JPH1089807A - Fluid compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce vibration and noise by checking the so-called hunting phenomenon from being presented in changing over fluid paths by means of a directional control valve housed in a case body, thereby obtaining improvement in dependability and reliability. SOLUTION: The fluid compressor has, in its closed case, a compression mechanism unit, an electric motor unit 3, and a directional control valve 12 for changing over a plurality of fluid paths by utilizing a rotational driving force of the electric motor unit 3. A means adapted to transmit the rotational driving force of the electric motor unit 3 to the directional control valve 12 is a means for magnetically coupling a drive side magnet Mb provided in the electric motor unit 3 to a driven side magnet Ma provided to the directional control valve. The driven side magnet Ma is connected to the directional control valve with the aid of a transmitting shaft 60 to be driven, which is freely movable in an axial direction. This transmitting shaft 60 is brought into contact with a rotary shaft 2 of the electric motor unit 3 at one end of the transmitting shaft 60, thereby holding a gap between the drive side magnet Mb and the driven side magnet Ma.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid compressor having a compression mechanism, an electric motor, and a switching valve for switching a plurality of fluid flow paths by using the rotational driving force of the electric motor in a case body. .

[0002]

2. Description of the Related Art In an air conditioner equipped with a heat pump refrigeration cycle in which a cooling operation and a heating operation can be easily switched, the above operation can be switched by changing the flow direction of a refrigerant gas as a fluid.

[0003] The refrigerant gas flow path is changed by a four-way valve provided in a refrigeration cycle. This four-way valve
It has one inlet and three outlets arranged in series, two of which are always closed by the valve body.

[0004] The valve element is driven by an electromagnetic coil and moves within a valve housing, and changes a lead portion to be opened in response to a signal to the electromagnetic coil. That is, the refrigerant gas guided into the valve housing from the introduction portion is led out from a different lead-out portion depending on the position of the valve body, and the flow path is switched.

[0005]

The four-way valve in which the switching of the flow path is performed quickly as described above has the following disadvantages. 1) A large piping space is required due to complicated piping connections constituting the refrigeration cycle, which hinders miniaturization of the air conditioner itself.

2) Due to the complicated structure of the four-way valve, internal leaks cannot be ignored, causing performance degradation, failure induction, and high cost. 3) The structure is such that the coil for driving the valve body is constantly energized, which increases power consumption.

Therefore, for the purpose of eliminating these problems, there has been proposed a type in which a four-way valve is housed inside a case of a fluid compressor constituting a refrigeration cycle and a plurality of fluid flow paths are switched by this valve. ing.

The fluid flow path switching means of the switching valve is a magnetic coupling means for switching by a motor coupling on the driving side and a magnet coupling provided on the switching valve on the driven side.

However, in such a switching valve,
Both the drive side magnet and the driven side magnet use a magnetized permanent magnet. Therefore, the driven magnet rotates after the flow path is switched, but the drive magnet continues to rotate, and the magnets periodically repeat suction and repulsion each time the polarity becomes the same phase. There is a problem that occurs.

The present invention has been made in view of the above circumstances, and an object thereof is to prevent a so-called turbulent phenomenon from occurring when a switching valve housed in a case body switches a fluid flow path. Reduce vibration and noise,
An object of the present invention is to provide a fluid compressor capable of improving reliability and reliability.

[0011]

According to a first aspect of the present invention, there is provided a fluid compressor using a compression mechanism, an electric motor, and a rotational driving force of the electric motor in a case body. In the fluid compressor having a switching valve for switching a plurality of fluid flow paths, the means for transmitting the rotational driving force of the electric motor unit to the switching valve includes a driving magnet provided in the electric motor unit and a driven magnet provided in the switching valve. The driven magnet is connected to a switching valve via a driven transmission shaft that is movable in the axial direction, and the driven transmission shaft has one end connected to the motor unit. The gap between the driving side magnet and the driven side magnet is maintained by contacting the shaft portion of the motor.

According to a second aspect of the present invention, at least one of the driving side magnet and the driven side magnet according to the first aspect uses a magnet material other than a magnetized metal magnet material.

According to a third aspect, the driving magnet according to the second aspect is made of a non-magnetized metal magnet material, and the driven magnet is made of a magnet material other than the magnetized metal magnet material. Features.

According to a fourth aspect of the present invention, the driven transmission shaft according to the first aspect contacts a shaft portion of the electric motor unit via a sliding member. According to a fifth aspect, the driven transmission shaft according to the first aspect is made of a synthetic resin material and is formed integrally with the driven magnet.

According to a sixth aspect of the present invention, the driven transmission shaft according to the fifth aspect has a hole into which a valve shaft protruding from the switching valve is inserted, and the hole has a large taper toward the opening side. It is characterized by being formed.

According to the first aspect of the present invention, by providing means for solving the above problems, the required rotational torque is increased by the sliding resistance of the contact surface generated by the attractive force of the magnet. And the lifting of the motor rotor due to the suction force is prevented. Furthermore, smooth transmission can be obtained without the occurrence of abnormal vibration noise by eliminating the turbulence phenomenon.

