JP5233715B2 - Absorption refrigeration system - Google Patents

Description

  The present invention relates to an absorption refrigeration apparatus, and more particularly, to an absorption refrigeration apparatus of an indirect air cooling (solution separation cooling) system in which the temperature of a heating source can be lowered.

  In the indirect air cooling (solution separation cooling) type absorption refrigeration apparatus, as shown in FIG. 20, the refrigerant vapor Rs obtained by heating and concentrating the dilute solution Ld in the generator G is cooled and liquefied in the condenser C. The liquid refrigerant Rw that has been liquefied is sprayed on the heat transfer surface of the evaporator E to cool the fluid W to be cooled, and the evaporated refrigerant vapor Rs is supercooled by the air-cooled supercooler 1 in the absorber A L (a solution obtained by mixing the dilute solution from the absorber A and the concentrated solution Lc sent from the generator G) is absorbed, and then the solution having a reduced concentration (that is, the dilute solution Ld) is sent to the generator G. Thus, an absorption cycle is to be formed. Reference symbol Pl denotes a solution pump that pumps the dilute solution Ld from the absorber A to the generator G, and Ha denotes solution heat exchange that exchanges heat between the concentrated solution Lc sent from the generator G and the dilute solution Ld sent to the generator G. , 2 is a cooling fan that cools the condenser C, and 3 is a cooling fan that cools the air-cooled supercooler 1. Therefore, the temperature of the heat source for heating the dilute solution Ld by the generator G is determined by the concentration of the solution Lc in the generator G and its saturated solution temperature. That is, since the saturated solution temperature becomes the saturated solution temperature at the condensation pressure in the condenser C, in order to lower the heating source temperature in the generator G, the condensation temperature (condensation pressure) is lowered or the solution concentration is decreased. It is also lowering and lowering the saturated solution temperature of the solution.

  However, in a single-effect chiller with absorption of hot water using a cooling water such as a gas engine, as shown in FIG. 19, the temperature of the exhaust water is 90 ° C., and the condensation temperature of the air-cooling absorption refrigerant at the rated time is set. When the temperature is 40 ° C., the saturated solution temperature of the generator G to be heated is about 85 ° C., and the solution concentration of the generator G is about 60% at a high concentration (see cycle (A) in FIG. 19). If the heat source temperature for heating the solution of the generator G can be lowered, solar heat or the like can be used as hot water for heating, and the use range of the exhaust heat absorption type can be greatly expanded, but the condensation temperature is lowered. Alternatively, the solution concentration is lowered to lower the saturated solution temperature. In order to reduce the condensation temperature (pressure), it is necessary to lower the temperature of the cooling air. When the absorption refrigerator is rated for air operation, the condensation temperature should be 40 ° C or less depending on the outside air temperature. Is very difficult and impractical even with a large condenser.

  Even if the solution concentration in the generator G is reduced to lower the saturated solution temperature, the solution concentration in the generator G is a concentration that is also related to the evaporation temperature in the evaporator E, so that a low cold water temperature is obtained. For this purpose, the concentration of the concentrated solution Lc at the inlet of the absorber A is inevitably determined. For example, as shown in the cycle (A) of FIG. 19, if the solution temperature at the inlet of the absorber A is 40 ° C. when the solution concentration is 60%, the evaporation temperature becomes 5 ° C., but it occurs at a low heating source temperature. At the low solution concentration of the vessel G, as shown in the cycle (B) of FIG. 19, the evaporation temperature rises even at the inlet solution temperature of the same absorber A, and the cold water temperature in the evaporator E during rated operation is lowered as prescribed. Therefore, it is difficult to obtain a predetermined low cold water temperature by simply lowering the solution concentration in the generator G and lowering the heating source temperature.

  As a means for lowering the temperature of the heating source of the generator, in this case, in the absorption refrigeration apparatus, two units in which an evaporator and an absorber are combined are prepared, and the absorber constituting one unit is prepared. A reflux circuit is provided to return the dilute solution from the outlet to the upper part of the absorber constituting one unit through the heat exchange part of the evaporator constituting one unit and the heat exchanging part of the absorber constituting the other unit. Thus, the temperature of the heating source of the generator can be lowered (see Patent Document 1). However, in this case, it is necessary to prepare two units in which an evaporator and an absorber are combined, and there is a demerit that the overall size of the apparatus cannot be avoided.

