piping 19 (FIGS. 1 and 2)
). As shown in FIG. 2, the high-pressure gas passes through the indoor heat exchanger 22, the pressure reducing device, and the outdoor heat exchanger 23 while sequentially changing the state, thereby heating the room.

The low-pressure gas, which has passed through the outdoor heat exchanger 23 and has been reduced in pressure, flows from the pipe 21 into the second connection port 17, passes through the communication passage 44 of the valve body 24, and The liquid is guided to the low-pressure gas port 16, passes through the suction pipe 20 and the accumulator 24 from the low-pressure gas port 16, and is introduced (returned) to the compression mechanism 2 in the case 1.

The low-pressure gas introduced into the compression mechanism 2 is compressed again by the compression mechanism 2 to become a high-pressure gas and is discharged into the case 1. Then, it is again introduced into the indoor heat exchanger 22 through the first connection port 15 of the valve base 14, and circulates in the piping of the refrigeration cycle. As a result, a heating operation is performed.

During this operation, the pressure inside the communication passage 40 of the valve body 24 becomes lower than that inside the case 1. Because of this pressure difference, the valve element 24 is pressed against the valve base 14, so that gas does not leak from between the valve base 14 and the valve element 24.

On the other hand, when the above-described heating operation is performed, frost may be formed on the outdoor heat exchanger 23. If the operation is continued in a state where frost is formed, the performance of the air conditioner may be reduced. Therefore, in such a case, the following defrosting operation is performed.

That is, when the control section 13 detects the necessity of defrosting, it temporarily stops the electric motor 7. Then, while detecting the rotation angle of the electric motor 7, the control unit 13 rotates the drive shaft 10 in a direction opposite to that in the normal operation, as indicated by an arrow in FIG.

As a result, the rotation of the valve-side rotor 55 (holding member 57) is released.
5 rotates about 360 ° in the direction of the arrow, and FIG.
As shown in FIG. 14B, the engaging projection 65 is engaged with the engaging pin 68 of the driving plate 51 from the opposite direction to that of FIG.
Contact.

Thus, the driving force applied to the valve rotor 55 is transmitted to the driving plate 51. At this time, the driving body 51 is operated during the normal operation (FIG. 14).
Unlike (a), since the rotation direction is not regulated by the spring 74, the spring 74 is rotated in this direction while being spread as shown in FIG. When the drive plate 51 is rotated by about 180 °, both ends 74a and 74b of the spring 74 are connected to the drive plate 51 as shown in FIG.
In the steps 69 and 70. The control unit 13
During this period, the rotation angle of the electric motor 7 is detected, and the electric motor 7 is stopped at the angle shown in FIG.

With the above operation, the pressure introducing shaft 25 is driven to rotate by 180 ° together with the driving plate 51. Thereby, as shown in FIG. 9B, the second pressure introduction hole 38 provided in the pressure introduction shaft 25 is opened in one room 44a of the pressure operation chamber 44, and this room 44a The low pressure gas port 16 provided on the valve base 14 communicates with the low pressure gas port 16. Therefore, a low pressure is introduced into the chamber 44a of the pressure operation chamber.

On the other hand, the second high-pressure preliminary chamber 48 is provided on the back side of the pressure introducing shaft 25 and is maintained at a high pressure similarly to the case 1. A pressure difference is generated in the chamber 44.

As a result, as described above, the valve element 2
Reference numeral 4 rotates toward the low-pressure room 44a, and switches the flow path as shown in FIG. 9C.

The switching of the flow path by the switching valve 3 is not performed immediately after the motor 7 (compression mechanism 2) is stopped, but is performed in the process of balancing the pressure in the piping of the refrigeration cycle. . That is, the electric motor 7
During normal operation, the valve element 24 is pressed against the valve base 14 by the differential pressure as described above, and a relatively large frictional force is generated during this time. , The valve element 24 does not rotate.

The pressure in each pipe is balanced, the pressing force of the valve element 24 is reduced, and the driving force of the valve element 24 due to the differential pressure in the pressure operating chamber 44 is reduced by the valve element 24 and the valve. The switching is performed when the frictional force with the base 14 becomes larger.

When the switching has been performed and the pressure balance in the piping has been almost completely achieved, the control unit 13 controls the electric motor 7 during the normal operation indicated by the arrow in FIG. And the compression mechanism 2 is operated.

As a result, as shown in FIG. 14E, the valve-side rotor 55 rotates about 360 ° in the direction of the arrow from the state shown in FIG.
5 is brought into contact with the projection pin 68 of the driving plate 51. However, the driving plate 51 does not rotate because the rotation in this direction is regulated by the spring 74. Accordingly, since the pressure introduction shaft 25 does not rotate, the operation of the compression mechanism 2 is performed with the valve body 24 maintained at the position shown in FIG. 9C.

In this position, the valve 24
The communication passage 40 communicates the low-pressure gas port 16 provided in the valve base 14 with the first connection port 15 (shown by a dotted line in the figure). The second connection port 17 of the valve base 14 is connected to the second through hole 4 of the valve body 24.
2 and the second through-hole 43b of the collar 28 and open into the case 1.

Accordingly, the high-pressure gas discharged from the compression mechanism 2 into the case 1 is introduced into the switching valve 3 through the second through-hole 43b and the second through-hole 42, and the second connection is performed. From the use port 17 to the pipe 21.
This high-pressure gas is supplied to the outdoor heat exchanger 2 as shown in FIG.
3. It passes through the pressure reducing device and the indoor heat exchanger 22 while sequentially changing the state.

The low-pressure gas, which has passed through the indoor heat exchanger 22 and has been reduced in pressure, flows from the pipe 19 into the first connection port 15 and passes through the communication passage 44 of the valve body 24.
Then, the gas is guided to the low-pressure gas port 16, passes through the suction pipe 20 and the accumulator 24, and is introduced (returned) to the compression mechanism 2 in the case 1.

