JPH0814708A - Fluid compressor and air conditioner - Google Patents

Abstract

(57) [Summary] [PROBLEMS] To provide a fluid compressor and an air conditioner which can be reduced in height and size and which can simplify the piping configuration of the air conditioner. A fluid compressor having a compressor body A having a compressor section for compressing low-pressure gas and a gas-liquid separator B for separating droplets contained in the low-pressure gas, wherein the gas-liquid separator B is provided. Is partitioned in the same case as the sealed case 28 and the gas-liquid separation chamber 29 which is partitioned inside the case 28 and separates liquid droplets from the low-pressure gas introduced from outside the case 28. A switching valve chamber 30 provided with a rotary switching valve portion 31. In the switching valve chamber, a high pressure gas introduction pipe for introducing the high pressure gas from the host compressor main body A into the switching valve chamber 30 is provided. 32
Is connected to the switching valve section 31.
Low-pressure gas discharge pipe 6 for communicating the gas-liquid separation chamber 29 with
7 is connected.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid compressor and an air conditioner provided with a switching valve for switching a flow path of a working fluid (refrigerant) of an air conditioner.

[0002]

2. Description of the Related Art Generally, in an air conditioner that performs both cooling and heating, the flow of a working fluid (refrigerant) flowing between an indoor heat exchanger and an outdoor heat exchanger is switched between cooling and heating. A four-way valve device is provided.

As such a four-way valve device, generally,
The one indicated by 1 in FIG. 18 is widely used. The four-way valve device 1 includes a valve main body 2, a high pressure gas introduction pipe 3 and a low pressure gas discharge pipe 4 connected to the valve main body 2, and a sliding valve provided in the valve main body 2. It is provided with first and second connecting pipes 6 and 7 which communicate with the low-pressure gas discharge pipe 4 or the high-pressure gas introduction pipe 3 by switching of 5.

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

As a device for introducing a pressure difference into the valve main body 2 to operate the sliding valve 5, an electromagnetic valve device shown in FIG. 10 is used. The solenoid valve device 10 is connected to the first and second copper capillaries 11 and 12 made of copper connected to the first and second spaces R1 and R2, and is led out from the low pressure gas discharge pipe 4. A third capillary tube 13, which is also made of copper, is connected between the first and second capillary tubes 11 and 12.

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

The pistons 8 and 9 provided in the four-way valve device are provided with fine through holes, respectively, and the pressure in the valve body 2 is previously set in the first and second spaces R1 and R2. Since (high pressure) is introduced, the first,
When the low pressure is introduced into either of the second spaces R1 and R2, a pressure difference is generated between them and the sliding valve 5 is switched.

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

The first connecting pipe 6 is connected to the outdoor heat exchanger shown in FIG. 19 and the second connecting pipe 7 is
It is connected to the indoor heat exchanger indicated by 20. Next, the operation of this air conditioner will be described.

When performing the heating operation, the slide valve 5 is placed at the position shown in FIG.
The connection pipe 7 and the high pressure gas introduction pipe 3 are communicated with each other, and the first connection pipe 6 and the low pressure gas discharge pipe 4 are communicated with each other.

As a result, the working fluid flowing in the refrigerant pipe of the air conditioner changes its state, as shown by the arrow in the figure, the compressor 18, the indoor heat exchanger 20, and the expansion valve 2.
1, the outdoor heat exchanger 19 and the compressor 18 flow in this order, and this air conditioner is caused to perform heating operation.

During cooling, by switching the sliding valve 5 of the four-way valve device 1 by the solenoid valve device 10, the first connection pipe 6 and the high pressure gas introduction pipe 3 are communicated with each other, and The second connecting pipe 7 and the low pressure gas discharge pipe 4 are connected to each other. As a result, contrary to the above case, the working fluid circulates from the outdoor heat exchanger side 19 to the indoor heat exchanger 20 side, and causes this air conditioner to perform the cooling operation.

[0013]

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

Also, conventionally, R- has been used as a refrigerant for air conditioners.
Although the HCFC (hydrochlorofluorocarbon) type refrigerant represented by No. 22 was used, the CFC regulation has been started, and an HFC (hydrofluorocarbon) type refrigerant is being considered as an alternative refrigerant.

This HFC-based refrigerant is a refrigerant having a property of easily transmitting sound as compared with the conventional HCFC-based refrigerant, and particularly in the above four-way valve device 1 using the reciprocating slide valve 5,
The collision noise at the time of switching operation is transmitted through the refrigerant to the indoor heat exchanger 20.
It can be considered that the noise propagates to and generates noise (abnormal noise).

On the other hand, the first to third capillaries 11 to 13 for connecting the valve body 2 and the electromagnetic valve device 10 are provided with the case 2 described above.
Since it is exposed to the outside of No. 4, it may be deformed by a small impact, resulting in malfunction.

As an invention made in order to solve such a problem, there is a conventional one disclosed in Japanese Patent Laid-Open No. 60-124595. As shown in FIG. 19, the present invention is a compressor of a type in which a high-pressure discharge gas discharged from the compressor section 22 is filled in a sealed case 24 which houses a compressor section 22 and an electric motor section 23. By incorporating the four-way valve device 1 and the electromagnetic valve device 10 having the above-described configurations in the case 24, the piping between the discharge side of the compressor and the four-way valve device is unnecessary, and the capillaries 11 to 11 It is intended to prevent breakage of 13 due to an external force.

However, even with such a structure, the problem that the structure is complicated and large has not been solved. Furthermore, by incorporating such a four-way valve device 1 in the case 24, The height of the compressor itself is high, it becomes large,
There arises a new problem that it is not possible to cope with the recent trend toward downsizing of compressors.

Further, since the four-way valve device 1 is configured to operate with a pressure difference, it is necessary that the sliding valve 5 is always in close contact with the valve seat, and when the valve is stopped, pressure balance between pipes (gas There is a problem that it is difficult to balance.

That is, in this case, since it takes a long time to balance the pressure, it may not be possible to quickly restart after stoppage and quickly switch between cooling and heating.

The fluid compressor is of a type in which the case 24 is filled with high pressure. For this reason,
The sealing property between the pipes 4, 6 and 7 taken out of the case 24 from the four-way valve device 1 incorporated in the case 24 and the case 24 becomes a problem.

That is, the pipes 4, 6, 7 and the cable
If the welding with the case 24 is not performed reliably and satisfactorily, when the fluid compressor is operated, the case 24 and the pipes 4, 6,
The high pressure gas in the case 24 may leak to the outside through the gap between the case 7 and the case 7, and good compression may not be performed.

Therefore, it is sometimes necessary to be careful in welding and handling the fluid compressor after welding. The present invention has been made in view of such circumstances, can simplify the piping configuration of the air conditioner, and can easily and quickly perform pressure balance at the time of stoppage, and reduce the compression leakage. An object of the present invention is to provide a fluid compressor that is low in noise and has a low profile.

[0024]

A first aspect of the present invention is a fluid compression having a compressor body having a compressor section for compressing a low pressure fluid, and a gas-liquid separator for separating droplets contained in the low pressure fluid. In the machine, the gas-liquid separator includes a closed case, a gas-liquid separating means for separating liquid droplets from a low-pressure fluid introduced from outside the case, the case being provided inside the case. Case
And a switching valve for rotating the valve element to switch the flow path of the high-pressure fluid discharged from the compressor section and the flow path of the low-pressure fluid to the gas-liquid separation means. It is a fluid compressor.

A second invention is the fluid compressor of the first invention, wherein the case is a gas-liquid separation chamber provided with the gas-liquid separation section and a switching valve chamber provided with the switching valve. And a high-pressure fluid introduction pipe for introducing high-pressure fluid from the compressor body into the switching valve chamber, and a low-pressure fluid discharge pipe for communicating the switching valve with the gas-liquid separation chamber. It is a fluid compressor.

A third invention is the fluid compressor of the second invention, wherein the switching valve has one surface and the other surface, one surface being exposed to the outside of the case and the other surface being the case. A first valve base which is attached to this case when positioned inside;
The first and second ports are provided so as to penetrate through the first valve base and open on one surface and the other surface of the valve base, and have one surface and the other surface. A second valve base provided opposite to the other surface of the first valve base and a second valve base penetrating the second valve base. And a high pressure fluid introduction port which is opened on one surface and the other surface and is provided at a predetermined angle in the circumferential direction with the first and second ports of the first valve base, respectively. It is interposed between the low-pressure fluid discharge port and the other surface of the first valve base and one surface of the second valve base, with respect to the first and second valve bases. And a valve body that is rotatably provided, and the valve body that is provided on the valve body and rotates by a predetermined angle causes the first and second ports of the first valve base to move, High pressure fluid guide of the second valve base, respectively. Port - DOO or low pressure fluid discharge port -
A fluid compressor having first and second communication holes for selectively communicating with the valve and drive means for rotationally driving the valve body.

A fourth invention is the fluid compressor of the second invention, wherein the switching valve chamber has a volume capable of partitioning a space around the switching valve.

A fifth aspect of the present invention is the fluid compressor of the first aspect of the present invention, wherein the switching valve includes drive means for driving the valve body, and the drive means includes a permanent magnet provided on the valve body. , A pair of magnetic pieces arranged to face the permanent magnet, and the pair of magnetic pieces are connected to the pair of magnetic pieces and are magnetized to have different polarities by applying a predetermined voltage,
Alternatively, the fluid compressor is provided with a magnetic force generating section that switches its polarity and rotationally drives the valve body via the permanent magnet.

A sixth invention is the fluid compressor of the first invention, wherein the gas-liquid separation means has a gas-liquid separation chamber filled with a low-pressure fluid, and the switching valve is provided in the gas-liquid separation chamber. The fluid compressor is provided with a high-pressure fluid introducing pipe for introducing high-pressure fluid from the compressor body into the switching valve.

