JP2012207912A - Refrigerant distributor and heat pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a refrigerant distributor that prevents refrigerant distribution from deviating due to an inertia force.SOLUTION: The refrigerant distributor includes an inner pipe 12 having a refrigerant flow-in port 11 in which a refrigerant flows and having an end which is opposite to the refrigerant flow-in port 11 and is closed, an outer pipe 13 for housing the inner pipe 12, and a plurality of a distribution pipes 14 provided to the outer pipe 13 at a predetermined interval for allowing the refrigerant to flow into each path. A plurality of refrigerant flow-out holes 15 are formed in the inner pipe 12 at intervals in the longitudinal direction of the pipe, and the hole diameter of the plurality of refrigerant flow-out holes 15 are gradually reduced at the respective refrigerant flow-out ports 15a, 15b, 15c as they are separated stepwise from the refrigerant flow-in port 11, and intervals among the refrigerant flow-out holes 15a, 15b, 15c are continuously formed and arranged at the substantially same interval.

Description

  The present invention relates to a refrigerant distributor and a heat pump apparatus, and mainly to a refrigerant distributor that is attached to a heat exchanger used in a heat pump apparatus such as an air conditioner and distributes the refrigerant.

A conventional refrigerant distributor is for distributing refrigerant to a plurality of refrigerant paths of a heat exchanger via a diverter pipe, and a sealed outer pipe in which the diverter pipes are connected at appropriate intervals in the vertical direction. It is composed of a bottomed inner tube inserted into the outer tube, and a slit extending in the vertical direction is formed in the inner tube (see, for example, Patent Document 1).
Another conventional refrigerant distributor has a cylindrical outer tube whose longitudinal direction is vertical, an inner tube inserted from the lower end of the outer tube to the vicinity of the upper end, and an equal interval in the vertical direction on the peripheral side surface of the outer tube. And an outflow hole whose diameter is reduced as it goes down gravitationally is provided on the side surface of the inner tube (see, for example, Patent Document 2).

Japanese Utility Model Publication No. 8-9578 (1st page, Fig. 3) Japanese Unexamined Patent Publication No. 3-195873 (first page, FIG. 1)

In a conventional refrigerant distributor, when a two-phase refrigerant is introduced into an inner pipe and distributed from the outer pipe to each shunt pipe, the two-phase refrigerant that has flowed into the inner pipe is blown into the outer pipe from the slit, and the refrigerant inside the outer pipe Although the distribution is made uniform and the refrigerant is evenly distributed to each path, the two-phase refrigerant flowing into the inner pipe has an inertial force, and the liquid refrigerant with a large mass is concentrated on the tip of the inner pipe. In order to blow out the inside of the outer pipe, there is a problem in that it is unevenly distributed to each branch pipe.
Further, when slit processing is performed on the inner tube, there is a problem that the processing process takes time and the processing cost increases.
Furthermore, if the downstream heat exchanger has a wind speed distribution and the heat load of each path is different, it is necessary to flow a large amount of refrigerant through the path with a large heat load. There was a problem that it was necessary to adjust by changing the length and the inner diameter.

Further, in another conventional refrigerant distributor, when the two-phase refrigerant flows into the inner pipe and is distributed from the outer pipe to each branch pipe, the inner pipe is a refrigerant whose diameter is increased gravitationally upward from the inlet. Although it has an outflow hole, the two-phase refrigerant flowing into the inner pipe has inertial force, and the liquid refrigerant with a large mass concentrates on the tip of the inner pipe and blows out into the outer pipe. There has been a problem that a large amount of liquid refrigerant flows out and is unevenly distributed to each branch pipe.
SUMMARY An advantage of some aspects of the invention is that it provides a refrigerant distributor and a heat pump device that suppress a deviation in refrigerant distribution due to inertial force.