The low-pressure gas introduced into the compression mechanism 2 is compressed again by the compression mechanism 2 to become a high-pressure gas and is discharged into the case 1. Next, the indoor heat exchanger 2 is again connected to the second connection port 15 of the valve base 14.
2 and circulates in the piping of this refrigeration cycle.
As a result, the same operation as in the cooling operation is performed, and the high-pressure high-temperature gas is introduced into the outdoor heat exchanger 23.
Defrosting is performed.

This defrosting operation is performed for a certain period of time. If the outdoor heat exchanger is defrosted, the electric motor 7 is stopped again, and the same control as in FIGS. 14 (a) to (e) is performed. The motor 7 is reversed. As a result, the pressure introduction shaft 25 rotates 180 ° from the state shown in FIG. 9C, and the second pressure introduction hole 38 is moved into the pressure operation chamber 44.
9, the pressure difference is generated in the pressure operation chamber 44 again with the pressure introduction shaft 25 interposed therebetween, and the valve body 24 is rotationally driven in a direction opposite to that of FIG. 9 (a).

Next, the heating operation is restarted by operating the electric motor 7 in the normal rotation direction.

Next, another mode of operation will be briefly described.

First, the case where the heating operation is stopped and then the heating operation is performed again will be described.

As described above, the heating operation is performed as shown in FIG.
In the heating position shown in FIG.
This is performed by operating in the direction indicated by the arrow in FIG.
The stop of the heating operation is performed by stopping the electric motor 7.

When restarting the heating operation, the motor 7 is operated again in the direction indicated by the arrow in FIG. 14A (normal operation direction) without reversing the motor 7. If the motor 7 is not to be reversed, the valve 24
Is not rotationally driven, the switching position is
The heating position shown in FIG. Therefore, the heating operation is performed again.

Next, a case where the cooling operation is performed after the heating operation is stopped will be described.

In this case, first, the heating operation (motor 7) is stopped by the method described above. As a result, the pressure in the case 1 decreases, and the pressure in the case 1, the pressures in the three ports 15 to 17 of the valve base 14, and the pressures in the pipes 19 to 21 are balanced (substantially the same pressure). become).

Then, before starting the operation again, FIG.
As shown in FIGS. 9B to 9D, the electric motor 7 is rotated in the reverse direction to rotate the rotary shaft 25 by 180 °, and FIG.
The second pressure introducing hole 38 is opposed to the one chamber 44a as shown in FIG. However, in this state, since the pressure in the refrigeration cycle is balanced as described above, no differential pressure is generated in the pressure operation chamber 44 and the valve element 2
4 does not rotate.

Subsequently, the electric motor 7 is operated in the normal rotation direction shown in FIG. As a result, the compression mechanism 2 performs the compression operation, but the valve 24 remains in the heating operation position as shown in FIG. 9B, so that the refrigeration cycle starts as a heating operation.

However, if the pressure balance in each of the ports 15 to 17 is lost during the start-up of the operation, a pressure difference is gradually generated in the pressure operation chamber 44 with the pressure introduction shaft 25 interposed therebetween. . Then, at a certain point in time, the valve element 24 is driven to rotate by the differential pressure. Thus, the valve body 24 is switched to the cooling position shown in FIG.

In order to switch the valve element 24 during the operation start-up, the valve element 2 caused by the pressure difference is required.
It is necessary that there is a point in time when the driving force of No. 4 becomes larger than the frictional force between the valve body 24 and the valve base 14. For this reason, the frictional force is set to an appropriate value by adjusting the contact area between the valve element 24 and the valve base 14, or a material having a small friction coefficient is used as the material of the valve base 14 and the valve element 24. And the like. Since the friction coefficient between the materials is known, a desired material can be adopted from among them.

When the output of the electric motor 7 is rapidly increased, the valve 24 is strongly pressed against the valve base 14 before the valve 24 is driven.
Therefore, when switching from the heating operation to the cooling operation, it is necessary to operate the electric motor 7 at a low rotation for a certain period of time.

Then, when the flow path of the valve element 24 is switched in this way, the rotation speed of the electric motor 7 is increased to perform the cooling operation. Note that the flow of the refrigerant during the cooling operation is the same as that during the above-described defrosting operation, and a description thereof will not be repeated.

According to such a configuration, the following effects can be obtained.

First, there is an effect that the piping structures of the fluid compressor and the air conditioner can be simplified.

That is, at the time of the heating operation or the cooling operation, the first or second connection port 15 or 17 opened on the lower surface of the valve base 14 is directly opened into the case 1. The need for piping is eliminated. This also eliminates the need for anti-vibration measures conventionally required for high pressure gas piping.

Further, since the switching valve 3 does not use a conventional reciprocating sliding valve, a solenoid valve for operation is not required, and a connection between the conventional switching valve and the solenoid valve is accordingly required. The capillary (small-diameter copper tube) that was required for the above is no longer necessary.

Therefore, the piping of the air conditioner can be simplified. Further, since the number of pipes can be reduced, the manufacture of the fluid air conditioner including the switching valve 3 is facilitated.

Further, there is no need to consider a failure due to the deformation of the capillary tube, and there is an effect that a highly reliable fluid compressor can be obtained.

Second, there is an effect that it is possible to effectively prevent an increase in the size of the fluid compressor incorporating the switching valve.

That is, the switching valve 3 incorporated in the case 1 of the compressor is of a type that switches the flow path by rotating the valve element 24, unlike the conventional direct-acting four-way switching valve. The valve 24 is driven to rotate using the pressure in the case 1.

Therefore, since the entire switching valve 3 including the driving means can be reduced in size, it is easy to incorporate the switching valve 3 into the case 1 of the fluid compressor, and the fluid compressor is large. It does not change.

Third, the structure of the means for driving the valve element 24 is small and simple, and there is an effect that maintenance can be easily performed.