JP2007-271165A

  The present invention has been made in view of the above points, and at a low solution concentration at a low heating source temperature in the generator, the evaporation temperature rises and the cold water temperature cannot be lowered as prescribed. By lowering the pressure, it is possible to reduce the pressure of the absorber and lower the evaporation temperature. Therefore, in the indirect air cooling (solution separation cooling) system, a separate heat exchanger for lowering the solution temperature is provided in the evaporator, and the fluid to be cooled from the evaporator is allowed to flow into the heat exchanger, and the outlet of the air cooling supercooler The solution is heat exchanged with the solution, and the solution temperature at the outlet of the air-cooled supercooler is further lowered to flow into the absorber. This lowers the absorber inlet solution temperature, lowers the absorber pressure, and allows for lower evaporation temperatures. As a result, the solution concentration in the generator can be lowered, the saturated solution temperature can be lowered, and the temperature of the heating source of the generator can be lowered without increasing the size of the apparatus.

  In the present invention, as a first means for solving the above-mentioned problems, a supercooling is provided which includes a generator G, a condenser C, an evaporator E and an absorber A, and supercools the absorbing solution L entering the absorber A. The air-cooling heat exchanger 1 is attached, and in the absorber A housed in the drive unit X integral with the evaporator E, the refrigerant vapor Rs evaporated by the evaporator E is simply absorbed and absorbed. In an absorption refrigeration apparatus of indirect air cooling (solution separation cooling) system in which heat is removed by sensible heat of the supercooled solution L, heat exchange for further cooling the solution L exiting the supercooling air cooling heat exchanger 1 An apparatus 4 is provided, and the heat exchanger 4 is configured to allow the entire amount or a part of the cooled fluid W of the evaporator E to flow into the heat exchanger 4.

  With the configuration described above, the solution L exiting the supercooling air-cooled heat exchanger 1 is to exchange heat with the whole or a part of the cooled fluid W of the evaporator E flowing into the heat exchanger 4. Then, it is further cooled and enters the absorber A in that state. This lowers the inlet solution temperature of the absorber A, lowers the pressure of the absorber A, and enables a low evaporation temperature. As a result, the solution concentration in the generator G can be lowered, the saturated solution temperature can be lowered, and the temperature of the heating source of the generator G can be lowered without increasing the size of the apparatus.

  In the present invention, as a second means for solving the above-described problem, in the absorption refrigeration apparatus including the first means, the heat exchanger 4 is cooled by the evaporator E. The entire amount or a part of the fluid W can be allowed to flow, and in such a case, the solution L exiting the supercooling air-cooled heat exchanger 1 can flow into the heat exchanger 4. By exchanging heat with the whole or a part of the cooled fluid W cooled by E, it is cooled, and the solution L can be further cooled.

  In the present invention, as a third means for solving the above-described problem, in the absorption refrigeration apparatus including the first means, the heat exchanger 4 is cooled before entering the evaporator E. The entire amount or a part of the fluid W may be allowed to flow, and in such a case, the solution L exiting the supercooling air-cooling heat exchanger 1 is cooled before entering the evaporator E. By exchanging heat with the whole or a part of the fluid W, the fluid W is cooled, and the solution L can be further cooled.

  In the present invention, as a fourth means for solving the above-described problem, in the absorption refrigeration apparatus including the first, second, or third means, the fluid W to be cooled is transferred to the heat exchanger 4. A bypass pipe 10 with a flow control valve 11 interposed can be attached to the introduction pipe 7 for introduction into the pipe. In such a case, the flow rate to the bypass pipe 10 is controlled by the flow control valve 11. The flow rate of the fluid W to be cooled flowing into the heat exchanger 4 can be adjusted, and the temperature of the solution L to be cooled can be adjusted.

  In the present invention, as a fifth means for solving the above-described problems, in the absorption refrigeration apparatus including the first, second, or third means, the fluid W to be cooled is transferred to the heat exchanger 4. A flow rate control valve 12 can also be provided in the introduction pipe 7 for introduction into the pipe. In such a configuration, the flow rate of the cooled fluid W flowing into the heat exchanger 4 can be adjusted by the flow rate control valve 12. Thus, the temperature of the solution L to be cooled can be adjusted.

  In the present invention, as the sixth means for solving the above-mentioned problems, in the absorption refrigeration apparatus comprising the first, second, third, fourth or fifth means, the supercooling air is provided. The solution pipe 14 directly connecting the cold heat exchanger 1 and the inlet of the absorber A is provided, and the solution temperature at the outlet of the supercooling air-cooled heat exchanger 1 is reduced to a predetermined value in the solution pipe 14. It is also possible to provide an on-off valve 13 that is operated to open when the temperature of the solution is lowered to a predetermined value when the temperature of the solution at the outlet of the supercooling air-cooling heat exchanger 1 is reduced to a predetermined value. The opening operation of the on-off valve 13 causes the solution L to flow directly into the absorber A not through the heat exchanger 4 side but through the solution pipe 14, and the heat load on the fluid W to be cooled can be suppressed.

