JP5338271B2 - Absorption refrigeration system - Google Patents

Description

  The present invention relates to an absorption refrigeration apparatus, and more particularly to an absorption refrigeration apparatus that can lower the temperature of a heating source of a generator.

  In the absorption refrigeration apparatus (for example, LiBr absorption refrigeration apparatus), as shown in FIGS. 12 and 13, refrigerant vapor obtained by heating and concentrating a dilute solution (for example, LiBr dilute solution) in the generator G Rs is cooled and liquefied by an air-cooled condenser C, and the liquefied liquid refrigerant Rw is sprayed on the heat transfer surface of the evaporator E to cool the fluid to be cooled, and the evaporated refrigerant vapor Rs is sent to the absorber A. Then, after absorbing with the concentrated solution Lc sent from the generator G, a solution having a reduced concentration (ie, dilute solution Ld) is sent to the generator G, thereby forming an absorption cycle. Here, FIG. 12 shows an absorption cycle using the refrigerant transient type evaporator E in which the liquid refrigerant Rw from the condenser C is scattered from the upper part of the evaporator E to the heat transfer surface, In FIG. 13, the liquid refrigerant Rw from the condenser C is supplied to the refrigerant reservoir 1 provided in the lower part of the evaporator E, and the liquid refrigerant Rw in the refrigerant reservoir 1 is transmitted from the upper part of the evaporator E by the refrigerant pump Pr. An absorption cycle using a refrigerant circulation type evaporator E circulating and sprayed on the hot surface is shown. 12 and 13, reference symbol Pl denotes a solution pump for pumping the solution from the absorber A, and Ha denotes solution heat exchange for exchanging heat between the concentrated solution Lc from the generator G and the diluted solution Ld sent to the generator G. , 2 is an air-cooled supercooling heat exchanger for supercooling the absorbing solution entering the absorber A, 7 is a cooling fan attached to the air-cooled condenser C, and 8 is an air-cooled supercooling heat exchange. It is a cooling fan attached to the device 2.

  Accordingly, the temperature of the heating source for heating the dilute solution Ld in the generator G is determined from the temperature required to exchange heat with a solution temperature equal to its saturated vapor temperature at the concentration of the concentrated solution Lc in the generator G. The Rukoto. That is, since the saturated vapor temperature is the solution temperature at a pressure equal to the condensation pressure determined by the condensation temperature in the condenser C, in order to reduce the heating source temperature in the generator G, the condensation in the condenser C ( Pressure) is to reduce the temperature (see FIG. 11).

  For example, in a single-effect refrigeration system using a warm water absorption type that uses cooling water such as a gas engine, when the solution concentration in the generator G is about 60%, the saturation of the solution under the condensation pressure is assumed to be 40 ° C. The solution temperature equal to the vapor temperature is from 85 ° C., and the heat source temperature is about 90 ° C., that is, the exhaust water temperature of the gas engine must be higher than this temperature (see cycle (A) in FIG. 11). 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 the hot water for heating, and the use range of the exhaust heat absorption refrigeration apparatus can be greatly expanded. In order to reduce the condensation temperature, it is necessary to reduce the cooling air temperature or reduce the outlet solution concentration (LiBr solution concentration) of the generator G to lower the saturated vapor temperature.

  However, in the case of an air-cooled condenser, it is very difficult to reduce the condensation temperature during rated operation of the absorption refrigeration system to 40 ° C. or less depending on the outside air temperature even if the condenser C is enlarged. Not right. In order to lower the heating source temperature by about 10 ° C., it is necessary to lower the condensation temperature by about 7 to 10 ° C. to 30 to 33 ° C. (see cycle (A ′) in FIG. 11).