That is, in the present invention, the means for driving the valve element 24 utilizes the electric motor 7 for driving the compression mechanism 2 of the fluid compressor, and the drive shaft 10 of the electric motor 7 and the valve element 24 are connected. Shaft 2 for switching pressure for driving
5 and a magnetic coupling 50 and this coupling 5
The driving force from zero is transmitted only in one direction, and the driving plate 51 and the regulating means 52 are connected to each other.

According to such a configuration, the configuration is simpler than when a drive source such as a solenoid valve is separately provided. Further, since the pressure introduction shaft 25 is driven to rotate instead of directly driving the valve body 24, the rotation transmission force may be weak. Therefore, the magnets 60 provided in the magnetic coupling 50 may be used. It is sufficient for 61 to have a relatively weak magnetic force. Therefore, it is not necessary to employ a large magnetic coupling 50, and a load (braking force by magnetic force) applied to the electric motor 7 during normal operation.
Is also very small.

Fourth, there is an effect that the control of the fluid compressor including the switching valve 3 can be easily performed.

That is, as described above, by reversing the electric motor 7 for operating the compression mechanism 2, the valve
Since the switching of No. 4 is performed, all controls including normal operation and switching can be performed only by controlling the electric motor 7. Therefore, control becomes very easy, and the wiring structure may be the same as that of the conventional fluid compressor. Therefore, the parts other than the lid 1a can use the same parts as the conventional fluid compressor.

According to the above configuration, the switching position of the valve element 24 can be maintained during normal operation without any control. Therefore, unlike the conventional example in which the position of the sliding valve is maintained by the spring and the electromagnet, the configuration and control for that purpose are not required.

Fifth, the switching valve 3 is connected to the valve base 1.
4, carbon steel, stainless steel, non-ferrous metal is adopted, and the material of the valve body 24 is a synthetic resin material such as PPS;
Alternatively, porcelain (ceramics) is adopted.

By selecting the material in this way, it is possible to improve the wear resistance between the valve element 24 and the valve base 14. Further, since the valve element 24 and the valve base 14 can be prevented from being attracted to each other by the magnetic force from the magnetic coupling 50, there is an effect that the valve element 24 can be easily and reliably driven. .

Next, a second embodiment of the present invention will be described with reference to FIG.
5, and will be described with reference to FIG. In the following description of the embodiment, components having the same functions as those of the first embodiment are denoted by the same reference numerals as much as possible, and description thereof will be omitted.

The fluid compressor according to the second embodiment includes:
The valve body 24 of the switching valve 3 of the first embodiment is provided with a pressure backup means indicated by reference numeral 80 in FIG.

As shown in FIGS. 16 and 17, the pressure backup means 80 is provided on the lower surface of the valve body 24 and faces the lower plate 29. 40 and a through hole 82 for communicating with 40.

According to such a configuration, the valve element 24
Is backed up by the low pressure introduced into the recess 81 from the communication passage 40, so that the pressing force of the valve body 24 against the valve base 14 can be reduced. Therefore, since the frictional force between the valve element 24 and the valve base 14 can be reduced, the switching of the valve element 24 can be performed quickly.

That is, by reducing the frictional force between the valve element 24 and the valve base 14, the pressure operation chamber 4
Since the driving force due to the pressure difference in the cylinder 4 becomes larger than the frictional force at a relatively early stage, the switching can be performed earlier than in the first embodiment.

Next, a third embodiment will be described with reference to FIGS.

In the first embodiment, the valve body 24 is held with its upper surface being in close contact with the lower surface of the valve base 14. In the third embodiment, a valve 83 shown in FIG. The body is rotatably externally inserted into a valve base 84 fixed to the lid 1a of the case 1.

As shown in FIG. 18 (a), this valve base 84 has a first connection port 15, a low-pressure gas port 16 and a second connection port as in the first embodiment. 17 are provided at 55 ° intervals in the circumferential direction, and open to the outside of the case 1. And each port 15-17
Are connected to the indoor heat exchanger 22, the compression mechanism 2, and the outdoor heat exchanger 23, respectively, as in the first embodiment (not shown).

Further, these ports 15 to 17 are
As shown in FIG. 7, the valve base 84 is bent into an L-shape in the case 1 and opens on the outer peripheral surface of the valve base 84 as shown in FIG. 18 and FIG. FIG. 17 shows only the low-pressure gas port 16.

At the center of the valve base 84, there is formed a low-pressure gas hole 87 which is connected to the low-pressure gas port 16 by a first fine hole (low-pressure introduction hole) shown at 86 in the figure. . A pressure introducing shaft 88 is inserted into the low-pressure gas hole 87.

The pressure introducing shaft 88 is provided with
The notch passage (low-pressure introduction hole) provided over the half circumference as shown at 88a in FIG.
Having. The direction of the notch passage 88a can be switched as shown in FIGS. 18A and 18B by rotating the pressure introducing shaft 88 by 180 °.

The pressure introducing shaft 88 and the notch passage 88a allow the first fine hole 86 to be inserted into the first through hole 86a as shown in FIG.
It has a function of selectively communicating with the second or third pores (low pressure introduction holes) indicated by 0 and 91.

On the other hand, as shown in this figure, two adjacent ports among the ports 15 to 16 opening on the outer peripheral surface of the valve base 84 are selectively connected to the valve element 83 as shown in FIG. There are provided a communication passage 93 to be opened, and first and second communication holes 94 and 95 for opening another port to the outside of the valve body 83 (inside the case 1).

The valve 83 is connected to the communication passage 93.
A pressure operation chamber indicated by reference numeral 96 in FIG. This pressure operation chamber 96
As in the first embodiment, the valve base 83 is provided with a length corresponding to the required rotation angle of the valve body 83, and
The two rooms 96a and 96b are partitioned by a partition plate 97 (partitioning means) protruding from 4.

The partition plate 97 is inserted into an insertion hole 98 provided in the valve element 83.
It is urged in a direction pressed against the valve body 83 by a spring 99 disposed therein.