  In the invention of the present application, as the seventh means for solving the above-mentioned problems, in the absorption refrigeration apparatus comprising the first, second, third, fourth, fifth or sixth means, the generation Exhaust heat can also be used as a heat source for the vessel G, and in such a configuration, a slightly low temperature exhaust heat hot water can be used effectively.

  In the present invention, as an eighth means for solving the above problems, in the absorption refrigeration apparatus provided with the seventh means, solar heat can also be used as the exhaust heat, and when configured as such The range of use of the absorption refrigeration apparatus can be greatly expanded.

  According to the first means of the present invention, a supercooling air-cooled heat exchanger 1 including a generator G, a condenser C, an evaporator E, and an absorber A, and supercooling the absorbing solution L entering the absorber A. In the absorber A housed in the body X integrated with the evaporator E, the absorbed heat is supercooled simply by absorbing the refrigerant vapor Rs evaporated by the evaporator E. In the absorption refrigeration apparatus of the indirect air cooling (solution separation cooling) method that is removed by sensible heat of the solution L, a heat exchanger 4 for further cooling the solution L exiting the supercooling air cooling heat exchanger 1 is provided. The total amount or a part of the cooled fluid W of the evaporator E is allowed to flow into the heat exchanger 4 so that the solution L exiting the supercooling air-cooled heat exchanger 1 is converted into a heat exchanger. 4 by exchanging heat with the whole or a part of the cooled fluid W of the evaporator E flowing into the Since it is cooled and enters the absorber A in that state, the solution temperature at the inlet of the absorber A is lowered, the pressure of the absorber A is lowered, and a low evaporation temperature is possible. As a result, the temperature of the saturated solution can be lowered, and the temperature of the heating source of the generator G can be lowered without increasing the size of the apparatus.

  As in the second means of the present invention, in the absorption refrigeration apparatus provided with the first means, the heat exchanger 4 has a total amount or a part of the cooled fluid W cooled by the evaporator E. In this case, the solution L exiting the supercooling air-cooled heat exchanger 1 is cooled by the evaporator E flowing into the heat exchanger 4. By exchanging heat with all or a part of W, the solution L is cooled, and the solution L can be further cooled.

  As in the third means of the present invention, in the absorption refrigeration apparatus provided with the first means, the heat exchanger 4 is supplied to the heat exchanger 4 with all or part of the cooled fluid W before entering the evaporator E. In such a case, the solution L that has exited the supercooling air-cooled heat exchanger 1 may be the entire amount or a part of the cooled fluid W before entering the evaporator E. As a result of the heat exchange, the solution L is cooled, and the solution L can be further cooled.

  As in the fourth means of the present invention, in the absorption refrigeration apparatus provided with the first, second or third means, the introduction pipe 7 for introducing the cooled fluid W into the heat exchanger 4. In addition, a bypass pipe 10 having a flow control valve 11 interposed therebetween can be provided. In such a configuration, the flow rate to the bypass pipe 10 can be controlled by the flow control valve 11, and the heat exchanger 4 The flow rate of the fluid W to be cooled can be adjusted, and the temperature of the solution L to be cooled can be adjusted.

  As in the fifth means of the present invention, in the absorption refrigeration apparatus provided with the first, second or third means, the introduction pipe 7 for introducing the cooled fluid W into the heat exchanger 4. In addition, a flow control valve 12 can be provided, and in such a case, the flow rate of the cooled fluid W flowing into the heat exchanger 4 can be adjusted by the flow control valve 12, and the temperature of the solution L to be cooled can be adjusted. Can be adjusted.

  As in the sixth means of the present invention, in the absorption refrigeration apparatus comprising the first, second, third, fourth, or fifth means, the supercooling air-cooling heat exchanger 1 and the absorber A solution pipe 14 directly connected to the inlet of A is provided, and the solution pipe 14 is opened when the solution temperature at the outlet of the supercooling air-cooling heat exchanger 1 is reduced to a predetermined value. The on-off valve 13 can also be provided. In such a configuration, the opening operation of the on-off valve 13 causes the solution L to flow directly into the absorber A via the solution pipe 14 instead of the heat exchanger 4 side. As a result, the heat load on the fluid W to be cooled can be suppressed.