  A refrigerant distributor according to the present invention has a refrigerant inlet into which refrigerant flows, an inner pipe whose end opposite to the refrigerant inlet is closed, an outer pipe that accommodates the inner pipe, A plurality of shunt pipes that are provided at predetermined intervals in the outer pipe, and flow refrigerant through each path, and a plurality of refrigerant outflow holes are formed in the inner pipe at intervals in the pipe length direction. The diameter of the refrigerant outflow holes is made smaller as each of the plurality of refrigerant outflow holes is stepped away from the refrigerant inlet, and the intervals between the refrigerant outflow holes are continuously formed at substantially the same interval. Is.

  The refrigerant distributor of the present invention has a refrigerant inlet into which refrigerant flows, an inner pipe whose end opposite to the refrigerant inlet is closed, an outer pipe that accommodates the inner pipe, and the outer pipe A plurality of shunt pipes that are provided at predetermined intervals in the pipe and flow refrigerant in each path, and a plurality of refrigerant outflow holes are formed in the inner pipe at intervals in the pipe length direction. Since the diameter of the outflow holes is made smaller for each of the plurality of refrigerant outflow holes as they are stepped away from the refrigerant inlet, the intervals between the refrigerant outflow holes are continuously formed at substantially the same interval. When the two-phase refrigerant is flowed into the inner pipe and the two-phase refrigerant is distributed from the outer pipe to each of the shunt pipes, the two-phase refrigerant that has flowed in is collided at the closed end of the inner pipe and homogenized. The closer to the closed end of the inner pipe where a large amount of refrigerant is distributed, the smaller the diameter of the refrigerant outlet hole, Even if there is a non-uniform distribution of liquid refrigerant due to inertial force, it becomes possible to make the distribution of liquid refrigerant inside the outer pipe uniform, and the two-phase refrigerant flowing out from each branch pipe can be uniformly distributed. effective.

Sectional drawing which shows the refrigerant distributor of Embodiment 1 of this invention. The perspective view which shows the heat exchanger using the same refrigerant | coolant divider | distributor. AA sectional view taken on the line AA of FIG. Sectional drawing of the refrigerant distributor which shows Embodiment 2 of this invention. The cross-sectional view of the refrigerant distributor showing Embodiment 3 of the present invention. Sectional drawing which shows the wall-hanging type indoor unit of the room air conditioner using the refrigerant distributor of Embodiment 4 of this invention. Sectional drawing which shows the refrigerant | coolant divider | distributor. The perspective view which shows the same refrigerant | coolant divider | distributor.

Embodiment 1 FIG.
FIG. 1 is a sectional view showing a refrigerant distributor according to Embodiment 1 of the present invention, and FIG. 2 is a perspective view showing a heat exchanger using the refrigerant distributor.
As shown in FIG. 1, a refrigerant distributor 1 that distributes an inflow two-phase refrigerant includes an inner pipe 12 having a refrigerant inlet 11, an outer pipe 13 that houses the inner pipe 12, and a predetermined interval between the outer pipe 13. And a plurality of flow dividing pipes 14 provided with a double pipe structure.
In the first embodiment, as shown in FIG. 1, a plurality of circular coolant outlet holes 15 are formed in the inner tube 12 at intervals in the tube length direction. The hole diameters of the plurality of refrigerant outflow holes 15 become smaller for each of the three refrigerant outflow holes 15a, 15b, and 15c as the distance from the refrigerant inlet 11 of the inner pipe 12 increases stepwise (15a <15b <15c). These refrigerant outflow holes 15a, 15b, 15c and the plurality of flow dividing pipes 14 are arranged at substantially equal intervals.
As shown in FIG. 2, a plurality of flow dividing tubes 14 of the refrigerant distributor 1 are connected to a heat exchanger 3 composed of heat transfer tubes and aluminum fins. The heat exchanger 3 is connected to a gas junction pipe 2 through which gas refrigerants merge and flow out. Reference numeral 21 denotes a refrigerant outlet provided in the gas junction pipe 2.

