JP2016217542A - Refrigerant distributor and manufacturing method thereof - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerant distributor capable of making a predetermined distribution ratio or a distribution ratio within a predetermined range, even in a case where a refrigerant flow rate greatly changes, and provide a manufacturing method thereof.SOLUTION: A refrigerant distributor 1 includes an introduction part 2 into which refrigerant is introduced, a first derivation part 4 and a second derivation part 5 to which refrigerant is derived, and a branch part 3 at which refrigerant fed from the introduction part 2 is branched into the first derivation part 4 and the second derivation part 5. The branch part 3 has a projection part n provided on an inner wall surface 3h1 so as to project toward the introduction part 2. The projection part n has a such a shape that the height of end parts n2, n2 is lower than that of a central part n1.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a refrigerant distributor and a manufacturing method thereof.

The recent global demand for energy saving has been recognized as a demand for improvement in refrigeration and air conditioning technology, in particular, heat exchange efficiency.
In the refrigerating and air-conditioning technology, technological innovation and performance improvement are required for each component, for example, each component of the compressor, the refrigeration cycle, the heat exchanger, and the blower.

It is well known that, in the refrigeration cycle, it is possible to improve the heat exchange efficiency of the heat exchanger and contribute to energy saving by realizing proper distribution of the refrigerant to the heat exchanger.
For example, as a prior art document, the refrigerant distributor described in Patent Document 1 is frequently used in the refrigeration and air conditioning industry.

Japanese Patent No. 3390565

Incidentally, in the refrigeration and air conditioning technology, it is important to improve the distribution performance of the refrigerant in the heat exchanger. In particular, stabilization of the refrigerant distribution is an important issue because it affects the heat exchange performance.
Generally, a refrigerant distributor having two refrigerant outlets for one refrigerant introduction part is used, and there are roughly two types of forms, and the outer shape is divided into a U-shape and a Y-shape. Is done.

In the U shape, the direction of the refrigerant outlet portion is substantially perpendicular to the direction of the refrigerant inlet portion serving as the refrigerant inlet. Therefore, the distribution of the refrigerant in the two lead-out parts is provided by giving a notch shape to the refrigerant branch part where the refrigerant between the refrigerant introduction part and the refrigerant lead-out part is separated from the center of the two lead-out parts. It becomes possible to provide a difference in the ratio.
The Y shape branches the refrigerant in the same direction as the refrigerant introduction portion and the refrigerant outlet direction.

As the derivation type, an eccentric type in which the refrigerant introduction part is not arranged at an equal distance from the derivation part is often used.
There are two manufacturing processes for the above-described refrigerant distributor.
Applying hydroforming to a straight pipe, so-called hydraulic bulge processing, forming a convex part to be a refrigerant introduction part, then bending, cutting and molding the convex part, and a distributor, After the straight pipe is bent, hydroforming is performed to process the convex portion.

When the hydroforming process is performed before the first process, the straight pipe process is long, so that it is easy to automate and the hydroforming process can be performed in a state close to ideal conditions.
As a demerit, it is often necessary to adjust the equipment to manufacture the eccentric type distributor.

  On the other hand, in the case of so-called bent pipe hydroforming, in which hydroforming is performed after the pipe of the second step is bent, the manufacture of the normal distributor such as the U-shape and the Y-shape described above and the eccentric distributor There is an advantage that production can be performed with the same equipment with relatively few setup changes.

  As a demerit, in the hydroforming process, it is ideal to apply a load to the end face of the material from the opposite direction, and to process in a straight pipe state corresponds to this ideal state. By performing hydroforming after first bending the pipe, it is not possible to process in an ideal state, but some consideration is required.

These processing methods have advantages and disadvantages, but there is no difference in the essence of using a tube with a convex shape added by hydroforming.
It is possible to form a bifurcated refrigerant distributor by cutting the convex end face added by the hydroforming process in a subsequent process and processing it into a specified pipe diameter to form a refrigerant introduction part.

  Up to this point, the method of manufacturing the refrigerant flow distributor by hydroforming has been described. One of the methods for improving the distribution performance is as follows. That is, as shown in FIG. 5 described later, a convex notch n100 is added to the pipe inner wall surface 103h1 of the collision surface of the refrigerant introduced from the refrigerant introduction portion 102 of the refrigerant distributor 100 to the branching portion 103, and the convex shape By setting the position of the notch n100 according to the distribution ratio of the refrigerant, the distribution ratio of the refrigerant can be adjusted, and the heat exchange efficiency can be improved.