  In the absorption refrigeration apparatus comprising the first, second, third, fourth, fifth or sixth means as in the seventh means of the present invention, exhaust heat is used as a heat source for the generator G. It can also be used, and in such a configuration, a slightly low temperature exhaust heat hot water can be used effectively.

  As in the eighth means of the present invention, in the absorption refrigeration apparatus provided with the seventh means, solar heat can also be used as the exhaust heat, and in such a case, the utilization range of the absorption refrigeration apparatus Can be greatly expanded.

It is an absorption refrigeration cycle in the absorption refrigeration apparatus according to the first embodiment of the present invention. It is an absorption refrigerating cycle in the absorption refrigeration apparatus concerning 2nd Embodiment of this invention. It is an absorption refrigerating cycle in the absorption refrigeration apparatus concerning 3rd Embodiment of this invention. It is an absorption refrigeration cycle in an absorption refrigeration apparatus according to a fourth embodiment of the present invention. It is an absorption refrigeration cycle in the absorption refrigeration apparatus concerning the 5th Embodiment of this invention. It is an absorption refrigerating cycle in the absorption refrigeration apparatus concerning the 6th Embodiment of this invention. It is an absorption refrigerating cycle in the absorption refrigeration apparatus concerning the 7th Embodiment of this invention. It is an absorption refrigeration cycle in the absorption refrigeration apparatus concerning the 8th Embodiment of this invention. It is an absorption refrigerating cycle in the absorption refrigeration apparatus concerning the 9th Embodiment of this invention. It is an absorption refrigeration cycle in an absorption refrigeration apparatus according to a tenth embodiment of the present invention. It is an absorption refrigeration cycle in the absorption refrigeration apparatus concerning the 11th Embodiment of this invention. It is an absorption refrigerating cycle in the absorption refrigeration apparatus concerning the 12th Embodiment of this invention. It is an absorption refrigeration cycle in the absorption refrigeration apparatus concerning 13th Embodiment of this invention. It is an absorption refrigeration cycle in the absorption refrigeration apparatus concerning 14th Embodiment of this invention. It is an absorption refrigeration cycle in the absorption refrigeration apparatus concerning 15th Embodiment of this invention. It is an absorption refrigeration cycle in the absorption refrigeration apparatus concerning 16th Embodiment of this invention. It is an absorption refrigeration cycle in the absorption refrigeration apparatus concerning 17th Embodiment of this invention. It is an absorption refrigeration cycle in the absorption refrigeration apparatus concerning 18th Embodiment of this invention. It is a solution cycle diagram in the absorption refrigeration apparatus concerning the conventional absorption refrigeration apparatus and each embodiment of this invention. This is an absorption refrigeration cycle of a conventional indirect air cooling (solution separation cooling) type absorption refrigeration apparatus including a refrigerant transient type evaporator.

  Hereinafter, several preferred embodiments of the present invention will be described with reference to the accompanying drawings.

First Embodiment FIG. 1 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a first embodiment of the present invention.

  In this absorption refrigeration cycle, in order to recover the refrigerant absorption capacity of an aqueous solution (hereinafter simply referred to as an absorption solution) of an absorbent (for example, LiBr) having an excellent ability to absorb a refrigerant (for example, water), the solution is heated to a heating medium. A generator G for heating and concentrating with (for example, waste water), and an air-cooled condenser that liquefies by introducing steam (refrigerant) Rs separated from the solution in the generator G and cooling it. C, an evaporator E that introduces the refrigerant Rw liquefied by the condenser C and evaporates (vaporizes) under low pressure, and the generator for absorbing the vapor (refrigerant) Rs generated in the evaporator E. Absorber A spraying concentrated solution Lc concentrated in G, and again to generator G to concentrate solution (dilute solution) Ld diluted by absorbing vapor (refrigerant) Rs in absorber A Solution pump for feeding And pl, and the absorption solution L entering the absorber A is configured by a supercool air-cooled heat exchanger 1 to supercooling. Reference numeral 2 is a cooling fan attached to the condenser C, 3 is a cooling fan attached to the supercooling air-cooling heat exchanger 1, Ha is a part of the diluted solution Ld from the absorber A (supplied to the generator G) The solution heat exchanger exchanges heat between the diluted solution Ld) and the concentrated solution Lc output from the generator G. In this absorption refrigeration cycle, a refrigerant transient type evaporator E in which the liquid refrigerant Rw from the condenser C is sprayed from the upper part of the evaporator E to the heat transfer surface is used. Then, in the absorber A housed in the drive unit X integrated with the evaporator E, the refrigerant vapor Rs evaporated by the evaporator E is simply absorbed, and the absorbed heat becomes the supercooled solution L. It is an indirect air cooling (solution separation cooling) type absorption refrigeration system that is removed by sensible heat.

