JPH062990A - Refrigerant flow dividing device - Google Patents

Abstract

PURPOSE:To improve the dividing performance of a refrigerant flow dividing device for dividing a drifting refrigerant flow from an inlet pipe into a plurality of discharge pipes and to control the generation of a pulsation sound upon diverting. CONSTITUTION:In a flow passage from an inlet pipe 21 connected to an end side 3 of a main body 1 to an agitating area 2 in the main body 1, a throttle part 16 having a diameter smaller than the inside diameter of the inlet pipe 21 is disposed coaxially therewith. On the bottom 8 of the agitating area 2, a conical part 1 protrudes, whose top 10 is separated from the throttle part 16 and provided substantially coaxially therewith, to radially guide a refrigerant from the throttle part 16. The respective inlet ports 23 of a plurality of inlet pipes 22 connected to the bottom 8 are arranged at points by which the concentric circle around the axis is equally divided and at substantially intermediate positions between the throttle 16 and the top 10.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant flow divider used in a refrigerating apparatus or the like, and more particularly to a refrigerant flow divider which divides an inflowing refrigerant into a plurality of pipelines.

[0002]

2. Description of the Related Art As a conventional refrigerant shunt, one shown in FIG. 2 can be cited (for example, Japanese Patent Publication No. 60-255).
No. 9). This refrigerant flow divider includes the main body 51, an inflow pipe 71 connected to one end of the main body 51, and both of them.
It has a connecting member 65 for connecting 1 and 71. A through hole 66 is formed in the connecting member 65 at a position smaller than the inner diameter of the inflow pipe 51 and coaxial therewith, and the through hole 66 allows the inside 52 of the main body and the inflow pipe 7 to pass through.
1 and the step portion 68 is formed in the inflow path. The stepped portion 68 is caused to collide with the inflowing refrigerant, and the turbulence of the inflowing refrigerant generated at this time alleviates the uneven flow state of the refrigerant that has already occurred in the refrigerant pipe, and then allows the refrigerant to flow through the through hole 66, and the inside of the main body 52
Is spurting out. Then, this refrigerant is directly distributed to each outflow pipe 72 via a cone portion 61 having its apex located substantially coaxially in the vicinity of the through hole 66 and facing the through hole 66. There is.

[0003]

However, only the collision of the refrigerant with the stepped portion 68 of the refrigerant flow divider has not completely eliminated the uneven flow state of the refrigerant, and the refrigerant ejected from the through hole 66 does not remain. Since it directly flows into each outflow pipe 72 via the cone portion 61, there is a problem that the distribution of the refrigerant remains uneven. In addition, since the apex of the cone portion 61 projects to the vicinity of the through hole 66, there is a problem that the volume of the inside 52 of the main body decreases and the pulsating sound of the refrigerant cannot be absorbed.

On the other hand, in a refrigerant flow divider having another structure shown in FIG. 3 (for example, Japanese Utility Model Laid-Open No. 3-103965), the main body 5
The refrigerant from the inflow pipe 71 connected to one end side of
It is once housed inside the main body 52. And this refrigerant,
The inflow port 73 is distributed to the outflow pipes 72 that are evenly distributed at the same height in the middle of the main body 52. Since this refrigerant shunt does not have the cone portion 61 unlike the first refrigerant shunt, a large volume of the inside 52 can be secured, so that the pulsating sound is generated more than the first refrigerant shunt. Although it can be suppressed, in order to evenly distribute the refrigerant to each outflow pipe 72, the main body 51 itself is attached with high precision, and the insertion angle and the insertion length of each outflow pipe 72 are kept accurately in the same state. There is a structural problem that must be done.

The present invention has been made to solve the above-mentioned conventional drawbacks, and an object thereof is to obtain good flow dividing performance without requiring high accuracy and to generate a refrigerant pulsating sound at the time of flow dividing. It is to provide a refrigerant flow divider that can be suppressed.

[0006]

Therefore, in the refrigerant distributor of claim 1, an inflow pipe 21 is connected to one end side 3 of the main body 1 and a plurality of outflow pipes 22 are connected to the other end side 4 thereof, and the main body 1 is also connected. In the refrigerant distributor in which the stirring region 2 is formed inside and the refrigerant from the inflow pipe 21 is distributed to the respective outflow pipes 22 via the stirring region 2, the stirring region 2 from the inflow pipe 21 A narrowed portion 16 having a diameter smaller than the inner diameter thereof is provided substantially coaxially with the inflow pipe 21 in the flow path leading to, and the apex 10 of the bottom portion 8 of the stirring region 2 is located at a position away from the narrowed portion 16. The conical portion 11 which is arranged and guides the refrigerant from the throttle portion 16 radially is projected, and the inflow port 23 of the outflow pipe 22 is a point at which concentric circles centering on the axis are equally arranged. The narrowing portion 16 and the apex 10
It is characterized in that it is arranged at a position approximately in the middle of.