  For example, in an outdoor unit of an air conditioner, the blower is not arranged at a uniform position with respect to the refrigerant pipe of the heat exchanger, and the refrigerant having a high heat exchange efficiency is surely determined from the positional relationship between each refrigerant pipe and the blower. A pipe and a low refrigerant pipe are generated.

It has been found that the heat exchange efficiency of the entire outdoor unit is improved by supplying a large amount of refrigerant to the refrigerant tubes with high heat exchange efficiency and supplying a small amount of refrigerant to the low refrigerant tubes.
On the other hand, in the technique of providing the convex notch n100 to the refrigerant flow distributor 100 described above, the position of the notch n100 is arranged at an unequal position with respect to the derivation units 104 and 105 in the two derivation directions. A large amount of refrigerant can be guided to one of the derivation unit 104 or the derivation unit 105. Thereby, it is possible to form an efficient heat exchange cycle.
The above is obvious from Patent Document 1, but even with these techniques, it is difficult to distribute the refrigerant at a perfect ratio.

As a specific technical problem, there is a change in refrigerant distribution behavior depending on the flow rate.
In general, it has been found that the larger the flow rate, the more prominent the refrigerant diversion ratio.
For example, the distribution ratio of 45%: 55% at a large flow rate is 46%: 54% at a medium flow rate and 47%: 53% at a low flow rate. It becomes close to an equal ratio of 50%.
These results are none other than the problem to be solved in the refrigerant distribution performance in an environment where the refrigerant flow rate greatly changes.

  The present invention was devised in view of the above circumstances, and it is an object of the present invention to provide a refrigerant distributor capable of setting a diversion ratio within a predetermined range or a predetermined range even in an environment where the refrigerant flow rate greatly changes, and a method for manufacturing the same. To do.

  In order to solve the above-described problem, the refrigerant distributor of the present invention includes an introduction part into which a refrigerant is introduced, a first derivation part and a second derivation part from which the refrigerant is derived, and a refrigerant sent from the introduction part. A branch portion branched into the first lead-out portion and the second lead-out portion, the branch portion having a convex portion projecting toward the introduction portion on an inner wall surface, The end portion has a shape lower than the central portion.

  ADVANTAGE OF THE INVENTION According to this invention, even in the environment where a refrigerant | coolant flow volume changes a lot, the refrigerant | coolant divider | distributor which can be made into a predetermined or the predetermined flow-division ratio, and its manufacturing method are realizable.

(A) is a top view of the refrigerant distributor according to the first embodiment of the present invention, (b) is a view in the direction of arrow A in (a), (c) is a view in the direction of arrow B in (a), (d) (A) CC sectional drawing. FIG. 3 is a cross-sectional perspective view of the refrigerant distributor according to the first embodiment. FIG. 1B is an enlarged view of the notch in the direction B of FIG. 1A, and FIG. (A) is a top view of a refrigerant distributor of a comparative example (conventional), (b) is a view taken in the direction of arrow D in (a), (c) is a view taken in the direction of arrow E, (d) is a view of FIG. FF sectional drawing of 4 (a). The cross-sectional perspective view of the refrigerant distributor of a comparative example. Branch performance results in a comparative example (prior art). The branch performance result in Embodiment 1 (this invention). The schematic diagram which shows the flow of the refrigerant | coolant in the notch vicinity in the refrigerant | coolant piping of the refrigerant | coolant branch part of Embodiment 1. FIG. The figure which shows the experimental data showing the relationship between the height of the notch n, and the dispersion | distribution of a shunt flow. (A) is a front view showing the original shape of the refrigerant distributor, (b) is a cross-sectional view showing a process of forming a notch in the original shape of the refrigerant distributor, and (c) is a front view of the completed refrigerant distributor. (A) is a perspective view of an upper mold | type, (b) is a perspective view of a lower mold | type, (c) is an enlarged front view which shows the state which press-molds a notch. (A) is a top view of the refrigerant distributor according to the second embodiment of the present invention, (b) is a view taken in the direction of the arrow G in (a), (c) is a cross-sectional view along HH in (b), (d). FIG. 11 is a cross-sectional view taken along the line II of FIG. The figure which shows a typical refrigeration cycle structure. The figure which shows a typical refrigeration cycle structure. FIG. 2A is a view corresponding to the arrow B in FIG. 1 of the notch of the first modification, and FIG. 2B is a view corresponding to the arrow A of FIG. (A) is a view corresponding to the arrow B in FIG. 1 of the notch of the second modification, and (b) is a view corresponding to the arrow A in FIG. 1A is a view corresponding to the direction of arrow B in FIG. 1 of the notch of the third modification, and FIG. 1B is a view corresponding to the direction of arrow A of FIG. (A) is a top view of the Y-shaped tube of modification 4, (b) is an L direction arrow view of (a), (c) is an M direction arrow view of (a). (A) is a top view of the U-shaped tube of the modified embodiment 5, (b) is a view in the R direction of (a), (c) is a view in the P direction of (b), and (d) is (a) ) QQ sectional view.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings as appropriate.
The present invention relates to an air conditioner and its refrigeration cycle components.
<< Embodiment 1 >>
FIG. 1A is a top view of the refrigerant distributor of Embodiment 1 according to the present invention, FIG. 1B is a view in the direction of arrow A in FIG. 1A, and FIG. 1A is a view in the direction of the arrow B in FIG. 1A, and FIG. 1D is a cross-sectional view taken along the line CC in FIG. FIG. 2 is a cross-sectional perspective view of the refrigerant distributor of the first embodiment.