  In the evaporator E, the condensed water (liquid refrigerant) Rw supplied from the condenser C exchanges heat with the water (cooled fluid W) flowing inside and evaporates, and cold water is obtained as a heat source on the use side. On the other hand, in the absorber A, the vapor (refrigerant) Rs obtained from the evaporator E is absorbed by the absorption solution L supercooled by the supercooling air-cooling heat exchanger 1, thereby diluting the solution concentration. Then, the diluted solution exiting the absorber A and the concentrated solution from the generator G are mixed and sent to the supercooling air-cooling heat exchanger 1 and the generator G.

  And in this Embodiment, the heat exchanger 4 for further cooling the solution L which came out of the said air-cooling heat exchanger 1 for the said supercooling is attached, and this evaporator is equipped with the said evaporator. The entire amount of the cooled fluid W that has exited E is introduced. That is, the heat exchanger 4 is interposed in the middle of the outlet side pipe 6 of the fluid W to be cooled. Reference numeral 5 denotes an inlet side pipe of the fluid W to be cooled.

  By configuring as described above, the solution L exiting the supercooling air-cooled heat exchanger 1 is heat-exchanged with the entire amount of the fluid W to be cooled cooled by the evaporator E flowing into the heat exchanger 4. Then, it is further cooled and enters the absorber A in that state. This lowers the inlet solution temperature of the absorber A, lowers the pressure of the absorber A, and enables a low evaporation temperature. As a result, the solution concentration in the generator G can be lowered, the saturated solution temperature can be lowered, and the temperature of the heating source of the generator G can be lowered without increasing the size of the apparatus. That is, the heating source temperature of the generator G in the conventional absorption refrigeration apparatus (shown in FIG. 20) is 5 ° C. as shown in the cycle (A) of FIG. In this embodiment, as shown in cycles (B) and (C) in FIG. 19, the temperature of the heating source is reduced by reducing (thinning) the solution concentration. As a heating source of the generator G, exhaust hot water (for example, hot water by solar heat) can be used.

  However, the evaporation temperature in the cycle (A) in FIG. 19 is 5 ° C. from the saturated vapor temperature at the absorber inlet, but in the cycle (B) in FIG. 19, when the solution concentration is 56%, the inlet of the absorber A is If the temperature is the same, the evaporation temperature will be as high as 10 ° C.

  Therefore, in the present embodiment, as shown in the cycle (C) of FIG. 19, the evaporation temperature can be made equal to the cycle (A) by lowering the absorber inlet temperature of the cycle (B). It is doing so.

Second Embodiment FIG. 2 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a second embodiment of the present invention.

  In this case, the heat exchanger 4 is configured to allow a part of the cooled fluid W cooled by the evaporator E to flow. That is, the heat exchanger 4 is interposed in the middle of the introduction pipe 7 branched from the outlet side pipe 6 of the fluid W to be cooled. In this way, the solution L exiting the supercooling air-cooled heat exchanger 1 is cooled by exchanging heat with a part of the cooled fluid W cooled by the evaporator E flowing into the heat exchanger 4. As a result, the solution L can be further cooled. Since other configurations and operational effects are the same as those in the first embodiment, the description thereof is omitted.

Third Embodiment FIG. 3 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a third embodiment of the present invention.

  In this case, in the first embodiment, a solution pipe 14 that directly connects the supercooling air-cooling heat exchanger 1 and the inlet of the absorber A is provided, and the solution pipe 14 includes the supercooling air. An on-off valve 13 that is opened when the solution temperature at the outlet of the cold heat exchanger 1 is lowered to a predetermined value is interposed. In this way, when the solution temperature at the outlet of the supercooling air-cooled heat exchanger 1 is reduced to a predetermined value, the opening of the on-off valve 13 causes the solution L not to be on the heat exchanger 4 side but to the solution pipe. Therefore, the heat load on the fluid W to be cooled can be suppressed. Since other configurations and operational effects are the same as those in the first embodiment, the description thereof is omitted.

Fourth Embodiment FIG. 4 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a fourth embodiment of the present invention.