As in the first embodiment, the high-pressure spare chamber 100,
101 is provided. Each pressure preparatory chamber 100, 101
Communicates with the outer peripheral surface of the valve element 83,
6, a high pressure pore 102 for introducing a high pressure in the case 1;
103 (high-pressure introduction hole) is provided.

Then, as shown in FIG. 18B, when the pressure introducing shaft 25 is driven to rotate by 180 °, the low pressure in the low-pressure gas port 16 is reduced by the pressure from the first fine holes 86. When the pressure operation chamber 96 is introduced into one of the chambers 96a of the pressure operation chamber 96 through the cutout groove 88a of the introduction shaft 88 and the second fine hole 90, the pressure in the pressure operation chamber 96 is sandwiched by the partition plate 97. A difference will result. As a result, the valve element 83 is connected to the low-pressure side chamber 9.
It turns in the direction in which 6a is lost, that is, in the direction indicated by the arrow in the figure.

Then, as shown in FIG. 18C, when the partition plate 97 comes into contact with the end face of the pressure operation chamber 96, the rotation of the valve element 83 is stopped. At this time, as shown in this figure, the second fine holes 9 communicating with the low pressure side are formed.
Since 0 is opposed to the inner surface of the valve element 83 and is closed, this low pressure does not leak into the case 1.

The driving means 26 (50 to 52) for driving the pressure introducing shaft 88 and the control method of the electric motor 7 at the time of this switching are the same as those in the first embodiment, and therefore will be described. Is omitted.

With such a configuration, the motor 7
, The valve element 83 can be rotationally driven by the pressure difference, and the flow path can be switched.
The same effect as that of the embodiment can be obtained.

Next, a fourth embodiment will be described with reference to FIGS.

The fourth embodiment has a configuration similar to that of the switching valve 3 of the first embodiment, and includes a valve body 111 on the lower surface of a valve base 110 fixed to the lid 1a of the case 1. Are provided rotatably.

However, the valve body 111 of this embodiment is mounted with the pressure introduction shaft 112 as the center of rotation.
Further, as shown in FIG.
Of the three ports 15 to 17 formed in
A communication portion 111a provided with a communication passage 113 for communicating the two ports, and a holding portion 111b formed integrally with the communication portion 111a and held by the pressure introduction shaft 112
And a shape consisting of

The holding section 111b is provided with a pressure operation chamber indicated by reference numeral 114 in FIG.
At both ends of the high-pressure spare chamber 1 as in the first embodiment.
15 and 116 and high-pressure holes 117 and 118 (high-pressure introduction holes) for communicating these with the case 1 are provided.

In FIG. 19, reference numeral 120 denotes a lower plate for holding the lower surface of the valve body 111.
Is fixed to the valve base 110 at a predetermined interval by a spacer indicated by 121 in the figure.

In the same figure, what is indicated by 122 is a partition member (partition means) for partitioning the pressure operation chamber 114 into two chambers 114a and 114b as shown in FIGS. 20 (a) and 20 (c). The partition member 122 is provided with the valve base 1.
It is fixed to 10. That is, in the first embodiment, the pressure introduction shaft 25 also serves as a partitioning means, but is provided separately as a separate member in this embodiment.

The lower surface of the valve base 110 has a first fine hole 123 for guiding the low pressure in the low pressure gas port 16 to the pressure introduction shaft 112 as shown in FIG.
(Low pressure introduction hole) is provided.

Then, as shown in FIG. 20A, the first fine holes 123 are formed in the pressure introducing shaft 112.
A notch passage 112a (low-pressure introduction hole) communicating with the pressure operation chamber 11 is provided on the upper surface of the valve body 111 in communication with the notch groove 112a.
4, second and third pores 125, 126 introducing a low pressure
(Low pressure introduction hole) is provided. Notch groove 112a
Is selectively connected to the second and third fine holes 125 and 126 as shown in FIGS. 20A and 20B by the rotation of the pressure introducing shaft 112 by 180 °. It is supposed to.

The driving means 26 for driving the pressure introducing shaft 112 is the same as that of the first embodiment as shown in FIG. 19, and the description is omitted.

According to such a configuration, the pressure introducing shaft 112 is shifted from the state shown in FIG.
When it is rotated to the state shown in FIG.
12a, the first and second fine holes 123 and 12
5 communicates with the low-pressure gas port 16 (communication passage 1).
13) The low pressure in one chamber 1 of the pressure operation chamber 114
14a is introduced.

As a result, a pressure difference is generated in the pressure operation chamber 114 with the partition member 122 interposed therebetween. Due to this pressure difference, the valve body 111 moves in the direction of eliminating the low-pressure side chamber 114a, that is, FIG. 20 (b)
In the direction indicated by the arrow.

Then, as shown in FIG.
As shown in the figure, the partition member 122 is connected to the pressure operation chamber 1.
When it comes into contact with the other end of the valve 14, the rotation of the valve body 111 stops. At this time, as shown in the figure, the notch groove 112a of the pressure introduction shaft 112 and the second fine hole 1 are formed.
The communication state with 25 is released.

Thus, the flow path can be switched by the valve element 111.

With such a configuration, the motor 7
, The valve element 111 can be rotationally driven by the pressure difference, and the flow path can be switched, so that the same effect as in the first embodiment can be obtained.

Next, a fifth embodiment of the present invention will be described with reference to FIG.
This will be described with reference to FIG.

In the fluid compressor according to the fifth embodiment, the valve body 111 of the switching valve according to the fourth embodiment is provided with a pressure for backing up the lower surface of the valve body 111 similarly to the second embodiment. It has a backup means 130. Therefore, the same components as those in the fourth embodiment are denoted by the same reference numerals, and description thereof is omitted.

That is, a concave portion 131 is provided on the lower surface of the valve body 111, and a through hole 132 is provided for communicating the concave portion 131 with the communication passage 113.