The refrigerant distributor 1 according to the first embodiment includes one refrigerant introduction unit 2 and two lead-out units 4 and 5.
The refrigerant distributor 1 functions to distribute the refrigerant from one introduction part 2 to two lead-out parts 4 and 5. The outer shape of the refrigerant distributor 1 is formed by subjecting a straight pipe to the above-described hydroforming process, so-called hydraulic bulge process.

A refrigerant branching section 3 is formed between the introduction section 2 and the two outlet sections 4 and 5. The refrigerant branch part 3 is formed with a notch n that protrudes toward the introduction part 2 so as to divert the refrigerant that has entered the introduction part 2 to the deriving part 4 and the deriving part 5 at a predetermined ratio ( (See FIG. 2).
The refrigerant flows into the refrigerant distributor 1 from the introduction unit 2, and is divided into the derivation unit 4 and the derivation unit 5 under the influence of the notch n in the refrigerant branching unit 3.

3A is an enlarged view of the notch as viewed in the direction B of FIG. 1A, and FIG. 3B is an enlarged view of the notch as viewed in the direction of the arrow A in FIG. 1A.
As shown in FIG. 3A, the notch n has an arch shape that forms a curve in which the central portion n1 is high and the end portions n2 and n2 are low when viewed from the lead-out portions 4 and 5. ing. Further, as shown in FIG. 3B, the notch n has a shape in which the central portion n1 is high and the end portions n3 and n3 are low with respect to the Y-axis direction. Note that the notch root n9 may or may not be present.
In other words, the end portions n2 and n2 of the notch n of the convex portion have a lower height than the central portion n1 of the notch n with respect to the tube inner wall surface 3h1 to which the refrigerant sent from the introduction portion 2 hits or its extended surface. Yes. In addition, as shown to the dashed-two dotted line of FIG.3 (b), it is preferable when the center part n1 is made into an arch shape with a high center. This facilitates smooth diversion of the refrigerant in the Y direction.

The notch n changes the flow rate diverted to the derivation unit 4 and the derivation unit 5 by the eccentricity of the derivation unit 4 and the derivation unit 5 from the center position and the shape of the notch n, and suppresses variation in the diversion. ing.
That is, by changing the position where the refrigerant is deflected from the central axis O (see FIGS. 1A and 1B) of the derivation part 4 and the five directions of the introduction part 2 of the notch n, the derivation part 4 and the derivation part 5 The diversion ratio at the two branches is adjusted.
For example, in a copper tube having an outer diameter of 8 mm and a wall thickness of 0.8 mm, when the diversion ratio at a large flow rate is set to 45:55, the center position of the notch n is approximately 1.5 mm in height and the diversion ratio from the center O. The set diversion ratio can be obtained by deflecting 1 mm toward the 45 side.
Further, as will be described later, the notch n has a predetermined arch shape with a curved center portion n1 and lower end portions n2 and n2 with respect to the X-axis direction when viewed from the lead-out portions 4 and 5. Therefore, the variation in the diversion ratio can be reduced. In addition, it is preferable that the central part n1 is high and the end parts n3 and n3 are low with respect to the Y-axis direction.

<Comparison between Notch n100 of Comparative Example and Notch n of Embodiment 1>
For comparison with the notch n of the first embodiment, FIG. 4 shows a refrigerant distributor 100 of a comparative example (prior art). 4A is a top view of a refrigerant distributor of a comparative example (conventional), FIG. 4B is a view in the direction of arrow D in FIG. 4A, and FIG. 4C is FIG. It is an E direction arrow directional view of (a), and FIG.4 (d) is FF sectional drawing of Fig.4 (a). FIG. 5 is a cross-sectional perspective view of a refrigerant distributor of a comparative example.
The refrigerant distributor 100 of the comparative example has one refrigerant introduction unit 102 and two lead-out units 104 and 105.

