JPS6144270A - Absorption type refrigerator - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to an absorption refrigerating machine used for air conditioning and the like, and particularly to an absorber and a condenser suitable for making the absorption refrigerating machine more compact.

[Background of the invention]

A conventional device of this type is disclosed in Japanese Patent Application Laid-Open No. 54-54554.
As described in the publication, 1) A condenser was placed above the absorber to exchange heat between the absorber and the condenser.

2) A precooler was installed inside the condenser to exchange heat between the concentrated solution sent to the absorber and the refrigerant.

something is known.

However, in the case of 1), since the bottom of the condenser is filled with refrigerant, it is difficult for the refrigerant to evaporate, and little consideration was given to the fact that more latent heat of vaporization is taken away from the absorber. Regarding point 2), crystals are likely to form in the concentrated solution in the precooler, and no measures have been taken against this point.

[Purpose of the invention]

The present invention utilizes absorber and condenser heat exchange to utilize an absorber with a smaller cooling water heat transfer tube body surface.
[Summary of the Invention] The heat passage rate of the cooling pipe in the absorber is 50 to 60, 1/
-・S・℃. On the other hand, the heat transfer rate of the cooling pipe in the condenser is approximately 250 K-17y? -s AC. Additionally, the saturation temperature of the solution in the absorber is 50°C, while the saturation temperature of the refrigerant in the condenser is 40°C.
It is.

Based on the above points, heat is transferred from the solution in the absorber to the refrigerant in the condenser, and the transferred heat is discharged to the cooling water in the condenser. At this time, due to the difference K in heat transfer rate, when discharging the same amount of heat I, the body surface of the cooling water heat transfer tube may be smaller if it is discharged through a condenser rather than through an absorber. Furthermore, when heat exchange is performed using the above method, there is no need to worry about crystals. That is, if the amount of heat exchanged is Q, the heat transfer coefficient is α, the temperature difference is ΔT, and the heat transfer area is A, then Q=ΔT·α·A. α of boiling and condensation is 10' Kd/rr in α
/h℃ (10KW/&K), which is extremely large.

In order to make maximum use of the above idea, the areas of the partition walls between the absorber and condenser are increased, and a portion of the concentrated solution is sprayed onto the partition wall in the absorber, and a portion of the concentrated solution is distributed from the low-temperature regenerator in the condenser. It is characterized by dispersing refrigerant onto the partition wall.

[Embodiments of the invention]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 shows one embodiment of the present invention. First, the cooling cycle will be explained using this diagram. Heat exchanger tube 4a in evaporator 4
The iC sprayed refrigerant exchanges heat with the cold water passing through 4a and evaporates. At that time, the latent heat of vaporization is taken away from the cold water, resulting in a cooling effect. The generated refrigerant vapor enters the absorber 5 and is absorbed by a concentrated solution cooled by cooling water passing through the heat transfer tube 10. At this time, the latent heat of condensation is discharged to the cooling water.

After absorbing the refrigerant vapor, the diluted solution is transferred to a low temperature heat exchanger 6. by a solution pump 8. Subsequently, the dilute solution is sent to the high temperature heat exchanger 7, during which time the dilute solution becomes high temperature and flows into the high temperature regenerator 1. In the high-temperature regenerator 1, the refrigerant becomes vapor and is sent to the flooded low-temperature regenerator 2, where the dilute solution discharged from the low-temperature heat exchanger 6 is heated and separated into refrigerant vapor and concentrated solution. The concentrated solution '+31' is concentrated in the high-temperature regenerator 1, merges with the concentrated solution that has passed through the high-temperature heat exchanger 7, passes through the low-temperature heat exchanger, and then is sprayed in the absorber. On the other hand, the l-vapor generated in the flooded low-temperature regenerator 2 enters the condenser 5 and is condensed therein. Additionally, the refrigerant vapor from the high temperature regenerator 2 is condensed within the low temperature regenerator drain 11 and flows into the condenser 5 . Furthermore, the refrigerant condensed in the condenser 5 flows into the evaporator. In a double-effect absorption refrigerator having this cycle, a concentrated solution is sprayed on the partition wall 12 between the absorber 5 and the condenser 6, and on the absorber 5 side, a concentrated solution is sprayed on the wall surface 12, and on the condenser 5 side, a low temperature The discharge port of the regenerator drain 11 is disposed in the condenser 5-1 section, and the structure is such that the refrigerant is sprayed onto the partition wall 12 from the discharge port.