According to such a configuration, the communication passage 1
13 is guided to the recess 131 and the lower plate 12
Since it acts on the upper surface of the valve base 110, the force with which the valve body 111 is pressed against the valve base 110 is weakened. As a result, the valve body 111 and the valve base 1 when the valve body is driven are
It is possible to reduce the frictional force between the valves 10 and to perform the switching operation of the valve body 111 earlier as in the second embodiment. Next, the fluid compressor of the sixth embodiment is This will be described with reference to FIGS.

In the fluid compressor of the sixth embodiment, a seal ring 133 for hermetically sealing the recess 131 of the pressure backup means 130 is inserted into the lower surface of the valve body 111 of the fifth embodiment. It is.

According to such a configuration, the valve body 111
It is possible to reliably prevent the low pressure introduced into the lower surface of the fluid compressor from leaking into the case 1, and to effectively prevent a decrease in the efficiency of the fluid compressor.

Next, the seventh embodiment will be described with reference to FIGS.
This will be described with reference to FIG.

The fluid compressor according to the seventh embodiment is similar to the fluid compressor of FIG.
9 has a configuration similar to that of the fluid compressor of the fourth embodiment shown in FIG. 9, and in the fourth embodiment, the communication passage 121 and the pressure operation chamber 114 provided in the valve body 111 Although it is arranged with the introduction shaft 112 interposed therebetween, in the valve body 111 ′ of this embodiment, as shown in FIG. 25, the pressure operation chamber 114 ′ is the same as the communication passage 121 with respect to the pressure introduction shaft 112 ′. Side and below the communication passage 121.

FIGS. 26 (a1) to 26 (a2) are cross-sectional views along the line VII-VII in FIG. 25. FIGS. 26 (b1) to 26 (b1) are VIII-II in FIG.
It is a cross-sectional view which follows the VIII line. (A1) and (b1), (a2) and (b2), (a3) and (b3)
Indicate the same operating state.

As shown in FIG. 26 (b1), the valve 1
11 'is formed with a first fine hole 135 (low pressure introduction hole) for communicating the communication passage 121 with the pressure introduction shaft 112', and the pressure introduction shaft 112 '
As shown in FIG. 25, a pressure introducing hole 136 (low pressure introducing hole) is provided along the central axis of the shaft 114 '.
As shown in FIG. 26 (b1), the pressure introduction shaft 1
14 ', the pressure introduction hole 136 is connected to the first pore 1
A notch 137 for communicating with 35 is provided.

The notches 137 are provided at positions 180 ° apart from each other, and even when the pressure introducing shaft 114 ′ is driven to rotate by 180 °, the first fine holes 135 are inserted into the pressure introducing holes 136. It is designed to communicate with

On the other hand, the lower part of the valve
6 (a1), the pressure introduction shaft 112
And the third and the third for communicating the pressure operation chamber 114 'with the pressure operation chamber 114'.
Are provided (low-pressure introduction holes). The pressure introduction shaft 112 ′ is provided with a notch groove indicated by 141 in the figure over a half circumference, and this notch groove 141 is connected to the pressure introduction hole 136.

The notch groove 141 is selectively communicated with the second or third fine holes 139 and 140 by rotating the pressure introducing shaft 112 'by 180 °. As a result, the pressure operation chamber 11 is moved through one of the fine holes 139 and 140.
A low pressure is introduced into 4 '.

The high pressure auxiliary chambers 144 and 145 and the high pressure auxiliary chamber
4, 145 high-pressure introduction holes 146, 1
47 are formed.

[0209] The pressure operation chamber 114 'is shown in FIG.
The two rooms 114a, 11
4b. Then, this partition member 142
26, the second pore 139 is closed in the state of FIG. 26 (a1), and the third pore 140 is closed in the state of FIG. 26 (a3).
Is configured to be closed.

The driving means of the pressure introducing shaft 112 'is the same as that of the first embodiment, and the description is omitted.

Next, the switching operation of the switching valve of this embodiment will be described.

Now, in FIGS. 26 (a1) and (b1), the valve body 111 'is held at the heating position. In this state, the low-pressure gas port 16 communicates with the second fine hole 139 through the first fine hole 135 and the pressure introducing shaft 112 ′, as described above. The fine holes 139 are provided in the partition member 142.
Is closed by the pressure operation chamber 114 ′.
No low pressure is introduced into one of the chambers 114a. Therefore, this compressor is continuously operated while maintaining the heating position shown in (b1).

Then, after stopping the motor 7, the motor 7 is rotated in the reverse direction, and the pressure introducing shaft 112 'is rotated by 180 °, as shown in FIGS. 26 (a2) and (b2).
The low pressure gas port 16 communicates with the third pore 140 through the first pore 135 and the pressure introduction hole 136 of the pressure introduction shaft 112 '. Therefore, the low pressure in the low pressure gas port 16 is reduced by the pressure operating chamber 114.
'Is introduced into one of the rooms 114a.

As a result, a pressure difference is generated in the pressure operation chamber 114 with the partition member 142 interposed therebetween, so that the low pressure side chamber 114a is eliminated, that is, FIG. The valve body 111 'rotates in the direction indicated by the arrow in a2).

Then, the valve element 111 ′ is arranged as shown in FIG.
As shown in 3), the partition member 142 rotates until it comes into contact with the other end of the pressure operation chamber 114 ′. In this state, the third pore 140 is closed by the partition member 142, The introduction of the low pressure into the pressure operation chamber 114 is stopped.

When the valve body 111 'is rotationally driven in this manner, the first connection port 15 and the low-pressure gas port 16 are connected to the valve body 1 as shown in FIG. 26 (b3).
The fluid compressor is switched to the cooling or defrosting position because it is connected by the communication passage 121 of 11 ′ and the second connection port 17 is opened into the case 1.

With such a configuration, substantially the same effects as in the first embodiment can be obtained.

Next, an eighth embodiment of the present invention will be described with reference to FIGS.

The switching valve 143 of the eighth embodiment is a direct acting type unlike the switching valve 3 of the first to seventh embodiments.

