JP3205673B2 - Refrigerant flow divider - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant diverter for branching a refrigerant flow into a plurality of paths in a refrigerant flow circuit such as a compression refrigerator, and more particularly to a refrigerant circuit in which a refrigerant flow rate changes. The present invention relates to a refrigerant flow divider to be used.

[0002]

2. Description of the Related Art A compression refrigeration method is known as a cooling method utilizing a heat change caused by compression or expansion of a substance in a gaseous state and absorption and release of heat caused by a phase change between a liquid phase and a gas phase. It is used in various cooling devices including equipment.
The compression refrigeration system circulates a phase-change medium, that is, a refrigerant, in a closed circuit, and performs a cycle of compression, condensation, evaporation, and expansion of the refrigerant in the circulation path to cool the object to be cooled.

FIG. 1 schematically shows the basic structure. First, a refrigerant in a gaseous state is compressed by a compressor.
Although the temperature of the compressed refrigerant increases, most of the refrigerant is liquefied by being externally cooled in the condenser. The cooled liquid-phase and gas-phase two-phase refrigerant exchanges heat with the object to be cooled in the heat exchanger to cool the object. The cooling target here is, for example, room air in the case of an air conditioner. The heat taken from the target is absorbed as heat of vaporization when the refrigerant changes from a liquid phase to a gas phase. Almost all of the refrigerant after heat exchange is in a gaseous state, which is compressed again by the compressor,
Condensed in the condenser and circulated.

In the heat exchanger, a heat transfer tube for passing a refrigerant and exchanging heat between the refrigerant and an object to be cooled is provided. Heat exchange is more efficient as the flow path of the refrigerant is longer, that is, as the total path of the heat transfer tubes is longer. Further, as the surface area per unit volume of the refrigerant is larger, that is, as the diameter of the heat transfer tube through which the refrigerant flows is smaller, the heat exchange efficiency is improved. For this reason,
A method has been adopted in which a coolant flow path is branched into a plurality of channels and a plurality of heat transfer tubes are arranged in a heat exchanger. In recent years, heat transfer tubes have been remarkably reduced in diameter and diversified in order to diversify and downsize cooling systems.

A plurality of paths for the refrigerant flowing through the heat exchanger are provided by installing a refrigerant flow divider before the refrigerant flows into the heat exchanger as shown in FIG. The path of the refrigerant discharged from the refrigerant flow divider requires the number of heat transfer tubes of the heat exchanger.

FIG. 24 shows an example of a refrigerant divider having the simplest structure.
Shown in The refrigerant flow divider 31 is provided with an inflow pipe 33 for flowing the refrigerant into one end of a flow distributor main body 32 having a hollow inside, and a plurality of outflow pipes 34 for flowing the refrigerant to the other end.
The outlet pipes 34 are respectively connected to the heat transfer pipes of the heat exchanger.
The refrigerant flowing from the inflow pipe 33 passes through the inside of the main body 32, branches into a plurality of paths, and flows through the outflow pipe 34 to the heat exchanger.

[0007] Before the refrigerant flows into the refrigerant flow divider 31,
Although it is liquefied in the condenser, it is not completely in the liquid phase, but in a state where the liquid phase and the gas phase are mixed. Although the flow is divided by the flow divider 31 in the two-phase state, this causes the following problem.

[0008] The liquid phase and the gas phase tend to separate from each other by nature, and it is difficult to form a uniformly mixed state. That is, since the liquid phase has a property of assembling in the liquid phase and the gas phase has the property of assembling in the gas phase, the distribution of the liquid phase and the gas phase is also biased inside the refrigerant flow divider 31.
Although the refrigerant flows inside the flow divider, it moves with an uneven distribution and reaches the outflow pipe 34. Therefore, an equal amount of refrigerant does not flow through each outflow pipe 34, and depending on the mounting position, a refrigerant in which a large amount of gas flows and a liquid in which a large amount of liquid flows.

[0009] This phenomenon is referred to as refrigerant drift, and when drift occurs, a difference occurs in the amount of refrigerant flowing through each heat transfer tube in the heat exchanger. Since a heat transfer tube through which a refrigerant containing a large amount of gas phase flows has a small amount of liquid phase refrigerant, even if all of the gas is vaporized, heat taken from a cooling target cannot be absorbed as vaporization heat, and the temperature rises. On the other hand, in a heat transfer tube through which a refrigerant containing more than a predetermined amount of liquid phase flows due to drift, a large amount of low-temperature liquid-phase refrigerant is present even after the refrigerant has passed through all the paths of the heat transfer tube.

[0010] For this reason, heat exchange becomes uneven for each heat transfer tube, and the heat exchange efficiency in the heat exchanger is reduced. Further, there is a problem that condensation occurs in the heat transfer tube in which a large amount of low-temperature liquid-phase refrigerant remains.

Several improvements have been made to the refrigerant flow divider to overcome these disadvantages due to drift.

A throttle valve 35 is provided inside a main body 32 of the refrigerant distributor 31 shown in FIG. This shunt 3
1 forcibly causes the refrigerant to pass through the small-diameter port 35a of the throttle valve 35, thereby segmenting the gas phase, and stirring the refrigerant inside the main body 32 by the high-speed refrigerant flow to homogenize the refrigerant. It is intended to suppress drift.

The inflow pipe 33 of the refrigerant flow divider 31 shown in FIG.
The vicinity of the connection with the main body 32 is constituted by a plurality of small diameter pipes 33a. The small diameter tubes 33a are bundled in a spiral shape. The refrigerant flowing into the flow divider main body 32 from the inflow pipe 33 passes through the small-diameter pipe 33a to be divided into a gas phase and a liquid phase. Furthermore, by the spiral arrangement of the small diameter pipe 33a,
The refrigerant that has flowed into the main body 32 moves toward the outflow pipe 34 while rotating helically, during which the refrigerant is agitated so that the liquid phase and the gaseous phase are uniformly mixed, and occurrence of drift is suppressed.

As described above, attempts to suppress the occurrence of drift in the flow divider and improve the heat exchange efficiency in the heat exchanger have been successful to some extent.

[0015]

However, the occurrence of the drift is greatly affected by the flow rate of the refrigerant. Figure 25 above
26 is configured so that the gas phase and the liquid phase are uniformly mixed by stirring the refrigerant inside the main body 32 in order to cause an equal amount of the refrigerant to flow out from each outflow pipe 34. I have. If there is a certain amount of refrigerant flow, this agitation is performed as scheduled, resulting in uniform mixing of the refrigerant. However, a positive stirring mechanism is not provided, and the stirring is performed using the flow rate of the refrigerant. Therefore, if the flow rate of the refrigerant is small, the desired stirring effect cannot be obtained.