According to the second aspect of the present invention, the attraction / repulsion between the magnets is achieved by utilizing the sliding resistance of the contact surface generated by the attraction force of the magnet as the rotational torque on the driven side (the driven side). The phenomenon of repetitive vibrations, that is, the phenomenon of turbulence, is eliminated, and smooth torque transmission can be obtained.

According to the third aspect of the present invention, since a metal magnet material having a high hardness and no occurrence of cracks is used as the driving side magnet, no mold is required. According to the fourth aspect of the invention, by interposing the sliding member, the wear resistance of the driven transmission shaft is improved, and the reliability is improved.

According to the fifth aspect of the present invention, since the driven magnet is integrally formed with the driven transmission shaft made of a synthetic resin material, the bearing portion can be easily installed, and inexpensive and simple assembly is possible. .

According to the sixth aspect of the present invention, the hole of the driven transmission shaft has a large taper toward the opening side.
Here, the valve shaft can be easily inserted, and assembling workability is improved.

[0021]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a fluid compressor A and an accumulator B. In the fluid compressor A, reference numeral 1 denotes a closed case which is a case body. The closed case 1 includes a main case 1a having an upper surface opened and an upper case 1b closing an upper surface opening of the main case. Be composed.

A rotating shaft 2 is rotatably supported in the sealed case 1 in the vertical direction so as to be rotatable in the vertical direction. An electric motor unit 3 is provided above the rotating shaft, and a compression mechanism (not shown) is provided below the rotating shaft.

The electric motor section 3 comprises a rotor 4 fitted to the rotating shaft 2 and a stator 5 having a narrow gap on the outer peripheral surface of the rotor and fitted to the main case 1a. Is done.

The motor unit 3 is electrically connected to an inverter device 6. The inverter device controls the rotation speed and the forward / reverse rotation of the compressor mechanism based on a control signal from the control unit 7. Is controlled.

The above-mentioned compression mechanism is a normal reciprocating type,
The compression mechanism may be a rotary type compression mechanism or a so-called scroll type compression mechanism.

In any case, the compression mechanism is provided with two cylinders, and the suction portions of each cylinder are provided with suction pipes 8a and 8a extending from an accumulator B provided in parallel with the fluid compressor A. 8b.

The discharge part of the compression mechanism part is open to the inside of the closed case 1, and compresses the low-pressure refrigerant gas sucked into the compression mechanism part from the accumulator B into high-pressure gas. High pressure type in the case.

The communication pipe 9 connected to the upper part of the accumulator A is connected to an S pipe 11 extending from the upper part of the fluid compressor A and described later. A switching valve 12, which will be described later, is housed inside the sealed case 1. The switching valve 12 is disposed in a space between the upper end surface of the electric motor unit 3 and the upper case 1b.

The switching valve 12 is mounted in a mounting hole 1b1 provided in the upper case 1b, as shown in an enlarged view in FIG. 2, and a valve body 13 whose upper surface is exposed to the outside of the closed case, 1 Valve switching assembly attached to the lower surface of the valve body inside 1
And 4.

As shown in FIG. 3, the valve body 13 is provided with an S hole 15, an E hole 16 and a C hole 17 penetrating the upper and lower surfaces 13a and 13b. Furthermore, two screw holes 1 are provided from the lower surface portion 13b to the upper middle portion.
8, 19 are provided. One screw hole 18 is located between the E hole 16 and the C hole 17. Other screw holes 19
Are located on the peripheral surface side of the S hole 15. In particular, the lower surface portion 13b is finished to an extremely flat surface. The holes 19a on both sides of the screw hole 19 are holes for positioning a stopper 24 described later.

As shown in FIGS. 1 and 2 again, the above S
The S pipe 11 described above is connected to the hole 15,
An E pipe 20 and a C pipe 21 (only one is shown) are connected to the hole 16 and the C hole 17, respectively.

As shown in FIGS. 8 and 9, the S pipe 11 is connected to the accumulator B provided in parallel with the fluid compressor A via the communication pipe 9, and
The pipe 20 is connected to the indoor heat exchanger E, and the C pipe 21 is connected to the outdoor heat exchanger C.

A throttle device K is provided in the middle of the pipe P connecting the indoor heat exchanger E and the outdoor heat exchanger C, and these constitute a heat pump type refrigeration cycle.

As shown in FIG. 2 again, a shaft 22 is screwed into one of the screw holes 18. The shaft 22 protrudes downward from the valve body lower surface portion 13b, and the components of the valve switching assembly 14 are attached thereto.

A mounting screw 23 is screwed into the other screw hole 19, and the stopper 2 constituting the valve switching assembly 14 is provided.
4 is attached. The stopper 24 is attached to the mounting screw 2
3, a mounting portion 24a screwed to the lower surface portion 13b of the valve body, and a stopper portion 24b which is vertically provided downward from the mounting portion and whose lower end portion is bent in the horizontal direction to be formed substantially in an L shape. Consists of

The valve switching assembly 14 includes the shaft 22 and the stopper 24, and a slider 25, a sleeve 26 and an upper magnet assembly 27 which are engaged with the shaft 22.

