JPH08200874A - Absorption refrigeration equipment - Google Patents

Abstract

(57) [Summary] [Purpose] By lowering the temperature of the concentrated solution supply to the generator, the heat of partial condensation is reduced and the COP is improved. A generator 1 which has a rectification device built therein and which heats a bottom solution by an external heat input means (burner 5) to evaporate a refrigerant, and a condenser which condenses and liquefies the refrigerant vapor introduced from the generator 1 In the absorption refrigerating apparatus, the absorption refrigeration system comprises: 2, an evaporator 3 for evaporating a refrigerant liquid introduced from the condenser 2, and an absorber 4 for absorbing a refrigerant vapor introduced from the evaporator 3 into a dilute refrigerant solution. A solution pump 17 for pumping the concentrated refrigerant solution obtained by the absorber 4, and a heat exchanger 16 for absorption heat recovery, which is installed inside the absorber 4 and in which the concentrated refrigerant solution is pumped by the solution pump 17, A concentrated solution heat exchanger 18, which is installed inside the generator 1, is supplied with a concentrated refrigerant solution from the heat exchanger 16 for recovering absorbed heat, and has its outlet 18a facing the inside of the generator 1, is additionally provided. ing.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an absorption refrigeration system, and more particularly to an absorption refrigeration system equipped with a GAX cycle in which absorbed heat is used for heat input to a generator.

[0002]

2. Description of the Related Art As shown in FIG. 9, a generator 1 for heating a bottom solution by external heat input means 5 to evaporate a refrigerant,
A condenser 2 that condenses and liquefies the refrigerant vapor that is introduced from the generator 1, an evaporator 3 that evaporates the refrigerant liquid that is introduced from the condenser 2, and a refrigerant dilute solution that absorbs the refrigerant vapor that is introduced from the evaporator 3. An absorption type refrigerating apparatus having an absorber 4 for causing the absorption is known.

In the absorption type refrigerating apparatus having the above-mentioned structure, the internal heat exchange between the high temperature solution and the low temperature solution is performed to improve the coefficient of performance (hereinafter referred to as COP). A GAX cycle in which the concentrated refrigerant solution obtained by the absorber is supplied to the inside of the generator via the heat exchanger for absorption heat recovery provided inside the absorber as a recycle for the generation process of the concentrated solution. (For example, see Japanese Patent Laid-Open No. 6-221710).

In the GAX cycle, the following two methods are used to transfer the high temperature part of the absorbed heat from the absorber to the generator.
The type is known.

(1) As shown in FIG. 10, a concentrated refrigerant solution in which a high temperature portion of absorption heat is directly recovered by an absorption heat recovery heat exchanger 16 installed in the absorber 4 is supplied into the generator 1. Method (hereinafter referred to as Conventional Example 1).

(2) As shown in FIG. 11, heat exchangers 30 and 31 are provided in the absorber 4 and the generator 1, respectively, and are circulated by a pump 32 between the heat exchangers 30 and 31. Generator for generating high temperature part of absorbed heat through secondary medium 1
Method (hereinafter referred to as Conventional Example 2).

[0007]

However, in the case of the conventional example 1, the generator supply temperature of the concentrated refrigerant solution becomes high (that is,
Since it is higher than the boiling point), there is a problem that the partial condensation heat that is discarded to the outside in the generator 1 increases, resulting in a decrease in COP.

On the other hand, in the case of the conventional example 2, since the heat exchange must be performed twice by the secondary medium, the heat transfer amount of the absorbed heat to the generator 1 side is reduced and the power for conveying the secondary medium is reduced. However, there is a problem that a pump is required and the configuration and piping are complicated.

The present invention has been made in view of the above points, and it is an object of the present invention to reduce the heat of partial condensation by lowering the temperature of the concentrated solution supplied to the generator, thereby improving the COP. It is a thing.