With the throttle valve 35 shown in FIG. 25, a small-diameter port 35a having a smaller hole area than the inner cross-sectional area of the inflow pipe 33 is provided.
Since the speed of the refrigerant passing through is increased, the refrigerant after passing through is stirred. However, as the amount of the refrigerant flowing from the inflow pipe 33 decreases from the predetermined amount, the flow velocity of the refrigerant passing through the small-diameter port 35a also decreases, and the stirring efficiency also decreases. Conversely, when a larger amount of refrigerant flows in than the predetermined amount, the high-speed refrigerant flow passing through the small-diameter port 35a directly reaches the outflow pipe 34, and the amount of refrigerant flowing out differs depending on the mounting position of the outflow pipe 34. obtain.

In the case where the inflow pipe 33 shown in FIG. 26 is formed by a small diameter pipe 33a, the bundle of the small diameter pipes 33a is formed in a helical shape, whereby the refrigerant flowing into the main body 32 is swirled, whereby stirring is performed. Also in this case, if the flow rate of the refrigerant is reduced, the desired stirring efficiency cannot be obtained because the flow rate of the refrigerant from the small-diameter pipe 33a is low.

In any of the examples, the effect of promoting the mixing of the solvent by subdividing the gas phase and the liquid phase remains,
This also decreases as the flow rate of the refrigerant decreases. As described above, in the refrigerant distributor having the fixed diameter throttle valve and the fixed means for restricting the refrigerant flow path, it is possible to effectively mix the refrigerant in accordance with the change in the flow rate of the refrigerant and suppress the occurrence of the drift. Have difficulty.

In particular, recently, an inverter-type cooling device that changes the flow rate of a refrigerant according to a heat load has been frequently used. For the above reasons, the conventional refrigerant flow divider cannot sufficiently cope with such a cooling device in which the flow rate of the refrigerant changes. The occurrence of the drift is also affected by the installation posture of the flow divider. 25 and FIG. 26 described above, if the inflow pipe 33 is installed so that the inflow pipe 33 is at the bottom and the outflow pipe 34 is at the top, the symmetry of the position of each outflow pipe with respect to the flow of the refrigerant is maintained. When the vessel 31 is placed horizontally, the position symmetry of the outflow pipe 34 is not maintained. The gas phase is lighter than the liquid phase.
In the upper part, a large amount of gas phase is contained, and in the lower part, a large amount of liquid phase is present, so that there is a difference in the amount of refrigerant flowing out between the upper outlet pipe and the lower outlet pipe.

This problem does not occur if the subdivision of the gas phase and the liquid phase and the stirring of the refrigerant are ideally performed. However, in actuality, as described above, stirring may not be performed sufficiently. Then, the installation posture of the flow splitter 31 is limited to the vertical installation, and the installation place is also restricted.

[0021] It is an object of the present invention to provide a refrigerant diverter that divides a flow to a desired flow ratio regardless of the flow rate and installation position of the refrigerant, and a refrigerant diverter that stably divides a uniform amount of refrigerant.

[0022]

In order to achieve the above object, according to the present invention, there is provided an inlet pipe for taking in a refrigerant and an outlet pipe for taking out the refrigerant.
A hollow body having a plurality of outlet pipes and a circular cross section,
A plurality of openings provided inside the main body and serving as refrigerant passage paths
Disk-shaped magnet rotor having an outer periphery of the main body
Stator mounted on the rotor for rotating the magnet rotor
Generated by the amount of refrigerant flowing out of each outlet pipe
Physical quantity, and based on the detected physical quantity, the stator
To rotate the magnet rotor
By stopping the data opening at the desired position,
The ratio of the amount of refrigerant flowing out of the compressor is controlled.

[0023]

[0024]

In the above configuration, the opening of the magnet rotor is formed in a circular shape, and a plurality of convex portions protruding inward are provided on the periphery thereof.

[0026]

A disk-shaped magnet rotor having a plurality of openings serving as a refrigerant passage is provided inside a hollow flow divider main body having a circular cross section, and a refrigerant passage is provided close to and parallel to the magnet rotor. An aperture plate having a plurality of openings serving as paths is fixedly installed, and an aperture for the refrigerant passing therethrough due to the overlap of the opening of the magnet rotor and the opening of the fixed aperture plate is formed. A stator for rotating the magnet rotor is provided on the outer periphery of the main body, and the magnet rotor is rotated and moved by the stator to change the overlapping area of the openings, thereby adjusting the aperture.

[0028]

When the movable opening plate is stopped and the refrigerant flow path is set by the opening, a difference occurs in the refrigerant partial flow rate. However, if the opening position is changed, a new refrigerant flow path is set and the difference in the partial flow rate also changes. . By changing the refrigerant flow path in this way, it is possible to divide the flow to a desired flow rate ratio. When the physical quantity resulting from the partial flow rate is adjusted based on the measurement of the physical quantity caused by the partial flow rate, the partial flow rate is adjusted at a flow rate suitable for matching the physical quantity to a desired value.

[0030]

[0031]

[Action] A magnet rotor having an opening is provided inside the main body.
This is rotated by a stator installed on the outer periphery of the main unit.
In the configuration, the refrigerant flow path is
Is set. Refrigerant due to rotational movement of magnet rotor
Since the flow path can be changed, the flow of refrigerant flowing out of each outlet pipe
The amount can be adjusted. This adjustment of the partial flow is caused by the partial flow.
Resulting physical quantity, such as the temperature of each branch refrigerant after heat exchange,
In this case, the flow is divided at an appropriate flow rate ratio.

The opening of the magnet rotor is formed in a circular shape.
And a plurality of protrusions protruding inward on the periphery.
The configuration provided increases the rotational force applied to the refrigerant.
Then, the refrigerant is swirled and mixed, and
Instability can be prevented.

In a configuration in which a magnet rotor having an opening and a fixed opening plate are provided inside the flow divider main body, and a stator is installed on the outer periphery of the main body, the refrigerant flow path is set by overlapping the opening of the magnet rotor and the opening of the fixed opening plate. Is done. Since the magnet rotor and the fixed aperture plate are arranged close to each other, this flow path functions as a throttle. The refrigerant passes through the throttle and is divided and speeded up, and is stirred and mixed. Since the magnet rotor can be rotated and moved by the stator, the overlap of the openings, that is, the size of the throttle can be adjusted, and thus the stirring can be adjusted and controlled.