The refrigerant flows into the refrigerant distributor 1 from the introduction unit 2, and is divided into the derivation unit 104 and the derivation unit 5 under the influence of the notch n100 in the refrigerant branching unit 3.
The notch n100 of the comparative example has a flat planar shape with the upper surface n101 as viewed in the direction of the arrow E in FIG. 4A (see FIG. 4C). On the other hand, the notch n of the first embodiment has an arch shape that forms a curve with the central portion n1 being high and the end portions n2 and n2 being low as seen in the direction of the arrow B in FIG. (See FIG. 5).

  FIGS. 6 and 7 show the branching performance results in the comparative example (prior art) and Embodiment 1 (the present invention). The experimental data when the flow rate of the refrigerant is large, medium, and small with the intention of flowing 45% out of% are respectively shown. The refrigerant is a pseudo refrigerant in which water and air are uniformly mixed at a specified ratio for the purpose of imitating the refrigerant state of the air conditioner. # 1 to # 5 represent test products.

The large flow, medium flow, and small flow during the experiment indicate the relative flow rate of the pseudo refrigerant. Specific flow conditions of the pseudo refrigerant are the following conditions at an air temperature of 20 to 25 ° C.
The small flow rate is 0.35L / liter for water and 15L / minute for air.
Medium flow rate is 0.70L / min for water and 32.5L / min for air.
The large flow rate is 1.17 L / min for water and 50 L / min for air.
It has been found that the study with this pseudo refrigerant closely follows the study with the actual machine.

From FIG. 6, the notch n100 in FIG. 4 of the comparative example has a large flow rate average of 45.2%, a medium flow rate average of 46.1%, and a small flow rate average of 47.0%.・ The average of the dispersion (maximum value-minimum value) of each medium and small flow rate was 2.1%.
On the other hand, the notch n of FIG. 1 and FIG. 3 of Embodiment 1 shows that the average of the large flow rate is 45.2%, the average of the medium flow rate is 45, 7%, and the average of the small flow rate is FIG. 46.0%, and the average of the variations (maximum value-minimum value) of the large, medium, and small flow rates was 0.76%.

With reference to FIGS. 6 and 7, it can be seen that in both the comparative example and the first embodiment, the large flow rate is close to 45% of the target value and the diversion is performed well.
Comparing the data of the comparative example and the first embodiment, the notch n shown in FIGS. 1 to 3 of the first embodiment is larger, the middle, and the lower flow rate than the notch n100 shown in FIGS. 4 and 5 of the comparative example. Equal to or closer to 45% of the target diversion. Moreover, the fluctuation of the partial flow rate is greatly suppressed by setting the notch n of the first embodiment to 0.76% in the first embodiment compared to 2.1% in the comparative example. I found out.

  When the branching performance of the refrigerant distributor 100 of the comparative example (prior art) illustrated in FIGS. 4 and 5 is measured, the resistance on the wall surface is reduced compared to the large flow rate when the medium flow rate and the small flow rate are considered. As a result, it has been found that the flow velocity difference between the tube center and the wall surface 103s (see FIG. 5) is reduced, and the branching performance is changed as described in the section of the prior art. This became clear from the results of FIG.

  On the other hand, in the arch shape of the notch n of the first embodiment (see FIG. 2 and FIG. 3A), as described in the results of FIG. 6 and FIG. It is possible to divert at a value closer to the set diversion ratio than the shape of the notch n100 according to the prior art. Furthermore, as described above, the fluctuation of the diversion ratio is suppressed from an average of 2.1% in the comparative example to an average of 0.76% in the first embodiment.

FIG. 8 is a schematic diagram illustrating a refrigerant flow in the vicinity of a notch in the refrigerant pipe of the refrigerant branching portion of the first embodiment.
As shown in FIG. 8, the flow r0 far from the notch n has a slow flow velocity of the flow r02 in the vicinity of the pipe inner wall surface 3h1 due to the frictional resistance of the pipe inner wall surface 3h1 of the refrigerant pipe 3h and the viscosity of the refrigerant. The flow rate is fast. Therefore, the flow r01 on the center side has a streamline closest to the notch n.

  Further, when the flow proceeds downstream, the flow rate of the refrigerant flow r1 becomes slow because the flow r11 on the central side starts to hit the notch n on the downstream side. Therefore, compared with the upstream flow r0, the flow r1 is a slow flow in which the central flow r11 is close to the flow r12 in the vicinity of the pipe inner wall surface 3h1, and the flow velocity difference between the central side and the vicinity of the pipe inner wall surface 3h1 is reduced.