The slider 25 is formed by, for example, a plastic mold, and its upper surface 25a is in contact with the flattened lower surface 13b of the valve body 13. The shaft 22 is rotatably supported on the shaft 22, and when rotated, rotates in a state of sliding contact with the valve body 13.

As shown in FIG. 4, a mounting hole 28 penetrating from the upper surface 25a to the lower surface 25b is provided at the axis of the slider 25. In particular, the periphery of the mounting hole 28 on the lower surface portion 25b side is a concave portion 29 having a diameter larger than that of the mounting hole.

A first discharge hole 30 and a second discharge hole 31 are provided at a position separated from the shaft center position by a predetermined distance and at a position 90 degrees from each other via the shaft center. Each of the discharge holes 30 and 31 penetrates the slider 25,
The upper and lower surfaces 25a, 25b are open.

A gas passage 32 having a semicircular cross section is provided from the upper surface portion 25a to the middle portion on the lower surface portion side. The gas passage 32 is formed in an arc shape in a plan view, and has a balance port 3 opening at the lower surface portion 25b substantially at the center thereof.
3 are provided.

The shaft 2 is inserted into the mounting hole 28.
2 is loosely inserted and is rotatable in the circumferential direction of the slider 25. Depending on the position of the slider 25, the gas passage 32
Can be selected between a position simultaneously facing the S hole 15 and the E hole 16 provided in the valve body 13 and a position simultaneously facing the C hole 17 and the S hole 15.

Therefore, in any of the above states, at least the S hole 15 is opposed to the gas passage 32 and
Since the S pipe 11 connected to the hole 15 extends from the fluid compressor A and communicates with the accumulator B, the pressure in the gas passage 32 and the balance port 33 is always low.

Further, the gas passage 32 has the S hole 15 and the E hole 16.
, The first ejection hole 30 communicates with the C hole 17. When the gas passage 32 faces the C hole 17 and the S hole 15, the second discharge hole 31 communicates with the E hole 16.

The rectangular seating surface 34 between the first and second ejection holes 30 and 31 in the slider upper surface 25a.
And the seat surface 3 surrounding the mounting hole 28 and the gas passage 32
5 is to reduce the contact area of the slider upper surface 25a with the valve body lower surface 13b,
Since the seat surfaces 34 and 35 are arranged at two places with the mounting hole 28 interposed therebetween, the slider 25 is prevented from tilting.

A first notch 36 and a second notch 37 are provided in the slider lower surface 25b. These notches 36 and 37 are provided along the peripheral end of the slider 25 and have an arc shape in plan view.

The cross section along each of the notches 36 and 37 has a gradually increasing depth a from one end side to the other end, as shown in FIG. A flat portion b having the same depth is formed at the deepest portion of the other end of the portion a.

The sleeve 26 is, as shown in FIG.
A mounting hole 38 and a spring supporting hole 39 having a diameter larger than the mounting hole are connected to each other. A cylindrical first projection 40 projecting downward is integrally formed on the peripheral portion, and a second projection radially projecting around the first projection 40. 41 are integrally provided.

The center of the mounting hole 38 is 90
The semi-circular projections 42 are provided at the positions where they exist. The projections 42 are provided so as to have the same shape as and overlap with the first projection 46 and the second projection 47 of the pilot valve 43 described later.

As shown in FIG. 2 again, the shaft 22 is loosely inserted into the mounting hole 38, and the sleeve 26 is rotatably pivotally supported. A coil spring 44 as an elastic member is housed in a space formed between the peripheral surface of the shaft 22 and the spring support hole 39.

The coil spring 44 protrudes from the upper surface of the sleeve 26, abuts against the concave portion 29 provided on the slider lower surface 25b, and elastically supports the slider. The slider 25 is pushed up and the valve body 1
3 are brought into sliding contact with each other in a state where a constant frictional force is generated.

The second protrusion 41 of the sleeve 26 is
Depending on the rotational position of the sleeve, the valve body 13
The stopper 24 is attached to the stopper portion 24b of the stopper 24 so that rotation in the stopper direction is prevented.

As shown in FIG. 6, most of the pilot valve 43 is a plate having an extremely thin plate thickness (about 0.3 mm), and is made of a material having elasticity in the plate thickness direction. The shaft has a mounting hole 45 having four flat surfaces.

A first protrusion 46 having a circular shape larger than a semicircle and a second protrusion 4 at a position 90 ° apart from the axis.
7 are provided. These first and second projections 46,
A driver 49 having a hollow boss 48 at the tip thereof is integrally provided at an intermediate portion of 47.

As shown in FIG. 2 again, the pilot valve 43 has a mounting hole 45 fitted to one end of the sleeve 26. Pilot valve 4 for sleeve 26
3 is determined by fitting the mounting hole 45 into the sleeve 26. As described above, the first and second protrusions of the pilot valve 43 are provided on the respective protrusions 42 and 42 of the sleeve 26. 46 and 47 are correctly aligned.

In the assembled state, the pilot valve 43
Are in close contact with the slider lower surface 25b. Therefore, depending on the position of the pilot valve 43, the first and second
Either one of the projections 46 and 47 is
The balance port 33 opening to 5b is opened and closed.