  In this case, in the second embodiment, a solution pipe 14 that directly connects the supercooling air-cooling heat exchanger 1 and the inlet of the absorber A is provided, and the supercooling air is connected to the solution pipe 14. An on-off valve 13 that is opened when the solution temperature at the outlet of the cold heat exchanger 1 is lowered to a predetermined value is interposed. In this way, when the solution temperature at the outlet of the supercooling air-cooled heat exchanger 1 is reduced to a predetermined value, the opening of the on-off valve 13 causes the solution L not to be on the heat exchanger 4 side but to the solution pipe. Therefore, the heat load on the fluid W to be cooled can be suppressed. Other configurations and operational effects are the same as those in the second embodiment, and thus description thereof is omitted.

Fifth Embodiment FIG. 5 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a fifth embodiment of the present invention.

  In this case, the heat exchanger 4 is provided in the middle of the introduction pipe 7 branched from the outlet side pipe 6 of the cooled fluid W and returned to the inlet side pipe 5 of the cooled fluid W. That is, a part of the cooled fluid W that has exited the evaporator E is supplied to the heat exchanger 4, and the cooled fluid W that has exited the heat exchanger 4 passes through the inlet side pipe 5 of the cooled fluid W from the evaporator. Is to be supplied to E. In this way, the solution L exiting the supercooling air-cooled heat exchanger 1 is cooled by exchanging heat with a part of the cooled fluid W cooled by the evaporator E flowing into the heat exchanger 4. As a result, the solution L can be further cooled. Since other configurations and operational effects are the same as those in the first embodiment, the description thereof is omitted.

Sixth Embodiment FIG. 6 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a sixth embodiment of the present invention.

  In this case, the heat exchanger 4 is interposed in the middle of the inlet-side piping 5 of the fluid to be cooled W, and is configured to allow the entire amount of the fluid to be cooled W before entering the evaporator E to flow. In this way, the solution L that has exited the supercooling air-cooled heat exchanger 1 is cooled by exchanging heat with the entire amount of the fluid to be cooled W before entering the evaporator E. Cooling becomes possible. Since other configurations and operational effects are the same as those in the first embodiment, the description thereof is omitted.

Seventh Embodiment FIG. 7 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a seventh embodiment of the present invention.

  In this case, in the fifth embodiment, a solution pipe 14 that directly connects the supercooling air-cooling heat exchanger 1 and the inlet of the absorber A is provided, and the supercooling air is connected to the solution pipe 14. An on-off valve 13 that is opened when the solution temperature at the outlet of the cold heat exchanger 1 is lowered to a predetermined value is interposed. In this way, when the solution temperature at the outlet of the supercooling air-cooled heat exchanger 1 is reduced to a predetermined value, the opening of the on-off valve 13 causes the solution L not to be on the heat exchanger 4 side but to the solution pipe. Therefore, the heat load on the fluid W to be cooled can be suppressed. Other configurations and operational effects are the same as those in the fifth embodiment, and thus description thereof is omitted.

Eighth Embodiment FIG. 8 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to an eighth embodiment of the present invention.

  In this case, in the sixth embodiment, a solution pipe 14 that directly connects the supercooling air-cooling heat exchanger 1 and the inlet of the absorber A is provided, and the supercooling air is connected to the solution pipe 14. An on-off valve 13 that is opened when the solution temperature at the outlet of the cold heat exchanger 1 is lowered to a predetermined value is interposed. In this way, when the solution temperature at the outlet of the supercooling air-cooled heat exchanger 1 is reduced to a predetermined value, the opening of the on-off valve 13 causes the solution L not to be on the heat exchanger 4 side but to the solution pipe. Therefore, the heat load on the fluid W to be cooled can be suppressed. Other configurations and operational effects are the same as those in the sixth embodiment, and thus description thereof is omitted.

Ninth Embodiment FIG. 9 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a ninth embodiment of the present invention.

  In this case, the heat exchanger 4 is provided in the middle of the introduction pipe 7 branched from the inlet side pipe 5 of the cooled fluid W and returned to the inlet side pipe 5 of the cooled fluid W. That is, a part of the cooled fluid W before entering the evaporator E is supplied to the heat exchanger 4, and the cooled fluid W exiting the heat exchanger 4 evaporates from the inlet side pipe 5 of the cooled fluid W. It is to be supplied to the container E. If it does in this way, the solution L which came out of the air cooling heat exchanger 1 for supercooling will be cooled by exchanging heat with a part of to-be-cooled fluid W which flows into the heat exchanger 4, and the solution L Further cooling is possible. Since other configurations and operational effects are the same as those in the first embodiment, the description thereof is omitted.

Tenth Embodiment FIG. 10 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a tenth embodiment of the present invention.