  Moreover, reducing the heat source temperature by greatly reducing (thinning) the outlet solution (for example, LiBr solution) concentration Lc of the generator G means that the evaporation temperature in the evaporator E is equal to the inlet solution temperature of the absorber A. Since it is determined by the outlet solution concentration Lc of the generator G, in order to obtain the same low chilled water temperature (that is, the cooled fluid temperature), the concentration of the concentrated solution (for example, LiBr concentrated solution) Lc at the inlet of the absorber A is Therefore, in order to obtain the same evaporation temperature, the temperature of the concentrated solution Lc at the inlet of the absorber A needs to be lowered, and the solution temperature is inevitably determined (see cycle (C) in FIG. 11). That is, at a low (thin) solution concentration of the generator G at a low heating source temperature, the evaporation temperature increases at the inlet solution temperature of the same absorber A (see cycle (B) in FIG. 11). The cold water temperature (cooled fluid temperature) at E cannot be lowered as prescribed, and it is difficult to simply lower the solution concentration at the generator G and lower 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

  In the present invention, the non-evaporated liquid refrigerant sprayed on the heat transfer surface of the evaporator is stored in the lower refrigerant pool, and the non-evaporated refrigerant is supercooled by the refrigerant pump into the absorber. The cooling air sent to the cooling heat exchanger is sent to an air cooler that cools it, and the temperature of the cooling air is lowered, so that the temperature of the absorber inlet solution is lowered by the supercooling heat exchanger, and the pressure of the absorber is reduced. By lowering, a low evaporation temperature is obtained. As a result, the solution concentration in the generator can be lowered and the saturated solution temperature can be lowered, so that the temperature of the heating source of the generator can be lowered.

  The present invention has been made in view of the above points, and by reducing the pressure of the absorber, enabling a low evaporation temperature, thereby reducing the concentration of the absorbing solution in the generator and lowering the saturated solution temperature. The object is to reduce the temperature of the heat source of the generator without increasing the size of the apparatus.

In the present invention, as a first means for solving the above problems, the generator G, the condenser C that condenses and liquefies the refrigerant vapor Rs obtained from the generator G, and the liquid condensed and liquefied by the condenser C An evaporator E for evaporating and evaporating the refrigerant Rw, and a refrigerant solution Rc evaporated and evaporated by the evaporator E is absorbed in the concentrated solution Lc obtained by the generator G, and a dilute solution Ld supplied to the generator G is obtained. In the absorption refrigeration apparatus including the absorber A to be generated and configured to send the absorption solution Ld cooled by the air-cooled supercooling heat exchanger 2 to the absorber A, a lower part of the evaporator E In addition, a refrigerant reservoir 1 for accumulating the unevaporated liquid refrigerant Rw sprayed on the heat transfer surface of the evaporator E is provided, and the liquid refrigerant Rw in the refrigerant reservoir 1 is sent to the supercooling heat exchanger 2. in order to use as a cooling heat source of the cooling air Ac, the coolant The liquid refrigerant Rw Mari 1 cooling means X for the Ru supercooling air cooler 4 to feed Kyusuru refrigerant circuit 3 for cooling the cooling air Ac to be delivered to a heat exchanger 2 Tona via the coolant pump Pr On the other hand, the liquid refrigerant Rw from the condenser C is used as the outlet of the air cooler 4 in the refrigerant circulation circuit 3 in which the unevaporated refrigerant in the refrigerant reservoir 1 circulates in the heat transfer surface of the air cooler 4. The liquid refrigerant Rw that joins at the side and branches off from the inlet side of the air cooler 4 in the refrigerant circulation circuit 3 is spread from the upper part of the evaporator E to the heat transfer surface .

By configuring as described above, the air-cooled supercooling heat exchanger 2 that supercools the absorbing solution Ld that enters the absorber A with the unevaporated component of the liquid refrigerant Rw spread on the heat transfer surface of the evaporator E. As a cooling heat source for the cooling air Ac sent to, a low evaporation temperature can be obtained by lowering the pressure of the absorber A. 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. Moreover, a cooling means comprising a refrigerant circulation circuit 3 for supplying the liquid refrigerant Rw in the refrigerant reservoir 1 to the air cooler 4 for cooling the cooling air Ac sent to the supercooling heat exchanger 2 via the refrigerant pump Pr. Since X is attached, the pressure of the absorber A can be reduced by a simple configuration in which the refrigerant reservoir 1, the air cooler 4, and the refrigerant circulation circuit 3 are attached. Further, the liquid refrigerant Rw from the condenser C is merged on the outlet side of the air cooler 4 in the refrigerant circulation circuit 3 in which the unevaporated refrigerant in the refrigerant pool 1 circulates in the heat transfer surface of the air cooler 4. In addition, since the liquid refrigerant Rw branched from the inlet side of the air cooler 4 in the refrigerant circulation circuit 3 is spread on the heat transfer surface from the upper part of the evaporator E, the refrigerant circulation type evaporation is performed. In the case of the vessel E, since the refrigerant reservoir 1 has already been attached, the configuration can be further simplified.