When the first projection 46 closes the balance port 33, the boss 48 of the driver 49 is positioned on the flat portion b of the first notch 36, and the second projection 4
7 closes the balance port 33, the boss 4
8 is set so as to be located on the flat portion b of the second cutout portion 37.

For example, the state where the boss portion 48 is located at the flat portion b of each of the notches 36 and 37 is changed to the inclined portion a.
When the pilot valve 43 attempts to rotate in the circumferential direction on the opposite side (clockwise direction in FIG. 4C), the slider 25 is urged to rotate in the same direction due to the shape of each notch. become.

That is, the first and second notches 36 and 37 of the slider 25 and the driver 49 of the pilot valve 43 constitute a feed mechanism 50 for urging the slider 25 to rotate.

A stop ring 51 is provided at an intermediate portion of the shaft 22 to prevent the slider 25 and the sleeve 26 from falling off. Shaft 2
The reference numeral 2 extends further downward from the stop position of the sleeve 26 and is loosely fitted into an upper magnet assembly 27 described later.

As shown in FIGS. 2 and 10, the upper magnet assembly 27 includes a driven transmission shaft 60 made of a synthetic resin, a yoke Y and a driven magnet integrally formed with the driven transmission shaft 60. And Ma.

The driven transmission shaft 60 will be further described. On the upper surface protruding from the yoke Y, a ridge 60a is provided.
Are integrally provided. The ridge 60a is set so as to abut the first ridge 40 of the sleeve 26 depending on the rotational position of the valve switching assembly 14.

The engaging hole 60b provided along the axis of the driven transmission shaft 60 has a shaft 2
2 is formed in a diameter to be loosely inserted. This hook hole 6
The upper part of the drawing of 0b is a tapered portion 60c whose diameter is increased toward the opening surface which is the upper end surface. A lower portion of the engaging hole portion 60b serves as a relief portion 60d, and a gas vent portion 60e formed by cutting out from the relief portion to the outer peripheral surface is provided.

The outer peripheral portion of the driven transmission shaft 60 is formed so as to protrude only at the central portion in the vertical direction. They are superimposed in a state, and only these inner peripheral portions are buried integrally.

The lower end of the driven transmission shaft 60 of the upper magnet assembly 27 is inserted into the inner periphery of the rotor 4 constituting the motor unit 3 and is a sliding member having a smooth characteristic. Rotating shaft 2 via moving plate 61
It is placed on the upper end of the.

The shaft 22 protruding from the lower portion of the sleeve 26 of the valve switching assembly 14 is inserted into the engaging hole 60b via the tapered portion 60c of the driven transmission shaft 60 constituting the upper magnet assembly 27.

The tapered portion 60c is connected to the driven transmission shaft 60.
Because it is formed with a large diameter toward the opening side of the upper surface,
From here, the shaft 22 can be inserted very easily, and the assembling work is simple.

On the other hand, the rotor 4
The lower magnet assembly 52 is mounted on the upper surface of the lower magnet assembly.
The lower magnet assembly 52 includes a driving magnet M
b and the magnet holder 53 are vertically stacked,
It is mounted on the upper surface of the rotor. Then, the driving-side magnet Mb and the magnet holder 53 are fastened to the rotor 4 by using the rivet 56 for caulking the rotor 4.

In this state, the gap GL between the upper surface of the driving magnet Mb and the lower surface of the driven magnet Ma is the distance P from the lower surface of the driven magnet Ma to the upper surface of the sliding plate 61, the thickness t of the sliding plate 61, Side magnet Mb
When the distance L from the upper surface to the sliding plate 61 is defined as GL = (P + t) -L.

That is, the lower magnet assembly 52 and the upper magnet assembly 27 have a small gap GL under the magnetic influence of each other. When setting the gap GL, as shown in the above equation, the gap GL is set based on each dimension based on the upper end surface of the rotating shaft 2, so that the gap GL can be extremely narrow and the variation can be reduced.

One of the driving magnet Mb of the lower magnet assembly 52 and the driven magnet Ma of the upper magnet assembly 27 is made of a non-magnetized metal magnet material, and the other is a magnetized metal magnet. A feature is that a magnet material other than the magnet material is used.

Here, the driving magnet Mb is
A non-magnetized metal magnet material is used. As this metal magnet material, there is an alnico material or an iron-chromium-cobalt material, which has an extremely high hardness and does not cause any cracking or chipping even when drilling.

Therefore, as described above, the drive-side magnet Mb can be directly mounted and fixed by using the rivet 56, so that it is not necessary to fix the resin mold like the driven-side magnet Ma, and it is troublesome to mount and the mounting parts. Get reductions.

As the driven magnet Ma, a magnet material other than a magnetized metal magnet material is used. That is, the rare earth magnet material, the oxide magnet material, and the bond magnet material are magnet materials other than the metal magnet material.

The rare earth magnet material includes rare earth cobalt, the oxide magnet material includes barium ferrite and strontium ferrite, and the bond magnet material includes oxide and rare earth cobalt. Since this mounting is liable to be cracked or chipped, a resin molding material (the driven transmission shaft 27) is required as described above.