[0034]

Embodiments of the present invention will be described below with reference to the drawings. In all the examples shown here,
An example of a flow divider that divides the refrigerant into four paths is given, and the number of outflow pipes is shown as four. However, the present invention is not limited to the four paths, and the refrigerant that divides the refrigerant into an arbitrary number of paths It is used for a shunt.

FIG. 2 shows the appearance of a refrigerant flow divider according to the first embodiment of the present invention, and FIG. 3 schematically shows a cross section thereof. FIG.
1 schematically shows the configuration of a main part of a refrigerant circuit to which the present flow divider is attached. The refrigerant distributor 1 has a cylindrical main body 2 at the center except for both ends, and one end of the main body 2 is connected to an inflow pipe 3 through which the refrigerant flows into the main body 2, and the other end of the refrigerant flows out. Four outflow pipes 4 to be connected are connected. The outlets 5 which are the connecting portions between the outflow pipe 4 and the main body 2 are circles having the same diameter, and the center of each outlet 5 is a circle centered on a point on the extension of the center line of the cylinder of the main body 2. It is arranged at equal intervals on the circumference.

Inside the main body 2, a magnet rotor 6 made of ferrite and formed in a disk shape as shown in FIG. 4 is arranged. The rotor 6 is disposed at a position close to the end to which the outflow pipe 4 is connected, perpendicular to the center line of the cylinder of the main body 2, and the periphery is supported by bearings (not shown). Rotate around the center line. The gap between the peripheral portion of the rotor 6 and the main body 2 is sealed by a sealing material (not shown).

A stator 7 for generating a magnetic force and rotating the rotor 6 is fixedly installed on the outer periphery of the main body 2 corresponding to the position of the rotor 6. As shown in FIG. 5, the stator 7 is connected to a controller 9 composed of a microcomputer, and the controller 9 controls generation of a magnetic force. Therefore, rotation and stop of the rotor 6 are controlled by the controller 9.

The disk-shaped rotor 6 has a predetermined thickness, and is provided with four openings 8 having a circular cross section that penetrate along the thickness direction. That is, each of the openings 8 is cylindrical and parallel to the center line of the cylinder of the main body 2. The distance from the center line of the main body to the center line of each opening 8 is equal to the distance from the center line of the main body to the center of the outflow port 5.
The center-to-center distance between them is also set at equal intervals. Therefore, depending on the stop position of the rotor 6, the center of the outlet 5 exists on the extension of the center line of each opening 8, and the opening 8 and the outlet 5 are all opposed to each other.

The four openings 8 are composed of one large opening 8L having a large diameter, one small opening 8S having a small diameter, and two medium openings 8M having a medium diameter. As shown in FIG.
The middle opening 8M is located on both sides of the small opening 8S. The diameter of the large opening 8L is substantially equal to the diameter of the outlet 5, and the middle opening 8M and the small opening 8S are smaller than the outlet 5.

On the other hand, the heat exchanger 11 to which the refrigerant flow divider 1 is attached is provided with four heat transfer tubes 12, and one end of the heat transfer tube 12 is connected to the outlet pipe 4 of the flow divider 1.
As shown in FIG. 5, on the outer surface near the other end of the heat transfer tube 12, temperature sensors 10 for detecting the temperature of the refrigerant after the heat exchange are provided. The temperature detected by the temperature sensor 10 is sent to the controller 9 and used for controlling the refrigerant flow divider 1. Note that the arrow F in FIG. 5 indicates the flow of the refrigerant.

In the refrigerant flow divider 1 configured as described above, the refrigerant liquefied by the condenser shown in FIG. 1 flows into the flow distributor main body 2 from the inflow pipe 3 in a two-phase state of a liquid phase and a gas phase ( FIG.
Arrow A). Inside the main body 2, the refrigerant is blocked in its flow path by the rotor 6, but passes through the opening 8 provided in the rotor 6 and goes to the outlet 5. At this time, since the space between the rotor 6 and the main body 2 is sealed, the refrigerant does not pass through the gap, and the inflowing refrigerant passes through any of the four openings 8. The refrigerant flowing out of the outlet 5 (arrow B in FIG. 3) passes through the outlet pipe 4 and passes through the heat transfer pipe 12 of the heat exchanger 11.
Flows through.

While passing through the heat transfer tube 12, the refrigerant exchanges heat with the object to be cooled and takes heat from the object. The removed heat is absorbed as heat of vaporization of the refrigerant in the liquid phase, whereby the refrigerant is almost in a gaseous state. The heat-exchanged refrigerant exits the heat exchanger 11, is collected in one flow path, flows to the compressor in FIG. 1, is compressed therein, and is then cooled and condensed in a condenser, and is again cooled in a cooling circuit. Circulate.

At the start of the operation of the cooling device, the rotor 6 is stopped at a position where the opening 8 faces the outlet 5. Rotor 6
Is disposed close to the outlet 5, so that the refrigerant that has passed through the opening 8 goes substantially straight, and
Leaks to A large amount of refrigerant flows out of the outlet facing the large opening 8L, and a small amount of refrigerant flows out of the outlet facing the small opening 8S. Therefore, at the start of the operation, there is a difference between the amounts of the refrigerant flowing out of the respective outlet pipes 5, and the amounts of the refrigerant flowing through the heat transfer tubes 12 are not equal.

After a short time, a control signal for rotating the rotor 6 by 90 ° is sent from the controller 10 to the stator 7 to rotate the rotor 6. The medium opening 8M opposes the outlet from which the large opening 8L opposes by the rotation of 90 °,
Another middle opening 8M faces the outlet from which S faces. As a result, a new non-uniform refrigerant outflow that is different from the non-uniform refrigerant flow generated at the start of the operation occurs. After a short time, the rotor 6 is further rotated by 90 ° in the same direction.
Due to this rotation, the small opening 8S faces the outlet where the large opening 8L first faces, and the large opening 8L similarly faces the outlet where the small opening 8S faces. In this state, an uneven refrigerant outflow that offsets the unevenness at the start of operation has occurred.

If the rotor 6 is further rotated twice by 90 ° each time, the rotor 6 has made one rotation from the start of the operation, and the amount of refrigerant flowing out of each outlet 5 during this period becomes equal. Thus, the amount of refrigerant flowing out of each outflow pipe 4 is not uniform at any time regardless of the stop position of the opening 8. However, while the stop time at each position of the rotor 6 is kept constant and the rotor 6 is repeatedly rotated by 90 ° as described above, the refrigerant flow from each outflow pipe 4 becomes uniform on a time average. If the stop time of the rotor 6 is set to several seconds to several tens of seconds, substantially sufficiently uniform refrigerant flow is achieved.