A seventh invention is the fluid compressor of the sixth invention, wherein the switching valve is a valve base attached to the case.
And three ports provided on the valve base and opened on the inner and outer surfaces of the case of the valve base, and a case on which the three ports of the valve base are opened. A valve body rotatably provided on the inner side surface of the seat and a surface of the valve body facing the valve base, and the valve body is rotated by a predetermined angle to select one of the three ports. A communication groove for selectively communicating the two of the above with each other, a through hole provided in the valve body for communicating another port in the case, and a drive means for driving the valve body. A fluid compressor having.

An eighth aspect of the present invention is the fluid compressor of the third aspect, further comprising an urging means for urging the valve element against the valve base, the urging force of the urging means being the above-mentioned. When the compressor is stopped, the fluid compressor is set to such a strength as to allow a gap to be formed between the valve body and the valve base.

A ninth aspect of the present invention is the fluid compressor of the second aspect of the present invention, which has temperature detecting means attached to the high-pressure fluid introducing pipe for detecting the temperature of the high-pressure fluid flowing in the high-pressure fluid introducing pipe. Is a fluid compressor.

A tenth aspect of the present invention has a compressor body, a flow path switching valve, an indoor heat exchanger, a pressure reducing device, and an outdoor heat exchanger, and the gas-liquid separator connected to the compressor body has the above-mentioned structure. In an air conditioner integrally provided with a flow path switching valve, the working fluid used in this air conditioner is an HFC refrigerant, and the gas-liquid separator has a case filled with a low-pressure working fluid. However, the switching valve is an air conditioner characterized by being provided in this case.

[0034]

By providing the gas-liquid separator with the switching valve as in the first aspect of the invention, the height of the compressor body can be reduced.
Further, by using a rotary switching valve, it is possible to rotate the valve element and change the flow path of the fluid introduced into the compressor,
Thus, in the air conditioner having the indoor heat exchanger and the outdoor heat exchanger, it is possible to switch between cooling and heating operations. Also, by making it a rotary type,
The switching valve can be made smaller and more compact.

When the switching valve is provided in the switching valve chamber into which the high pressure fluid is introduced as in the second and third inventions,
When stopped, the valve element can be separated from the valve base, and the pressure in the pipe can be quickly balanced.

Further, by increasing the volume of the switching valve chamber as in the fourth aspect of the invention, it is possible to prevent noise generated from the switching valve from leaking to the outside due to the muffler effect.

As in the fifth aspect of the invention, the drive means for driving the valve element of the switching valve is composed of a permanent magnet and a magnetic force generating section for switching the magnetism applied to the permanent magnet to drive the valve element. By doing so, this driving means can be downsized.

Further, when the switching valve is provided in the gas-liquid separation chamber as in the sixth and seventh inventions, since the pressure in the gas-liquid separation chamber is low, the switching valve is installed from the mounting portion. Gas leak problems can be reduced.

By setting the urging force as in the eighth aspect of the invention, the valve element can be switched with a low torque. Further, as in the ninth invention, by providing the high-pressure fluid introducing pipe with the temperature detecting means, the temperature of the high-pressure fluid can be detected.
It becomes possible to control this fluid compressor appropriately.

Further, this fluid compressor has the structure of the tenth aspect of the invention, and is an HF alternative refrigerant which is an HF having a high sound propagating property.
It can be operated with a C-based refrigerant, and in this case, the generation of noise can be effectively prevented.

[0041]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. The same components as those described in the conventional example are designated by the same reference numerals, and the description thereof will be omitted.

First, the first embodiment will be described. As shown in FIG. 1, the fluid compressor of the first embodiment comprises a compressor body A and a gas-liquid separator B connected to the compressor body A.

The compressor body A has a first closed case 2
Have 5. In the first closed case 25, a compressor section 26 and a motor section 27 for driving the compressor section 26 to perform a compression operation are provided at a lower end portion and a middle portion in the height direction.
Is provided.

On the other hand, the gas-liquid separator B has a second closed case 28. In the second closed case 28,
A gas-liquid separation chamber 29 is defined on the lower end side in the height direction, and a switching valve chamber 30 is defined on the upper end side.

Inside the switching valve chamber 30, there is provided a switching valve portion 31 (rotary switching valve) which is a main part of the present invention. This switching valve unit 31 is shown in FIG.
A flow path of high-temperature high-pressure refrigerant gas (hereinafter, simply referred to as high-pressure gas) introduced into the switching valve chamber 30 through the high-pressure gas introduction pipe indicated by 2 is an indoor heat exchanger indicated by 20 in the figure or a chamber indicated by 19 It has a function of switching to the outer heat exchanger and a function of switching the flow path of the low pressure gas passing through the heat exchangers 20 and 19 to the gas-liquid separation chamber 29.

Further, inside the gas-liquid separation chamber 29, a retainer 33 which constitutes a gas-liquid separation means is provided. The retainer 33 separates droplets of the refrigerant liquid from the low-pressure low-temperature refrigerant gas (hereinafter, simply referred to as low-pressure gas) introduced into the gas-liquid separation chamber 29 through the switching valve portion 31 ( (Liquid separation), and has a function of supplying the low-pressure gas after liquid separation to the compressor section 26 of the compressor body A.

Each constituent element will be described in detail below. First, the configuration of the compressor body A will be described. The electric motor section 27 is a DC brushless motor composed of a stator 34 fixed to the inner surface of the first hermetic case 25 and a rotor 35 arranged inside the stator 34. −
It is The rotor 35 is shrink-fitted on the upper portion of the drive shaft shown by 36 in the figure.

The lower end of the drive shaft 36 is
It extends into the compressor section 26. At the lower end of the drive shaft 36, there are formed two cranks 36a which are vertically spaced apart from each other by a predetermined distance and are 180 ° out of phase with each other.

On the other hand, the compression mechanism section 26 is held by a partition member 37 fixed to the first hermetic case 25, and is vertically connected via an intermediate plate 38 shown in FIG. It comprises two cylinders 39, 39 of cylindrical shape. And, in these two cylinders 39, 39,
The two crank portions 36a, 36 of the drive shaft 36
a are located respectively.

The shaft 36 is provided between the first bearing member 40 (main bearing) fixed to the partition member 37 and the upper ends of the two cylinders 39, 39 between the first bearing member 40 and the first bearing member 40. And a second bearing member 42 (auxiliary bearing) that closes the cylinders 39, 39 by locating the lower ends thereof and is rotatably supported about the vertical axis thereof.

The two crank portions 36a, 36a of the shaft 36 have cylindrical rollers 44, 4 respectively.
4 is fitted. This roller 44 is used for the cylinder 3
The cylinder 39 is held in a state of being eccentric with the outer peripheral surface of the cylinder 39 and having a part of the outer peripheral surface thereof in contact with the inner peripheral surface of the cylinder 39.

Therefore, a compression space 45 having a crescent cross section is defined between the inner peripheral surface of the cylinder 39 and the outer peripheral surface of the eccentric roller 44. A blade 46 for partitioning the compression space 45 into a high pressure side and a low pressure side is provided in the cylinder 39 (the upper cylinder 39 is not shown). This blade 4
6 is a roller 4 by means of a spring shown in FIG.
It is urged toward the 4th side (in the direction of the center of the cylinder 39) so as to move in and out of a blade groove (not shown) provided in the cylinder 39 so that its tip always comes into contact with the outer peripheral surface of the roller 44. Has become.

Suction passages 48 for sucking the refrigerant gas into the compression space 45 and discharge ports for discharging the compressed refrigerant gas (discharge gas) are provided on both sides of the blade 39 of the cylinder 39. And a passage is formed. The suction passage 48 is shown only in the upper cylinder 39.

In the suction passage 48, 49 are respectively provided.
The suction pipe indicated by is connected. This pair of suction pipes 49
Is extended to the outside of the first closed case 25 and is connected to the gas-liquid separation chamber 29 of the gas-liquid separator A. That is,
The tip of the suction pipe 49 is inserted into the gas-liquid separation chamber 29 from the lower end of the second hermetically sealed case 28 of the gas-liquid separator A substantially vertically with a predetermined dimension and opened upward.

On the other hand, the discharge passage has the first discharge valve 5 provided on the flange portion of the first bearing member 41.
From the first passage that opens to the upper portion of the first hermetic casing 25 through the muffler 52 of one or two stages, and the second discharge valve 53 provided in the flange portion of the second bearing member 42. It communicates with the muffler 54 and the cylinder 3
9, a middle plate 38, and a second passage which penetrates the first bearing member 41 and is also opened to the upper part of the case 25.

Therefore, the compressor section 26 sucks the low-pressure gas, which is a working fluid, from the inside of the gas-liquid separation chamber 29 into the cylinder 39 through the suction pipe 49, and the above-mentioned
After being compressed by swirling the la 44, the high-pressure gas is discharged into the upper portion of the case 25 through the discharge passage including the first and second passages. That is, the inside of the first closed case 25 is filled with the high-pressure gas and kept at a high pressure.

The high pressure gas introduction pipe 32 is attached to the central portion of the upper end wall of the first hermetic case 25. The other end of the high-pressure gas introduction pipe 32 is inserted into the switching valve chamber 30 of the gas-liquid separator A and is open inside the switching valve chamber 30.

Therefore, the high pressure gas introduction pipe 32 is
It has a function of discharging the high-pressure gas filled in the first closed case 25 to the outside of the case 25 and introducing the high-pressure gas into the switching valve chamber 30 of the gas-liquid separator A.