The magnet holder 53 interposed between the driving magnet Mb made of a non-magnetized metal magnet material and the rotor 4 constituting the electric motor section 3 must be made of a non-magnetic material. Must.

The driven magnet Ma of the upper magnet assembly 27 and the drive magnet Mb of the lower magnet assembly 52 constitute a magnet coupling 54 as a magnetic coupling means. The magnet coupling 54 is housed in the upper coil end 5a of the stator 5 constituting the electric motor.

Next, the operation of the fluid compressor A, the operation of the switching valve 12 housed in the compressor and the heat pump type refrigeration cycle will be described. The motor unit 3 in the fluid compressor A is started, and the compression mechanism performs the compression operation of the refrigerant gas. For example, when the rotation shaft 2 rotates forward (clockwise as viewed from below), the upper magnet assembly 27 is torque-transmitted and rotates with the lower magnet assembly 52 in a non-contact state due to the configuration of the magnet coupling 54.

That is, when the driving magnet Mb rotates together with the rotor 4, the non-magnetized driving magnet Mb is magnetized by the magnetic field of the driven magnet Ma which is a magnetized product.

However, since the driving magnet Mb is not magnetized, it does not have the same phase as the magnetic field of the magnetized driven magnet Ma and has a certain phase difference, and the magnetic hysteresis phenomenon occurs. The torque is transmitted in the state where the torque is generated.

To explain, the upper magnet assembly 2
7, the driven magnet M is driven by the driven magnet Ma.
b, a magnetic attraction force acts. A part of the upper magnet assembly 27 is in contact with the rotating shaft 2 via the sliding plate 61, and the magnetic attractive force applies a load F to the contact portion.

This load F is applied to the upper magnet assembly 27.
It is determined by the magnetic flux density and the attracting cross-sectional area generated between the magnet and the drive-side magnet Mb. The rotational torque T is given by: T = FS · S
is determined by μ.

Since the rotational torque is applied only in the rotational direction on the drive side, no turbulent phenomenon occurs in the magnet coupling 54, and no abnormal vibration and noise occur. The rotation of the upper magnet assembly 27 is smooth and quiet.

Since the magnet holder 53 made of a non-magnetic material is interposed between the driving magnet Mb and the rotor 4 as the lower magnet assembly 52, even in the DC brushless motor structure using a magnet for the rotor 4, this rotor It is not affected by the magnetic flux leakage of the magnet.

When the upper magnet assembly 27 rotates forward,
The ridge 60a of the driven transmission shaft 60 is
When the sleeve abuts on the peripheral surface of the projection 40, the sleeve is synchronously rotated forward. After one rotation, the side surface of the second protrusion 41 abuts against the stopper portion 24b of the stopper 24, and the rotation of the sleeve is prevented.

As shown in FIG. 7A, at this time, the pilot valve 43 integrated with the sleeve 26 has a boss portion 48 at the tip of a driver 49 and a flat portion of a first notch portion 36 provided on the slider 25. b.

In this position, the balance port 33 provided on the slider lower surface 25b is closed by the second projection 47 of the pilot valve 43 as described later. Such a position of the slider 25 is called, for example, a position L.

On the other hand, in this position L, in the slider upper surface 25a, the gas passage 32 is
Are in communication with both the S hole 15 and the E hole 16 provided in the slider, and the C hole 17 communicates with the second ejection hole 31 of the slider.

While the slider 25 holds the L position, the upper magnet assembly 27 does not rotate because the tip of the driver 49 is abutted against the stopper portion 24b, but the lower magnet assembly 52 rotates freely. That is,
The compression mechanism draws in and compresses the low-pressure refrigerant gas from the accumulator B, converts it into high-pressure gas, and discharges it into the closed case 1.

The high-pressure gas filling the closed case 1 is supplied to the second discharge hole 31 of the slider 25 and the C
As shown in FIG. 8, the water is discharged from the hole 17 to the outdoor heat exchanger C via the C pipe 21.

The high-pressure gas refrigerant is condensed in the outdoor heat exchanger C, converted into a liquid refrigerant, guided to the expansion device K, expanded under reduced pressure, and then guided to the indoor heat exchanger E. In this indoor heat exchanger E,
It exchanges heat with the air to be conditioned to be blown here and evaporates. The heat exchange air is blown into the room to be air-conditioned in a state where the latent heat of evaporation has been taken away and dehumidified at a low temperature. That is, at the position L, the cooling operation for the air-conditioned room is performed.

The refrigerant evaporated in the indoor heat exchanger E is E
It is led to the fluid compressor A via the pipe 20. However, the E hole 16 to which the E pipe 20 is connected communicates with the S hole 15 by the gas passage 32 of the slider 25.
The evaporated refrigerant is guided from the E pipe 20 to the S hole 15 and the S pipe 11 via the gas passage 23.

That is, although the low-pressure evaporated refrigerant is once guided to the fluid compressor A, it immediately exits the fluid compressor and is introduced into the accumulator B immediately thereafter. Here, gas-liquid separation is performed, and the liquid is again guided to the compression mechanism of the fluid compressor A as described above.