  In this case, the heat exchanger 4 is interposed in the middle of the outlet side pipe 6 of the fluid W to be cooled. The outlet side pipe 6 bypasses the heat exchanger 4 and is connected to the flow control valve 9. A bypass pipe 8 is provided. If it does in this way, the flow volume of the to-be-cooled fluid W which flows into the heat exchanger 4 can be adjusted by the opening degree adjustment of the flow control valve 9, and the cooling degree of the solution L in the heat exchanger 4 can be adjusted. Since other configurations and operational effects are the same as those in the first embodiment, the description thereof is omitted.

Eleventh Embodiment FIG. 11 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to an eleventh embodiment of the present invention.

  In this case, in the ninth embodiment, a solution pipe 14 for directly connecting the supercooling air-cooling heat exchanger 1 and the inlet of the absorber A is provided, and the supercooling air is connected to the solution pipe 14. An on-off valve 13 that is opened when the solution temperature at the outlet of the cold heat exchanger 1 is lowered to a predetermined value is interposed. In this way, when the solution temperature at the outlet of the supercooling air-cooled heat exchanger 1 is reduced to a predetermined value, the opening of the on-off valve 13 causes the solution L not to be on the heat exchanger 4 side but to the solution pipe. Therefore, the heat load on the fluid W to be cooled can be suppressed. Other configurations and operational effects are the same as those in the ninth embodiment, and thus description thereof is omitted.

Twelfth Embodiment FIG. 12 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a twelfth embodiment of the present invention.

  In this case, in the tenth embodiment, a solution pipe 14 that directly connects the supercooling air-cooling heat exchanger 1 and the inlet of the absorber A is provided, and the supercooling air is provided in the solution pipe 14. An on-off valve 13 that is opened when the solution temperature at the outlet of the cold heat exchanger 1 is lowered to a predetermined value is interposed. In this way, when the solution temperature at the outlet of the supercooling air-cooled heat exchanger 1 is reduced to a predetermined value, the opening of the on-off valve 13 causes the solution L not to be on the heat exchanger 4 side but to the solution pipe. Therefore, the heat load on the fluid W to be cooled can be suppressed. Since other configurations and operational effects are the same as those in the tenth embodiment, description thereof will be omitted.

13th Embodiment FIG. 13 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a 13th embodiment of the present invention.

  In this case, in the second embodiment, a bypass pipe 10 provided with a flow control valve 11 is attached to the introduction pipe 7 for introducing the fluid W to be cooled into the heat exchanger 4. In this way, the flow rate to the bypass pipe 10 can be controlled by the flow rate control valve 11, the flow rate of the fluid W to be cooled flowing into the heat exchanger 4 can be adjusted, and the temperature of the solution L to be cooled is adjusted. be able to. Other configurations and operational effects are the same as those in the second embodiment, and thus description thereof is omitted.

14th Embodiment FIG. 14 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a 14th embodiment of the present invention.

  In this case, in the fifth embodiment, a flow rate control valve 12 is interposed in the introduction pipe 7 for introducing the cooled fluid W into the heat exchanger 4. If it does in this way, the flow volume of the to-be-cooled fluid W which flows in into the heat exchanger 4 with the flow control valve 12 can be adjusted, and the temperature of the solution L to cool can be adjusted. Other configurations and operational effects are the same as those in the fifth embodiment, and thus description thereof is omitted.

15th Embodiment FIG. 15 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a fifteenth embodiment of the present invention.

  In this case, in the thirteenth embodiment, a solution pipe 14 for directly connecting the supercooling air-cooling heat exchanger 1 and the inlet of the absorber A is provided, and the supercooling air is connected to the solution pipe 14. An on-off valve 13 that is opened when the solution temperature at the outlet of the cold heat exchanger 1 is lowered to a predetermined value is interposed. In this way, when the solution temperature at the outlet of the supercooling air-cooled heat exchanger 1 is reduced to a predetermined value, the opening of the on-off valve 13 causes the solution L not to be on the heat exchanger 4 side but to the solution pipe. Therefore, the heat load on the fluid W to be cooled can be suppressed. Other configurations and operational effects are the same as those in the thirteenth embodiment, and a description thereof will be omitted.

Sixteenth Embodiment FIG. 16 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a sixteenth embodiment of the present invention.

  In this case, in the fourteenth embodiment, a solution pipe 14 that directly connects the supercooling air-cooling heat exchanger 1 and the inlet of the absorber A is attached, and the supercooling air is connected to the solution pipe 14. An on-off valve 13 that is opened when the solution temperature at the outlet of the cold heat exchanger 1 is lowered to a predetermined value is interposed. In this way, when the solution temperature at the outlet of the supercooling air-cooled heat exchanger 1 is reduced to a predetermined value, the opening of the on-off valve 13 causes the solution L not to be on the heat exchanger 4 side but to the solution pipe. Therefore, the heat load on the fluid W to be cooled can be suppressed. Other configurations and operational effects are the same as those in the fourteenth embodiment, and a description thereof will be omitted.