The effect of the above structure will be explained.

The solution saturation temperature in the absorber 5 is 50°C, and the refrigerant saturation temperature in the condenser 5 is 40°C.

Therefore, heat transfer occurs from the absorber 5 to the condenser 5.In addition, in the condenser 6, for boiling heat transfer, refrigerant is sprayed on the partition wall 12, so that the partition wall 12 is thin (4). This results in a state in which evaporation becomes easier, and the amount of heat exchanged increases. Thereby, the amount of heat exchanged with the cooling water in the condenser 3 can be increased. When exchanging a certain amount of heat, it is better to exchange more heat on the side with a higher heat transfer rate, which requires less body surface.
It becomes possible to reduce the size of the body.

FIG. 2 shows another embodiment. In addition to the above-described embodiment, in order to perform heat exchange between the concentrated solution flowing into the absorber 5 and the refrigerant flowing through the low-temperature regenerator drain 11, K,
A heat exchanger 16 is provided between the low temperature heat exchanger 6 and the absorber 50 on the concentrated solution side, and between the low temperature regenerator 2 and the condenser 5 on the refrigerant side. As a result, heat exchange is first performed between the concentrated solution and the refrigerant in the heat exchanger 16, and then heat exchange is also performed in the partition wall 12 as described above, so that the body surface of the cooling water heat transfer tube 10 is reduced. Increase the effect.

FIGS. 5 and 4 show the embodiments of FIGS. 1 and 2 applied to a low-temperature spray regenerator 2. In FIGS.

Other structures, operations, and effects are the same in the embodiment shown in FIG. 5 as in the embodiment in FIG. 1, and in the embodiment in FIG. 4 as in the embodiment in FIG. 2. Therefore, the present invention may be fully applicable to a dual-effect absorption refrigerator having a spray bottom temperature resetting device 2. Furthermore, in the embodiments shown in FIGS. 1 to 4, Using a Teflon-treated plate for the partition wall 12 has the effect of stably holding the steam core, so that steam bubbles are generated by slight heating, and the heat transfer performance is improved. Furthermore, using a plate with irregularities on the surface of the partition wall or providing fins on the partition wall has the effect of increasing the body surface and the amount of heat exchanged.

Although the effects of the invention have been explained above based on the cooling cycle, similar effects can be obtained in the heating cycle as well.

〔Effect of the invention〕

As described above, according to the present invention, the partition wall 12 between the absorber 5 and the condenser 5 can be used as an efficient heat transfer surface, and more heat can be transferred from the absorber 5 to the condenser 5. It becomes possible to do so.

As a result, by discharging most of the discharged heat through the condenser 5, which has a high heat transfer rate, the heat transfer surface of the cooling water heat transfer tube 10 used for discharging the heat through the absorber 5 can be made smaller. This has the effect of making the dual-effect absorption chiller more compact and lower in price.

[Brief explanation of the drawing]

Figures 1 and 2 are cycle diagrams of a dual-effect absorption refrigerating machine with a liquid-filled low and temperature regenerator embodying the present invention, and Figures 5 and 4 are cycle diagrams of a dual-effect absorption refrigerator embodying the present invention. FIG. 2 is a cycle diagram of a dual-effect absorption refrigerator with a set of low temperature regenerators. 1... High temperature regenerator, 2... Low temperature regenerator, 6... Condenser, 4... Evaporator, 4a... Cold water heat transfer tube, 5...
・Absorber, 6... Low temperature heat exchanger, 7... High temperature heat exchanger, 8... Solution pump, 9... Refrigerant pump, 10.
... Cooling water heat transfer tube, 11 ... Low temperature regenerator drain, 1
2... Absorber-condenser partition, 15... Ladder to refrigerant spray, 14... Ladder to solution spray, 15.1
6... Eliminator-117... Heat exchanger.

Claims (1)

[Claims] 1. An absorption refrigerator comprising an evaporator, an absorber, a regenerator, a condenser, etc., characterized in that the absorber and the condenser are arranged side by side with one partition wall in between. type refrigerator. 2. Spray the solution on the absorber side against the partition wall,
2. The absorption refrigerator according to claim 1, wherein refrigerant from a low-temperature regenerator is sprayed on the condenser side. 3. The absorption refrigerator according to claim 1, wherein the partition wall between the absorber and the condenser has an uneven surface.