By the way, generally, the arrangement of the heat transfer tubes inside the heat exchanger is not symmetrical. Further, in the case of an air conditioner, for example, air having cooling symmetry is blown to exchange heat with a refrigerant, but the amount of air blown in the heat exchanger also varies depending on parts. Therefore, even if the refrigerant is divided equally, and there is no difference in the amount of refrigerant flowing through each heat transfer tube, there is a difference in heat exchange efficiency for each heat transfer tube.

If this is serious, even if all the refrigerant vaporizes in one heat transfer tube, the heat taken up cannot be absorbed as heat of vaporization, causing a rise in temperature. However, there is a disadvantage that the water flows out of the heat exchanger while remaining in the heat exchanger. This not only causes a significant decrease in cooling efficiency, but also adversely affects the apparatus and installation environment due to condensation on the low-temperature heat transfer tubes.

When such a heat exchange bias exists in the heat exchanger 11, the flow rate of the refrigerant to the outlet pipes 4 of the flow divider 1 is not equalized, but the flow rate ratio is positively changed. To compensate for the bias of heat exchange. As shown in FIG. 5, in the heat exchanger of the present embodiment, a temperature sensor 10 is provided near the refrigerant outflow end of each heat transfer tube 12, so that the temperature of the refrigerant after heat exchange can be detected. The detected temperature of each heat transfer tube 12 is used for controlling the rotation of the rotor 6 by the controller 9.

After the operation of the cooling device is started, the stop time of the rotor 6 at each stop position is equalized, and the refrigerant is divided into equal amounts. However, the temperature of one of the four heat transfer tubes 12 is lower than that of the other. When the heat transfer tube 1 rises, the large opening 8L
The time of facing the outlet 5 of the outflow pipe 4 connected to 2 is lengthened. As a result, more refrigerant flows through the heat transfer tube 12, so that the temperature rise due to the shortage of the refrigerant flow rate is eliminated, and the heat exchange efficiency of the heat exchanger 11 is improved.

Conversely, if one of the heat transfer tubes 12 has a lower temperature than the other, the time for making the small opening 8S face the outlet 5 corresponding to the heat transfer tube 12 is increased, and the heat transfer tube 12 Reduce the amount of refrigerant flowing through. As a result, the outflow of excess refrigerant that does not contribute to heat exchange is suppressed, and the heat exchanger 11
Heat exchange efficiency is improved. Similarly, when the temperature of the two heat transfer tubes 12 is different from those of the other two tubes, by appropriately adjusting the facing time of the large opening 8L and the small opening 8S, the flow is divided into an appropriate flow ratio, and The heat can be uniformly exchanged in the exchanger 11.

In the above embodiment, the opening 8 provided in the rotor 6 as a refrigerant passage has a large opening 8L, a medium opening 8M,
The small opening 8S is set in three stages, but is not limited to this.
For example, as shown in FIG. 6, one large opening 8L and three middle openings 8M may be provided. Also in this case, if the stop time of the rotor 6 to be stopped at every 90 ° is made constant, the refrigerant is evenly distributed over time. Also, by making the time when the large opening 8L faces a specific outlet relatively longer or shorter than the other outlets, the amount of refrigerant flowing out from the outlet can be made relatively large or small. it can. Therefore, it is possible to divide the flow into an arbitrary flow ratio.

Further, the opening 8 provided in the rotor 6
Even if it is one, flow control is possible. However, in this case, a large difference occurs in the flow rate depending on whether or not the opening 8 faces the outflow port 5, so that the rotor 6 may need to be rotated frequently.

In this method for setting the flow path of the refrigerant inside the refrigerant flow divider 1, the efficiency of setting the flow path changes depending on the installation position of the rotor 6 and its thickness. If the rotor 6 is installed too far from the end of the main body 2 provided with the outlet 5, the refrigerant flow after passing through the opening 8 does not go straight toward the outlet 5, and the refrigerant flowing through all the openings 8 is mixed. Therefore, it is difficult to set the refrigerant flowing out of the outlet 5 to a desired flow ratio. Therefore, in this embodiment, the rotor 6 is installed near the outlet as shown in FIG.

In order to make the refrigerant flow after passing through the opening 8 go straight, the thicker the rotor 6, the better. If the thickness is too thin, the refrigerant after passing through the opening 8 is mixed without going straight, and the refrigerant outflow amount from the outlet 5 cannot be set to a desired ratio. However, if it is too thick, the magnet rotor 6 becomes heavy, and a larger stator 7 for driving the magnet rotor 6 is required, and more drive power is required. In this embodiment, the thickness of the rotor 6 is set substantially equal to the distance from the rotor 6 to the outlet 5.

As described above, in the present embodiment, the refrigerant flow path inside the flow divider 1 is set by the openings 8 having different sizes provided in the rotor 6 and the flow path is adjusted by the rotation of the rotor 6, so that the uniform flow is achieved. In addition to the split flow, the split flow of the refrigerant at an arbitrary ratio is possible. Therefore, even in the case where there is a difference in heat exchange efficiency between the heat transfer tubes due to a difference in the amount of blown air in the heat exchanger, the refrigerant can be diverted to an appropriate flow ratio corresponding to the difference. As a result, the heat exchange efficiency of the entire heat exchanger is improved. In addition, the disadvantage that a large amount of liquid phase remains after heat exchange due to the flow of excess refrigerant and condensation occurs on the heat transfer tube is also solved.

Further, the flow divider 1 can be installed not only vertically but also horizontally. When installed horizontally,
Since the gaseous phase is lighter than the liquid phase, a large amount of gaseous state refrigerant flows out of the outlet provided above, and the outflow of the liquid state refrigerant decreases. This means that the flow rate of the refrigerant in the outlet pipe and the heat transfer pipe connected to the outlet is reduced. In the flow divider 1 of the present embodiment, since the flow rate of the refrigerant flowing out is controlled by the position of the opening 8, the time when the large opening 8L is opposed to the outlet provided above is lengthened, so that the amount of refrigerant flowing out is insufficient. Can be supplemented. Therefore, the shunt 1
No problem arises with respect to the flow rate of the refrigerant even if it is installed horizontally. The fact that the refrigerant flow splitter can be installed not only vertically but also horizontally is that the degree of freedom in mounting the flow splitter to the heat exchanger is increased, and the size of the apparatus is reduced as a whole.