Theoretically, when the target fluid is assumed to be an incompressible Newtonian fluid, it receives a frictional resistance from the inner wall surface 3h1 when passing through the refrigerant pipe 3h.
From Hagen-Poiseuille's law derived from theoretical states with limited conditions from the Navier-Stokes equation, the flow velocity distribution in the pipe is expressed by the following equation.

u (r) = (gI / 4ν) · (a ² −r ² ) (1)
Here, u is a flow velocity, a is a circular pipe radius of the refrigerant pipe 3h, r is a distance from the center of the circular pipe of the refrigerant pipe 3h, g is a gravitational acceleration, ν is a kinematic viscosity coefficient, and I is an energy gradient.
This equation shows that in a viscous fluid laminar fluid, the fluid velocity distribution in the circular tube draws a parabola with the center of the circular tube being fast and the wall surface side being slow.

  Further, when the flow proceeds downstream, the refrigerant flow r2 close to the notch n, the central flow r21 hits the notch n, and due to viscosity, the refrigerant flows r22 near the inner wall surface 3h1 of the refrigerant pipe 3h, and merges and advances. .

  From the above, as an operation principle in the first embodiment (the present invention), the refrigerant (r01, r11, r21) at the center of the refrigerant pipe 3h having a high flow velocity has a high arched portion of the notch n ( By colliding with the central portion n1), it is presumed that the structure and shape are suitable for the flow path for guiding and following the refrigerant (r02, r12, r22) on the pipe inner wall surface 3h1 side, which is slow in speed.

In the prior art, the convex shape at the center of the circular tube and the inner wall surface 103h1 (see FIG. 5) has the same height and shape despite the difference in flow velocity as described above.
On the other hand, in the present invention, the notch-added mold is formed so that the convex shape of the central part of the circular tube is higher than the inner wall surface 3h1 of the pipe (see FIG. 2) so that the central part of the circular tube is arched. The shape of n is formed.

FIG. 9 is a diagram showing experimental data representing the relationship between the height of the notch n and the variation in the diversion. Using the arch height h1 (see FIG. 3A) and the wall thickness t of the refrigerant pipe 3h as the arch height H on the horizontal axis, the arch height H is defined as follows.
H = h1 / t
The vertical axis represents the variation in the diversion (= maximum% -minimum%).
The alternate long and short dash line in FIG. 9 indicates the diversion variation of the refrigerant pipe 3h having an outer diameter of 6.35 mm and a wall thickness of t0.8 mm. The broken line shows the variation in the shunt flow of the refrigerant pipe 3h having an outer diameter of 7.0 mm and a wall thickness of t0.8 mm. The solid line shows the variation in the diversion of the refrigerant pipe 3h with an outer diameter of 8.0 mm and a wall thickness of t0.8 mm.

From FIG. 9, by providing the height difference (arch portion height H) at least 1.5 times the pipe wall thickness t, fluctuations in the diversion ratio due to the magnitude of the flow rate due to the flow rate of the refrigerant are improved. be able to. More specifically, when the arch height H of the height difference between the tube center of the notch n and the tube inner wall surface 3h1 is less than 1.5 times, the effect is generally small, and the effect is saturated when 2.5 times or more. Turned out to be.
Here, since the notch n is formed by press molding, if the arch portion height H becomes too large (for example, H> 3.0), the refrigerant pipe 3h is insufficient in thickness, and a phenomenon such as meat breaking occurs. .
Further, when the arch height H is increased, a vibration sound is generated.

  In summary, if the arch height H = h1 / t is too small, the effect of the notch n on the refrigerant flow is reduced. If the arch height H = h1 / t is too large, the effect on the refrigerant flow is saturated, and no effect exceeding a certain effect (effect at H = 1.5 to 2.5 hours) is observed. Further, when H is large, a phenomenon that vibration noise is generated occurs.

As a result of the examination, when the arch height H is 1.3 t or more and 2.6 t or less, the variation in shunt flow is small and good, and when the arch height H is 1.5 t or more and 2.5 t or less is optimal.
From these examinations, it was confirmed that the refrigerant distributor 1 according to Embodiment 1 can obtain the shunt ratio set in the flow region in the air conditioner more accurately than in the prior art.

<Formation method of notch n>
Next, a method for forming the notch n shown in FIGS. 1 and 2 will be described.
The notch n is formed after the shape of the refrigerant distributor 1 is formed by hydroforming. FIG. 10A is a front view showing the original shape of the refrigerant distributor, and FIG. 10B is a cross-sectional view showing a process of forming a notch in the original shape of the refrigerant distributor, and FIG. ) Is a front view of the completed refrigerant distributor.
11A is a perspective view of the upper die, FIG. 11B is a perspective view of the lower die, and FIG. 11C is an enlarged front view showing a state where the notch is press-molded. .

