JPH04163A - Laminated refrigerant evaporator - Google Patents

Abstract

PURPOSE:To effectively operate a gas pressure difference on a refrigerant and oil existent at an inlet tank part by a method wherein the inlet tank is disposed at the bottom of an evaporation unit and the upper part of a communication part between the inlet tank part and a heat exchange flow passage part is drawn by a dam part. CONSTITUTION:Refrigerant on which a refrigeration cycle is operated is introduced from an inlet pipe 6 to an inlet tank part 1. Thereupon, even through a fluid level of an inlet tank part 1 located in the vicinity of an inlet pipe 6 is higher than the lower end of a dam part 9, a flow rate flowing to a heat exchanger flow passage 3 is substantially not increased because of the existence of the dam part 9, and flows longitudinally of the inlet pipe 6. Accordingly, owing to the existence of the dam part 9 there is reduced a difference between a flow rate of an evaporation unit 4 in the vicinity of the inlet pipe 6 and a flow rate of the evaporation unit 4 remove from the inlet pipe 6. Further, owing to the installation of the dam part 9 a refrigerator flow is drawn by an inlet of the heat exchange flow passage part 3, and when a fluid level in the evaporation unit 4 is higher than the lower end of the dam part 9, a communication passage 8 is interrupted by the refrigerant, and a pressure difference formed by attraction force of a compressor is applied between the fluid surface of the inlet tank part 1 and a fluid surface of an outlet tank 2.

Description

[Detailed description of the invention] [Industrial application field] The present invention relates to a stacked refrigerant evaporator.

[Prior Art] A conventional stacked refrigerant evaporator is shown in FIG. 7, and only one of the plates 200 constituting it is shown in FIG. 8.

This stacked refrigerant evaporator is an evaporation unit that includes an inlet tank part 1a for introducing refrigerant liquid, an outlet tank part 2a for leading out refrigerant liquid, and a heat exchange passage part 3a that communicates both tank parts 1a and 2a. 4a and corrugated fins 5a are alternately stacked in the extending direction of the inlet tank portion 1a, and each evaporation unit 4a is joined by making a pair of plates 200 face each other and brazing the outer peripheral edge and the center portion.

In this refrigerant evaporator, the gas-liquid two-phase refrigerant introduced from the inlet pipe 122 into the inlet tank portion 1a is supplied to each evaporator unit 4.
It falls into the heat exchange flow path section 3a of a.

The heat exchange flow path section 3a has a partition wall 112a in the center.
It has a letter-shaped passage, and the refrigerant evaporates while passing through this passage and flows out from the outlet tank portion 2a to the outlet pipe 121.

FIG. 6 shows an example of a conventional stacked refrigerant evaporator.

In this device, an entry tank 1b and an outlet tank 2b are provided on the floor of the device.

[Problems to be Solved by the Invention] However, in the conventional device described above, since the inlet tank portion 1a is located above the heat exchange flow path portion 3a, the evaporator unit 4a that is closer to the inlet pipe 122 among the evaporator units 4a A large amount of refrigerant flows into the inlet pipe 122, and the amount of refrigerant flowing into the remote side evaporation unit 4a decreases.
There is a problem that the overall cooling efficiency decreases.

There is also the problem that oil accumulates at the bottom of the heat exchange passage section 3a. This problem similarly occurs in the conventional example shown in FIG.

The present invention was made in view of these problems, and an object of the present invention is to provide a stacked refrigerant evaporator in which there is little difference in the amount of refrigerant flowing into each evaporation unit, and there is also little oil accumulation in the evaporation units. do.

[Means for Solving the Problems] The stacked refrigerant evaporator of the present invention includes an inlet tank section consisting of a pipe section for introducing refrigerant liquid, and a pipe section extending in the same direction as the inlet tank section for leading out refrigerant gas. evaporation units each having an outlet tank section, and a heat exchange passage section extending in a direction perpendicular to the axial direction of the inlet tank section and communicating the two tank sections, stacked in the extending direction of the inlet tank section. In the stacked refrigerant evaporator, the inlet tank section is relocated to the bottom of the evaporation unit, and the communication section is opened at a side of the inlet tank section and communicates the inlet tank section and the heat exchange flow path section. It is characterized by a hanging part.

In a preferred embodiment, an inlet pipe for introducing the refrigerant into the inlet tank section is connected to one end of the inlet tank section in the stacking direction.