FIG. 7 is a sectional view of a refrigerant flow divider according to a second embodiment of the present invention. In this flow divider, a magnet rotor 6 having an opening 8 is disposed inside a main body 2 having a cylindrical central portion, and a stator 7 for rotating the rotor 6 by magnetic force is fixedly installed on the outer periphery of the main body, similarly to the first embodiment. And
An opening plate 13 is fixedly installed inside the main body 2. An inflow pipe 3 is connected to one end of the main body 2, and four outflow pipes 4 are connected to the other end.

The rotor 6 is formed in a thin disk shape.
It is arranged near the inflow pipe 3, and its outer peripheral portion is supported by bearings (not shown) and is rotatable about the center line of the cylinder of the main body 2. The gap between the main body 2 and the rotor 6 is sealed by a sealing material. Fixed aperture plate 13
It is also formed thinner, and is installed closer to and parallel to the rotor 6 on the inflow pipe 3 side of the rotor 6. The rotation of the rotor 6 is controlled by the controller 9 of FIG. However, in this embodiment, the temperature sensor 10 for detecting the temperature of the heat transfer tube 12 of the heat exchanger 11 is not provided.

As shown in FIG. 8, the rotor 6 has four fan-shaped openings 8 through which the refrigerant passes. The fixed opening plate 13 is also provided with an opening 14 through which the refrigerant passes. As shown in FIG. 9, the opening 14 is formed in a narrow band shape along the circumference of a concentric circle, and constitutes a fan-shaped four group. The central angle of each group is set slightly larger than the central angle of the fan-shaped opening 8 of the rotor 6. Depending on the stop position of the rotor 6, the opening 8 may be completely open to completely oppose the opening 14, or the opening 14 may slightly overlap the opening 8.
Will not be completely closed.

Since the rotor 6 and the fixed opening plate 13 are arranged close to each other, the overlap between the opening 8 and the opening 14 forms a refrigerant flow path. The larger the overlap, the wider the refrigerant flow path at this location, and the smaller the overlap, the narrower the refrigerant flow path at this location. Therefore, the opening 14 of the fixed opening plate 13 and the opening 8 of the rotor 6 cooperate to form a throttle for the refrigerant flow. The size of the aperture can be adjusted by rotating the rotor 6.

When the amount of refrigerant flowing in per unit time is constant, the speed of the refrigerant passing through the throttle changes depending on the size of the throttle formed by the openings 14 and 8. When the opening 14 of the rotor 6 is completely opposed to the opening 14 of the fixed opening plate 13 and the opening 14 is fully opened, that is, when the throttle is fully opened, the refrigerant passes through the throttle at a relatively low speed and the opening 8 When the overlap between the aperture and the opening 14 is small, that is, when the throttle is narrowed, the refrigerant passes at a relatively high speed.

In such a configuration, the refrigerant flowing from the inflow pipe 3 into the flow divider main body 2 passes through the throttle formed by the openings 14 and 8, and then flows out of the outflow port 5 to the outflow pipe 4. The refrigerant then exchanges heat with the object to be cooled while passing through the heat transfer tube 12 in the heat exchanger 11, and is vaporized and collected in one path.
After passing through the compressor, it is cooled and liquefied in the condenser and recirculated through the refrigerant circuit.

As described above, the refrigerant flowing into the main body 2 from the inflow pipe 3 is in a two-phase state of a liquid phase and a gaseous phase, and the drift tends to occur. However, by adjusting the size of the throttle, The drift is suppressed. First, when the refrigerant inflow amount is large, the throttle is widely opened. Since each of the openings 14 is formed in a thin band shape, the gas phase and the liquid phase are subdivided when passing through the openings. Furthermore, even if the throttle is fully opened, the area of the refrigerant passage is only a fraction of the cross-sectional area of the main body 2, and the refrigerant passes through the throttle at a considerably high speed. Therefore, the refrigerant after passing through the throttle is sufficiently stirred. Therefore, the refrigerant after passing through the fixed opening plate 13 is uniformly mixed.

On the other hand, when the amount of refrigerant flowing in is small,
The rotor 6 is rotated by the stator 7 to reduce the overlap of the opening 8 with the opening 14 and reduce the aperture. A small inflow per unit time means that the flow of the refrigerant is low, which inherently reduces the stirring effect.However, by reducing the size of the throttle, the speed of the refrigerant flow is increased. Will be kept. In addition, since the flow path of the refrigerant passing through each opening 14 of the fixed opening plate 13 is smaller than when the throttle is fully opened, the gas phase and the liquid phase are further subdivided. Therefore, even when the flow rate of the refrigerant is small, the refrigerant after passing through the throttle is sufficiently mixed and stirred.

As described above, according to the refrigerant flow divider 1 of the present embodiment, the size of the throttle can be variably adjusted in accordance with the amount of refrigerant flowing in, so that the refrigerant can always be appropriately stirred and mixed.
Therefore, the occurrence of the drift is suppressed, and a uniform amount of the refrigerant is diverted.

Further, since the throttle is increased when the refrigerant inflow is large, the refrigerant is safe without generating excessive refrigerant pressure, and the load for circulating the refrigerant can be reduced. Further, the disadvantage that the refrigerant after passing through the throttle becomes too high in speed and reaches the outlet 5 directly to cause a difference in the refrigerant outflow amount from the outlet pipe 4 is also prevented.

In this embodiment, the refrigerant is always uniformly agitated by the variable throttle to suppress the occurrence of drift and to perform a uniform amount of refrigerant divergence. Therefore, a suitable space is required in the main body 2 for agitation. is there. For this reason, the rotor 6 and the fixed aperture plate 13
Is desirably installed in the vicinity of the refrigerant inflow portion away from the outlet 5. Since the aperture is formed by the opening 8 and the opening 14, it is preferable that the rotor 6 and the fixed opening plate 13 are brought close to each other to reduce the gap therebetween. if,
If the gap is large, the refrigerant that has passed through the opening 14 can pass through the gap and pass through the entire opening 8, and the effect of the throttle is reduced.

In this embodiment, the fixed opening plate 13 and the rotor 6 are arranged in this order with respect to the flow path of the refrigerant. The plate 13 may be provided on the outflow pipe 4 side. Further, although the opening 14 of the fixed opening plate 13 is shown as being formed in a narrow band shape on a concentric circle, it may be formed as a set of many small holes as shown in FIG. The effect of is obtained.

FIG. 11 shows a cross section of a refrigerant flow divider according to a third embodiment of the present invention. As in the first and second embodiments, the flow divider 1 also includes a main body 2 having a cylindrical central portion. An inflow pipe 3 is connected to one end of the main body 2 and four outflow pipes 4 are connected to the other end.