Incidentally, 55 shown in the figure is an indoor heat exchanger temperature sensor, 56 is an outdoor heat exchanger temperature sensor, 57 is a first pressure sensor, and 58 is a second pressure sensor. These sensors 55 to 58 are all electrically connected to the above-described control unit 7 shown in FIG. 1 and constitute monitoring means M for transmitting a detection signal.

To switch from the cooling operation to the heating operation, the slider 25 is finally switched to a state called, for example, a position H shown in FIG. This switching procedure is as described below.

When an operation switching command signal is input to the control unit 7 from an operation unit such as a remote controller (not shown), the control unit 7 performs control to temporarily stop the operation of the motor unit 3 of the fluid compressor A as a first step. Eggplant

Immediately thereafter, as a second step, the control section 7 controls the electric motor section 3 to perform reverse rotation drive. When the lower magnet assembly 52 provided in the motor unit 3 rotates in the reverse direction, the upper magnet assembly 27 that forms the magnetic coupling is also driven to rotate in the same direction (counterclockwise).

When the upper magnet assembly 27 makes one rotation in the same direction, the ridge 60a of the driven transmission shaft 60 abuts the first projection 40 of the sleeve 26 and the side surface on the opposite side to the former. The sleeve is urged to rotate in the same direction.

The pilot valve 43 integral with the sleeve 26 also rotates in the same direction, and the boss 48 of the driver 49 moves from the flat portion b of the first notch 36 to the inclined portion a,
Get out of here. Therefore, during this time, the slider 2
The position of 5 is kept unchanged from before.

As the pilot valve 43 moves, the second protrusion 47 separates from the balance port 33 of the slider 25, and this port is opened. Therefore, a part of the high-pressure gas filling the closed case 1 is guided to the opened balance port 33 and further flows to the gas passage 32 communicating with this port.

Thus, the pressure difference on the slider 25 is eliminated, and the slider is moved to the valve body 13.
The force pressed against the side is removed. That is, the frictional force between the slider upper surface portion 25a and the valve body lower surface portion 13b is released, and preparations are made for rotation with an extremely small torque.

Further, the rotation of the pilot valve 43 continues with the sleeve 26, and the driver boss portion 48
After being separated from the notch 36 of the second notch 37 and once falling into the flat portion b of the second notch 37, the second notch 37 stops at the position reaching the inclined portion a.

As shown in FIG. 7 (B), when the sleeve 26 has made one rotation, the side of the second projection 41 opposite to the previous one is stopped by the stopper 24, and this rotation is stopped. .

In the above gas balance step, the motor unit 3 may be energized to maintain a state where torque is applied.
In addition, there is no functional problem even if the power is turned off. Next, as a third step, the control unit 7 controls the driving of the electric motor unit 3 in the forward rotation direction.

Therefore, the ridge 6 of the driven transmission shaft 60
Oa makes one rotation away from the first projection 40 of the sleeve 26, and again contacts the opposite side surface of the first projection to rotate the sleeve in the same direction.

As shown in FIG. 7C, the pilot valve 43 integral with the sleeve 26 also rotates in the same direction, and the driver boss 48 moves from the inclined portion a of the second notch 37 to be flat. It engages with the part b.

Due to the shape of the notch 37, the slider 25 rotates in the same direction as the pilot valve 43 moves. That is, the feed mechanism 50 operates. In this state, the first projection 46 closes the balance port 33, and the flow of the high-pressure gas to the gas passage 32 is shut off.

Along with the upper magnet assembly 27, the sleeve 26, the pilot valve 43 and the slider 25 simultaneously rotate in the same direction. After one rotation, the second protrusion 41 of the sleeve 26 is stopped by the stopper 24.

As shown in FIG. 7D, when the rotation of the sleeve 26 stops, the pilot valve 43 stops rotating at the same position. Of course, the upper magnet assembly 27 and the slider 25 also stop. This state is called, for example, position H.

In this position H, in the slider upper surface 25a, the gas passage 32 communicates with both the S hole 15 and the C hole 17 provided in the valve body 13, and the E hole 1
6 is communicated with the first ejection hole 30 of the slider 25.

Further, the closed state of the balance port 33 by the first projection 46 is maintained, and therefore, gas balance is not achieved. While the slider 25, the sleeve 26 and the upper magnet assembly 27 hold the H position, the upper magnet assembly 27 does not rotate, but the lower magnet assembly 52 rotates freely.

As shown in FIG. 9, the compression mechanism sucks low-pressure refrigerant gas from the accumulator B, compresses it, converts it into high-pressure gas, and discharges it into the closed case 1. Sealed case 1
The high-pressure gas filling the inside of the E pipe 20 flows through the first discharge hole 30 of the slider 25 and the E hole 16 of the valve body 13.
And is guided to the indoor heat exchanger E.

The heat is condensed in the indoor heat exchanger E, and the heat of condensation is released to the heat exchange air. The heat exchange air rises in temperature and is blown out to the room to be conditioned. That is, at position H,
A heating action is performed on the room to be conditioned.

The refrigerant liquefied in the indoor heat exchanger E is guided to the expansion device K, where it is expanded under reduced pressure, and then guided to the outdoor heat exchanger C to evaporate. Then, the fluid is guided to the fluid compressor A via the C pipe 21.