[0010]

In the basic constitution of the present invention, as a means for solving the above-mentioned problems, a rectification device is built in, and an external heat input means 5 heats a bottom solution to evaporate a refrigerant. The generator 1, the condenser 2 for condensing and liquefying the refrigerant vapor introduced from the generator 1, the evaporator 3 for evaporating the refrigerant liquid introduced from the condenser 2, and the refrigerant vapor introduced from the evaporator 3 In an absorption type refrigeration system provided with an absorber 4 for absorbing a refrigerant dilute solution, a solution pump 17 for pumping a concentrated refrigerant solution obtained by the absorber 4, and a solution pump internally provided in the absorber 4 A heat exchanger 16 for absorbing heat recovery, in which the concentrated refrigerant solution is pumped by 17;
A concentrated solution heat exchanger 18, which is installed inside the generator 1, is supplied with a concentrated refrigerant solution from the heat exchanger 16 for recovering absorbed heat, and has its outlet 18a facing the inside of the generator 1, is additionally provided. ing.

In the basic configuration of the present invention, a condenser 11 for recovering the heat of partial condensation in the generator 1 is provided in the concentrated solution passage X from the bottom of the absorber 4 to the heat exchanger 16 for recovering absorbed heat. It is preferable to interpose it because the heat of partial condensation can be effectively recovered.

A branch passage 19 is provided which branches from the concentrated solution passage X from the bottom of the absorber 4 to the concentrated solution heat exchanger 18 and directly supplies a part of the concentrated refrigerant solution into the generator 1. It is preferable to do so from the viewpoint that the temperature decrease of the concentrated refrigerant solution in the concentrated solution heat exchanger 18 can be promoted.

[0013]

In the basic configuration of the present invention, the following actions can be obtained by the above means.

That is, in the concentrated refrigerant solution obtained by the absorber 4, absorption heat is recovered in the absorption heat recovery heat exchanger 16, and the concentrated refrigerant solution is concentrated solution heat exchanger 18 in the generator 1. The heat is applied to the refrigerant solution in the generator 1 to lower the temperature, and then the refrigerant solution is introduced into the generator 1. Therefore, the high temperature portion of the absorbed heat is transferred to the generator 1 by the concentrated refrigerant solution, and at the same time, the temperature of the concentrated refrigerant solution supplied into the generator 1 is suppressed to near the boiling point.
The absorbed heat can be efficiently recovered without increasing the heat of partial condensation.

In the basic configuration of the present invention, a condenser 11 for recovering the heat of partial condensation in the generator 1 is provided in the concentrated solution passage X from the bottom of the absorber 4 to the heat exchanger 16 for recovering absorbed heat. When installed, after effectively recovering the partial condensation heat,
The absorbed heat can also be recovered.

A branch passage 19 is provided which branches from the concentrated solution passage X extending from the bottom of the absorber 4 to the concentrated solution heat exchanger 18 and directly supplies a part of the concentrated refrigerant solution into the generator 1. In this case, since the flow rate of the concentrated refrigerant solution flowing to the concentrated solution heat exchanger 18 can be adjusted, the temperature decrease of the concentrated refrigerant solution can be promoted.

[0017]

According to the present invention, the concentrated solution heat exchanger provided in the generator 1 is the concentrated refrigerant solution obtained in the absorber 4 and having the absorbed heat recovered in the heat exchanger 16 for recovering absorbed heat. Since it is supplied to the generator 18 through the outlet 18a of the concentrated solution heat exchanger 18, the temperature of the concentrated refrigerant solution supplied to the generator 1 is equal to that of the refrigerant solution in the generator 1. Due to the exchange (that is, heat exchange in the concentrated solution heat exchanger 18), the temperature is lowered (that is, lowered to near the boiling point),
There is an excellent effect that the heat of partial condensation that is discarded to the outside in the generator 1 is reduced, and as a result, the COP is improved. Further, unlike the conventional example 2, there is an advantage that the power for conveying the secondary medium and the pump are not required and the piping is not complicated.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Some preferred embodiments of the present invention will be described below with reference to the accompanying drawings.