First, the element shape 1S of the refrigerant distributor 1 shown in FIG. 10A is formed by hydroforming from a straight pipe or the like of the element pipe.
After that, a flat (flat) flat portion u2 is formed at the top shown in FIG. 11A, and an upper mold U having a convex portion u1 having inclined portions u3 and u4 that spread upward is prepared. . Further, as shown in FIG. 11B, a lower mold S having an arch-shaped recess s1 is prepared. The concave part s1 of the lower mold S has a shape in which the central part s1a is deep, the end parts s1b and s1c are formed to a shallow depth, and an arch-shaped convex notch n is formed.

Then, as shown in FIG. 10B and FIG. 11C, the refrigerant distributor 1 having the notch n is pressed by pressing with the lower mold S and the upper mold U in the directions of the white arrows β1 and β2. Completed (see FIG. 10C).
As described above, it is better to provide the flat portion u2 (see FIG. 11 (a)) than the arched shape of the press jig tool (upper die U) outside the pipe because of the configuration of the die jig tool.
In the first embodiment (the present invention), the thickness of the notch n forming portion is approximately 20 to 40% thicker than the raw tube due to the effect of hydroforming before the press forming of the notch n. ing.
With the above-mentioned jig / tool structure, an arch-shaped convex notch n can be formed.

Moreover, when the main circular pipe center part of this Embodiment 1 comprises convex shape in an arch shape, the notch part n of a circular pipe center part can be shape | molded more thickly than a raw tube thickness. In the region of the branch portion 3 where the notch n of the convex portion is formed, the central region of the notch n is thicker than the end region of the notch n.
This thickening effect can reduce the vibration at the time of the diversion observed above the notch n height of about 3t, and as a result, it is effective for the stable diversion of the refrigerant.

  As described above, in the prior art, there is a problem (problem) in the stability of distribution performance depending on the flow rate of the refrigerant. However, in the first embodiment, a deviation from the target value of the distribution performance due to the flow rate of the refrigerant. Became smaller. In addition, variation in distribution performance can be suppressed depending on the flow rate of the refrigerant.

Therefore, the problem (problem) of the stability of the distribution performance can be improved and solved by the flow rate of the conventional refrigerant. That is, the distribution performance of the refrigerant distributor 1 which is difficult to obtain the target diversion ratio accurately due to the flow rate of the refrigerant is more stable than that of the prior art.
According to the configuration of the first embodiment, it is possible to effectively suppress the deviation with respect to the deviation from the predetermined diversion ratio due to the change in the flow rate of the refrigerant, and to make it close to the predetermined diversion ratio.

<< Embodiment 2 >>
Although the refrigerant distributor 1 of the cheese tube (T-shaped tube) has been described in the first embodiment, an actual U-shaped refrigerant distributor 21 (see FIG. 12) in the air conditioner will be described in the second embodiment.
When the configuration of the present invention is mounted on an air conditioner, a U-shaped pipe joint saves more space than a T-shaped cheese pipe, and the degree of freedom in arrangement is high.

  12 (a) is a top view of the refrigerant distributor of Embodiment 2 according to the present invention, FIG. 12 (b) is a view in the direction of the arrow G in FIG. 12 (a), and FIG. FIG. 12B is a cross-sectional view taken along the line H-H, and FIG. 12D is a cross-sectional view taken along the line II in FIG.

The refrigerant distributor 21 according to the second embodiment includes one introduction unit 22, two derivation units 24 and 25, and an introduction unit 22 and a branching unit 23 between the derivation units 24 and 25.
The refrigerant distributor 21 has a U-shape with a branch portion 23 and lead-out portions 24 and 25 in FIG.

  As shown in FIG. 12C, a notch 2n similar to that of the first embodiment is formed in the branch portion 23. The notch 2n has an arch shape in which the center 2n1 is high and the ends 2n2 and 2n2 are low when viewed from the lead 24 or the lead 25. Further, as shown in FIG. 12 (d) of the II cross section of FIG. 12 (a) in FIG. 12 (a), the notch 2n has a high central portion 2n1 and a low one end 2n3 and the other end 2n4. It has a shape.

As shown in FIGS. 12B and 12D, the receiving portion 2u of the notch 2n is different from the symmetrical V-shaped receiving portion 1u of the first embodiment (see FIGS. 1B and 1D), It is an asymmetric receiving portion 2u.
Regarding the notch 2n, in consideration of the life of the press tool, it is desirable that the notch 2n has an asymmetrical receiving portion 2u to release the processing pressure, rather than a symmetrical V-shaped receiving portion 1u. Accordingly, as shown in FIGS. 12B and 12D, the one end 2n3 and the other end 2n4 as viewed in the G direction in FIG. 12A are relative to the center line O1 of the center 2n1. Asymmetric.
The notch 2n is press-molded by the same method as in the first embodiment.