Incidentally, one end of the high pressure gas introduction pipe 32 connected to the first hermetically sealed case 25 has the electric motor portion 27.
Disk-shaped oil separation plate 5 fixed to the upper end of the shaft 36 of
7 is opened at a position facing the upper surface of 7. This prevents the lubricating oil scattered in the closed case 25 from being sucked into the high pressure gas introduction pipe 32.

Next, the gas-liquid separator B will be described. The second closed case 28 of the gas-liquid separator B is, as shown in the figure, a lower end case forming the gas-liquid separation chamber 29.
58 and the upper case 5 forming the switching valve chamber 30.
It can be separated into 9.

Further, as shown in the figure, a partition plate 60 hermetically partitions the lower end side case 58 and the upper end side case 59 into the gas-liquid separation chamber 29 and the switching valve chamber 30. Is partitioned.

As described above, in the switching valve chamber 30, the switching valve portion 31 which is the main part of the present invention is provided. As shown in FIG. 1, the switching valve portion 31 has first and second connection ports 63 and 64 connected to the indoor heat exchanger 20 and the outdoor heat exchanger 19, respectively.

Further, the switching valve portion 31 is provided with a high pressure gas port 6 for sucking the high pressure gas from the compressor main body A introduced into the switching valve chamber into the switching valve portion 31.
5 is provided.

Further, the switching valve portion 31 is provided with a low pressure gas port indicated by 66 in the figure, and an upper end portion of a low pressure gas discharge pipe 67 is connected to the low pressure gas port 66. . The lower end of the low-pressure gas discharge pipe 67 is inserted into the gas-liquid separation chamber 29, and the low-pressure gas that has passed through the switching valve portion 31 is introduced into the gas-liquid separation chamber 29.

That is, the switching valve portion 31 selectively selects the first connection port 63 and the second connection port 64 to the high pressure gas port 65 or the low pressure gas port 66. By communicating with the heat exchangers 19 and 20, as described above, the high pressure gas flowing out to the heat exchangers 19 and 20 and the flow path of the low pressure gas flowing from the heat exchangers 19 and 20 are switched.

Next, the specific structure of the switching valve portion 31 will be described in detail with reference to FIGS. As shown in FIG. 1, the switching valve portion 31 is provided with the first and second connection ports 63 and 64, and is a first valve base fixed to the second hermetically sealed case. 69 and a second valve base 70 provided on the lower surface side of the first valve base 69 and having the above-mentioned high-pressure gas port 65 and low-pressure gas port 66, and this second valve base 70. A valve body 71, which is rotatably interposed between the first valve base 69 and the second valve base 70 and switches the passages of the high pressure gas and the low pressure gas, as shown in FIG. 2 (b). In addition, by applying a magnetic force to the magnet member 72 fixed to the radially outer edge portion of the valve body 71 and the magnet member 72, the valve body 7
1 has the magnetic force switching section 74 for rotationally driving the first and second valve bases 69, 70 to switch the flow path, and a holder 75 for covering the switching valve section 31.

In FIG. 1, for convenience of explanation, FIG.
A part of the configuration of the switching valve portion 31 shown in FIG. 3 is omitted, and the phase relationship between the first valve base 69 and the second valve base 70 is intentionally changed.

On the other hand, the first valve base 69 has a circular shape in plan view as shown in FIG. 3, and is formed with a larger diameter at the lower end (other surface side) than at the upper end (one surface side). It has a collar portion 69a. The first valve base 69 is provided on the upper wall of the upper end case 59 of the gas-liquid separator B, as shown in FIG.
It is attached with the upper end side exposed outside the case 59.

That is, a through hole shown by 77 in the drawing is formed in the upper wall of the upper case 59. The first valve base 69 has the through hole 77 on the upper end side.
It is attached to the upper case 59 by inserting it inside.
For example, the through hole 77 is fixed so as to be airtightly closed by welding.

Further, as shown in FIG. 3, the first valve base 69 is provided on the center axis L of the valve base 69, and the lower end side thereof is the case 59 (switching valve). A central shaft 78 protruding into the chamber 30) is fixed.

The first and second valve bases 69 are axially pierced through the valve base 52 at positions symmetrical about the central axis 78. Port 6
3, 64 are provided.

As described above, the two ports 63 and 64 are connected to the indoor heat exchanger and the outdoor heat exchanger shown by 20 and 19 in FIG. 1, respectively.
(Corresponding to 6 and 7 in the conventional example) As shown in FIG. 3, the first valve base 69 is
9 in the circumferential direction from the first and second connection ports 63, 64.
As shown in FIG. 2 and FIG. 2B, a stopper 79 (shown by a mesh in the figure) having a lower end protruding slightly from the lower surface of the valve base 69 is embedded at a position separated by 0 °. ing.

As shown in FIG. 2B, the stopper 79 is attached by screwing the upper end portion thereof to the first valve base 69. The portion of the stopper 79 protruding from the lower surface (other surface) of the first valve base 69 has an outer diameter slightly smaller than the inner diameters of the two ports 63 and 64. ing.

On the other hand, the second valve base 70 is formed in a disk shape having a circular upper surface (one surface) and a lower surface (the other surface) as shown in FIG. A central hole indicated by 80 is provided so as to penetrate from the upper surface to the lower surface. As shown in FIG. 2 (b), the second valve base 70 has the center hole 80 through which the central shaft 78 projecting from the first valve base 69 is inserted. It is arranged concentrically with the first valve base 69.

In the second valve base 70, the high-pressure gas port 65 and the low-pressure gas port 66 are provided at positions symmetrical with respect to the center hole 80.
It is equipped with. Each port 65, 66 is connected to this second valve base.
It is provided so as to penetrate the space 70 in the axial direction.

The second valve base 70 is provided so as not to rotate relative to the first valve base 69, as will be described later. The second valve base 70 is shown in FIG.
As shown in (a), the high-pressure gas port 65 and the low-pressure gas port 66, and the first and second connection ports 63 provided on the first valve base 69. , 64 are attached so as to be respectively located around the central axis 78 with a phase difference (angle) of 90 °.

Next, the valve body 71 will be described. This valve body 71 is, as described above, the first valve base 6
It is interposed between the lower surface of 9 and the upper surface of the second valve base 70. (FIG. 2 (b)) This valve body 71 is a disc-shaped component having a central hole 71a in the center thereof as shown in FIG. 5, and as shown in FIG. 71a to the first valve base 69
By inserting the central shaft 78 projecting from the above, the upper surface of the central shaft 78 is brought into contact with the lower surface of the first valve base 69 and is rotatable with respect to the first valve base 69. It is installed.

As shown in FIG. 5, the valve body 71 is provided with first and second switching flow passages 82 and 83 which penetrate in the axial direction. The first and second switching flow paths 82 and 83 are
90 out of the above-mentioned four ports 63 to 66, respectively.
It is provided with a predetermined width and in the range of about 90 ° along the circumferential direction centering on the center hole 71a so that two adjacent ports can be communicated with each other at an interval.

That is, in the first switching passage 82, when the valve body 71 is rotated 90 °, the first switching passage 82 shown in FIG.
As shown in (a) to (d), the ports adjacent to each other in the circumferential direction, that is, the high pressure gas port 65 and the first connection port 63, or the high pressure gas port 65. And the second connection port 64 are communicated with each other.

The second switching passage 83 is formed point-symmetrically with respect to the first switching passage 82 with respect to the central hole 71a and has a similar shape in plan view. By being moved, as shown in FIGS. 10A to 10D, the ports adjacent to each other in the circumferential direction, that is, the low-pressure gas port 66 and the second connection port 64, Alternatively, the low-pressure gas port 66 and the first connection port 63 can be switched so as to communicate with each other.

From the positional relationship between the first switching passage 82 and the second switching passage 83, as shown in FIGS. 10 (a) and 10 (b), the second switching passage 83 allows the first connection port to be connected. To 6
3 and the low pressure gas port 66 are communicated with each other, the second switching port 82 is used by the first switching passage 82.
The port 64 and the high-pressure gas port 65 communicate with each other.

On the other hand, as shown in FIGS. 2 (a) and 2 (b), the valve body 71 is attached to the first switching passage 82 with the valve body 71 attached to the first valve base 69. The lower end projecting portion of a stopper 79 provided on the valve base 69 is located.

The stopper 79 contacts one end or the other end of the first switching passage 82 in the circumferential direction so as to restrict the movement of the valve body 71 in the rotating direction within the range of 90 °. Has become.

As shown in FIG. 5, the upper surface of the valve body 71 encloses the second switching passage 83, and the space between the valve body 71 and the first valve base 69 is hermetically sealed. Sealing Sea
A ruler member 86 is formed.

Further, the upper end portion of the valve body 71 is a flange-shaped flange portion 7 protruding slightly outward in the radial direction of the valve body 71.
1b. A positioning projection 88 that engages with the magnet member 72 is formed at a predetermined position along the lower surface circumferential direction of the flange portion 71b.

On the other hand, the magnet member 72 is, as shown in FIGS. 2B and 6, a thin-walled cylindrical collar 89 to be externally inserted on the lower end side of the valve body 71, and an outer surface of the collar 89. And a fixed permanent magnet 90.

As shown in FIG. 6, a slit 89a in FIG. 6 is provided in a part of the collar 89 in the circumferential direction, and the slit 89a is provided with the projection 88 provided in the valve body 71. By matching and engaging, the valve body 71
It is designed to be combined so that it cannot rotate relative to. It should be noted that such a connection is not made with the second valve base 70.

Further, as shown in FIG.
0 is composed of an N pole portion 90a and an S pole portion 90b divided into two at 180 ° intervals, and is driven by the attraction / repulsion force by the magnetic force switching portion 74.