A magnet rotor 6 is arranged inside the main body 2. As shown in FIG. 12, the rotor 6 is formed in a thin disk shape, and is fixed vertically to an axis 16 passing through the center thereof. A fan-shaped opening 8 is formed in the rotor 6, and four blades 15 for stirring the refrigerant are provided on one side.

As shown in FIG. 11, a support arm 17 is provided inside the main body 2, and the rotor 6 is
Are supported by the support arm 17, the blade 15 is directed toward the outflow pipe, and the shaft 16 is arranged so as to coincide with the center line of the cylinder of the main body 2. Both ends of the shaft 16 are sharply formed so that the contact area with the support arm 17 is reduced, and the rotor 6 easily rotates about the shaft 16. There is a gap between the inner wall of the main body 2 and the outer periphery of the rotor 6.

A stator 7 is fixedly installed on the outer periphery of the main body 2 corresponding to the position of the rotor 6. The stator 7 generates a magnetic force under the control of the controller 9 in FIG. 5 to rotate the rotor 6. Rotation, stop, and rotation speed of the rotor 6 are controlled by a controller 9 via a stator 7.

In the shunt 1 configured as described above,
A refrigerant in a two-phase state of a gas phase and a liquid phase flows into the main body 2 from the inflow pipe 3, passes through the opening 8 of the rotor 6 or the gap between the rotor 6 and the main body 2, and flows to the outlet 5. When the rotor 6 is rotating under the control of the controller 9, the refrigerant that has passed through the rotor 6 is stirred by the blade 15, and the stirring efficiency is adjusted by the rotation speed of the rotor 6.

When the amount of refrigerant flowing in is large, the refrigerant has a certain flow velocity, and the refrigerant flow itself has an agitation action. Therefore, even if the rotation of the rotor 6 is slowed to attenuate the agitation by the blades, sufficient agitation is achieved, and the gas phase and the liquid phase are uniformly mixed. When the inflow refrigerant is small, the flow of the refrigerant is low, and the stirring action by the refrigerant itself hardly occurs. In this case, the rotor 6 is rotated at a high speed, and is strongly stirred by the blade 15. Then, the gas phase and the liquid phase separated at the time of inflow are uniformly mixed, and an equal amount of refrigerant flows out of the outflow pipe 4.

The flow rate of the refrigerant flowing through the cooling circuit per unit time is determined by the amount of compression of the compressor per unit time. When the flow divider 1 of the present embodiment is used for a conventional cooling device that constantly circulates a fixed amount of refrigerant, the rotor 6 is constantly rotated at a constant speed. In the inverter-type cooling device, the refrigerant flow rate changes almost linearly and continuously from the refrigerant stop state to the maximum flow rate. In this case, the controller 9 receives an inverter control signal, and The controller 9 adjusts the rotation speed of the rotor 6. Thereby, it is possible to always divide the refrigerant into an equal amount.

In this embodiment, the blade 1 provided on the rotor 6
By agitating the refrigerant actively by 5, the occurrence of drift is suppressed and a uniform amount of refrigerant is diverted, and an appropriate space is required in the main body 2 for stirring. For this reason, it is desirable that the rotor 6 is installed in the vicinity of the refrigerant inflow portion away from the outlet 5. The shape and the number of the blades 15 may be arbitrarily set.

Instead of supporting the rotor 6 by the shaft 16, the periphery of the rotor 6 may be supported by bearings as in the first and second embodiments. In this case, the gap between the rotor 6 and the inner wall of the main body 2 does not need to be sealed.

The variable throttle of the second embodiment can be combined with the positive stirring of the third embodiment. In the fourth embodiment of the present invention, a thick disk-shaped rotor 6 shown in FIG. 13 is used instead of the thin rotor in the second embodiment shown in FIG. The other configuration is the same as that of the second embodiment, and a duplicate description will be omitted.

The rotor 6 shown in FIG. 13 is made of a ferrite magnet and is formed in a thick disk shape. The rotor 6 is provided with a fan-shaped opening 8 through which the refrigerant passes,
When the rotor 6 rotates, the inner section 8 of the opening 8 parallel to its diameter
The passing refrigerant is pushed by a and the refrigerant is stirred.

When the flow rate of the refrigerant is equal to or more than a predetermined amount, the refrigerant is subdivided, accelerated and uniformly mixed by a throttle formed by the overlap of the opening 14 of the fixed opening plate 13 and the opening 8 of the rotor 6. At this time, the controller 9 rotates the rotor 6 in accordance with the inflowing refrigerant amount to adjust the size of the throttle, as described in the second embodiment, by rotating the rotor 6 in accordance with the inflowing refrigerant amount. Then, stop at a position where the aperture becomes a desired size.

When the amount of refrigerant flowing in per unit time is significantly reduced, the refrigerant is mixed by performing positive stirring by rotation of the rotor 6 instead of mixing the refrigerant by the throttle. After passing through the opening 14 of the fixed opening plate 13, the refrigerant passes through the opening 8 of the rotor 6. At this time, since the rotor 6 is rotating, it is strongly pushed by the inner section 8 a of the opening 8. The refrigerant pushed by the inner section 8a does not flow backward because the fixed opening plate 13 is provided close to the inflow pipe 3 side of the rotor 6, and moves while turning to the outflow port 5 side without obstacles. Therefore, the rotor 6
The refrigerant that has passed through is stirred.

Further, since the opening 14 of the fixed opening plate 13 is formed in a thin band shape, the gas phase and the liquid phase of the refrigerant are subdivided when passing through the opening. The combination of the subdivision by the opening 14 and the agitation by the rotor 6 allows the refrigerant to be uniformly mixed, thereby suppressing the occurrence of drift. Therefore, according to the present embodiment, even when the amount of the refrigerant flowing in is extremely small, the stirring and mixing of the refrigerant are reliably performed, and the equal amount of the divided flow can always be stably performed.

According to the present embodiment, since the rotor 6 is continuously rotated only when the refrigerant inflow is small, the power consumption can be reduced as compared with the third embodiment in which the rotor 6 is constantly rotated during the operation of the cooling device.

FIG. 14 is a sectional view of a refrigerant flow divider according to a fifth embodiment of the present invention. This shunt is similar to the first embodiment.
A magnet rotor 19 is disposed inside, and a stator 7 for rotating the rotor 19 by magnetic force is fixedly installed on the outer periphery of the main body. An inflow pipe 3 is connected to one end of the main body 2, and four outflow pipes 4 are connected to the other end. The body 19 of the main body 2 (the rotor 19 installation part) slides the rotor 19. A protruding portion 2a for preventing the rotor 19 from rotating is provided.