[Operations and Effects] In the stacked refrigerant evaporator of the present invention, the inlet tank section is disposed at the bottom of the evaporation unit, and the upper part of the communication section between the inlet tank section and the heat exchange flow path section is arranged in the housing section. narrowed down by. Therefore, by the action of this storage part, a gas pressure difference can be effectively applied to the refrigerant and oil in the inlet tank part, and these refrigerant and oil can be effectively blown up into the heat exchange passage part.

In addition, the refrigerant flowing into the inlet tank quickly flows in the longitudinal direction within the inlet tank and is distributed throughout each part of the inlet tank, allowing heat exchange before reaching the end of the inlet tank as in the conventional system (Fig. 7). Much of it fell into the flow path,
This solves the problem of variations in the amount of refrigerant flowing into each evaporation unit.

Therefore, the evaporation capacity of each evaporation unit can be utilized to the maximum, and the overall cooling efficiency can be improved. Moreover, the temperature of the air passing between each evaporation unit can be made uniform.

Furthermore, as in the conventional device described above (FIG. 7), it is not easy to blow the fallen oil up into the outlet tank against gravity by the refrigerant fluid, which is dominated by gas phase as a result of evaporation, but in the device of the present invention. As shown in the figure, the refrigerant fluid that has just entered the heat exchange flow path and is still in the liquid phase and the oil mixed in the liquid are once blown up into the heat exchange flow path, and then the oil that has become vapor phase dominant due to evaporation. It is very easy to lower it by gravity into the outlet tank.

Therefore, in the stacked refrigerant evaporator of the present invention, oil accumulation in the heat exchange flow path portion can be reduced.

[Example] Hereinafter, an example of the stacked refrigerant evaporator of the present invention will be described based on the drawings.

As shown in FIGS. 1 and 3, this stacked refrigerant evaporator has an inlet tank section 1 for introducing the refrigerant liquid, an outlet tank section 2 for leading out the refrigerant liquid, and both tank sections 1.2 are connected to each other. An evaporation unit 4 equipped with a heat exchange flow path section 3 is stacked alternately with corrugated fins 5 in the longitudinal direction X of the inlet tank section 1 and the outlet tank section 2, and a An inlet pipe 6 is connected to the right end of the outlet tank section 2 in FIG. 3, and an outlet pipe 7 is connected to the right end of the outlet tank section 2 in FIG.

Each evaporation unit 4 includes a pair of plates 100 (see FIG. 1, only one of which is shown).

) are facing each other and are joined by brazing at the outer periphery, center, and around each tank part, and the inlet tank part 1 is connected to the first tank part.
In the figure, the evaporation unit 4 is disposed at the bottom left side, and the outlet tank section 2 is disposed directly above the inlet tank section 1. In the internal space formed by the pair of plates 100, the part other than both tank parts 1.2 becomes an inverted U-shaped heat exchange flow path part 3 with a partition rib 112 extending vertically in the center as a partition wall. The heat exchange passage section 3 is arranged from the bottom right side of the evaporation unit 4 to just above the outlet tank section 2 in FIG. The right side of the inlet tank part 1 is a communication part 8 that communicates with the bottom of the heat exchange flow path part 3, and
The upper part of the heat exchange channel section 3 communicates with the end section of the heat exchange channel section 3. Therefore, both tank portions 1.2 extend in a direction perpendicular to the surface direction of the plate 100, and the heat exchange flow path portion 3
It extends in the direction of the plane.

The communication portion 8 is located on the downward extension line of the partition rib 112 as shown in FIG.
(see FIG. 1) is located on this downward extension line. The upper right end of the inlet tank section 1 is separated from the heat exchange channel section 3 by a recess 9 hanging from a partition rib 112, and the communication section 8 is narrowed by the recess 9.

The plate 100 is formed with a passage recess 101 having a 0-shape except for the brazed portion such as the outer peripheral edge, an inlet tank recess 102, and an outlet tank recess 103. There is. A partition 112 is formed in the center of the passage recess 101, and further recesses 109 and ribs 107 are formed in the passage recess 101.

The inlet tank recess 102 and the outlet tank recess 103 are deeper than the passage recess 101 and are bottomless.
．． 103 respectively constitute a part of the inlet tank part 1 and the outlet tank part 2 after being joined.

When a pair of plates 100 press-formed as described above are joined facing each other, the outer circumferential portion 100a of the plates 100, the partition ribs 112, and the ribs 107 are brought into contact with each other. The heat exchange flow path section 3 is formed by combining the depressions 101, and the evaporation unit 4 is formed.