As shown in FIGS. 2 (d) and 7, the magnetic force switching section 74 includes a pair of strip-shaped iron-made stations 92 provided in parallel with each other and a base of the station 92. It is composed of an iron core 93 installed between the end portions, and an electromagnet 94 configured by applying a coil winding to the iron core 93.

The tip portion of the step 92 is bent along the outer peripheral surface of the permanent magnet 90 fixed to the valve body,
The bending radius is set to be slightly larger than the outer diameter of the permanent magnet 90 so that the inner surface has a predetermined minute gap with the outer peripheral surface of the permanent magnet 90.

The tips of the two stations 92 are arranged at an angle of about 90 ° to each other along the bending direction of the station 92.
It is set so as to be separated at an angle of. The magnetic force switching unit 74 can magnetize the tip portion of the station 92 to a predetermined polarity by applying a direct current to the electromagnet 94, and by switching the magnetism, the attraction with the permanent magnet 90 can be achieved. The valve body 71 is rotationally driven by the repulsive action.

Further, a holder indicated by 75 in FIGS. 2 (b) to 2 (e) is provided on the outer side of the tip portion of the stay 92. This holder 75 is a thin-walled cylindrical member,
The upper end is fixed to the lower surface of the outer edge of the flange 69a of the first valve base 69.

In this holder 75, (c) and (d) in FIG.
As shown in FIG.
Notch 7 for taking out the side) to the outside of this holder 75
5a is provided. The holder 75 is configured to position and prevent rotation of the magnetic force generating portion 74 by the cut portion 75a.

On the other hand, the lower end of the holder 75 and the first valve base 69 to the valve body 71 and the second valve base 7 are connected.
A pressing member indicated by 97 in FIGS. 2B and 2E is fixed to the lower end of the central shaft 78 extending downward through 0.

The pressing member 97 is formed in a disk shape as shown in FIG. 8, and its outer edge is fixed to the lower end of the holder 56 by welding as shown in FIG. Further, the lower end of the central shaft 78 is fixed to the central portion thereof.

Further, a spring 98 shown in the drawing is inserted between the central portion of the pressing member 97 and the lower surface of the second valve base 70 in a state of being compressed in the axial direction. The valve base 70, the valve body 71, and the magnet member 72 are pressed against the lower surface of the first valve base 69.

The urging force of the spring 98 is such that the valve body 71 and the second valve base are in a state where the compressor is not operating, that is, when high pressure is not acting in the switching valve chamber. It is adjusted to have such a strength as to allow a minute gap to be formed between the upper surface of the valve body 71 and the lower surface of the first valve base 69 by its own weight.

On the other hand, the pressing member 97 has a structure shown in FIG.
As shown in (b) and FIG. 8, the low pressure gas discharge pipe 6 is
7, the support hole 100 for supporting the middle part of the switch 7, and the switching valve chamber 3
An introduction hole 101 is provided for introducing the high pressure gas in 0 into the second valve base 70 side.

As shown in FIG. 2B, the middle portion of the low-pressure gas discharge pipe 67 is located at the support hole 10 of the pressing member 97.
No. 0 is inserted and is supported by the support hole 100 so as to be vertically movable. The upper end of the low pressure gas discharge pipe 67 is connected to the low pressure gas port 6 of the second valve base 70.
It is inserted and fixed in 6.

The lower end of the low-pressure gas discharge pipe 67 is slidably inserted into a partition plate 60 for partitioning the closed case 28 of the gas-liquid separator B, as shown in FIG. The gap between the partition plate 60 and the low pressure gas discharge pipe 67 is hermetically sealed by a seal member (not shown).

That is, the low-pressure gas discharge pipe 67 moves up and down integrally with the second valve body 70. When assembling the switching valve portion 31 described above, first, the holder 75 is attached to the first valve base 69.
Is fixed. On the other hand, the magnet member 72 (color 89 and permanent magnet 90) is adhered to the outer peripheral surface of the valve body 71.

Then, the upper end portion of the first valve base 69 is inserted into the insertion hole 77 provided in the upper end side case 59 and welded and fixed. Thereafter, the valve body 70 formed by adhering the magnet member 72 is attached to the central shaft 78 of the first valve base 69, and the magnetic force switching portion 7 is attached.
Assemble 4.

Then, the second valve base 70 is attached to the central shaft 78 of the first valve base 69 projecting through the valve body 71. The low pressure gas discharge pipe 67 is previously provided in the low pressure gas port 66 of the second valve base 70.
Insert and fix the upper end of the.

The low-pressure gas port 66 and the high-pressure gas port 65 of the second valve base 70 and the first
The mounting angle of the second valve base 70 is adjusted so that the angle formed by the first and second connection ports 63 and 64 of the second valve base 69 is 90 ° as described above. I'll do it.

Finally, the pressing member 97 is fixed to the lower ends of the central shaft 78 and the holder 75 while compressing the spring 98. This work is performed by the second valve base described above.
The low-pressure gas discharge pipe 67 fixed to the low-pressure gas port 66 of the nozzle is inserted into the support hole 100 formed in the pressing member. The pressing member 97 is fixed by screwing the pressing member 97 to the lower end of the central shaft 78.

By fixing the pressing member 97 in this manner, the second pressure gas is discharged through the low pressure gas discharge pipe 67.
The valve base 70 is held non-rotatable. Further, as shown in FIG. 9, a first power supply terminal 102 for supplying power to the magnetic force switching section 74 is fixed to the upper end case 59.

Thus, the upper case 59 is formed.
Once the necessary parts have been attached to the upper case 5,
9 is attached to the lower case 58. With this, the gas-liquid separator B is completed.

On the other hand, the first power supply terminal 102 has the same structure as in FIG.
Is connected to the control unit indicated by 103. This control unit 1
Reference numeral 03 designates an inverter circuit 105 for driving the electric motor section 27 of the compressor and a control circuit 108 for driving the switching valve section 31,
The temperature detection unit 107 detects the temperature of the discharge gas.

That is, the inverter circuit 105 is connected to each wiring from the second hermetically sealed terminal 109 fixed to the upper end of the compressor body A, and the inverter control of the electric motor section 27 can be performed. It is like this.

Further, as described above, the control circuit 108 for driving the switching valve portion 31 has the first sealed terminal 10 as described above.
2 is connected. The control circuit 108 is configured, for example, as shown in FIG.

That is, as shown in FIG.
The energization from 0 to the electromagnet 94 of the magnetic force switching unit 74 is
It is designed to be performed via a phototriac 111 which performs half-wave control. At this time, the micro computer
The data 112 and the phototransistor 113 that detects the AC 0V (zero cross) timing determine whether or not to energize the phototriac 111 at the zero cross point and output the result.

As a result, the magnetic force switching section 28 can switch the magnetism of the pair of stations 92 between the N pole and the S pole (FIGS. 10 (a) and 10 (c)), and generate the magnetic force. It can also be stopped (Figs. 10 (b) and 10 (d)).

Further, as shown in FIG. 1, a temperature detection sensor 114 (for example, a thermocouple) provided on the high pressure gas discharge pipe 32 is connected to the temperature detection unit 107, and the temperature detection sensor 114 detects the temperature. The temperature of the high pressure gas is detected based on the value.

Next, the structure of the gas-liquid separation chamber 29 provided below the switching valve chamber 30 will be described. In the gas-liquid separation chamber 29, the compressor section 27 of the compressor body A is
A suction pipe 49 connected to the suction side of the above is inserted by a predetermined dimension upward from the lower end wall of the lower end case 58 and opened upward.

Further, the retainer 3 is provided between the lower end opening of the low pressure gas discharge pipe 67 and the upper end opening of the suction pipe 49 inserted from the switching valve chamber 30 into the gas-liquid separation chamber 29.
3 is provided.

The retainer 33 is in the form of a net having a single layer or a plurality of layers, and removes only the liquid droplets of the refrigerant liquid in the low pressure gas discharged from the low pressure gas discharge pipe 67 so as to perform liquid separation. It has become.

The low-pressure gas, which has been liquid-separated by the retainer 33, is led out below the retainer 33, sucked into the suction pipe 49, and supplied to the compressor section 26. The droplets removed by the retainer 33 travel along the inner wall surface of the lower end case 58 and are collected at the lower end of the lower end case 58.

Next, the control of this fluid compressor will be described. First, the control during the cooling operation will be described. During the cooling operation, the voltage applied to the electromagnet 94 of the switching valve unit 31 is controlled as shown in the waveform diagram of FIG. As a result, the station 92 located on the upper side in the figure is magnetized to the N pole, and the station 92 located on the lower side is magnetized to the S pole.

Therefore, the S pole portion 90b of the magnet member 90 fixed to the valve body 71 is located at the upper side in the figure.
The N pole portion 90a is attracted to the station 92 and is located on the lower side.
It is sucked by 92, whereby the valve body 71 rotates counterclockwise.

When rotated by a predetermined angle, as shown in FIG. 2A, a stopper 79 protruding from the lower surface of the first valve base 69 is provided in the first switching passage 82 of the valve body 71. The valve body 71 comes into contact with one end in the circumferential direction, and the rotation of the valve body 71 is stopped. As a result, as shown in FIG. 10A, the first connection port 63 and the high-pressure gas port 65 communicate with each other through the first switching flow path 82, and the first connection. Port 6
4 and the low pressure gas port 66 communicate with each other through the second switching flow path 83.

That is, the first connection port 63 is opened into the switching valve chamber 30 (upper end case 59) through the high pressure gas port 65, and the second connection port 63 is opened. -To 6
4 communicates with the gas-liquid separation chamber 29 by a low-pressure gas discharge pipe 67 fixed to the low-pressure gas port 66.