Further, the refrigerant distributor of claim 2 is characterized in that a peripheral surface of the conical portion 11 is formed with an inclined surface 9 which is inclined toward the inflow pipe 21 side.

[0008]

In the refrigerant distributor of the first aspect, even if a refrigerant that is already in a non-uniform flow state flows in, the stirring effect by colliding with the throttle portion 16 and the refrigerant ejected from the throttle portion 16 at high speed are conical. With the stirring effect by colliding with 11, and being radially guided to the periphery and circulating in the stirring region 2, the above-mentioned uneven flow state of the inflowing refrigerant can be eliminated, and the stirring region 2 can be made into a uniform dispersion state. The outlet 23 of the outflow pipe 22 has an apex 10 of the constricted portion 16 and the conical portion 11.
Since it is arranged so as to be located approximately in the middle of the above, it is possible to let out not the refrigerant directly from the throttle portion 16 but the circulating refrigerant in which the uneven flow state has been eliminated from the outflow pipe 21. Therefore, the flow dividing performance can be further improved. Further, since the apex 10 is separated from the throttle portion 16, a large volume of the stirring area 2 can be secured, so that stirring by the circulation can be improved and pulsating sound at the time of diversion can be absorbed.
The occurrence can be suppressed.

According to the refrigerant distributor of claim 2, the refrigerant flowing from the conical portion 11 to the periphery can be guided by the inclined surface 9, so that the stirring effect is improved.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, specific embodiments of the refrigerant flow divider of the present invention will be described in detail with reference to the drawings. FIG. 1 is a vertical sectional view showing an embodiment of the present invention. In the figure, reference numeral 1 denotes a main body, and the main body 1 has a stirring region 2 having a circular cross section inside thereof. On the upper end surface 3 of the main body 1,
The agitating region 2 and the axial center 5 thereof are substantially the same and a slightly larger diameter perforation hole 6 is bored toward the lower end surface 4 side by a predetermined distance. Therefore, the stepped portion 7 is formed at the rear end of the drilled hole 6. Reference numeral 15 is a connecting member, to which a refrigerant inflow pipe 21 is connected. The connecting member 15 is fitted in the hole 6 and is positioned in the axial direction by coming into contact with the step 7 and fixed by brazing. An insertion hole 17 having a diameter slightly larger than the outer diameter of the inflow pipe 21 is formed in the connection member 15 toward the lower end surface 4 side to a predetermined depth, and further adjacent thereto. A through hole (throttled portion) 16 having a diameter sufficiently smaller than the inner diameter of the inflow pipe 21 is formed so as to be substantially the same as the shaft center 5. Therefore, a step portion 18 is formed at the boundary with the through hole 16 which is the innermost end of the insertion hole 17. The inflow pipe 21 made of copper is inserted into the insertion hole 17 until the tip of the inflow pipe 21 comes into contact with the step portion 18, and is joined by brazing so that the refrigerant can flow into the stirring region 2.

On the other hand, on the inner surface of the bottom portion 8 on the lower end surface 4 side of the main body 1, a conical portion (pyramidal portion) 11 is formed at the center portion thereof, and at the outer peripheral portion thereof, there is a gentle upward inclination toward the outside. Each slope 9 is formed. The apex 10 of the conical portion 11 is located on the axial center 5, is at substantially the same height as the upper portion of the slope 9, and has a shape protruding toward the upper end surface 3 side. The cone portion 11 is not a large cone portion such as the first conventional example (FIG. 2) in which the apex 10 is arranged in the vicinity of the outlet of the through hole 16, but is sufficient from the outlet of the through hole 16. Since they are arranged at a distance, a large volume of the stirring area 2 can be secured. Further, a copper capillary tube (outflow pipe) 22 is provided at each position where the circumference of a circle concentric with the center of the bottom portion 8 is equidistantly provided, and an inflow port 23 of the copper capillary tube (outflow pipe) 22 is provided substantially parallel to the axial center 5 toward the upper end surface 3 side.
Are inserted so as to be arranged at a position approximately in the middle between the apex 10 and the through hole 16. The bottom portion 8 is formed with a wall thickness that can be fixed so that the insertion angle of the capillary tube 22 does not shift.