That is, in the first to seventh embodiments, the first to third ports 15 to 17 are disposed on the circumference of the valve base 14 to drive the valve body 24 to rotate. The ports 15 to 17 were switched. On the other hand, in the eighth embodiment, as shown in FIG. 27, the three ports 15 to 17 provided on the valve base 144 are arranged in parallel on a straight line, and the valve body 145 shown in FIG. By reciprocatingly driving, two adjacent ports among the three ports 15 to 17 are communicated with each other by a communication passage 146 provided in the valve body 145.

In the first to seventh embodiments, the pressure operation chamber 44 is provided in the valve body 24, and a partition member (the pressure introduction shaft 2) for partitioning the pressure operation chamber 24 is provided.
5) was attached to the valve base 14. On the other hand, in this embodiment, the two chambers constituting the pressure operation chamber are formed in the holder 150 fixed to the valve base 144 as shown by 148 and 149 in FIG. The reference numeral 151 denotes a partition member of this embodiment, which is attached to the lower surface of the valve body 145 and has both ends 151.
a and 151b are inserted into the two rooms 148 and 149 to partition these rooms.

The pressure backup member 152 is provided on the lower surface of the partition member 151. The pressure backup member 152 is slidably held on the upper surface of a lower plate 153 fixed to the lower end of the holder 150. The pressure backup member 152 is provided with a concave portion 154 facing the upper surface of the lower plate 153, and the concave portion 154 is connected to the communication groove 146 of the valve body 145 via a connection pipe 155 shown in FIG. Communicating. Therefore, the low pressure in the communication groove 146 is introduced into the concave portion 154. Also,
The connection pipe 155 includes the valve body 145, the partition member 151,
Also, it has a function of connecting the pressure backup member 152 and fixing it integrally.

The lower plate 153 holds a pressure introducing shaft 157 rotatably about a vertical axis. The pressure introduction shaft 157 has a function of selectively introducing the low pressure introduced into the concave portion 154 of the pressure backup portion 152 into each of the chambers 148 and 149 constituting the pressure introduction chamber. The end surface is exposed on the upper surface of the lower plate 153, and is always located in the concave portion 154 even when the pressure backup member 152 is driven left and right.

This pressure introducing shaft 157 has
A pressure introduction hole (low pressure introduction hole) indicated by 58 is formed. One end of the pressure introducing hole 158 is opened at the upper end surface of the pressure introducing shaft 157, and the other end is opened at the outer peripheral surface of the pressure introducing shaft 157.

The lower plate 153 and the holder 150
In the first, the pressure introduction shaft 157 is rotated by 180 ° so that the first and second pressure communication holes communicate with the pressure introduction hole 158.
The second fine holes 159 and 160 (low pressure introducing holes) are provided. The first and second pores 159 and 160 are provided from the lower plate 153 to the holder 150, and the one and other chambers 1 provided in the holder 150 are provided.
48 and 149 are formed. In addition,
The two chambers 148 and 149 are provided with high-pressure holes 161 and 162 for introducing high pressure in the case 1 into the chambers, as in the first to seventh embodiments.

The means 26 for rotationally driving the pressure introducing shaft 157 is provided on the lower surface of the lower plate 153, and has the same configuration as that of the first embodiment. That is, when the electric motor 7 is rotating forward,
The rotation restricting means 52 restricts the rotation of the pressure introduction shaft 157, and the electric motor 7 is rotated in the reverse direction, so that the driving force of the electric motor 7 is reduced by the magnetic coupling 50 and the driving plate 5.
1, the pressure is transmitted to the pressure introduction shaft 157, and the pressure introduction shaft 157 is rotated by 180 degrees.

Next, the switching operation of the switching valve in the fluid compressor will be described.

Now, in the state shown in FIG. 27, the low pressure gas port 16 and the second connection port 17 are
The first connection port 15 communicates with the inside of the case 1 through the 45 communication passages 146. Therefore, this state is the same as that in FIG. 9A, and the air conditioner performs the heating operation by rotating the electric motor 7 in the forward direction and operating the compression mechanism 2.

As described above, when the electric motor 7 is rotating forward, the rotation of the pressure introducing shaft 157 is restricted. And this pressure introduction shaft 1
Since the pressure introducing hole 158 communicates with the other chamber 149 through the second pore 160, the communication passage 146 is formed by performing the compression operation.
Is acting on the other chamber 149. On the other hand, since the high pressure in the case 1 is introduced into the one chamber 148 by the high-pressure introduction hole 161, the pressure difference between the two chambers 148 and 149 causes the partition member 151 to move in the direction of the arrow. And the operation in this switching position is continued.

Next, if it becomes necessary to defrost the outdoor heat exchanger during the heating operation, the electric motor 7 is stopped, and then, as shown in FIGS. 14 (b) to 14 (d). As described above, the electric motor 7 is rotated in the reverse direction while detecting its rotation angle.
As a result, the pressure introduction shaft 157 is rotated about 180 degrees, and the pressure introduction hole 158 is connected to the second chamber 148, as shown in FIG.
Communicating with the fine pores 159.

As a result, the pressure of the one room 148 becomes lower than that of the other room 149, contrary to the case of the heating operation.
1 is urged toward the one room 148 side. As a result, the valve element 145 is switched as shown in FIG. 28 (b), the low pressure gas port 16 communicates with the first connection port 15, and the second connection port 17 is connected to the case 1 Communicate within.

Next, when the compression operation is performed by rotating the electric motor 7 in the forward direction, the high-pressure high-temperature gas in the case 1 is introduced from the second connection port 17 into the outdoor heat exchanger. , The outdoor heat exchanger is defrosted.

That is, according to the eighth embodiment,
As in the first to seventh embodiments, all control of the compressor including the switching valve can be performed by rotating the electric motor 7 forward and backward.

Therefore, the same effects as those of the first embodiment can be obtained.

Next, ninth and tenth embodiments of the present invention will be described with reference to FIGS. 29 and 30, respectively.