In the present invention, as a second means for solving the above-described problem, in the absorption refrigeration apparatus provided with the first means, the air cooler 4 and the supercooling heat exchanger 2 are arranged. It is also possible to provide a gap S through which the outside air Ao can flow, so that the cooling air Ac sent from the air cooler 4 to the supercooling heat exchanger 2 can be mixed with the outside air Ao. In such a configuration, the cooling air Ac sent from the air cooler 4 to the supercooling heat exchanger 2 and the outside air Ao are mixed, whereby the temperature of the air sent to the supercooling heat exchanger 2 is changed. Can be optimized.

In the present invention, as a third means for solving the above problems, in the absorption refrigeration apparatus including the second means, the air cooler 4 sends the heat to the supercooling heat exchanger 2. A flow rate adjusting mechanism 13 such as a damper can be provided so that the cooling air Ac and the outside air Ao can be mixed at an arbitrary ratio. In such a case, the temperature of the air sent to the supercooling heat exchanger 2 Can be easily optimized.

In the invention of the present application, as a fourth means for solving the above problems, in the absorption refrigeration apparatus provided with the first , second or third means, the condenser C is an air-cooled condenser. And a cooling circuit 6 for sending the liquid refrigerant Rw in the refrigerant reservoir 1 to the air cooler 5 for cooling the cooling air Ac sent to the condenser C. In this case, a part of the liquid refrigerant Rw in the refrigerant pool 1 is sent to the air cooler 5 that cools the cooling air Ac sent to the condenser C, and the condenser As a result of the temperature decrease of the cooling air Ac sent to C being promoted, the condensation temperature also decreases, and the temperature of the heating source of the generator G can be further decreased.

In the present invention, as a fifth means for solving the above problems, in the absorption refrigeration apparatus including the fourth means, the outside air Ao is provided between the air cooler 5 and the condenser C. It is also possible to provide a gap S that can flow in so that the cooling air Ac sent from the air cooler 5 to the condenser C can be mixed with the outside air Ao. By mixing the cooling air Ac sent from the cooler 5 to the condenser C and the outside air Ao, the temperature of the air sent to the condenser C can be optimized.

In the present invention, as a sixth means for solving the above problem, in the absorption refrigeration apparatus including the fifth means, the cooling air Ac sent from the air cooler 5 to the condenser C is provided. It is also possible to provide a flow rate adjusting mechanism 14 such as a damper so that the air and the outside air Ao can be mixed at an arbitrary ratio, and in such a case, the temperature of the air sent to the condenser C can be easily optimized.

In the present invention, further, as the seventh means for solving the above problems, the first, second, third, fourth, fifth or absorption refrigerating apparatus provided with a sixth means, wherein Exhaust heat can also be used as a heating source for the generator 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, the generator G, the condenser C that condenses and liquefies the refrigerant vapor Rs obtained from the generator G, and the liquid refrigerant Rw condensed and liquefied by the condenser C is evaporated. An evaporator A and an absorber A that absorbs the refrigerant vapor Rs evaporated by the evaporator E into the concentrated solution Lc obtained by the generator G to generate a diluted solution Ld supplied to the generator G. In the absorption refrigeration apparatus, which is configured to send the absorption solution Ld cooled by the air-cooled supercooling heat exchanger 2 to the absorber A, the evaporator E is disposed below the evaporator E. A refrigerant pool 1 is provided for storing the unevaporated liquid refrigerant Rw spread on the heat transfer surface of the refrigerant, and the liquid refrigerant Rw in the refrigerant pool 1 is used as a cooling heat source for cooling air Ac sent to the supercooling heat exchanger 2. With a cooling means X used as a heat transfer surface of the evaporator E The unevaporated portion of the sprayed liquid refrigerant Rw is used as a cooling heat source for the cooling air Ac sent to the air-cooling supercooling heat exchanger 2 that supercools the absorbing solution Ld entering the absorber A. Since the low evaporation temperature can be obtained by lowering the pressure, 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 reduced. There is an effect that it can be reduced. Moreover, a cooling means comprising a refrigerant circulation circuit 3 for supplying the liquid refrigerant Rw in the refrigerant reservoir 1 to the air cooler 4 for cooling the cooling air Ac sent to the supercooling heat exchanger 2 via the refrigerant pump Pr. Since X is attached, there is an effect that the pressure of the absorber A can be lowered by a simple configuration in which the refrigerant reservoir 1, the air cooler 4, and the refrigerant circulation circuit 3 are attached. Further, the liquid refrigerant Rw from the condenser C is merged on the outlet side of the air cooler 4 in the refrigerant circulation circuit 3 in which the unevaporated refrigerant in the refrigerant pool 1 circulates in the heat transfer surface of the air cooler 4. In addition, since the liquid refrigerant Rw branched from the inlet side of the air cooler 4 in the refrigerant circulation circuit 3 is spread on the heat transfer surface from the upper part of the evaporator E, the refrigerant circulation type evaporation is performed. In the case of the vessel E, since the refrigerant reservoir 1 is already attached, there is an effect that the configuration can be further simplified.