Embodiment 1 FIG. 1 shows a refrigerant circuit diagram of an absorption refrigerating apparatus according to Embodiment 1 of the present invention.

The absorption refrigerating apparatus of this embodiment uses ammonia as a refrigerant and water as an absorbent, has a built-in rectification device (not shown), and is equipped with an external heat input means (for example, a burner 5) to cool the bottom portion. A generator 1 for heating the solution to evaporate the refrigerant,
A condenser 2 that condenses and liquefies the refrigerant vapor that is introduced from the generator 1, an evaporator 3 that evaporates the refrigerant liquid that is introduced from the condenser 2, and a refrigerant dilute solution that absorbs the refrigerant vapor that is introduced from the evaporator 3. And an absorber 4 for allowing the absorption.

The generator 1 and the condenser 2 are connected by a high pressure refrigerant vapor conduit 6, the condenser 2 and the evaporator 3 are connected by a refrigerant liquid conduit 7, and the evaporator 3 and the absorber 4 are low pressure refrigerant. They are connected by a steam conduit 8. Reference numeral 9 is a refrigerant expansion valve, 10 is a refrigerant heat exchanger for exchanging heat between the refrigerant liquid conduit 7 and the low-pressure refrigerant vapor conduit 8, 11 is a partial condenser, and 12 is an absorption radiator.

On the upper part of the absorber 4, the dilute refrigerant solution stored in the bottom part of the generator 1 is diluted solution heat exchanger 13.
After that, it is to be supplied via the dilute solution conduit 14. Reference numeral 15 is a dilute solution pressure reducing valve.

The absorption type refrigerating apparatus of this embodiment includes
A solution pump 17 for pumping the concentrated refrigerant solution obtained by the absorber 4, and a heat exchanger 16 for absorption heat recovery, which is installed inside the absorber 4 and pumps the concentrated refrigerant solution by the solution pump 17. A concentrated solution heat exchanger 18 that is internally provided in the generator 1, is supplied with a concentrated refrigerant solution from the heat exchanger 16 for recovering absorption heat, and has its outlet 18a facing the inside of the generator 1. The concentrated solution passage X is attached. The concentrated solution heat exchanger 18 is configured so that the concentrated refrigerant solution flows from the lower side to the upper side.

In the absorption type refrigerating apparatus constructed as described above, the following effects can be obtained.

The aqueous ammonia solution cooled by the absorption radiator 12 to completely absorb the refrigerant vapor and become a concentrated refrigerant solution is temporarily stored in the bottom of the absorber 4. The stored concentrated refrigerant solution is pressurized by the solution pump 17 and guided into the heat exchanger 16 for recovering absorbed heat, which is installed in the absorber 4. On the outer surface of the heat exchanger 16 for recovering absorbed heat, absorption of the refrigerant vapor by the dilute solution supplied from the upper portion thereof occurs, and the concentrated solution of refrigerant flowing in the heat exchanger 16 for recovering absorbed heat absorbs the absorbed heat. It is deprived and the temperature is raised from the supercooled state to the boiling point or higher. The concentrated refrigerant solution thus heated is guided to the concentrated solution heat exchanger 18 installed in the generator 1. The concentrated refrigerant solution flowing in the concentrated solution heat exchanger 18 is cooled to near the boiling point by the refrigerant solution flowing down in the generator 1, and then exits 18a.
Supplied into the generator 1. At this time, by setting the flow direction of the concentrated refrigerant solution in the concentrated solution heat exchanger 18 from the lower side to the upper side, the temperature distribution in the generator 1 (from the lower side to the upper side becomes a high temperature portion → a low temperature portion) is dealt with. This means that the temperature of the concentrated solution of the refrigerant drops (that is, the concentrated solution heat exchanger 18
Heat exchange) can be efficiently obtained.