Between each of the evaporation units 4 stacked in multiple stages, corrugated fins 5 are arranged in a wavy manner to increase the contact area with air and promote the heat dissipation effect.
The joint is made by integral brazing in a furnace.

Next, the operation will be explained.

When the refrigeration cycle operates, refrigerant is introduced into the inlet tank section 1 from the inlet pipe 6.

At this time, even if the liquid level in the inlet tank section 1 located near the inlet pipe 6 becomes higher than the lower end of the reservoir section 9, the flow rate flowing horizontally to the heat exchange channel section 3 will almost increase due to the presence of the reservoir section 9. Instead, it flows in the longitudinal direction of the inlet pipe 6. Therefore, due to the presence of this storage part 9, the flow rate of the evaporation unit 4 near the inlet pipe 6 and the evaporation unit 4 remote from the inlet pipe 6 can be adjusted.
The difference between the flow rate and the flow rate is reduced, and variations in cooling performance among the evaporation units 4 can be reduced.

Furthermore, due to the installation of the storage section 9, the refrigerant flow is restricted at the inlet of the heat exchange channel section 3, and if the liquid level in the evaporation unit 4 becomes higher than the lower end of the storage section 9, the communication path 8 will be restricted. The difference in pressure between the inlet tank section 1 and the outlet tank 2, which is cut off by the refrigerant and is formed by the attraction force of the compressor (not shown), is the difference between the liquid level in the inlet tank section 1 and the outlet. As a result, the refrigerant liquid and oil stored at the bottom of the evaporation unit 4 are blown up to the upper part of the heat exchange passage section 3. Therefore, the presence of the storage portion 9 also provides the effect that refrigerant liquid and oil are less likely to accumulate at the bottom of the evaporation unit 4.

Then, the refrigerant blown up into the heat exchange passage section 3 evaporates and becomes gas-rich, and is sent to the outlet tank 2, and then guided from the outlet pipe 7 to a compressor (not shown).

In addition, as a modified form, as shown in FIG. 5, the lower right bottom part of the heat exchange flow path section 3 has a slope 199. In this way, the blowing up of the refrigerant discharged from the inlet tank 1 is further improved.

Further, the shape of the receiving portion 9 is free as long as it blocks or narrows the upper part of the communication path 8.

Furthermore, as shown in FIG. 7, the distance from the inlet pipe 6 is different at both ends of the inlet tank section 1, and therefore the fluid resistance is different. In order to offset this difference in fluid resistance, the communication passage 8 near the inlet pipe 6 may be provided with a narrower cross-sectional area, and the communication passage 8 remote from the inlet pipe 6 may be provided with a wider cross-sectional area.

In this way, the fluid resistance difference described above can be compensated for, and further,
The flow rate between each evaporation unit 4 can be made uniform.

[Brief explanation of the drawing]

FIG. 1 is a front view of a plate 100 used in an embodiment of the stacked refrigerant evaporator of the present invention, FIG. 2 is an enlarged front view of the vicinity of the communication passage 8 in FIG. 1, and FIG. 3 is a stacked layer of this embodiment. Fig. 4 is a schematic diagram showing the refrigerant flow, Fig. 5 is a front view showing a modified example of the plate, and Figs. 6 and 7 are respectively the conventional stacked type refrigerant evaporator. A side view of the refrigerant evaporator, FIG. 8 is a front view of the plate 100 of FIG. 7. DESCRIPTION OF SYMBOLS 1... Inlet tank part, 2... Outlet tank part, 3... Heat exchange channel part 4... Evaporation unit 5... Corrugated fin 6... Inlet pipe 7... Outlet pipe 8 ... Communication path 9 ... Accommodation section 100 ... Plate,

Claims (2)

[Claims] (1) An inlet tank section consisting of a pipe section for introducing refrigerant liquid, an outlet tank section extending in the same direction as the inlet tank section and consisting of a pipe section for deriving refrigerant gas, and perpendicular to the axial direction of the inlet tank section. In the stacked refrigerant evaporator, evaporation units are stacked in the extending direction of the inlet tank section, and the evaporation units are stacked in the extending direction of the inlet tank section. placed at the bottom,
A stacked refrigerant evaporator characterized in that a dam part hangs down from a communication part that is opened on a side of the inlet tank part and communicates the inlet tank part and the heat exchange flow path part. (2) The stacked refrigerant evaporator according to claim 1, wherein an inlet pipe for introducing the refrigerant into the inlet tank section is connected to one end of the inlet tank section in the stacking direction.