As in the second means of the present invention, in the absorption refrigeration apparatus having the first means, a gap through which the outside air Ao can flow between the air cooler 4 and the supercooling heat exchanger 2 S can be provided so that the cooling air Ac sent from the air cooler 4 to the supercooling heat exchanger 2 can be mixed with the outside air Ao. By mixing the cooling air Ac sent from the cooler 4 to the supercooling heat exchanger 2 and the outside air Ao, the temperature of the air sent to the supercooling heat exchanger 2 can be optimized.

As in the third means of the present invention, in the absorption refrigeration apparatus having the second means, the cooling air Ac and the outside air Ao sent from the air cooler 4 to the supercooling heat exchanger 2 It is also possible to provide a flow rate adjusting mechanism 13 such as a damper so that the air temperature sent to the supercooling heat exchanger 2 can be easily optimized.

As in the fourth means of the present invention, in the absorption refrigeration apparatus provided with the first or second means, an air-cooled condenser is adopted as the condenser C, and the refrigerant circulation circuit 3 is used. In addition, a cooling circuit 6 for sending the liquid refrigerant Rw in the refrigerant pool 1 to the air cooler 5 for cooling the cooling air Ac sent to the condenser C can be provided. A part of the liquid refrigerant Rw in the refrigerant pool 1 is sent to the air cooler 5 that cools the cooling air Ac sent to the condenser C, and the temperature of the cooling air Ac sent to the condenser C decreases. As a result, the condensation temperature is also lowered, and the temperature of the heating source of the generator G can be further lowered.

As in the fifth means of the present invention, in the absorption refrigeration apparatus having the fourth means, a gap S through which the outside air Ao can flow is provided between the air cooler 5 and the condenser C. The cooling air Ac sent from the air cooler 5 to the condenser C can be mixed with the outside air Ao, and in such a case, the air cooler 5 to the condenser C can be mixed. The air temperature sent to the condenser C can be optimized by mixing the cooling air Ac to be sent and the outside air Ao.

As in the sixth means of the present invention, in the absorption refrigeration apparatus provided with the fifth means, the cooling air Ac and the outside air Ao sent from the air cooler 5 to the condenser C are in an arbitrary ratio. It is also possible to provide a flow rate adjusting mechanism 14 such as a damper so as to be able to mix the air temperature, and in such a case, the temperature of the air sent to the condenser C can be easily optimized.

As in the seventh means of the present invention, the first, second, third, fourth, fifth or absorption refrigerating apparatus provided with a sixth means, discharge as a heat source for the generator G Heat can also be used, and when configured in this way, 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.

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

First Reference Example FIG. 1 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a first reference example 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 Ld entering the absorber A is configured to include a heat exchanger for supercooling 2 air-cooled for supercooling. Reference numeral Ha denotes a solution heat exchanger for exchanging heat between a part of the dilute solution Ld (the dilute solution Ld supplied to the generator G) exiting from the absorber A and the concentrated solution Lc from the generator G, and 7 denotes air cooling. A cooling fan 8 attached to the condenser C of the type, and a cooling fan 8 attached to the air-cooling supercooling heat exchanger 2. 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.