In this state, the motor section 27 shown in FIG.
Operate. When the electric motor unit 27 operates, the compressor unit 26 operates, and the working fluid is compressed. The compressed high-pressure gas is discharged into the first closed case 25 of the compressor body A. Then, the high-pressure gas filled in the first closed case 25 passes through the high-pressure gas introduction pipe 32 and is introduced into the switching valve chamber 30 provided in the gas-liquid separator B.

The high-pressure gas in the switching valve chamber 30 flows into the high-pressure gas port 65 and the first connection port 63.
And is supplied to the outdoor heat exchanger 19. The high-pressure gas passes through the outdoor heat exchanger 19, the capillary tube 115 of the decompression device, and the indoor heat exchanger 20 while sequentially changing the state to cool the room.

The gas (low-pressure gas) which has passed through the indoor heat exchanger 20 and has a low temperature and low pressure is supplied to the second connection port 64.
Flow into the low pressure gas port 66 through the second switching flow path 83, and from the low pressure gas discharge port 66 through the low pressure gas discharge pipe 67 to the gas-liquid separation chamber 29. be introduced.

The low-pressure gas introduced into the gas-liquid separating section 29 is supplied to the compressor section 26 of the compressor main body A through the suction pipe 49. Then, this low-pressure gas is again compressed by the compressor section 26, becomes high-pressure gas, and is discharged into the above-mentioned first closed case 25.

Then, this high-pressure gas is introduced again from the compressor main body A into the switching valve chamber 30 of the gas-liquid separator B, passes through the switching valve portion 31 and then from the first connection port 63. It is introduced into the outdoor heat exchanger 19 and circulates in the piping of this air conditioner.

During this time, the control circuit 108 is controlled as shown in the waveform diagram of FIG. 10 (b). That is, the applied voltage is controlled to 0, and the pair of stations 92 are not magnetized.

Even in such a state, the above-mentioned step 9
Since 2 is made of iron (magnetic material), the state of FIG. 10A can be maintained by the attractive force with the magnet member 90. At this time, the inside of the second switching passage 83 is at a lower pressure than the inside of the switching valve chamber 30, so the pressure inside the switching valve chamber 30 causes the second valve base to move.
The sleeve 70, the valve body 71, and the first valve base 69 are pressed against each other in an airtight manner so that the valve body 71 cannot rotate.

On the other hand, when the cooling operation is stopped, the electric motor section 27 is stopped. As a result, the pressure in the switching valve chamber 30 decreases, so that the valve body 71 and the valve base are closed.
The close contact with the rollers 69 and 70 is eliminated. Further, as a result, the spring 98 is slightly compressed by the weight of the valve body 71 and the second valve base 70, and the valve body 5
3 and the first valve base 69, a minute gap is formed, so that the first and second connection ports 63 and 64, the high pressure gas port 65, and the low pressure gas discharge port. The pressure in 66 will be balanced.

As a result, the valve body 71 can be easily driven with a low torque when switching to the heating operation described below. Next, control and operation during heating operation will be described.

During the heating operation, the voltage applied to the electromagnet 74 of the switching valve section 31 is controlled as shown in the waveform diagram of FIG. 10 (c). As a result, contrary to the case shown in FIG. 10A, the stay 92 located on the upper side in the figure is magnetized to the S pole, and the stay 92 located on the lower side is magnetized to the N pole.

As a result, the N pole portion 90a of the permanent magnet 90 fixed to the valve body 53 is located at the upper side in the figure.
92, and the south pole portion 90b is located on the lower side.
92 is sucked. This causes the valve body 71 to rotate clockwise.

When rotated by a predetermined angle, the stopper 79 protruding to the lower surface of the first valve base 69 is provided with the valve body 7.
The valve body 71 comes into contact with the other end of the first switching passage 82 in the circumferential direction, and the rotation of the valve body 71 is stopped.

As a result, as shown in FIG.
Contrary to the cooling operation, the first connection port 63 and the low pressure gas port 66 communicate with each other through the second switching flow path 83, and the second connection port 64 and the high pressure gas. Port 65
And are communicated with each other by the first switching flow path 82.

That is, the first connection port 63 is
The low pressure gas discharge pipe 67 fixed to the low pressure gas port 66 communicates with the gas-liquid separation chamber 29, and the second connection port 64 passes through the high pressure gas port 65. The switching valve chamber 30 (upper case 59) is opened.

When the operation of the electric motor section 27 is started in this state, the switching valve chamber 30 of the gas-liquid separator B is filled with high pressure gas by the operation of the compressor section 26,
Due to this pressure, the second valve base 70 and the valve body 71 are brought into close contact with the lower surface of the first valve base 69.

The high-pressure gas in the switching valve chamber 30 is transferred from the second connection port 64 to the indoor heat exchanger 2
0, the capillary tube 115 of the decompression device, and the outdoor heat exchanger 19 are sequentially circulated while changing the state to heat the room.

The fluid that has passed through the indoor heat exchanger 20 flows into the first connection port 63, and the flow path is switched by the second switching flow path, so that the low pressure gas port is switched. From the port 66 through the low-pressure gas discharge pipe 67 to the gas-liquid separation chamber 29.

During the heating operation, the voltage applied to the electromagnet 94 is controlled to 0 as in the cooling operation (FIG. 10 (d)). However, even in such a state, since the stay 92 is made of iron (magnetic material), the state shown in FIG. 10C can be maintained by the attractive force with the permanent magnet 90. It has become.

At this time, the first switching passage 82
Since the pressure inside the switching valve chamber 30 is lower than the pressure inside the switching valve chamber 30, the pressure inside the switching valve chamber 30 causes the valve element 71 and the second valve
The valve base 70 is pressed against the first valve base 69 in an airtight manner so that the valve body 71 cannot easily rotate.

The structure described above has the following effects. First, the size and height of the compressor as a whole can be reduced as compared with the case where the switching valve is provided in the compressor body.

That is, when the switching valve 1 is provided in the case 24 of the compressor body A as in the conventional example shown in FIG. 19, a space for providing the switching valve 1 in the case 24 is provided. -Because it is necessary to secure sufficient space, the height of this compressor may increase.

Therefore, when the compressor is provided in the outdoor unit, there is a limit in reducing the height of the outdoor unit. However, in the present invention, since the switching valve portion 31 is built in not on the compressor body A side but on the gas-liquid separator B side, there is an effect that the height of the compressor body A can be reduced.

Further, the switching valve portion 31 built in the gas-liquid separator B is a conventional example (direct acting type) shown in FIGS.
Unlike the above, it is a rotary type, and since it does not have an electromagnetic valve device for operation, the total length can be shortened accordingly.

Further, in the conventional example, since the sliding valve 5 is always in close contact with the valve seat 2 regardless of the operation and stop of the compressor, the sliding valve 5 is driven to open the flow path. A large drive torque was required to switch. For this reason, the solenoid valve device 10 as the driving means is relatively large.

On the other hand, in the fluid compressor of the present invention, when the compressor is stopped, the valve body 71 is slightly lowered due to its own weight, so that the close contact state with the first valve base 69 is eliminated. Thus, the valve body 71 can be rotationally driven with low torque.

Therefore, in the present invention, since the driving torque can be reduced, the magnetic force switching section 74 as the driving means can be downsized. Due to these, even when the switching valve portion 31 is built in the gas-liquid separator B, the size increase of the gas-liquid separator B can be suppressed as much as possible. Therefore, it is possible to reduce the size and height of the fluid compressor as a whole, and it is possible to sufficiently cope with the recent trend toward miniaturization of the fluid compressor and the air conditioner.

Secondly, there is an effect that a fluid compressor having a built-in switching valve can be easily assembled. That is, the switching valve portion 31 is different from the conventional pilot type in that the solenoid valve device 10 for driving is used. Is not used, the fine capillary tube required for the conventional switching valve 1 (see FIGS. 11 and 12) is used.
11 to 12) shown in FIG. Therefore, when assembling this compressor, it is not necessary to worry about the deformation of the capillaries.

In the conventional example, the case 2 of the compressor body is also used.
Although the four pipes 4, 6 and 7 are taken out from 4 separately, in the present invention, the first valve base for attaching the first and second ports 63 and 64 to the upper case 59 is provided. Integrated into 69. As a result, the total length of the connecting portion of the case 59 can be shortened, so that the welded portion also becomes small,
The reliability of the gas leak and the workability of welding work are also improved.

The second hermetically sealed case of the gas-liquid separator B is also used.
Since the case 28 is divided into the upper end side case 59 and the lower end side case 58, the switching valve portion 31 can be easily assembled and the maintenance can be easily performed.

As a result, even a compressor of the type having the switching valve portion 31 built therein can be easily assembled (manufactured). Thirdly, there is an effect that the gas balance at the time of stop can be easily and promptly.

That is, in the case of the conventional reciprocating sliding valve 5, it is necessary to keep the sliding valve 5 in close contact with the valve seat 2 at all times in order to prevent gas leakage. It is impossible to perform gas balance by leaking gas at the sliding valve portion, and wait for a long time until gas leaks from the inside of the compressor or the expansion valve 115 portion to achieve gas balance. There was a need.

However, in the compressor of the present invention, when stopped, the valve body 71 is slightly lowered due to its own weight, and the gap with the first valve base 69 is enlarged. Therefore, the first and second ports 63 provided on the valve base 69,
Since 64 communicates with the upper surface of the valve body 53 through a gap formed between the valve body 53 and the valve body 53, gas balance can be performed quickly.

Further, during operation, the valve body 71 is pressed against the first valve base 69 by the pressure in the compression chamber 30 and is brought into close contact with the first valve base 69, so that no gas leakage occurs between them. . Further, as a result, the valve body 71 is held so as not to easily rotate in the rotating direction during operation of the compressor.