First, operation | movement of the heat exchanger 3 is demonstrated using FIG.
The arrows in FIG. 2 indicate the flow of refrigerant when the heat exchanger 3 is used as an evaporator. The two-phase refrigerant in which the gas refrigerant and the liquid refrigerant are mixed flows in from the refrigerant inlet 11 of the refrigerant distributor 1 and is distributed to each branch pipe 14.
The distributed two-phase refrigerant flows into the heat transfer tubes constituting each path of the heat exchanger 3. The two-phase refrigerant that has flowed into the heat transfer tube exchanges heat with the air 4 indicated by the white arrow passing through the heat exchanger 3 through the aluminum fin integrated with the heat transfer tube, and becomes a gas refrigerant from each path outlet. The gas flows out into the gas merge pipe 2, merges, and flows out from the refrigerant outlet 21.

Next, the internal operation of the refrigerant distributor 1 of the first embodiment will be described with reference to FIG.
The two-phase refrigerant that has flowed from the refrigerant inlet 11 flows into the inner pipe 12 with inertial force, collides with the closed end that is the upper part of the inner pipe 12, and the gas refrigerant and the liquid refrigerant are mixed. Although it is in a homogeneous state, a large amount of liquid refrigerant is distributed above the inner pipe 12 due to the influence of inertial force.
The two-phase refrigerant inside the inner pipe 12 flows out from the refrigerant outflow hole 15, but the diameter of the plurality of refrigerant outflow holes 15 is stepped from the refrigerant inlet 11 of the inner pipe 12 every three refrigerant outflow holes 15a, 15b, 15c. In order to suppress the outflow of the liquid refrigerant toward the closed end portion, which is the upper part of the inner pipe 12 in which a large amount of liquid refrigerant is distributed, the plurality of refrigerant outflow holes are reduced as the distance from each other increases (15a <15b <15c). The amount of liquid refrigerant flowing out is equalized, and the two-phase refrigerant is ejected evenly in the height direction.
In addition, the two-phase refrigerant that has flowed out of the refrigerant outflow holes 15a, 15b, and 15c collides with the inner wall of the outer tube 13 to be in a homogenized state, and the liquid refrigerant is uniformly distributed in the vertical direction inside the outer tube 13. Thus, the two-phase refrigerant can be evenly distributed to the plurality of branch pipes 14.

As described above, in the first embodiment, the two-phase refrigerant that has flowed in is collided with the closed end, which is the upper part of the inner pipe 12, to be homogenized, and further at the upper part of the inner pipe 12 where a large amount of liquid refrigerant is distributed. Since the refrigerant outflow holes 15a, 15b, and 15c are reduced in diameter toward the closed end side to suppress the outflow of the liquid refrigerant, there is an uneven distribution of the liquid refrigerant due to inertial force inside the inner pipe 12. In addition, the liquid refrigerant distribution inside the outer pipe 13 can be made uniform, and the two-phase refrigerant flowing out from each branch pipe 14 can be uniformly distributed.
Moreover, since the refrigerant outflow hole 15 of the inner pipe 12 is formed in a circular shape, it can be easily processed by a press or a drill, and the processing cost can be reduced.
In the first embodiment, the diameter of the plurality of refrigerant outflow holes 15 decreases as the three refrigerant outflow holes 15a, 15b, and 15c are stepped away from the refrigerant inlet 11 of the inner pipe 12 in stages. Even if the hole diameters of the plurality of refrigerant outflow holes 15 of the inner pipe 12 are gradually reduced as they move away from the refrigerant inlet 11 of the inner pipe 12, the same effects and advantages as described above are obtained.

Another configuration according to the first embodiment will be described with reference to FIG.
FIG. 3 is a cross-sectional view taken along line AA in FIG. Here, θ is an angle formed by the pipe center line of the branch pipe 14 and the hole center line of the refrigerant outflow hole 15 provided in the inner pipe 12, and the refrigerant outflow hole 15 is disposed within a range of 90 ° to 270 °. ing.
As described above, the two-phase refrigerant flowing out of the refrigerant outlet hole 15 spreads by setting the angle θ formed by the center line of the branch pipe 14 and the center line of the refrigerant outlet hole 15 of the inner pipe 12 to 90 ° to 270 °. Even if it flows out, it always collides with the inner wall of the outer tube 13, the liquid refrigerant is refined and mixed homogeneously with the gas refrigerant, and the inside of the outer tube 13 can be made to have a homogeneous refrigerant distribution. The two-phase refrigerant can be evenly distributed to the branch pipes 14.