The C hole 17 to which the C pipe 21 is connected communicates with the S hole 15 through the gas passage 32 of the slider 25, and the evaporative refrigerant flows from the C pipe 21 through the gas passage 32 to It is led to 11.

That is, the evaporative refrigerant is once guided to the fluid compressor A, and then exits the fluid compressor and is introduced into the accumulator B. Here, gas-liquid separation is performed, and the liquid is again guided to the compression mechanism of the fluid compressor A as described above.

Next, in order to switch from the heating operation mode to the cooling operation mode, the state shown in FIG.
(C)-(A) may be repeated. As a result, the slider 25 returns from the position H to the position L.

In the above embodiment, the sliding plate 61 is interposed between the end of the rotating shaft 2 and the driven transmission shaft 60, and the thickness of the sliding plate 61 is adjusted to the driving magnet Mb and the driven magnet Ma. Is set as one of the conditions for setting the gap, but the present invention is not limited to this.

That is, in this modified embodiment, as shown in FIG. 11, the driven transmission shaft 60A has its lower end portion shortened to the length where the shaft 22 projects. Then, a newly provided magnet holder 62 is fitted to the lower end of the shaft 22 protruding from the driven transmission shaft 60A. (Note that the same parts as those in the above embodiment are denoted by the same reference numerals and will not be described again.) The magnet holder 62 is formed in an inverted hat shape in cross section, and the upper end flange portion is driven to transmit power. It is in contact with the lower surface of the shaft 60A. A claw portion 62 a that is bent inward is provided in the peripheral portion, and is elastically engaged with the shaft 22.

Further, as shown in FIG.
When the compression mechanism 65 disposed in the lower portion is of a rotary type, the eccentric portion 2 a provided on the rotating shaft 2 via the roller 67 is accommodated in the cylinder chamber 66.

The end portions 2b and 2c are integrally formed on the upper and lower portions of the eccentric portion 2a, and these are located in the roller 67 together with the eccentric portion. Due to its own weight, especially the lower end portion 2c rests on the sub-bearing 68, but the upper end portion 2b has a gap with the main bearing 69.
This gap is called an end pre-E.

Here, the distance between the upper surface of the drive side magnet Mb and the upper end surface of the rotary shaft 2 is L, and the distance between the driven side magnet Ma
Assuming that the distance between the lower surface and the end face of the magnet holder 62 is n, the distance GL between the driving magnet Mb and the driven magnet Ma is determined by GL = (n + E) -L.

In other words, in the embodiment shown in FIGS. 11 and 12, it is possible to set the gap GL which is small and has no variation by the assembling method described below. Shaft 2
2 and the upper magnet assembly 27 is inserted into the switching valve 12.
The upper case 1b provided with is attached to the main case 1a. Then, the lower end surface of the magnet holder 62 comes into contact with the upper end surface of the rotating shaft 2, and the upper magnet assembly 27 is lifted together with the magnet holder 62 toward the rotor 4. However, in this state, the lower end surface of the magnet holder 62 remains in contact with the upper end surface of the rotating shaft 2.

Here, the entire compressor is displaced upside down. Then, since the rotating shaft 2 has a margin to move in the axial direction by the amount of the above-mentioned emblem E, the end surface of the rotating shaft 2 is opposed to the magnet holder 62 by its own weight of the rotor 4 integrally formed with the rotating shaft 2. Move to the rotor side by the end pre-E.

Since the shaft 22 is screwed and fixed to the valve body 13 constituting the switching valve 12, the magnet holder 62 is moved by the end shaft E by the rotary shaft 2 and the shaft 22
, And is restricted by the claw portion 62a so as not to move to the rotor side. Magnet holder 6
Driven transmission shaft 60A supported by the second flange portion
Is also held in that position.

Then, again, the whole compressor is turned upside down,
Return to normal state. The rotary shaft 2 returns to the state shown in FIG. 12, and a gap for the end pre-E is secured between the upper end portion 2b and the main bearing 69.

On the other hand, the magnet holder 62 is in the state shown in FIG. 11, and a gap corresponding to the end pre-E is formed between the lower end face of the magnet holder 62 and the upper end face of the rotary shaft 2, and the drive side magnet Mb The gap GL between the driven side magnet Ma and the gap GL is accurately secured based on a relational expression of GL = (n + E) -L.

Therefore, according to the above-described assembling method,
The gap GL between the magnets can be ensured with high accuracy, and the magnet holder 62 does not slide on the rotating shaft 2 during operation, so that sliding loss does not occur and reliability can be improved.

In the present invention, an example of application to a four-way valve has been shown and described as being effective as a multi-stage valve device.
The present invention is not limited to this, and application to a three-way valve or a so-called unloader function is also possible.