Next, the flow state of the refrigerant in the refrigerant distributor having the above structure will be described. Generally, the refrigerant that has passed through the expansion valve of the air conditioner is in a gas-liquid mixed phase in which it is separated from saturated vapor into gas and liquid in the subsequent circulation process. Further, when the fluid flows through the bent portion of the pipe, centrifugal force acts, but when the mixed-phase refrigerant flows as described above, the difference in specific gravity causes the liquid phase to be biased to one side in a certain pipe cross section, for example. A so-called drift phenomenon occurs.
Then, if the refrigerant that is already in a non-uniform flow state flows in from the inflow pipe 21, the flow collides with the step portion 18 and the flow is disturbed. Due to this turbulence, both the gas and liquid phases are agitated and mixed to some extent. Further, this refrigerant passes through the through hole 16 having a diameter smaller than the inner diameter of the inflow pipe 21, thereby increasing the speed thereof and ejecting from the through hole 16. The jet stream of the high-speed refrigerant has a cone 10 whose apex 10 is on the same axis 5 as that of the through hole 16.
1 and then, as shown by the arrow in FIG. 1, scattered from the slope 9 to the inner peripheral surface of the main body 1, and the inside volume of the stirring area 2 became larger than that of the first conventional example (FIG. 2). Circulate. By this circulation, the gas-liquid mixed-phase refrigerant is further agitated and mixed from the mixed state caused by the collision, and the above-mentioned non-uniform flow state can be eliminated. And the capillary tube 22
Is inserted until the inflow port 23 is located approximately in the middle of the through hole 16 and the apex 10, so that the high-speed refrigerant jet is not directly received by the inflow port 23. Since the stirring region 2 is in a uniform mixed state in this way, the refrigerant is evenly divided even without increasing the mounting accuracy of each capillary tube 22. Furthermore, since the volume of the stirring area 2 is increased, the generation of pulsating sound at the time of branching is also suppressed.

As described above, in the refrigerant distributor of the above embodiment, the primary agitation by the collision of the refrigerant at the step portion 18 of the connecting member 15 and the secondary agitation by the circulation of the refrigerant in the wide agitation region 2 are performed. By this, it is possible to eliminate the uneven flow state of the inflowing refrigerant and obtain a uniform dispersed state in the stirring region 2. Further, the bottom portion 8 is made thicker than in the conventional example so that the capillary tube 22 can be firmly fixed so that the insertion angle does not shift and the insertion margin into the stirring area 2 is increased, so that the refrigerant is diverted. The performance can be more evenly implemented, and the performance can be improved without increasing the mounting accuracy of the capillary tube 22 as in the conventional example. Further, since the volume of the stirring area 2 is also increased, even if a pulsating sound is generated at the time of branching, it can be sufficiently absorbed.

[0014]

As described above, in the refrigerant flow divider according to the first aspect of the present invention, the volume of the agitation region is increased, and the conical portion is provided at the bottom to improve the agitation due to the circulation of the inflowing refrigerant. Since the inflow pipe is inserted so that the inflow port is arranged in the middle of the stirring region, the flow dividing performance can be improved. In addition, as the stirring area becomes larger, it is possible to suppress the generation of pulsating sound when the flow is divided.

Further, according to the refrigerant distributor of the second aspect, the stirring effect is improved, so that the flow dividing performance can be further improved.

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing an embodiment of a refrigerant flow divider of the present invention.

FIG. 2 is a vertical sectional view showing a conventional example.

FIG. 3 is a vertical cross-sectional view showing another conventional example.

[Explanation of symbols]

 1 Main Body 2 Stirring Region 3 One End Side 4 Other End Side 8 Bottom 10 Apex 11 Cone-Shaped Part 16 Throttling Part 21 Inflow Pipe 22 Outflow Pipe 23 Inlet

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Yoichi Onuma Yoichi Onuma 1000 Otani, Okamoto-cho, Kusatsu-shi, Shiga No. 2 at Shiga Works, Daikin Industries, Ltd. (72) Inventor Hiko Tsuji 1000 Otani, Okamoto-cho, Kusatsu-shi, Shiga No. 2 Inside Daikin Industries, Ltd. Shiga Works

Claims (2)

[Claims] 1. An inflow pipe (2) is provided at one end side (3) of the main body (1).
1) is connected to a plurality of outflow pipes (22) on the other end side (4), and a stirring region (2) is formed inside the main body (1), and the refrigerant from the inflow pipe (21) is In the refrigerant flow distributor, which is distributed to each of the outflow pipes (22) via the stirring region (2), an inflow pipe is provided in a flow path from the inflow pipe (21) to the stirring region (2). (2
1), a throttle portion (16) having a diameter smaller than its inner diameter is provided substantially coaxially with the apex (10) of the bottom portion (8) of the stirring area (2) separated from the throttle portion (16). The conical portion (11), which is arranged at a position and radially guides the refrigerant from the throttle portion (16), is projected, and the outflow pipe (22) is further provided.
The inflow port (23) is located at each point that equidistantly arranges concentric circles centered on the axial center, and is located at a position approximately in the middle between the narrowed portion (16) and the apex (10). A refrigerant shunt characterized by. 2. The refrigerant according to claim 1, wherein an outer peripheral surface of the conical portion (11) is formed with an inclined surface (9) inclined toward the inflow pipe (21) side. Shunt.