Therefore, the gas balance after the stop can be easily and quickly performed, the restart after the stop, the switching between cooling and heating can be performed quickly, and the injection of the refrigerant and the like can be performed for the gas balance. There is an effect that it can be done quickly without waiting for time.

Fourthly, there is an effect that the electric power for controlling the switching valve portion 31 can be reduced. That is, since the stay 92 is made of iron, the stay 92 and the magnet member 90 are not magnetized even when the stay 92 is not magnetized except when the valve body 71 is driven (when the flow path is switched). The switching force can be maintained by the suction force.

Also, as described above, during operation, the valve body 71 is held by the pressure in the switching valve chamber 30 so as not to easily rotate. Therefore, unlike the direct acting type conventional example in which the position of the sliding valve 5 is maintained by the spring and the electromagnet, it is not necessary to apply a voltage to the magnetic force switching unit 74 (electromagnet 94) during operation. Power consumption can be reduced.

Fifth, according to this compressor, the generation of noise can be reduced, and particularly when HFC type refrigerant which is a CFC substitute refrigerant is used as the refrigerant gas, there is a particularly remarkable noise prevention effect. .

That is, according to the present invention, by making the switching valve portion 31 a rotary type, it is possible to reduce the generation of the switching collision noise that occurs in the reciprocating type. In addition, the switching valve section 31
Is housed in the switching valve chamber 30 (upper case) having a large volume, so that the muffler effect of the switching valve chamber 30 (having a large capacity and being shielded from the outside even if noise occurs). The sound can be effectively prevented from leaking to the outside.

Further, the high-pressure gas port 65 and the high-pressure gas introduction pipe 32 are not directly connected to each other, but a predetermined space is provided therebetween. Therefore, the vibration of the switching valve portion 31 is rarely transmitted to the high pressure gas pipe 32. Therefore, the antivibration measures that have been conventionally required for this high-pressure gas pipe are no longer necessary.

As a result, it is possible to effectively prevent the generation of noise, and particularly when the HFC refrigerant, which is a CFC substitute refrigerant having a high sound propagation property, is used as the refrigerant gas, a particularly remarkable effect is exhibited. .

Since the high pressure gas introduction pipe 32 is not directly connected to the switching valve portion 31, the piping work of the switching valve portion 31 can be reduced, and the piping structure of the air conditioner can be reduced. There is an effect that can be simplified.

Sixth, the switching valve chamber 30 of the gas-liquid separator B
One end of a high-pressure gas introduction pipe 32 for introducing high-pressure gas into the compressor is attached to the center of the upper end wall of the first hermetic casing 25 of the compressor body A, and is opposed to the upper surface of the oil separation plate 57. I was allowed to.

As a result, it is possible to effectively prevent the lubricating oil scattered in the compressor body A from being sucked into the high pressure gas introduction pipe 32.
There is an effect that it is possible to realize a safer air conditioner with high heat exchange efficiency.

Seventh, there is an effect that the temperature of the discharge gas can be detected. That is, the conventional compressor (see FIG.
In 9), since the high pressure gas introduction pipe 32 does not exist, the temperature of the high pressure gas sucked into the switching valve 1 could not be detected. However, since the compressor of the present invention includes the high pressure gas introduction pipe 32, the temperature of the high pressure gas sucked into the switching valve portion 31 can be detected. As a result, there is an effect that the fluid compressor can be controlled more appropriately.

Eighth, even when the design of the switching valve portion 31 is changed, the design of the compressor main body A does not have to be changed, so that the production cost of this fluid compressor can be kept low. is there. For example, there is a case where the configurations of the switching valve 31 and the gas-liquid separator B are changed as shown in the second embodiment described below.

Next, a second embodiment of the present invention will be described. The same components as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted.

The fluid compressor of the second embodiment is shown in FIG.
The configuration is different from that of the first embodiment only in the gas-liquid separator B. Therefore, only the structure of the gas-liquid separator B will be described.

The second closed case 28 of this gas-liquid separator B
Is separable into an upper case 59 and a lower case 58, as in the first embodiment. However, the partition plate 60 is not provided, and the second case 28 as a whole constitutes the gas-liquid separation chamber 120.

In the gas-liquid separation chamber 120, as in the first embodiment, a suction pipe 49 which is inserted from the lower end of the lower case 58 and opens upward, and an upper opening of the suction pipe 49. And a retainer 33 provided above.

A switching valve portion 121 is attached to the upper case 59. Therefore, in this embodiment, unlike the first embodiment, the switching valve section 12 is
1 is located in the gas-liquid separation chamber 120.

Next, the switching valve portion 121 will be described. As shown in FIG. 12, the switching valve portion 121 includes a valve base 122 fixed to the upper end case 25 and a flow passage for a working fluid rotatably provided on the lower surface of the valve base 122. A valve element 123 for switching the valve element, a magnet member 72 fixed to a radially outer edge portion of the valve element 123, and a magnetic force applied to the magnet member 72 to drive the valve element 123 to switch the flow path. A portion 74 and a holder 75 that covers the switching valve portion 121 are provided.

As shown in FIG. 13, the valve base 122 has a circular shape in plan view, and has a lower end portion with a flange portion 122a having a larger diameter than the upper end portion. The valve base 122 is attached to the upper end case 59 as shown in FIG.

That is, as in the first embodiment, the upper wall of the upper case 59 is formed with a through hole indicated by 77 in the figure. The upper end of the valve base 122 is inserted into the through hole 77 so that the upper end case of the valve base 122 is inserted.
The through hole 77 is attached to the space 59 and is fixed so as to hermetically close the through hole 77 by welding, for example.

Further, as shown in FIG. 13, the valve base 122 is provided on the central axis L of the valve base 122, and the lower end side is projected into the gas-liquid separation chamber 30. The central shaft 124 is fixed. And this valve base 12
In FIG. 2, there are three porosities that pass through the valve base 122 in the axial direction at 90 ° intervals in the circumferential direction around the central axis 123.
125 to 127 are provided.

As shown in FIG. 1, the port 126 located at the center of the three ports 125 to 127 is connected to the high pressure gas introducing pipe 32 extending from the compressor main body A. High-pressure gas port (corresponding to 3 in the conventional example)
The other two ports 125 and 126 sandwiching this high pressure gas port 126 are shown in FIG.
The first and second connection ports (corresponding to 6 and 7 in the conventional example) connected to the outdoor heat exchanger and the indoor heat exchanger shown in FIG.

Incidentally, as shown in FIG. 13, the valve base 122 is circumferentially moved from the high pressure gas port 126 by 1 in the circumferential direction.
The lower end of the valve base 122 is located at a position separated by 80 °.
A stopper 129 (indicated by a mesh in the figure) that is slightly projected from the lower surface of the is embedded.

This stopper 129 is shown in FIG. 11 and FIG.
As shown in FIG. 2 (b), the upper end portion is attached to the valve base 122 by screwing. The portion of the stopper 129 projecting from the lower surface of the valve base 122 has an outer diameter slightly smaller than the inner diameters of the three ports 125 to 127.

The valve base 122 thus formed.
As shown in FIG. 12B, the lower surface of the valve body 12 is
3 is attached. The valve body 123 has a central hole 123a provided at the center thereof, and the central shaft 124 projecting from the valve base 122 is inserted into the central hole 123a, so that the upper surface of the valve body 123 is made the lower surface of the valve base 122. It abuts and is rotatably attached to the valve base 122.

On the upper surface side of the valve body 123, as shown in FIG.
As shown by reference numeral 31, two of the three ports 125 to 127 adjacent to each other at 90 ° intervals (125,
126 or 126, 127) are provided with a recessed groove communicating with each other.

As shown in the drawing, the recessed groove 131 is a passage having an inner surface formed in a semicircular cross section, and when the valve body 123 is rotated in the range of 90 °,
As shown in FIGS. 15A to 15D, the adjacent ports, that is, the high-pressure gas port 126 and the first connection port 125, or the high-pressure gas port 126, as shown in FIGS.
And the second connection port 127 can be switched to communicate with each other.

Also, the concave groove 13 of the valve body 123 is
A through hole 132 penetrating from the upper surface to the lower surface of the valve body 123 is provided at a position symmetrical with respect to 1 and the central hole 123a. The through hole 132 is provided in a shape similar to that of the concave groove 131 in plan view.

On the upper surface of the valve body 123, around the through hole 132, the valve body 123 and the valve base 1 are provided.
A seal member 132a is formed integrally with the valve base 122 to hermetically seal between the valve base 122 and the valve 22.

Further, as shown in FIG. 12B, the lower end projecting portion of the stopper 129 provided on the valve base 122 has the valve body 123 attached to the valve base 122. It is located in the through hole 132.

The stopper 129 contacts one end or the other end in the circumferential direction of the through hole 132 to move the valve body 123 in the rotating direction by 90 °, as shown in FIG. It is regulated to the range. Also,
By rotating the valve body 123 within the range of 90 °, the through hole 132 can be switched so as to communicate with the first or second connection port 125, 127.

Incidentally, the concave groove 131 and the through hole 13
From the positional relationship of No. 2, as shown in FIGS. 15A and 15B, when the first connection port 125 communicates with the through hole 132, the second connection port 127. The high pressure gas port 126 and the high pressure gas port 126 communicate with each other through the recessed groove 131.

As shown in FIGS. 15C and 15D, when the second connection port 127 communicates with the through hole 132, the first connection port 125 and the first connection port 125 are connected to each other. The high pressure gas port 126 is communicated with the concave groove 131.

Since the through hole 132 is opened to the inside of the gas-liquid separation chamber 120, the low pressure gas port 66 and the low pressure gas discharge pipe 67 in the first embodiment.
It has the same function as.