The concentrated solution supplied into the generator 1 comes into contact with ammonia vapor containing a large amount of water, which has a high temperature rising from the lower side, boils and simultaneously absorbs the water to release ammonia, thereby purifying the concentrated solution. Do the staying action.

The solution flowing down in the generator 1 takes heat from the high temperature refrigerant dilute solution flowing in the dilute solution heat exchanger 13 to generate ammonia vapor and further lower the ammonia concentration.

The burner 5 gives external heat such as combustion heat to the refrigerant solution that has fallen to the bottom of the generator 1 and stored therein. The solution heated by the burner 5 boils and reaches the highest temperature and the lowest ammonia concentration. The high-temperature steam thus generated rises in the generator 1 to increase the ammonia concentration while decreasing the temperature, and has a sufficient concentration to exert the refrigerating capacity.
Leave. The vapor exiting the generator 1 is guided to the condenser 2 via the high pressure refrigerant vapor conduit 6.

On the other hand, the aqueous ammonia solution (refrigerant dilute solution) that has become high temperature and low concentration by evaporating ammonia vapor at the bottom of the generator 1 is diluted solution heat exchanger 13 from the bottom of the generator 1.
The temperature of the solution, which is introduced into the dilute solution heat exchanger 13 and is boiled on the outer surface of the dilute solution heat exchanger 13, is reduced by heating the solution. The refrigerant dilute solution that has passed through the dilute solution heat exchanger 13 and is in a supercooled state is decompressed by the dilute solution pressure reducing valve 15 and then supplied to the upper portion of the absorber 4. The diluted refrigerant solution supplied to the absorber 4 is transferred to the evaporator 3
The refrigerant vapor obtained from the above is absorbed into a concentrated solution, but the refrigerant dilute solution dropped on the outer surface of the heat exchanger 16 for recovering absorption heat is the refrigerant flowing in the heat exchanger 16 for recovering absorption heat. Cooling to a concentrated solution increases the absorption capacity. The dilute refrigerant solution having an increased absorption capacity absorbs the refrigerant vapor while flowing down the outer surface of the heat exchanger 16 for absorbing heat recovery. The refrigerant solution that has absorbed the refrigerant vapor and increased the ammonia concentration passes through the outer surface of the heat exchanger 16 for absorbing heat recovery, and then is dripped onto the outer surface of the absorption radiator 12. An external cooling medium such as cooling water flows inside the absorption radiator 12, and the solution dropped on the outer surface is cooled to a lower temperature. Here again, the solution that has absorbed the refrigerant vapor becomes a concentrated refrigerant solution and is stored in the bottom of the absorber 4. The concentrated solution of the refrigerant stored in the bottom of the absorber 4 is pressurized by the solution pump 17, and the above cycle is repeated.

The refrigerant vapor generated by the generator 1 is
Part of the vapor is condensed in the partial condenser 11, but the remaining vapor is guided to the condenser 2 via the high-pressure refrigerant vapor conduit 6 as described above. The refrigerant vapor guided to the condenser 2 is cooled by the condenser coil 2a through which an external cooling medium such as cooling water flows,
Condensed and liquefied. The liquid refrigerant thus liquefied and accumulated at the bottom of the condenser 2 is guided to the heating fluid side of the refrigerant heat exchanger 10 via the refrigerant liquid conduit 7. The liquid refrigerant guided to the heating fluid side of the refrigerant heat exchanger 10 is cooled by the low pressure refrigerant vapor generated in the evaporator 3 and passed through the low pressure refrigerant vapor conduit 8 to the heated fluid side of the refrigerant heat exchanger 10. Will be supercooled. The liquid refrigerant in the supercooled state is decompressed by the expansion valve 9 and reaches the saturation temperature.