The rotor 19 is formed in a columnar shape as shown in FIG. 15, which is a cross-sectional view taken along the line AA of FIG. 14, and a groove 20 serving as a refrigerant passage is provided on the outer periphery thereof. The rotation is performed with the center line 2 as a rotation axis.

In such a configuration, the refrigerant flowing from the inflow pipe 3 into the flow divider main body 2 flows out to the outflow pipe 4 through the groove 20 of the rotor 19. When the refrigerant passes through the groove 20 of the rotor 19, a rotational force (centrifugal force) is given to the refrigerant because the rotor 19 is rotating, and the refrigerant flows out while being swirled and mixed. Evenly distributed and drained.

FIG. 16 is a sectional view of a refrigerant flow divider according to a first modification of the fifth embodiment of the present invention. This shunt,
As in the fifth embodiment, a magnet rotor 21 is disposed inside, and a stator 7 for rotating the rotor 21 by magnetic force is fixedly installed on the outer periphery of the main body. The inflow pipe 3 is connected to one end of the main body 2, and four outflow pipes 4 are connected to the other end, and the body 21 (the rotor 21 installation part) slides the rotor 21. A protruding portion 2a for preventing the rotor 21 from rotating is provided.

The rotor 21 is formed in a columnar shape as shown in FIG. 17 which is a cross-sectional view taken along the line BB of FIG. 16, and a circular opening 22 is provided inside the rotor 21. Of the main body 2 is rotated by the magnetic force of the stator 7 around the center line of the main body 2.

In such a configuration, the refrigerant flowing from the inflow pipe 3 into the flow divider main body 2 flows out to the outflow pipe 4 through the opening 22 of the rotor 21. Opening 22 of rotor 21
When the refrigerant passes through, the rotor 21 is rotating, so that the rotational force (centrifugal force) is applied to the refrigerant by the convex portion 23 of the opening 22.
Is given, and the refrigerant flows out while being swirled and mixed.
The water is evenly distributed to the plurality of outflow pipes 4 and discharged.

FIG. 18 is a sectional view of a refrigerant flow divider according to a second modification of the fifth embodiment of the present invention. As in the fifth embodiment, a magnet rotor 24 is disposed inside the current divider, and a stator 7 for rotating the rotor 24 by magnetic force is fixedly installed on the outer periphery of the main body. The inflow pipe 3 is connected to one end of the main body 2, and four outflow pipes 4 are connected to the other end, and the body 24 (rotor 24 installation part) of the main body 2 slides the rotor 24. A protrusion 2a is provided to prevent the rotor 24 from rotating.

The rotor 24 is formed in a columnar shape as shown in FIG. 19 which is a cross-sectional view taken along the line C--C in FIG. 18, and a plurality of circular openings 25 are provided inside the rotor 24 so as to be circumferentially arranged. The main body 2 is rotated around the center line of the main body 2 by the magnetic force of the stator 7.

In such a configuration, the refrigerant flowing from the inflow pipe 3 into the flow divider main body 2 flows out to the outflow pipe 4 through the plurality of openings 25 of the rotor 24. When the refrigerant passes through the plurality of openings 25 of the rotor 24,
Is rotating, a rotational force (centrifugal force) is applied to the refrigerant by the opening 25, and the refrigerant flows out while being swirled and mixed. Therefore, the refrigerant is uniformly distributed to the plurality of outflow pipes 4 and flows out.

FIGS. 20 to 22 show a magnet rotor of a refrigerant flow divider according to a third modification of the fifth embodiment of the present invention.
Shown in The rotor 26 is formed in a cylindrical shape, and a plurality of, for example, four circular openings 27 are provided in the inside thereof in a circumferential shape. The rotor 26 has a structure similar to that of the fifth embodiment.
It is arranged inside the flow divider main body 2.

The refrigerant inlet (the refrigerant inflow side) of the opening 27 is located at the center of the rotor 26 as shown in FIG. 21, and the refrigerant outlet (the refrigerant outflow side) is near the periphery of the rotor 26 as shown in FIG. Is provided.

In such a configuration, the refrigerant flowing from the inflow pipe 3 into the flow divider main body 2 flows out to the outflow pipe 4 through the plurality of openings 27 of the rotor 26. When the refrigerant passes through the plurality of openings 27 of the rotor 26,
Is rotating, centrifugal force is applied to the refrigerant by the openings 27, and the refrigerant flows out while being swirled and mixed. Therefore, the refrigerant is uniformly distributed to the plurality of outflow pipes 4 and flows out.

Although the refrigerant flow divider according to the present invention has been described with reference to the five embodiments, the thick rotor shown in the fourth embodiment is used for stirring instead of the rotor provided with the blades 15 in the third embodiment. You may. At this time, it is not necessary to seal the gap between the outer periphery of the rotor and the inner wall of the main body. Further, in any of the embodiments, a ferrite magnet rotor is used as the rotary aperture plate. However, the present invention is not limited to this, and other aperture plates can be used as long as they rotate by magnetic force. For example, as shown in FIG. 23, a bar-shaped magnet 18 may be attached to a synthetic resin opening plate 6 'and used as a rotor.

As described at the beginning, the flow divider of the present invention is not limited to the one in which the refrigerant flow path is branched into four paths. For example, in order to branch into six paths, in the case of the first embodiment, six outlets may be formed at equal intervals on the same circumference, and openings may be formed at positions facing the rotors. In other embodiments, the rotor and the fixed aperture plate can be used without modification. Furthermore, the attachment of the outflow pipe to the main body does not have to be on the same circumference, and can be freely performed.

The refrigerant distributor of the present invention has a rotatable opening plate in the distributor main body and actively controls the flow of the refrigerant in the distributor by external control so that the refrigerant can be uniformly distributed. The present invention is also applicable to an inverter type cooling device in which the flow rate of the refrigerant changes, and has the following effects.

[0099]

[0100]

[0101]

[0102]

[0103]

[0104]

According to the refrigerant distributor of the first aspect, the refrigerant is supplied to the mug.
By flowing through multiple openings in the net rotor
A plurality of refrigerant channels are set inside the flow
The refrigerant flows out of the outlet pipe. These channels are magnetic
It can be changed by the rotational movement of the rotor. Duplicate
Apertures of different sizes can be set without changing the size of
If so, the outflow ratio can be adjusted. Also, even if all apertures
For the same size, keep the number of openings smaller than the number of outflow tubes.
If it is eliminated, it will not be opposed to the refrigerant flow path, so the outflow amount will be
There will always be a sharp decrease in the outflow pipe,
By changing the non-opposed time for each outflow pipe, the
The ratio can be set arbitrarily. In addition, it is easy to set and adjust the split flow ratio.
It is easy to set the desired flow ratio even if the flow divider is installed horizontally.
This allows the mounting posture of the heat exchanger to be adjusted automatically.
The degree of freedom increases. Therefore, downsizing of equipment including heat exchanger
Can be achieved.