Embodiment 2. FIG.
FIG. 4 is a sectional view of the refrigerant distributor showing Embodiment 2 of the present invention.
In the second embodiment, the same configurations as those of the first embodiment are denoted by the same reference numerals, and the description of the overlapping configurations is omitted, and different configurations will be described.
In the second embodiment, as shown in FIG. 4, the diameter of the inner pipe 12 </ b> A gradually decreases with increasing distance from the refrigerant inlet 11. The diameters of the refrigerant outflow holes 15 provided in the inner pipe 12A are the same.

Next, the operation of the refrigerant distributor according to the second embodiment will be described with reference to FIG.
The two-phase refrigerant that has flowed from the refrigerant inlet 11 flows into the inner pipe 12A with inertial force, collides with the closed end of the upper part of the inner pipe 12A, and the gas refrigerant and the liquid refrigerant are mixed. Although it becomes a homogeneous state, the density of the liquid refrigerant tends to increase toward the closed end side, which is the upper part of the inner tube 12A, due to the influence of inertial force.
On the other hand, the diameter of the inner pipe 12A becomes smaller as the distance from the refrigerant inlet 11 decreases, and the amount of liquid refrigerant flowing out from the plurality of refrigerant outlet holes 15 decreases as the distance from the refrigerant inlet 11 decreases. The amount of liquid refrigerant flowing out from the plurality of refrigerant outflow holes 15 is equalized in the height direction in combination with the density of the liquid refrigerant increasing toward the closed end side, which is the upper part, and the two-phase refrigerant is high. Spouts evenly in the direction.
In this way, the two-phase refrigerant flowing out from the plurality of refrigerant outflow holes 15 is uniformly ejected in the height direction, and further collides with the inner wall of the outer tube 13, whereby the liquid refrigerant is refined and mixed homogeneously with the gas refrigerant, The inside of the outer tube 13 can be made to have a homogeneous refrigerant distribution in the vertical direction, and the two-phase refrigerant can be evenly distributed to the plurality of flow dividing tubes 14.

  As described above, by reducing the diameter of the inner pipe 12A as the distance from the refrigerant inlet 11 decreases, the amount of liquid refrigerant flowing out from the plurality of refrigerant outlets 15 decreases as the distance from the refrigerant inlet 11 increases. The amount of liquid refrigerant flowing out from the plurality of refrigerant outflow holes is equalized in the height direction in combination with the increase in the density of the liquid refrigerant toward the closed end side that is the upper part of the pipe 12A. The two-phase refrigerant flowing out from the refrigerant outflow hole 15 is uniformly ejected in the height direction, and further collides with the inner wall of the outer tube 13, whereby the liquid refrigerant is refined and mixed homogeneously with the gas refrigerant. The interior can be made to have a homogeneous refrigerant distribution in the vertical direction, and can be evenly distributed to each path of the heat exchanger from the branch pipe 14.

Embodiment 3 FIG.
FIG. 5 is a cross-sectional view of a refrigerant distributor showing Embodiment 3 of the present invention.
In the first and second embodiments, in order to evenly distribute the homogeneous two-phase refrigerant to each branch pipe 14, the diameter of the refrigerant outlet hole 15 of the inner pipe 12 is changed in the vertical direction or the position is set. The diameter of the inner tube 12 has been changed in the vertical direction. However, in the case of this third embodiment, when the liquid refrigerant distribution in the vertical direction cannot be sufficiently uniform by itself, the refrigerant flow rate in each path is appropriately distributed. It is a thing. Note that in the third embodiment, the same configurations as those in the first embodiment are denoted by the same reference numerals, the description of the overlapping configurations is omitted, and different configurations will be described.