[0129]

As described above, according to the first aspect of the present invention, a drive side magnet and a driven side magnet are provided in a motor section as a fluid flow path switching means of a switching valve, and the driven side magnet is a shaft. The driven transmission shaft is connected to a switching valve via a driven transmission shaft that is movable in one direction, and one end of the driven transmission shaft is brought into contact with the shaft portion of the electric motor to maintain a gap between the driving magnet and the driven magnet. Therefore, the required rotational torque can be increased by the sliding resistance of the contact surface generated by the attractive force of the magnet, and the lifting of the motor rotor by the attractive force is prevented. Then, there is an effect that smooth transmission can be obtained without the occurrence of abnormal vibration noise due to the elimination of the turbulence phenomenon.

According to the second aspect of the present invention, since at least one of the drive side magnet and the driven side magnet uses a magnet material other than the magnetized metal magnet material, the sliding resistance of the contact surface generated by the attraction force of the magnet. Is used as the rotational torque on the driven side (the driven side) to eliminate the phenomenon of turbulence and to obtain a smooth torque transmission.

According to the third aspect of the present invention, the driving magnet is made of a non-magnetized metal magnet material, and the driven magnet is made of a magnet material other than the magnetized metal magnet material. Since a metal magnet material that does not generate cracks is used, a mold is not required.

According to the fourth aspect of the present invention, the driven transmission shaft is brought into contact with the shaft portion of the electric motor section via the sliding member, so that the wear resistance of the driven transmission shaft can be improved by interposing the sliding member. And reliability can be improved.

According to the fifth aspect of the present invention, since the driven transmission shaft is formed integrally with the driven magnet as a synthetic resin material, the bearing portion can be easily installed, and inexpensive and simple assembly becomes possible.

According to a sixth aspect of the present invention, the driven transmission shaft has a hole into which the valve shaft protruding from the switching valve is inserted, and this hole is formed in a large tapered shape toward the opening side. The valve shaft can be easily inserted into the hole of the drive transmission shaft, and assembling workability is improved.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a fluid compressor according to an embodiment of the present invention, with a part thereof omitted;

FIG. 2 is a longitudinal sectional view of a switching valve and a magnetic coupling of the embodiment.

FIG. 3A is a longitudinal sectional view of a valve body constituting a switching valve according to the embodiment. (B) is a bottom view of the valve body.

FIG. 4A is a top view of a slider constituting the switching valve according to the embodiment. (B) is a longitudinal sectional view of the slider.
(C) is a bottom view of the slider, and (D) is a view in which a notch provided in the slider is developed and longitudinally sectioned.

FIG. 5A is a bottom view of the sleeve constituting the switching valve according to the embodiment; (B) is a side view in which the sleeve is partially cut away.

FIG. 6A is a longitudinal sectional view of a pilot valve constituting the switching valve according to the embodiment; (B) is a bottom view of a pilot valve.

FIGS. 7A to 7D are diagrams sequentially illustrating a switching operation of a switching valve according to the embodiment;

FIG. 8 is a configuration diagram of a refrigeration cycle in a cooling operation mode of the embodiment.

FIG. 9 is a configuration diagram of a refrigeration cycle in a heating operation mode according to the embodiment.

FIG. 10 is an explanatory view for assembling a switching valve and a magnetic coupling according to the embodiment;

FIG. 11 is an explanatory view for assembling a switching valve and a magnetic coupling according to another embodiment.

FIG. 12 is a longitudinal sectional view of a compression mechanism of the fluid compressor according to the embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Closed case, 3 ... Electric motor part, 12 ... Switching valve, Mb ... Drive side magnet, Ma ... Driven side magnet, 54 ... Magnet coupling, 60 ... Driven transmission shaft, 2 ... Rotating shaft, 61 ... Sliding member (Sliding plate), 22: valve shaft, 60b: engaging hole, 60c: taper.

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Masao Ozu 336 Tatehara, Fuji City, Shizuoka Prefecture Toshiba Corporation Fuji Plant

Claims (6)

[Claims] 1. A fluid compressor comprising a case body, a compression mechanism, an electric motor, and a switching valve for switching a plurality of fluid flow paths by using a rotational driving force of the electric motor. The means for transmitting the driving force to the switching valve is a magnetic coupling means of a driving magnet provided in the electric motor section and a driven magnet provided in the switching valve, and the driven magnet is movable in the axial direction. The driven transmission shaft is connected to a switching valve via a driven transmission shaft, and the driven transmission shaft has one end thereof in contact with a shaft portion of the electric motor unit to maintain a gap between the driving magnet and the driven magnet. A fluid compressor, characterized in that: 2. The fluid compressor according to claim 1, wherein at least one of the driving side magnet and the driven side magnet is made of a magnet material other than a magnetized metal magnet material. 3. The driving magnet according to claim 2, wherein the driving magnet is made of a non-magnetized metal magnet material, and the driven magnet is made of a magnet material other than the magnetized metal magnet material. Fluid compressor. 4. The power transmission shaft according to claim 1, wherein the driven transmission shaft contacts a shaft portion of the motor unit via a sliding member.
A fluid compressor as described. 5. The fluid compressor according to claim 1, wherein the driven transmission shaft is made of a synthetic resin material and is formed integrally with the driven magnet. 6. The driven transmission shaft has a hole into which a valve shaft protruding from the switching valve is inserted, and the hole is formed in a large tapered shape toward the opening side. The fluid compressor according to claim 5.