Seventeenth Embodiment FIG. 17 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a seventeenth embodiment of the present invention.

  In this case, in the eleventh embodiment, a flow control valve 12 is interposed in the introduction pipe 7 for introducing the cooled fluid W into the heat exchanger 4. If it does in this way, the flow volume of the to-be-cooled fluid W which flows in into the heat exchanger 4 with the flow control valve 12 can be adjusted, and the temperature of the solution L to cool can be adjusted. Other configurations and operational effects are the same as those in the eleventh embodiment, and a description thereof will be omitted.

Eighteenth Embodiment FIG. 18 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to an eighteenth embodiment of the present invention.

  In this case, in the seventeenth embodiment, a solution pipe 14 that directly connects the supercooling air-cooling heat exchanger 1 and the inlet of the absorber A is provided, and the supercooling air is connected to the solution pipe 14. An on-off valve 13 that is opened when the solution temperature at the outlet of the cold heat exchanger 1 is lowered to a predetermined value is interposed. In this way, when the solution temperature at the outlet of the supercooling air-cooled heat exchanger 1 is reduced to a predetermined value, the opening of the on-off valve 13 causes the solution L not to be on the heat exchanger 4 side but to the solution pipe. Therefore, the heat load on the fluid W to be cooled can be suppressed. Other configurations and operational effects are the same as those in the seventeenth embodiment, and thus the description thereof is omitted.

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

1 is an air-cooled heat exchanger for supercooling 4 is a heat exchanger 7 is an introduction pipe 10 is a bypass pipe 11 and 12 is a flow control valve 13 is an on-off valve 14 is a solution pipe A is an absorber C is a condenser E is an evaporator G Is the generator L is the solution (absorbing solution)
Lc is a concentrated solution Ld is a diluted solution Pl is a solution pump Rs is a refrigerant vapor Rw is a liquid refrigerant W is a fluid to be cooled X is a precursor

Claims (8)

  A supercooling air-cooled heat exchanger comprising a generator (G), a condenser (C), an evaporator (E), and an absorber (A), and supercooling the absorbing solution (L) entering the absorber (A) (1) is attached, and in the absorber (A) housed in the drive unit (X) integral with the evaporator (E), the refrigerant vapor (Rs) evaporated by the evaporator (E) is supplied. It is an indirect air-cooling absorption refrigeration system in which absorption heat is removed by sensible heat of the supercooled solution (L) simply by absorbing the solution (1) from the supercooling air-cooling heat exchanger (1) ( L) is provided with a heat exchanger (4) for further cooling, and all or a part of the cooled fluid (W) of the evaporator (E) flows into the heat exchanger (4). An absorption refrigeration apparatus, characterized in that the apparatus is configured to allow the absorption refrigeration apparatus.   The absorption according to claim 1, wherein the heat exchanger (4) is configured to allow the whole or a part of the fluid to be cooled (W) cooled by the evaporator (E) to flow into the heat exchanger (4). Type refrigeration equipment.   The absorption according to claim 1, wherein the heat exchanger (4) is configured to allow the whole or a part of the cooled fluid (W) before entering the evaporator (E) to flow into the heat exchanger (4). Type refrigeration equipment.   The introduction pipe (7) for introducing the cooled fluid (W) into the heat exchanger (4) is provided with a bypass pipe (10) provided with a flow control valve (11). The absorption refrigeration apparatus according to any one of claims 1, 2, and 3.   A flow rate control valve (12) is interposed in the introduction pipe (7) for introducing the cooled fluid (W) into the heat exchanger (4). The absorption refrigeration apparatus according to any one of the above.   A solution pipe (14) for directly connecting the supercooling air-cooling heat exchanger (1) and the inlet of the absorber (A) is provided, and the solution cooling pipe (14) includes the air-cooling heat for supercooling. 6. An on-off valve (13) that is opened when the solution temperature at the outlet of the exchanger (1) is lowered to a predetermined value is provided. The absorption refrigeration apparatus as described in any one of Claims.   The absorption refrigeration apparatus according to any one of claims 1, 2, 3, 4, 5, and 6, wherein exhaust heat is used as a heat source of the generator (G).   The absorption refrigeration apparatus according to claim 7, wherein solar heat is used as the exhaust heat.

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