Further, as shown in FIG.
The upper end of 3 is a flange-shaped flange portion 123b protruding slightly outward in the radial direction of the valve body 123. A positioning projection 134 that engages with the magnet member 72 is formed at a predetermined position along the lower surface circumferential direction of the flange 123b.

Since the construction and operation of the magnet member 72 (color 89, permanent magnet 90) and the magnetic force switching portion 74 for driving the magnet member 72 are the same as those in the first embodiment, the same reference numerals are used. The description is omitted.

Unlike the first embodiment, the pressing member 97 attached to the lower end of the central shaft 124 does not need to hold the low-pressure gas discharge pipe, so that it may be a strip-shaped member.

Next, the control (operation) when the fluid compressor of the second embodiment described above is applied to an air conditioner will be described. First, the control during the cooling operation will be described.

During the cooling operation, as shown in the waveform diagram of FIG. 15A, the voltage applied to the electromagnet 94 of the switching valve section 121 is controlled. As a result, the station 92 located on the upper side in the figure is magnetized to the N pole, and the station 92 located on the lower side is magnetized.
Is magnetized to the S pole.

Therefore, the S pole portion 90b of the permanent magnet 90 fixed to the valve body 123 is attracted to the station 92 located on the upper side in the figure, and the N pole portion 90a is attracted to the station 92 located on the lower side. To be done. As a result, the valve body 123
Rotates counterclockwise.

When rotated by a predetermined angle, FIG. 15 (a)
As shown in FIG. 5, the stopper 129 protruding from the lower surface of the valve base 122 contacts one end of the through hole 132 of the valve body 123 in the circumferential direction, and the valve body 123 stops. As a result, the second connection port 127 and the high pressure gas port 126 communicate with each other through the concave groove 131, and the first connection port 127
The connection port 125 is opened to the inside of the gas-liquid separation chamber 120 through the through hole 132.

In this state, the motor section 2 shown in FIG.
Activate 7. By operating this electric motor unit 27,
The compression mechanism section 26 operates to compress the working fluid.
The compressed high pressure gas is discharged into the closed case 25 of the compressor body A. Then, the high-pressure fluid filled in the closed case 25 flows from the compressor main body A through the high-pressure gas introduction pipe 32 into the high-pressure gas port 126.

The high-pressure gas flowing into the high-pressure gas port 126 passes through the recessed groove 131 and the second connection port.
And then passes through the outdoor heat exchanger 19, the capillary tube 115 of the pressure reducing device, and the indoor heat exchanger 20 while sequentially changing the state to cool the room.

The gas (low-pressure gas) which has passed through the indoor heat exchanger 20 and has a low temperature and low pressure is supplied to the first connection port 12
5 through the through hole 132 provided in the valve body 123.
And is introduced into the gas-liquid separation chamber 120.

The low pressure gas is introduced into the compressor section 26 of the compressor main body A through the suction pipe 49 after liquid separation is performed in the gas-liquid separation chamber 120. Compressor section 26
The low-pressure gas introduced into the inside is again compressed by the compressor section 26 and discharged into the first closed case 25. Then, the high pressure gas port of the switching valve unit 121 is again turned on.
Port 126, recessed groove 131, and the second connection port 127.
Is introduced into the outdoor heat exchanger 19 and circulates in the pipe of the air conditioner.

During this time, the control circuit 108 is controlled as shown in the waveform chart of FIG. 15 (b). That is, the applied voltage is controlled to 0, and the pair of stations 92 are not magnetized.

Even in such a state, the state shown in FIG. 15A can be maintained as in the first embodiment. On the other hand, when stopping the cooling operation, the electric motor unit 27 is stopped. As a result, the pressure in the gas-liquid separation chamber 120 is further reduced, so that the close contact between the valve body 53 and the valve base 122 is eliminated. Further, the spring 98 is slightly compressed by the self-weight of the valve body 123, and a minute gap is generated between the valve body 123 and the valve base 122, so that the first and second connection ports 125 are formed. , 127 and the pressure in the high pressure gas port 126 will be balanced.

As a result, the valve body 52 can be easily driven with a low torque when switching to the heating operation described below. Next, control and operation during heating operation will be described.

During the heating operation, as shown in the waveform diagram of FIG. 15C, the voltage applied to the electromagnet 94 of the switching valve section 121 is controlled. As a result, contrary to the case shown in FIG. 15A, the stay 92 located on the upper side in the figure is magnetized to the S pole, and the stay 92 located on the lower side is magnetized to the N pole.

As a result, the N pole portion 90a of the permanent magnet 90 fixed to the valve body 123 is attracted to the station 92 located on the upper side in the figure, and the S pole portion 90b is located on the lower side. The valve body 123 is rotated clockwise by this.

When rotated by a predetermined angle, FIG. 15 (c)
As shown in FIG. 5, the stopper 129 protruding from the lower surface of the valve base 123 comes into contact with the other end of the through hole 132 of the valve body 123 in the circumferential direction, and the valve body 123 stops.

As a result, the first connection port 125 and the high-pressure gas discharge port 126 communicate with each other through the recessed groove 131, as opposed to the cooling operation, and the second connection port 1
27 denotes the gas-liquid separation chamber 12 through the through hole 132.
Release within 0.

When the operation of the electric motor section 27 is started in this state, the high pressure gas filled in the compressor main body A passes through the high pressure gas introduction pipe 32 and the high pressure gas port of the switching valve section 121. It flows into 126.

The high-pressure gas flowing into the high-pressure gas port 126 passes through the concave groove 131, the first connection port 125, the indoor heat exchanger 20, the capillary tube 115 of the pressure reducing device, and the like. The air is circulated to the outdoor heat exchanger 19 while sequentially changing the state to heat the room.

The low-temperature low-pressure gas (low-pressure gas) that has passed through the outdoor heat exchanger 19 flows into the second connection port 126, passes through the through-hole 132, and then the gas. It is introduced into the liquid separation chamber 120.

During this heating operation, the voltage applied to the electromagnet 94 is controlled to 0 as in the cooling operation (FIG. 15 (d)). However, even in such a state, since the stay 92 is made of iron (magnetic material), the state of 15 (c) can be maintained as in the first embodiment. There is.

With this structure, it is possible to obtain substantially the same effect as that of the first embodiment. Further, by incorporating the switching valve part 121 in the gas-liquid separation chamber 120, the following effects are obtained.

[0212] The switching valve portion 121 of the second embodiment.
Is provided in the gas-liquid separation chamber 120 which is filled with a low pressure gas unlike the first embodiment, the airtightness with the case 28 is not required as much as the first embodiment.

That is, since the pressure in the gas-liquid separation chamber 120 is close to the atmospheric pressure, gas leakage is unlikely to occur. Therefore, the work precision when mounting the switching valve part 121 is eased, and the mounting work is facilitated. Further, as compared with the first embodiment, defects due to gas leakage are less likely to occur, so that there is an effect that highly reliable operation can be performed.

Further, according to the second embodiment, since the low pressure gas discharge pipe can be omitted, there is an effect that the piping structure of the air conditioner can be simplified. It should be noted that the present invention is not limited to the above-mentioned one embodiment, and can be variously modified without changing the gist of the invention.

First, as a modification of the first embodiment, for example, a fluid compressor shown in FIG. 17 (a) can be considered. This compressor includes a switching valve chamber 30 of a gas-liquid separator B and a gas-liquid separation chamber 2
9 is not separated by a partition plate, but is separated completely independently. Even with such a configuration, the same effect as that of the first embodiment can be obtained.

Next, as a modification of the second embodiment, for example, a fluid compressor shown in FIG. 17 (b) can be considered. In this compressor, the switching valve portion 121 is not provided in the gas-liquid separation chamber 120 of the gas-liquid separator B, but the upper surface of the upper end wall of the second closed case 28 which constitutes the gas-liquid separation chamber 120. It is fixed to. The switching valve portion 121 communicates only the space defined below the valve body 123 with the gas-liquid separation chamber through a communication hole 130 shown in the drawing.

Even with such a structure, the valve body 12
Since the through hole 132 provided in No. 3 communicates with the gas-liquid separation chamber 120 through the communication hole 130, the same effect as that of the second embodiment can be obtained.

In the first and second embodiments (one embodiment), the rotatably provided valve bodies 71 and 123 are rotationally driven by the magnetic force switching of the magnetic force switching unit 74. However, the present invention is not limited to this, and another rotation drive mechanism may be used.

For example, a driven gear may be fixed to the outer peripheral surfaces of the valve bodies 71 and 123 in place of the magnet member 72, or driven teeth may be directly formed on the valve body 53, and the driven gear may be a servo gear having a drive gear. -Alternatively, it may be driven.

In the above embodiment, the magnet member 7 is used.
2 is adhered to the valve bodies 71 and 123,
The spring 98 is urged against the valve bases 69 and 122, but the present invention is not limited to this.

For example, a holding member for holding the lower surfaces of the valve bodies 71, 123 and the magnet member 72, which are combined without being adhered, is provided, and the holding member is urged upward so that the valve body 71, 123 and the magnet member 72 are integrated, and the valve bodies 71 and 123 are connected to the valve bases 69 and 1 respectively.
It may be pressed against 22.

Further, the control circuit 108 for operating the switching valve portions 31, 121 is not limited to the one shown in FIGS. 10 and 15, but any circuit capable of switching the magnetism of the magnet member. Other circuits may be used.

Further, in the above embodiment, the DC brushless motor is used as the electric motor section 27.
The present invention is not limited to this, and may be a single-phase motor.

Although the compressor body of the above-described embodiment has the two-cylinder type compressor section 26, the present invention is not limited to this and may be a one-cylinder type compressor.