As an air conditioner to which the present invention is applied, FIGS. 13 and 14 show typical refrigeration cycle configurations. FIGS. 13 and 14 are configuration diagrams of one refrigeration cycle to which the refrigerant distributor 1 (21) of the first embodiment (2) is applied.
13 and 14 show the configuration of the refrigeration cycle during heating operation. FIG. 13 shows an outdoor unit, and FIG. 14 shows an indoor unit.

  The high-temperature and high-pressure gas refrigerant discharged from the compressor 6 shown in FIG. 13 flows into the indoor heat exchanger 12 of FIG. 14, and heat is exchanged with indoor air in the indoor heat exchanger 12 to give heat. Thereafter, the refrigerant recirculates to the outdoor unit in a gas-liquid mixed state, the pressure is adjusted by the electric expansion valve 11 of FIG. 13, and is distributed by the refrigerant distributor 1 (21) at a predetermined diversion ratio. The refrigerant distributed by the refrigerant distributor 1 (21) flows into the outdoor heat exchanger 7.

Thereafter, the refrigerant gasified by heat exchange in the outdoor heat exchanger 7 is returned to the compressor 6 via the flow path switch 8.
In addition, in the refrigeration cycle, the silencer 9 and the strainer 10 (see FIG. 13) are used for the purpose of homogenizing and quieting the refrigerant and protecting the equipment from contamination, and the refrigerant throttle valve 13 (see FIG. 14) for the purpose of improving the dehumidification efficiency. ) Etc. are arranged.

A plurality of refrigerant distributors 1 (21) may be used indoors and outdoors.
In this example, in the outdoor unit shown in FIG. 13, one refrigerant distributor 1 (21) is applied near the outdoor heat exchanger 7, and in the indoor unit shown in FIG. 14, four refrigerants are provided around the indoor heat exchanger 12. The case where distributor 1 (21) is applied is shown.

In summary, according to the present invention, after the external shape of the refrigerant distributor 1 (21) is manufactured by hydroforming, a convex notch n (2n) is formed by pressing, and the refrigerant has a specified flow dividing ratio. Shunt 1 (21) is provided.
In the notch n (2n) formation step, when the convex shape is formed, the center of the convex shape is 1.3 to. A press mold (lower mold S, upper mold U) is manufactured so that a convex shape having a curved surface shape with a height difference of 5 times or more can be formed.

Specifically, the convex shape n1 (2n1) on the tube center side of the refrigerant introduction portion 2 (22) is increased, and the end portion n2 (2n2) on the tube inner wall surface 3h1 (23h1) side is decreased. A convex shape is formed.
In consideration of the tool life of the press die, the shape may be asymmetric when viewed from the front as a convex shape as shown in FIGS. 12 (a), 12 (b), and 12 (d).
As described above, the convex notch n (2n) of the refrigerant introduction part 2 (22), which is indispensable for component functions, is provided with a height difference between the center of the refrigerant introduction part 2 (22) and the pipe inner wall surface 3h1 (23h1). This is the point of the present invention.

<< Modification 1 >>
15A is a view corresponding to the arrow B in FIG. 1 of the notch of the first modification, and FIG. 15B is a view corresponding to the arrow A of FIG.
As shown in FIG. 15A, the notch 3n of the first modification has a triangular shape with a sharp central portion 3n1 and high end portions 3n2 and 3n2. Further, as shown in FIG. 15B, the central portion 3n1 is high and the end portions 3n3 and 3n3 are low. The notch root 3n9 may or may not be present.
Even in the first modification, the same effects as in the first and second embodiments are obtained.

<< Modification 2 >>
FIG. 16A is a view corresponding to the arrow B in FIG. 1 of the notch of the second modification, and FIG. 16B is a view corresponding to the arrow A of FIG.
As shown in FIG. 16A, the notch 4n of the second modification has a trapezoidal shape in which the central portion 4n1 is planar and the end portions 4n2, 4n2 are low. Further, as shown in FIG. 16B, the central portion 4n1 has a planar shape and the end portions 4n3 and 4n3 have a low shape. The notch root 4n9 may or may not be present.
In the second modification, the same effects as those in the first and second embodiments are obtained.