By cooling this refrigerant liquid in the refrigerant heat exchanger 10, the amount of flash after passing through the expansion valve 9 is reduced, which is effective in improving the coefficient of performance (hereinafter referred to as COP). The refrigerant liquid that has reached the saturation temperature as described above is guided to the evaporator 3, and the evaporation coil 3a installed in the evaporator 3
Sprinkled on the outer surface of. The refrigerant liquid thus dispersed removes heat from the medium to be cooled (for example, water) flowing in the evaporation coil 3a on the surface of the evaporation coil 3a and evaporates.
The cooled medium to be cooled is used as a cold heat source for cooling or the like. The refrigerant evaporated in the evaporator 3 flows into the heated fluid side of the refrigerant heat exchanger 10 via the low pressure refrigerant vapor conduit 8,
There, it exchanges heat with the refrigerant liquid to become a superheated state.
The superheated refrigerant vapor is guided to the lower part of the absorber 4, absorbed by the dilute refrigerant solution supplied from the upper part of the absorber 4 to become a concentrated refrigerant solution, and stored in the bottom part of the absorber 4. The cycle is repeated.

As described above, in the present embodiment, the concentrated refrigerant solution obtained in the absorber 4 and having the absorbed heat recovered in the heat exchanger 16 for recovering absorbed heat is the concentrated solution provided in the generator 1. The concentrated heat exchanger 18 is introduced to the heat exchanger 18.
The temperature of the concentrated refrigerant solution supplied to the generator 1 is controlled by the outlet 18a of the generator 1.
Decrease due to heat exchange with the refrigerant solution inside (ie heat exchange in concentrated solution heat exchanger 18) (ie decrease to near boiling point)
As a result, the heat of partial condensation that would be discarded to the outside in the generator 1 is reduced, and as a result, the COP is improved.
Moreover, unlike the conventional example 2, there is an advantage that the power for conveying the secondary medium and the pump are not required, and the piping is not complicated.
By the way, the theoretical cycle COP under the conditions of the evaporation temperature of 4 ° C., the condensation temperature and the absorption temperature of 45 ° C. is 0.9 in the conventional example 1 and 1.0 in the conventional example 2, whereas the theoretical cycle COP is 1.0 in the present example. Met. That is, the present embodiment is more effective than the second conventional example in that the power for conveying the secondary medium and the pump are not required.

Embodiment 2 FIG. 2 shows a refrigerant circuit diagram of an absorption refrigerating apparatus according to Embodiment 2 of the present invention.

In the case of the present embodiment, a branch passage 19 is provided which branches from the outlet side of the heat exchanger 16 for absorbing heat recovery in the concentrated solution passage X and directly supplies a part of the concentrated refrigerant solution to the generator 1. ing. Reference numeral 20 is a flow rate adjusting mechanism provided in the branch passage 19. By appropriately setting the resistance value in the flow rate adjusting mechanism 19, the amount of the refrigerant concentrated solution flowing into the concentrated solution heat exchanger 18 is appropriately adjusted. (Ie generator 1
The flow rate of the concentrated solution of the refrigerant is adjusted to match the cooling capacity in). In the case of the present embodiment, since the concentrated refrigerant solution introduced from the branched passage 19 to the generator 1 has a boiling point or higher, the branched passage 19 can be avoided so that the concentrated solution heat exchanger 18 can be prevented from being affected by heat. The outlet 19a of the is located below the concentrated solution heat exchanger 18 in the generator 1. With this configuration, the concentrated solution heat exchanger 1
Since the flow rate of the concentrated refrigerant solution flowing to 8 can be adjusted to the flow rate of the concentrated refrigerant solution that matches the cooling capacity of the concentrated solution heat exchanger 18, the temperature decrease of the concentrated refrigerant solution can be promoted. Other configurations, functions and effects are the same as those of the first embodiment, and the description will be omitted to avoid duplication.

Embodiment 3 FIG. 3 shows a refrigerant circuit diagram of an absorption refrigerating apparatus according to Embodiment 3 of the present invention.