The fluid compressor of the ninth embodiment is as shown in FIG. 29 and has substantially the same configuration as the switching valve of the first embodiment. Unlike the magnetic coupling 5 according to the ninth embodiment,
0 'is different in that no motor-side rotor is provided.

That is, in this embodiment, the rotor 7b (rotating rotor) of the electric motor 7 itself functions as the electric motor-side rotor of the magnetic coupling 50 '. Therefore, in this embodiment, the electric motor 7 Rotor 7b and the valve-side rotor 5 of the magnetic coupling 50 '
5 face each other via a predetermined gap in a non-contact state.

Even with such a configuration, the electric motor 7
Can be transmitted to the switching valve side,
Almost the same effects as those of the first embodiment can be obtained. On the other hand, in a tenth embodiment shown in FIG. 30, the magnetic coupling 50 'of the fluid compressor of the eighth embodiment is configured in the same manner as the ninth embodiment. Are the same as in the ninth embodiment.

FIG. 31 shows the eleventh embodiment.

In the eleventh embodiment, the compression mechanism connected to the electric motor 7 sucks and compresses the low-pressure fluid filled in the case 1 and discharges the high-pressure fluid out of the case. The discharged high-pressure fluid enters the high-pressure gas port 16 'located at the center of the three ports of the switching valve through the discharge pipe.

The high-pressure fluid that has flowed into the high-pressure gas port 16 ′ is, for example, cooled during the cooling operation.
The communication path 146 formed in the second connection port 1
7 ′, circulates through the refrigeration cycle to a low pressure, and then returns from the first connection port 15 into the case 1.

In the eleventh embodiment, the first to the first
0 means a communication passage 1 between the inside of the case and the valve body 145.
Since the pressure relationship at 46 is reversed, the pressure relationship introduced into the pressure working chamber by the pressure introduction shaft is similarly reversed.

The present invention relates to the above-described first to first embodiments.
The present invention is not limited to only the tenth embodiment, and can be variously modified without changing the gist thereof.

For example, in the first embodiment, the valve body 24 is made of a synthetic resin such as PPS. However, the valve body 24 itself is made of a metal material. A synthetic resin may be interposed on the surface that slides, or one of the surfaces may be coated with a synthetic resin.

In the first embodiment, as shown in FIG. 10, the permanent magnets 60 and 61 provided on the rotor 55
Is fixed by holding members 55, 57 and yokes 58, 59. Alternatively, a permanent magnet is integrally formed with a yoke made of synthetic resin and a holding member, and the entire surface of the permanent magnet is made of synthetic resin. Alternatively, the configuration may be covered with a.

Further, in the first embodiment, a plurality of permanent magnets are divided at a pitch of 45 ° and arranged in a disk shape. It may be magnetized in a divided fan shape.

In the first to tenth embodiments, the switching valve is housed in the case, but the switching valve may be mounted on the outer surface of the case. In this case, if the switching valve is provided outside the lid closing the upper opening of the case and the first magnetism generating means is provided inside, the lid is attached to the upper opening of the case. At this time, the first and second magnetism generating means can face each other to form a magnetic coupling means.

Further, in the above embodiment, the compression mechanism 2 is of a rotary type in which the roller-shaped piston 9 is eccentrically rotated in the cylinder 8, but the present invention is not limited to this. For example, a scroll-type compression mechanism that forms a compression space by combining orbiting scroll blades and non-orbiting scroll blades, and compresses fluid in the compression space by orbiting the orbiting scroll with respect to the non-orbiting scroll. Is also good. In short, any type may be used as long as the inside of the case 1 is filled with the compressed high-pressure gas.

[0249]

According to the present invention, in a fluid compressor having a switching valve, an electric motor for driving a compression mechanism can be used as a switching operation source of the switching valve. It is not necessary to provide the electromagnetic valve or the like, and the fluid compressor can be made compact.

In addition, the operation of the compression mechanism and the switching of the flow path by the switching valve can be performed only by controlling the electric motor, so that the control system of the fluid compressor having the switching valve can be simplified.

[Brief description of the drawings]

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

FIG. 2 is also a top view.

FIG. 3 is a vertical sectional view showing the switching valve.

FIG. 4 is an assembly diagram showing the order of assembling the switching valve.

FIG. 5 is a plan view, a side view, and a bottom view showing the valve base of the switching valve.

FIG. 6 is a longitudinal sectional view showing a pressure introduction shaft.

FIG. 7 is a plan view and a longitudinal sectional view showing a valve body.

FIG. 8 is a plan view and a longitudinal sectional view similarly showing a partial cross section showing a collar.

FIG. 9 is a process chart showing a switching operation of the switching valve.

FIG. 10 is also a top view, a longitudinal sectional view, and a bottom view showing the valve-side rotor of the magnetic coupling.

FIGS. 11A and 11B are a plan view and a longitudinal sectional view showing a driving plate, respectively.

FIG. 12 is a plan view and a side view similarly showing a spring.

FIG. 13 is a plan view and a longitudinal sectional view showing the holding plate.

FIG. 14 is a process chart showing a driving process of a driving unit for driving the pressure introduction shaft.

FIG. 15 is an enlarged longitudinal sectional view showing a part of a switching valve of the fluid compressor of the second embodiment.

FIG. 16 is a top view showing the valve element.

FIG. 17 is an enlarged longitudinal sectional view showing a portion of a switching valve of a fluid compressor according to a third embodiment.

FIG. 18 is a process chart showing a switching operation of the switching valve.

FIG. 19 is an enlarged longitudinal sectional view showing a portion of a switching valve of a fluid compressor according to a fourth embodiment.

FIG. 20 is a process chart showing a switching operation of the switching valve.

FIG. 21 is an enlarged longitudinal sectional view showing a portion of a switching valve of a fluid compressor according to a fifth embodiment.

FIG. 22 is a top view showing the valve element.

FIG. 23 is an enlarged longitudinal sectional view showing a part of a switching valve of a fluid compressor according to a sixth embodiment.