<< Modification 3 >>
17A is a view corresponding to the arrow B in FIG. 1 of the notch of the third modification, and FIG. 17B is a view corresponding to the arrow A in FIG. 1 of the notch of the third modification.
As shown in FIG. 17A, the notch 5n of the third modification has a trapezoidal shape in which the central portion 5n1 is flat and the end portions 5n2 and 5n2 are low, and the inclined portion 5n5 is recessed. Further, as shown in FIG. 17B, the central portion 5n1 is high and the end portions 5n3 and 5n3 are low. Note that the notch root portion 5n9 may or may not be present.
The modification 3 has the same effect as the first and second embodiments.

<< Modification 4 >>
18 (a) is a top view of the Y-shaped tube of variant 4, FIG. 18 (b) is a view in the direction of the arrow L in FIG. 18 (a), and FIG. 18 (c) is a view in FIG. It is an M direction arrow directional view of (a).
As shown in FIG. 18 (a), the refrigerant distributor 61 of the modified embodiment 4 has a Y-shaped tube having an introduction part 62 and lead-out parts 64, 65, 66, and has a shape in which the central part 6n1 is high and the end part 6n2 is low. The notch 6n (see FIG. 18C) is applied.
The notch 6n is provided eccentric from the branch part 63.
The modification 4 has the same effects as those of the first and second embodiments.

<< Modification 5 >>
FIG. 19A is a top view of the U-shaped tube of the modified embodiment 5, FIG. 19B is a view as viewed in the R direction of FIG. 19A, and FIG. 19C is FIG. It is a P direction arrow view of (b), and FIG.19 (d) is QQ sectional drawing of Fig.19 (a).
As shown in FIG. 19 (a), the refrigerant distributor 71 of the modified embodiment 5 has a U-shaped tube having an introduction part 72 and lead-out parts 74 and 75, and a notch 7n having a shape in which the center part 7n1 is high and the end part 7n2 is low. (See FIG. 19C) is applied.
The notch 7n is provided eccentric to the U-shaped tube.
The modification 5 has the same effect as the first and second embodiments.

  In the above-described embodiment, various configurations have been described. However, each configuration may be selected, or each configuration may be appropriately selected and combined.

  The above-described embodiments are examples of the present invention, and the present invention can be modified in various ways within the scope of the claims or the scope described in the embodiments.

1, 21, 61, 71 Refrigerant distributor 2 Introduction part 3 Refrigerant branch part (branch part)
3h1, 23h1 Pipe inner wall surface 4, 24, 64, 74 Deriving section (first deriving section)
5, 25, 65, 75 Deriving unit (second deriving unit)
n, 2n, 3n, 4n, 5n, 6n, 7n Notch (convex part)
n1, n2 central part n2, n3, 2n2, 2n3 end S lower mold (second mold)
s1 Recess t Thickness U Upper mold (first mold)
u2 Flat part u1 Convex part

Claims (7)

An introduction part into which the refrigerant is introduced;
A first derivation unit and a second derivation unit from which the refrigerant is derived;
A branching part for branching the refrigerant sent from the introduction part into the first lead-out part and the second lead-out part;
The branch portion is
A convex portion projecting toward the introduction portion on the inner wall surface of the tube;
The convex portion has a shape in which an end portion is lower in height than a central portion. The refrigerant distributor according to claim 1, wherein
The refrigerant distributor according to claim 1, wherein an end of the convex portion is lower than a central portion of the convex portion with respect to the inner wall surface of the pipe. The refrigerant distributor according to claim 1, wherein
The convex portion is
The refrigerant distributor has a height of 1.3 t or more and 2.6 t or less with respect to a wall thickness t of the branch portion. The refrigerant distributor according to claim 1, wherein
As for the area | region of the said branch part in which the said convex part is formed, thickness is thick in a center part area | region than an edge part area | region. The refrigerant distributor according to claim 1, wherein
The convex portion is
The refrigerant distributor is characterized in that a pipe center portion of the branch portion is high and an arch shape having a height difference of 1.5 times or more of a wall thickness of the tube center portion and the inner wall surface side of the tube. The refrigerant distributor according to claim 1, wherein
The convex portion is
The refrigerant distributor is characterized in that a diversion ratio between the first derivation unit and the second derivation unit is adjusted. An introduction part into which the refrigerant is introduced;
A first derivation unit and a second derivation unit from which the refrigerant is derived;
A branching part for branching the refrigerant sent from the introduction part into the first lead-out part and the second lead-out part;
The branch portion is
A convex portion projecting toward the introduction portion on the inner wall surface;
The end of the convex part is a method of manufacturing a refrigerant distributor having a shape having a lower height than the other convex part,
The branch portion is pressed by a first die having a convex portion having a flat portion at the center portion and a second die having a concave portion having a shallow end portion and a deep central portion. A method of manufacturing a refrigerant distributor, wherein: a portion is formed.

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