Further, the swirl scroll blade and the non-swirl scroll
It may be a scroll type compressor which forms a compression space by combining with a wing and swirls the swirl scroll with respect to the non-swirl scroll to compress the fluid in the compression space. .

Furthermore, in the above-mentioned one embodiment, the compressor section A has the first hermetic casing 25, but it does not have to be hermetically sealed. In short, the above-mentioned second closed case 28
It is sufficient that the (gas-liquid separator B) is hermetically sealed and the inside thereof is filled with a high pressure gas or a low pressure gas.

Also, in the above-mentioned one embodiment, the switching valve section 3
Although the reference numerals 1 and 121 are four-way switching valves, the present invention is not limited to this, and may be three-way switching valves or five-way or six-way switching valves, for example.

[0228]

According to the first aspect of the present invention, the switching valve is provided not on the compressor body side but on the gas-liquid separator side, and the switching valve is a rotary switching valve. The height and the size can be reduced.

By providing the switching valve in the switching valve chamber as in the second to fourth inventions or in the gas-liquid separation chamber as in the sixth and seventh inventions, the piping structure can be simplified. ,
Due to the muffler effect and the like, it is possible to effectively prevent the noise generated by the switching valve from leaking to the outside.

Further, when the switching valve is provided in the switching valve chamber into which the high-pressure fluid is introduced, the pressure balance at the time of stop can be easily and quickly performed. Furthermore, when the switching valve is provided in the gas-liquid separation chamber, gas leak can be prevented, and highly reliable operation can be performed.

As in the fifth aspect of the invention, the drive means for driving the valve element of the switching valve is composed of a permanent magnet and a magnetic force generating section for switching the magnetism applied to the permanent magnet to drive the valve element. By doing so, this driving means can be downsized.

By setting the urging force as in the eighth aspect of the invention, the valve element can be switched with a low torque. Further, as in the ninth invention, by providing the high-pressure fluid introducing pipe with the temperature detecting means, the temperature of the high-pressure fluid can be detected.
It becomes possible to control this fluid compressor appropriately. Further, as in the configuration of the tenth aspect of the invention, when an HFC-based refrigerant that is a CFC substitute refrigerant having a high sound propagation property is used, it is possible to prevent noise from occurring more significantly.

[Brief description of drawings]

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

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

FIG. 3 is likewise a top view, a side view and a bottom view of the first valve base.

FIG. 4 is likewise a top view, a vertical sectional view and a bottom view showing the second valve base.

FIG. 5 is a top view, a vertical cross-sectional view, and a bottom view of the valve body.

FIG. 6 is a plan view and a longitudinal sectional view showing a magnet member.

FIG. 7 is a top view, a side view, and a front view showing a magnetic force switching unit.

FIG. 8 is a top view, a vertical cross-sectional view, and a bottom view of the pressing member.

FIG. 9 is a plan view showing a fluid compressor.

FIG. 10 is an explanatory view showing a control circuit and a control process similarly.

FIG. 11 is a vertical cross-sectional view of a fluid compressor showing a second embodiment.

FIG. 12 is a plan view, a front view, a side view, and a vertical cross-sectional view showing the switching valve section.

FIG. 13 is a top view, a side view, and a bottom view of the valve base.

FIG. 14 is a top view, a vertical cross-sectional view, and a bottom view of the valve body.

FIG. 15 is an explanatory view similarly showing a control circuit and a control process.

FIG. 16 is likewise a plan view of the fluid compressor.

FIG. 17 is a vertical sectional view showing a fluid compressor of another embodiment.

FIG. 18 is a vertical sectional view showing a conventional four-way valve.

FIG. 19 is a longitudinal sectional view showing a compressor, likewise.

[Explanation of symbols]

19 ... Outdoor heat exchanger, 20 ... Indoor heat exchanger, A ... Compressor body, 26 ... Compressor section, 27 ... Electric motor section, B ... Gas-liquid separator, 28 ... Second closed case ( Case), 29 ... gas-liquid separation chamber, 30 ... switching valve chamber, 31 ... switching valve section (switching valve,
Rotary switching valve), 32 ... high-pressure gas introduction pipe, 33 ... retainer
Na (gas-liquid separating means), 63 ... First connection port, 64 ...
Second connection port, 65 ... High pressure gas port, 66 ... Low pressure gas port, 67 ... Low pressure gas discharge pipe, 69 ... First valve base, 70 ... Second valve base -Su, 71 ... Valve, 82 ...
First switching channel, 83 ... Second switching channel, 74 ... Magnetic force switching section (driving means, magnetic force generating section), 90 ... Permanent magnet, 72
... Steer (magnetic piece), 120 switching valve chamber, 121 ... Switching valve portion (switching valve), 122 ... Valve base, 123 ... Valve body, 12
5 First connection port, 126 High pressure gas port, 127
Second connection port, 131 concave groove (communication groove), 132 through hole (communication hole).

Front page continued (72) Inventor Hideaki Tsuchiyama 336 Tatehara, Fuji City, Shizuoka Prefecture, Toshiba Corp., Fuji Factory (72) Inventor Hiroyuki Mizuno 336 Tatehara, Fuji City, Shizuoka Prefecture, Toshiba A & V Co., Ltd. (72) ) Inventor Toshihiko Funakura 336 Tatehara, Fuji City, Shizuoka Prefecture Toshiba ABY Co., Ltd.

Claims (10)

[Claims] 1. A fluid compressor having a compressor body having a compressor section for compressing low-pressure fluid, and a gas-liquid separator for separating liquid droplets contained in the low-pressure fluid, wherein the gas-liquid separator is: A closed case, a gas-liquid separating means provided in the case for separating droplets from a low-pressure fluid introduced from outside the case, and a valve body provided in the case. A fluid compressor, comprising: a switching valve that, when rotated, switches the flow path of the high-pressure fluid discharged from the compressor section and the flow path of the low-pressure fluid to the gas-liquid separating means. 2. The fluid compressor according to claim 1, wherein the case has a gas-liquid separation chamber in which the gas-liquid separation section is provided and a switching valve chamber in which the switching valve is provided. A fluid compressor having a high-pressure fluid introduction pipe for introducing high-pressure fluid from the compressor body into the switching valve chamber, and a low-pressure fluid discharge pipe for communicating the switching valve with the gas-liquid separation chamber. . 3. The fluid compressor according to claim 2, wherein the switching valve has one surface and the other surface, one surface is exposed to the outside of the case, and the other surface is located inside the case. A first valve base attached to the case in a closed state, and a first valve base penetrating the first valve base and opening on one surface and the other surface of the valve base. A second valve base having first and second ports, one surface and the other surface, and one surface facing the other surface of the first valve base; The second valve base is provided so as to penetrate therethrough, and the first valve base and the second port of the second valve base are opened on one surface and the other surface of the second valve base. A high-pressure fluid introduction port and a low-pressure fluid discharge port, which are respectively provided at predetermined angles in the circumferential direction, the other surface of the first valve base and one surface of the second valve base. Interposed between and this A valve body rotatably provided with respect to the first and second valve bases and a valve body provided on the valve body, and the valve body is rotated by a predetermined angle, whereby the first valve base of the first valve base is rotated. First and second communication holes for selectively communicating the first and second ports with the high pressure fluid introduction port or the low pressure fluid discharge port of the second valve base, respectively. A fluid compressor comprising: a drive unit that rotationally drives the valve body. 4. The fluid compressor according to claim 2, wherein the switching valve chamber has a volume capable of partitioning a space around the switching valve. 5. The fluid compressor according to claim 1, wherein the switching valve includes drive means for driving a valve body, and the drive means includes a permanent magnet provided on the valve body and the permanent magnet. And a pair of magnetic pieces arranged to face each other, and the pair of magnetic pieces are magnetized to have different polarities or switched in polarity by applying a predetermined voltage to the permanent magnets. And a magnetic force generating unit that rotationally drives the valve body via the fluid compressor. 6. The fluid compressor according to claim 1, wherein the gas-liquid separation means has a gas-liquid separation chamber filled with a low-pressure fluid, and the switching valve is provided in the gas-liquid separation chamber. A fluid compressor characterized in that a high-pressure fluid introducing pipe for introducing high-pressure fluid from the compressor body to the switching valve is connected to the switching valve. 7. The fluid compressor according to claim 6, wherein the switching valve is provided on the valve base and the valve base is attached to the case, and the switching valve is provided on the valve base. Three ports open to the inside and outside of the case and the three ports of the valve base.
A valve body rotatably provided on the inner side surface of the case where the valve opens, and a surface of the valve body facing the valve base,
The valve body is provided with a communicating groove for selectively communicating two of the three ports with each other by rotating the valve body by a predetermined angle and another port provided in the valve body. A fluid compressor having a through hole communicating with the inside of the valve and a drive means for driving the valve body. 8. The fluid compressor according to claim 3, further comprising an urging means for urging the valve element against the valve base, the urging force of the urging means stopping the compressor. At times, the fluid compressor is set to such a strength that allows a gap to be formed between the valve body and the valve base. 9. The fluid compressor according to claim 2, further comprising temperature detecting means attached to the high-pressure fluid introducing pipe and detecting a temperature of the high-pressure fluid flowing in the high-pressure fluid introducing pipe. Fluid compressor. 10. A compressor body, a flow path switching valve, an indoor heat exchanger, a pressure reducing device, and an outdoor heat exchanger, wherein the flow path switching valve is provided in a gas-liquid separator connected to the compressor body. In the air conditioner integrally provided with, the working fluid used in the air conditioner is an HFC refrigerant, and the gas-liquid separator has a case filled with a low-pressure working fluid, and the switching An air conditioner characterized in that the valve is provided in this case.