FIG. 24 is a top view showing the valve element.

FIG. 25 is an enlarged longitudinal sectional view showing a portion of a switching valve of a fluid compressor according to a seventh embodiment.

FIG. 26 is a process chart showing a switching operation of the switching valve.

FIG. 27 is an enlarged longitudinal sectional view showing a portion of a switching valve of a fluid compressor according to an eighth embodiment.

FIG. 28 is a process chart showing a switching operation of the switching valve.

FIG. 29 is an enlarged longitudinal sectional view showing a portion of a switching valve of a fluid compressor according to a ninth embodiment.

FIG. 30 is an enlarged longitudinal sectional view showing a portion of a switching valve of a fluid compressor according to a tenth embodiment.

FIG. 31 is an enlarged longitudinal sectional view showing a portion of a switching valve of a fluid compressor according to an eleventh embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Case, 1a ... Lid, 2 ... Compression mechanism, 3 ... Switching valve,
13: control unit (control means), 24: valve body, 25: pressure introduction shaft (partition member), 14: valve base, 26: shaft drive mechanism (valve body drive means), 31: first pressure introduction hole ( Low pressure introduction hole), 38: second pressure introduction hole (low pressure introduction hole), 45: first high pressure introduction hole (high pressure introduction hole), 4
6 ... second high pressure introduction hole (high pressure introduction hole), 40 ... communication passage, 44 ... pressure operation chamber, 44a ... one room, 44b ...
The other room, 50: magnetic coupling, 52: regulating mechanism, 54: motor-side rotor (magnetic generating means), 55: valve-side rotor (magnetic generating means).

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification code FI F25B 41/04 F25B 41/04 B (72) Inventor Shinichi Ide 336 Tatehara, Fuji City, Shizuoka Prefecture Higashi Shiba Fuji Plant (72 ) Inventor Yutaka Sasahara 336 Tatehara, Fuji-shi, Shizuoka Prefecture, in the Toshiba Fuji Plant (72) Inventor Kazuhiko Miura 336 Tatehara, Fuji-shi, Shizuoka Prefecture, in the Toshiba Fuji Plant, (56) References 323458 (JP, A) JP-A-7-305916 (JP, A) JP-A-6-307739 (JP, A) JP-A-8-128553 (JP, A) JP-A-8-152075 (JP, A) JP-A-59-47572 (JP, A) JP-A-61-145392 (JP, A) JP-A-60-124595 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F04C 23/00-29/10 F04C 18/356 F04B 39/00-39/16 F04B 49/00-51/00 F16K 11/074 F16K 31/04 F25B 41/04

Claims (2)

(57) [Claims] 1. A fluid compressor comprising a case, a compression mechanism housed in the case, and an electric motor for driving the compression mechanism, wherein three ports are formed on the case and communicate with the outside of the case. And the valve base is movably held in sliding contact with the opening surfaces of the three ports of the valve base.
A valve body having a communication passage that connects two adjacent ports among the three ports to each other is provided. By moving the valve body, a discharge flow path to the outside of the case and a suction flow path to the compression mechanism are formed. A switching valve for switching, a first magnetic generating means connected to the switching valve, and a second magnetic generating means connected to a rotor of the electric motor rotatably opposed to each other, and the driving force of the electric motor is changed to the switching valve A pressure operating chamber provided in the switching valve for guiding the high-pressure fluid compressed by the compression mechanism; a partitioning means for dividing the pressure operating chamber into two chambers; A pressure introduction switching means for selectively introducing a low pressure into one of the pressure operation chambers or the other chamber by rotating, and driving the valve movably by a pressure difference generated between the rooms. A valve body driving means for transmitting the driving force of the magnetic coupling means to the valve body; provided on the valve body driving means, when the motor rotates forward, the driving force from the electric motor to the valve body is provided. The driving force control means for transmitting the driving force from the electric motor to the valve body when the electric motor rotates in the reverse direction; and the pressure introduction switching when the electric motor rotates in the forward direction. A fluid compressor, comprising: a rotation regulating mechanism that regulates driving of the means and drives the pressure introduction switching means when the electric motor rotates in the reverse direction to switch the fluid flow path. 2. A fluid compressor having a compression mechanism driven by an electric motor for sucking and compressing a fluid and discharging a compressed fluid, and a first heat exchanger and a second heat exchanger for exchanging heat of the fluid. In the heat pump type refrigeration cycle, the fluid compressor includes a case, a compression mechanism housed in the case, an electric motor driving the compression mechanism, and three ports attached to the case and communicating with the outside of the case. The valve base is formed and held movably in sliding contact with the opening surfaces of the three ports of the valve base,
A valve body having a communication passage that connects two adjacent ports of the three ports to each other is provided. By moving the valve body, a discharge flow path to the outside of the case and a suction flow path to the compression mechanism are formed. A switching valve for switching, a first magnetic generating means connected to the switching valve, and a second magnetic generating means connected to a rotor of the electric motor rotatably opposed to each other, and the driving force of the electric motor is changed to the switching valve A pressure operating chamber provided in the switching valve and guiding the high-pressure fluid compressed by the compression mechanism; a partitioning means for dividing the pressure operating chamber into two chambers; Pressure introduction switching means for selectively introducing a low pressure into one of the pressure operation chambers or the other chamber by rotating, and driving the valve movably by a pressure difference generated between the rooms. A valve element driving means for transmitting the driving force of the magnetic coupling means to the valve element; and a valve element driving means provided in the valve element driving means, wherein when the electric motor rotates forward, the driving force from the electric motor to the valve element is provided. The driving force control means for transmitting the driving force from the electric motor to the valve body when the electric motor rotates in the reverse direction; and the pressure introduction switching when the electric motor rotates in the forward direction. A heat pump type refrigeration cycle, comprising: a rotation restricting mechanism for restricting the driving of the means and driving the pressure introduction switching means when the electric motor rotates reversely to switch the flow path of the fluid.