In the third embodiment, as shown in FIG. 5, the four circular refrigerant outlet holes 15d, 15e, 15f, the inner pipe 12B are located in the circumferential direction, for example, closest to the refrigerant inlet 11 of the inner pipe 12B. 15g, the number of the refrigerant outflow holes 15 decreases as the distance from the refrigerant inlet 11 of the inner pipe 12B increases.
Moreover, the diameter of each refrigerant | coolant outflow hole 15d, 15e, 15f, 15g is the same.
Further, the refrigerant outflow holes having a reduced number of the refrigerant outflow holes 15d, 15e, 15f, and 15g are also angle θ formed by the pipe center line of the branch pipe 14 and the hole center line of the refrigerant outflow hole 15 provided in the inner pipe 12. It is arrange | positioned in the range which is 90 degrees -270 degrees.

Next, the operation of the refrigerant distributor according to the third embodiment will be described with reference to FIG.
The two-phase refrigerant flowing in from the refrigerant inlet 11 flows into the inner pipe 12B with inertial force, collides with the closed end, which is the upper part of the inner pipe 12B, and the gas refrigerant and the liquid refrigerant are mixed. Although it becomes a homogeneous state, the density of the liquid refrigerant tends to increase toward the closed end, which is the upper part of the inner tube 12B, due to the influence of inertial force.
On the other hand, the number of refrigerant outlet holes 15 of the inner pipe 12B decreases as the distance from the refrigerant inlet 11 decreases, and the amount of liquid refrigerant flowing out from the plurality of refrigerant outlet holes decreases as the distance from the refrigerant inlet 11 increases. The amount of liquid refrigerant flowing out from the plurality of refrigerant outflow holes is equalized, and the two-phase refrigerant is higher in height as the density of the liquid refrigerant increases toward the closed end side that is the upper part of the inner pipe 12B. Spouts evenly in the direction.
Furthermore, by colliding with the inner wall of the outer pipe 13, the liquid refrigerant is refined and mixed homogeneously with the gas refrigerant, and the inside of the outer pipe 13 can be made to have a homogeneous refrigerant distribution in the vertical direction. Two-phase refrigerant can be evenly distributed.

  As described above, the number of the refrigerant outlet holes 15 of the inner pipe 13B decreases as the distance from the refrigerant inlet 11 decreases, so that the amount of liquid refrigerant flowing out from the plurality of refrigerant outlets decreases as the distance from the refrigerant inlet 11 increases. The liquid refrigerant flowing out from the plurality of refrigerant outflow holes is uniformly ejected in the height direction in combination with the increase in the density of the liquid refrigerant toward the closed end portion that is the upper portion of the inner pipe 12B. Furthermore, by colliding with the inner wall of the outer pipe 13, the liquid refrigerant becomes finer and is mixed homogeneously with the gas refrigerant, and the inside of the outer pipe 13 can be made to have a homogeneous refrigerant distribution in the vertical direction. Can be distributed to each path of the heat exchanger.

Embodiment 4 FIG.
6 is a cross-sectional view showing a wall-mounted indoor unit of a room air conditioner using the refrigerant distributor according to Embodiment 4 of the present invention, FIG. 7 is a cross-sectional view showing the same refrigerant distributor, and FIG. 8 shows the same refrigerant distributor. It is a perspective view.
In the first to third embodiments, a homogeneous two-phase refrigerant is evenly distributed to each branch pipe, but this fourth embodiment is used when the heat exchanger has a wind speed distribution. The refrigerant flow rate is appropriately distributed according to the heat load of each path.
As an example of a heat pump device using the refrigerant distributor 1A of the fourth embodiment, there is a wall-mounted indoor unit of a room air conditioner as shown in FIG.

As shown in FIG. 6, the wall-mounted indoor unit 5 is provided with an air suction port 51 in the upper part, a blower 52 is provided in the interior, and an air outlet 53 is provided in front of the lower part.
In addition, heat exchangers 3 a and 3 b are arranged in a square shape in front of the interior of the wall-mounted indoor unit 5, and another heat exchanger 3 c is disposed in the upper rear of the interior of the wall-mounted indoor unit 5. Has been placed.
And the refrigerant distributor 1A of this Embodiment 4 is formed in the shape bent according to the heat exchangers 3a and 3b. Note that 4b and 4c indicate the directions of airflow.