In the case of the present embodiment, the branch path 19 is branched from the middle of the absorption heat recovery heat exchanger 16 in the concentrated solution path X, and the outlet 19a of the branch path 19 is concentrated solution heat exchange in the generator 1. It differs from the second embodiment in that it is exposed above the container 18. In this case, since the concentrated refrigerant solution flowing through the branch passage 19 is not higher than the boiling point, even if the branched concentrated solution is supplied from above the concentrated solution heat exchanger 18, the concentrated solution heat exchanger 18 is supplied.
It does not impede the temperature decrease of the concentrated refrigerant solution. Other configurations and operational effects are the same as those described in the first and second embodiments, and the description thereof will be omitted to avoid duplication.

Embodiment 4 FIG. 4 shows a refrigerant circuit diagram of an absorption refrigerating apparatus according to Embodiment 4 of the present invention.

In the case of the present embodiment, the branch passage 19 is branched from the upstream side of the heat exchanger 16 for absorbing heat recovery in the concentrated solution passage X, and the outlet 19a of the branch passage 19 in the generator 1 has the concentrated solution heat. It is different from the second embodiment in that it is exposed above the exchanger 18. In this case, since the concentrated refrigerant solution flowing through the branch passage 19 is below the boiling point, the concentrated solution heat exchanger 18
Even if the branched concentrated solution is supplied from above, the concentrated solution heat exchanger 1
It does not impede the temperature decrease of the concentrated refrigerant solution in 8 and rather a cooling effect can be expected. Other configurations and operational effects are the same as those described in the first and second embodiments, and the description thereof will be omitted to avoid duplication.

Embodiment 5 FIG. 5 shows a refrigerant circuit diagram of an absorption refrigerating apparatus according to Embodiment 5 of the present invention.

In the case of the present embodiment, between the solution pump 17 and the heat exchanger 16 for absorbing heat recovery in the concentrated solution passage X, the partial condenser 11 for recovering the partial condensation heat in the generator 1.
To be interposed. With this configuration, in the concentrated solution passage X, after the partial condensation heat is effectively recovered, the absorption heat can also be recovered. Other configurations, functions, and effects are the same as those described in the first embodiment, and the description will be omitted to avoid duplication.

Embodiment 6 FIG. 6 shows a refrigerant circuit diagram of an absorption refrigeration system according to Embodiment 6 of the present invention.

In the case of this embodiment, a branch passage 19 is provided which branches from the outlet side of the heat exchanger 16 for absorbing heat recovery in the concentrated solution passage X and directly supplies a part of the concentrated refrigerant solution to the generator 1. Moreover, the difference from the fifth embodiment is that the outlet 19a of the branch passage 19 is located below the concentrated solution heat exchanger 18 in the generator 1. Other configurations and operational effects are the same as those described in the first, second, and fifth embodiments, and the description thereof will be omitted to avoid duplication.

Embodiment 7 FIG. 7 shows a refrigerant circuit diagram of an absorption refrigerating apparatus according to Embodiment 7 of the present invention.

In the case of the present embodiment, the branch path 19 is branched from the middle of the heat exchanger 16 for absorbing heat recovery in the concentrated solution path X, and the outlet 19a of the branch path 19 in the generator 1 is concentrated solution heat exchange. It differs from the sixth embodiment in that it is exposed above the container 18. Other configurations, functions and effects are the same as those described in the first, third and sixth embodiments, and therefore description thereof will be omitted to avoid duplication.

Embodiment 8 FIG. 8 shows a refrigerant circuit diagram of an absorption refrigerating apparatus according to Embodiment 8 of the present invention.

In the case of the present embodiment, the branch passage 19 is branched from the middle of the heat exchanger 16 for absorbing heat recovery in the concentrated solution passage X, and the outlet 19a of the branch passage 19 is in the generator 1 for the concentrated solution heat exchange. It differs from the sixth embodiment in that it is exposed above the container 18. Other configurations and operational effects are the same as those described in the first, fourth, and sixth embodiments, and thus the description thereof will be omitted to avoid duplication.

The invention of the present application is not limited to the configuration of each of the above-described embodiments, and it goes without saying that the design can be appropriately changed without departing from the scope of the invention.