In the refrigerant flow divider according to the second aspect, the flow path of the refrigerant
It is formed in a circular shape and protrudes inward at the periphery
Dividing the magnet rotor provided with an opening with a projection
Since it is arranged and rotated inside the container body, the time given to the refrigerant
Rolling force (centrifugal force) can be increased, improving the swirling mixing effect
The flow path of the refrigerant inside the flow divider.
Setting and agitation of the refrigerant inside the flow divider can be performed easily.
When the refrigerant is agitated by swirling, the occurrence of drift is reduced.
Suppression and an equal amount of refrigerant diverting is achieved.

[0106]

According to the third aspect of the present invention, the aperture is formed by the overlap of the opening of the magnet rotor and the opening of the fixed aperture plate, and the size of the aperture is changed by the rotational movement of the magnet rotor. Therefore, even when the inflow amount of the refrigerant is small, the flow rate of the refrigerant passing therethrough can be increased by reducing the throttle, and the refrigerant can be sufficiently stirred. In addition, if the throttle is reduced, the gas phase and the liquid phase of the refrigerant are subdivided, and uniform mixing of the two phases is facilitated. When these actions are combined, even if the refrigerant inflow amount is small, the refrigerant is uniformly mixed, the occurrence of drift is suppressed, and a uniform flow can be divided.

When the amount of refrigerant flowing in is large, sufficient stirring can be performed even if the throttle is increased, so that a uniform amount of refrigerant can be divided. In addition, since the refrigerant flow does not need to be speeded up more than necessary by enlarging the throttle, there is no inconvenience that the high-speed refrigerant flow directly reaches the outflow pipe and an equal amount of divided flow is not performed. Furthermore, if the throttle is made large, excessive pressure is not applied to the inside of the flow divider, which is safe, and the load on the entire cooling device is reduced.

As described above, since a uniform amount of refrigerant can be diverted stably irrespective of the flow rate of the refrigerant, it is useful for an inverter type cooling device.

[Brief description of the drawings]

FIG. 1 is a block diagram schematically showing a basic configuration of a compression refrigeration apparatus.

FIG. 2 is a perspective view showing the appearance of the refrigerant flow divider according to the first embodiment of the present invention.

FIG. 3 is a front sectional view of the refrigerant flow divider according to the first embodiment.

FIG. 4 is a plan view of the rotor of the first embodiment.

FIG. 5 is a block diagram showing main components of the refrigerant flow divider and the heat exchanger of the first embodiment.

FIG. 6 is a plan view of a modified example of the rotor of the first embodiment.

FIG. 7 is a front sectional view of a refrigerant flow divider according to a second embodiment of the present invention.

FIG. 8 is a plan view of a rotor according to a second embodiment.

FIG. 9 is a plan view of a fixed aperture plate according to a second embodiment.

FIG. 10 is a plan view of a modification of the fixed aperture plate of the second embodiment.

FIG. 11 is a front sectional view of a refrigerant flow divider according to a third embodiment of the present invention.

FIG. 12 is a plan view of a rotor according to a third embodiment.

FIG. 13 is a perspective view of a rotor according to a fourth embodiment of the present invention.

FIG. 14 is a front sectional view of a refrigerant flow divider according to a fifth embodiment of the present invention.

FIG. 15 is a sectional view taken along line AA of FIG. 14;

FIG. 16 is a front sectional view of a refrigerant flow divider according to a first modification of the fifth embodiment of the present invention.

FIG. 17 is a sectional view taken along line BB of FIG. 16;

FIG. 18 is a front sectional view of a refrigerant flow divider according to a second modification of the fifth embodiment of the present invention.

FIG. 19 is a sectional view taken along the line CC in FIG. 18;

FIG. 20 is a front sectional view of a magnet rotor according to a third modification of the fifth embodiment of the present invention.

FIG. 21 is a plan view of a magnet rotor according to a third modification of the fifth embodiment as viewed from the refrigerant inflow side.

FIG. 22 is a plan view of a magnet rotor according to a third modification of the fifth embodiment as viewed from a refrigerant outflow side.

FIG. 23 is a perspective view of a modified example of the rotor of the present invention.

FIG. 24 is a front sectional view of a conventional refrigerant distributor.

FIG. 25 is a front sectional view of a conventional refrigerant flow divider provided with a throttle valve.

FIG. 26 is a front sectional view of a conventional refrigerant distributor in which an inflow pipe is formed by a bundle of small diameter pipes.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Refrigerant flow divider 2 Divider main body 3 Inflow pipe 4 Outflow pipe 5 Outflow port 6 Rotor 7 Stator 8 Rotor opening 9 Controller 10 Temperature sensor 11 Heat exchanger 12 Heat transfer pipe 13 Fixed opening plate 14 Fixed opening plate opening 15 Stirrer blade

Claims (3)

(57) [Claims] 1. An inflow pipe for taking in a refrigerant and an outflow pipe for taking out the refrigerant.
A hollow body having a plurality of outlet pipes,
A plurality of openings that are provided inside the main body and serve as refrigerant passage paths
Having a disk-shaped magnet rotor and an outer periphery of the main body.
A stator installed to rotate the magnet rotor;
Generated by the amount of refrigerant flowing out of each outlet pipe
Detects the physical quantity and sends it to the stator based on the detected physical quantity.
Rotate and move the magnet rotor
By stopping the opening of the outlet at the desired position,
A refrigerant flow divider characterized by controlling the ratio of the amount of refrigerant flowing out from the refrigerant . 2. The magnet rotor has a circular opening.
And a plurality of protrusions protruding inward on the periphery.
The refrigerant flow divider according to claim 1, wherein the refrigerant flow divider is provided. 3. An inflow pipe for taking in the refrigerant and an outflow pipe for taking out the refrigerant.
A hollow body having a plurality of outlet pipes,
A plurality of openings that are provided inside the main body and serve as refrigerant passage paths
Disc-shaped magnet rotor, and the magnet rotor
Inside the body parallel to the magnet rotor close to
Has a plurality of openings that are fixedly installed on the
A fixed opening plate;
And a stator that rotates the rotor
Passing due to the overlap of the rotor opening and the fixed opening plate opening
A restrictor is formed for the flowing refrigerant, and the stator
Rotate the rotor to change the overlapping area of the openings.
A refrigerant diverter characterized in that the throttle is adjusted by causing the flow to flow.