As shown in FIGS. 7 and 8, the bent refrigerant distributor 1A according to the fourth embodiment includes a bent inner pipe 12C having a refrigerant inlet 11A, a bent outer pipe 13A containing the inner pipe 12C, It consists of a plurality of flow dividing tubes 14A and 14B provided at a predetermined interval on the outer tube 13A, and has a double tube configuration.
The diameters of the plurality of refrigerant outflow holes 15h arranged above the bent portion of the inner pipe 12C are larger than the diameter of the refrigerant outflow holes 15i below the bent portion. These refrigerant outflow holes 15h and 15i and the diversion pipes 14A and 14B are arranged at substantially equal intervals.

Next, the operation | movement at the time of the air_conditionaing | cooling operation of the wall-mounted indoor unit 5 of the room air conditioner using the refrigerant distributor 1A of this Embodiment 4 is demonstrated based on FIGS.
During the cooling operation, the two-phase refrigerant equally distributed by the refrigerant distributor 1A flows through the heat exchangers 3a and 3b disposed inside the wall-mounted indoor unit 5. A blower 52 is disposed downstream of the heat exchangers 3 a and 3 b, and the indoor air 4 b is sucked from the air suction port 51 as the blower 52 rotates.
The sucked air passes through the heat exchangers 3a and 3b, exchanges heat with the low-temperature two-phase refrigerant flowing inside the heat exchangers 3a and 3b, becomes low-temperature air, and is sucked into the blower 52. After passing through, it flows out to the air outlet 53 and is blown out into the indoor space.

Next, the operation of the refrigerant distributor 1A used in the wall-mounted indoor unit 5 of the fourth embodiment will be described in detail with reference to FIG.
The two-phase refrigerant that has flowed in from the refrigerant inlet 11A flows into the inner pipe 12C, but collides with a closed end that is the upper part of the inner pipe 12C, and the gas refrigerant and the liquid refrigerant are mixed to become a homogeneous state. .
The homogenous two-phase refrigerant flows out of the refrigerant outflow holes 15h and 15i and out of the outer pipe 13A. The refrigerant that has flowed out of the refrigerant outflow holes 15h and 15i collides with the inner wall of the outer pipe 13A, becomes a more homogenized state, and becomes a state in which a homogeneous two-phase refrigerant is distributed in the vertical direction inside the outer pipe 13A. Two-phase refrigerant is distributed to the tubes 14A and 14B.

Here, the wall-mounted indoor unit 5 of the room air conditioner may have a front panel in consideration of design, and in this case, the air suction port 51 is disposed only on the upper surface of the indoor unit 5.
In such a configuration, the air sucked from the air suction port 51 is easy to pass through the heat exchanger 3a installed in the upper part, and difficult to pass through the heat exchanger 3b installed in the lower part. Wind speed distribution occurs in the front wind speed of 3a, 3b.
Thereby, since the heat load of the upper heat exchanger 3a with a fast front wind speed is larger than the heat load of the lower heat exchanger 3b with a slow front wind speed, when the two-phase refrigerant is evenly distributed, the upper heat exchanger 3a is not capable of providing sufficient capacity due to insufficient refrigerant, and the lower heat exchanger 3b is in a state where the flow rate of the refrigerant is too large with respect to the heat load. Problems such as reduced reliability occur.

  In the refrigerant distributor 1A of the fourth embodiment, the diameter of the refrigerant outflow hole 15h disposed above the bent portion of the inner pipe 12C is made larger than the diameter of the refrigerant outflow hole 15i below the bent portion. Therefore, the refrigerant distribution inside the outer pipe 13A is larger in the upper part than in the bent part, and the refrigerant distribution amount is larger in the upper diverter pipe 14A side than in the bent part, and is smaller in the lower diverter pipe 14B side. Combined with the fact that the heat load of the upper heat exchanger 3a with the fast front wind speed is larger than the heat load of the lower heat exchanger 3b with the slow front wind speed, the heat load of the downstream heat exchangers 3a and 3b Therefore, an appropriate refrigerant flow rate can be realized.