[Brief description of drawings]

FIG. 1 is a refrigerant circuit diagram of an absorption refrigerating apparatus according to a first embodiment of the present invention.

FIG. 2 is a refrigerant circuit diagram of an absorption refrigerating apparatus according to a second embodiment of the present invention.

FIG. 3 is a refrigerant circuit diagram of an absorption refrigeration system according to a third embodiment of the present invention.

FIG. 4 is a refrigerant circuit diagram of an absorption refrigeration system according to a fourth embodiment of the present invention.

FIG. 5 is a refrigerant circuit diagram of an absorption refrigeration system according to a fifth embodiment of the present invention.

FIG. 6 is a refrigerant circuit diagram of an absorption refrigeration system according to Embodiment 6 of the present invention.

FIG. 7 is a refrigerant circuit diagram of an absorption refrigeration system according to a seventh embodiment of the present invention.

FIG. 8 is a refrigerant circuit diagram of an absorption refrigerating apparatus according to Embodiment 8 of the present invention.

FIG. 9 is a refrigerant circuit diagram of a conventionally known absorption refrigeration system.

FIG. 10 is a partial refrigerant circuit diagram of an absorption refrigeration system according to Conventional Example 1.

FIG. 11 is a partial refrigerant circuit diagram of an absorption refrigerating apparatus according to Conventional Example 2.

[Explanation of symbols]

1 is a generator. 2 is a condenser, 3 is an evaporator, 4 is an absorber, 5
Is an external heat input means (burner), 11 is a partial condenser, 16 is a heat exchanger for absorption heat recovery, 17 is a solution pump, 18 is a concentrated solution heat exchanger, 18a is an outlet, 19 is a branch passage, and 19a is an outlet. ,
20 is a flow rate adjusting mechanism, and X is a concentrated solution passage.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Fumikazu Taniguchi 1304 Kanaoka-cho, Sakai-shi, Osaka Daikin Industries, Ltd.Kanaoka factory, Sakai Manufacturing Co., Ltd. (72) Katsuhiro Kawabata 1304 Kanaoka-cho, Sakai-shi, Osaka Daikin Industries Ltd. Company Sakai Seisakusho Kanaoka Factory (72) Inventor Koichi Yaseo 1304 Kanaoka-cho, Sakai City, Osaka Daikin Industry Co., Ltd. Sakai Works Kanaoka Factory

Claims (3)

[Claims] 1. An external heat input means (5) having a built-in rectification device.
(1) for heating the bottom solution to evaporate the refrigerant, a condenser (2) for condensing and liquefying the refrigerant vapor led from the generator (1), and a condenser (2) An absorption type refrigerating apparatus comprising: an evaporator (3) for evaporating a refrigerant liquid; and an absorber (4) for absorbing a refrigerant vapor introduced from the evaporator (3) into a dilute refrigerant solution. A solution pump (17) for pumping the concentrated refrigerant solution obtained by (4), and an absorption heat recovery system that is installed inside the absorber (4) and pumps the concentrated refrigerant solution by the solution pump (17). The heat exchanger (16) and the generator (1) are internally provided with the concentrated refrigerant solution supplied from the heat exchanger for absorbing heat recovery (16), and the outlet (18a) of the concentrated solution is supplied to the generator (1). ) And a concentrated solution heat exchanger (18) which is located inside That absorption refrigerating apparatus. 2. The concentrated solution passage (X) extending from the bottom of the absorber (4) to the heat exchanger for absorbing heat recovery (16),
A partial condenser (1) for recovering partial condensation heat in the generator (1)
The absorption refrigerating apparatus according to claim 1, wherein 1) is interposed. 3. Branching from a concentrated solution passage (X) from the bottom of the absorber (4) to the concentrated solution heat exchanger (18),
The absorption type refrigerating apparatus according to any one of claims 1 and 2, further comprising a branch passage (19) for directly supplying a part of the concentrated refrigerant solution into the generator (1). .