As described above, since the diameter of the refrigerant outflow hole 15h disposed above the bent portion of the inner pipe 12C is larger than the diameter of the refrigerant outflow hole 15i below the bent portion, the refrigerant distribution amount is bent. It is possible to reduce the lower diverter pipe 14B side more than the upper part, and the heat load of the upper heat exchanger 3a with a fast front wind speed is lower heat exchanger with a slow front wind speed. Realizing an appropriate refrigerant flow rate for the heat load of the downstream heat exchangers 3a and 3b without changing the diameter and length of the branch pipes 14A and 14B in combination with being larger than the heat load of 3b Can do.
In the fourth embodiment, the room air conditioner has been described as an example of the heat pump device. However, the same effect can be obtained even when used in other air conditioners, heat pump water heaters, chillers, and the like.
As an application example of the present invention, heat exchange performance can be improved by evenly distributing the two-phase refrigerant, and it can be used for a heat exchanger of a heat pump apparatus that needs to improve performance.

  DESCRIPTION OF SYMBOLS 1 Refrigerant flow divider, 2 Gas merge pipe, 3 Heat exchanger, 4 Air, 11 Refrigerant inlet, 12 Inner pipe, 13 Outer pipe, 14 Shunt pipe, 15 Refrigerant outflow hole, 15a-15c Refrigerant outflow hole.

Claims (7)

An inner pipe having a refrigerant inlet into which the refrigerant flows and having an end opposite to the refrigerant inlet closed, an outer pipe accommodating the inner pipe, and a predetermined interval between the outer pipe and the outer pipe. Provided with a plurality of shunt pipes for flowing refrigerant in each path,
A plurality of refrigerant outflow holes are formed at intervals in the pipe length direction in the inner pipe, and the diameters of the plurality of refrigerant outflow holes are made smaller as they are stepped away from the refrigerant inlet for each of the plurality of refrigerant outflow holes. The refrigerant distributor is characterized in that the intervals between the refrigerant outflow holes are continuously formed at substantially the same interval. An inner pipe having a refrigerant inlet into which the refrigerant flows and having an end opposite to the refrigerant inlet closed, an outer pipe accommodating the inner pipe, and a predetermined interval between the outer pipe and the outer pipe. Provided with a plurality of shunt pipes for flowing refrigerant in each path,
A plurality of refrigerant outflow holes are formed in the inner pipe at intervals in the pipe length direction, and the diameter of the plurality of refrigerant outflow holes decreases as the distance from the refrigerant inflow port increases stepwise for every two or more refrigerant outflow holes. The refrigerant distributor is characterized in that the refrigerant outlet holes are continuously formed and arranged at substantially the same intervals. An inner pipe having a refrigerant inlet into which the refrigerant flows and having an end opposite to the refrigerant inlet closed, an outer pipe accommodating the inner pipe, and a predetermined interval between the outer pipe and the outer pipe. Provided with a plurality of shunt pipes for flowing refrigerant in each path,
A plurality of refrigerant outflow holes are formed in the inner pipe at intervals in the pipe length direction, and the intervals between the refrigerant outflow holes are continuously formed at substantially the same interval, and are arranged.
The refrigerant distributor according to claim 1, wherein a diameter of the inner pipe is reduced with increasing distance from the refrigerant inlet. An inner pipe having a refrigerant inlet into which the refrigerant flows and having an end opposite to the refrigerant inlet closed, an outer pipe accommodating the inner pipe, and a predetermined interval between the outer pipe and the outer pipe. Provided with a plurality of shunt pipes for flowing refrigerant in each path,
A plurality of refrigerant outflow holes are formed in the inner pipe at the same interval as the plurality of flow dividing pipes in the tube length direction and in the circumferential direction, and the number of the plurality of refrigerant outflow holes decreases as the distance from the refrigerant inflow port increases. Thus, the refrigerant distributor is characterized in that the refrigerant outlet holes are continuously formed and arranged at substantially the same interval.   The refrigerant distributor according to any one of claims 1 to 4, wherein an angle formed by a hole center line of the refrigerant outflow hole and a pipe center line of the branch pipe is 90 ° to 270 °.   The refrigerant distributor according to claim 1, wherein the refrigerant outflow hole is circular.   A heat pump device comprising a heat exchanger using the refrigerant distributor according to claim 1.

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