  In the absorption refrigeration cycle, the evaporator E and the absorber A are integrated to form a unit U. In the evaporator E, the condensed water (liquid refrigerant) Rw supplied from the condenser C exchanges heat with the water (cooled fluid) flowing inside, evaporates, and cold water is obtained as a heat source on the use side. On the other hand, in the absorber A, the vapor obtained from the evaporator E into the absorption solution Ld supplied from the generator G and joined with the solution from the absorber A and then supercooled by the supercooling heat exchanger 2. (Refrigerant) The solution concentration is diluted by absorbing Rs. In this case, in the absorber A, an indirect air cooling method (in other words, a solution separation cooling method) in which the absorption heat is removed by sensible heat of the supercooled absorption solution Ld simply by absorbing the refrigerant vapor Rs. .

In this reference example , the lower part of the evaporator E is provided with a refrigerant reservoir 1 for storing the unevaporated liquid refrigerant Rw sprayed on the heat transfer surface of the evaporator E. The refrigerant reservoir 1 The refrigerant circulation circuit 3 for supplying the liquid refrigerant Rw to the air cooler 4 for cooling the cooling air Ac sent to the supercooling heat exchanger 2 via the refrigerant pump Pr is attached. The refrigerant circulation circuit 3 constitutes a cooling means X used as a cooling heat source for the cooling air Ac sent to the supercooling heat exchanger 2.

  By configuring as described above, the air-cooled supercooling heat exchanger 2 that supercools the absorbing solution Ld that enters the absorber A with the unevaporated component of the liquid refrigerant Rw spread on the heat transfer surface of the evaporator E. As a cooling heat source for the cooling air Ac sent to, a low evaporation temperature can be obtained by lowering the pressure of the absorber A. 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. That is, the heating source temperature of the generator G in the conventional absorption refrigeration apparatus (shown in FIGS. 12 and 13) required 90 ° C. as shown in the cycle (A) of FIG. In the case of the form, as shown in the cycle (B) of FIG. 11, it becomes possible to set the temperature to 80 ° C., and as the heating source of the generator G, exhaust heat hot water (for example, hot water by solar heat) can be used. is there.

  However, the evaporation temperature in the cycle (A) in FIG. 11 is 5 ° C. from the solution concentration and the solution temperature at the absorber inlet, but in the cycle (B) in FIG. 11, the inlet solution temperature at the absorber A is the same. When the solution concentration is 56.5%, the evaporation temperature is increased to 10 ° C.

Therefore, in this reference example , as shown in the cycle (C) of FIG. 11, the evaporation temperature can be made equal to the cycle (A) by lowering the absorber inlet temperature of the cycle (B). It is. The inlet temperature of the absorber A can be made lower than the cycle (C) in FIG. 11 and the solution concentration at the inlet of the absorber A can be made lower (thinner). Can be further reduced.

The embodiment Figure 2 of the first embodiment, the absorption refrigeration cycle in the first absorption refrigerating apparatus according to the embodiment of the present invention is shown.

In this case, the evaporator E is a refrigerant circulation system. That is, the liquid refrigerant Rw from the condenser C merges at the outlet side of the air cooler 4 in the refrigerant circulation circuit 3 in which the unevaporated refrigerant in the refrigerant pool 1 circulates in the heat transfer surface of the air cooler 4. The liquid refrigerant Rw branched from the inlet side of the air cooler 4 in the circulation circuit 3 is scattered from the upper part of the evaporator E to the heat transfer surface. In this case, in the case of the refrigerant circulation type evaporator E, since the refrigerant reservoir 1 is already attached, the configuration can be further simplified. Other configurations and operational effects are the same as those in the first reference example , and thus description thereof is omitted.

The Second Embodiment FIG. 3, the absorption refrigeration cycle in the second absorption type refrigerating apparatus according to the embodiment of the present invention is shown.

In this case, a clearance S through which the outside air Ao can flow is provided between the air cooler 4 and the supercooling heat exchanger 2, and the cooling is sent from the air cooler 4 to the supercooling heat exchanger 2. It is comprised so that the air Ac and the external air Ao can be mixed. Further, at the inlet side of the gap S, a flow rate of a damper or the like is provided so that the cooling air Ac and the outside air Ao sent from the air cooler 4 to the supercooling heat exchanger 2 can be mixed at an arbitrary ratio. An adjustment mechanism 13 is provided. Reference numeral 9 is a connecting plate for connecting the air cooler 4 and the supercooling heat exchanger 2 via the gap S, and 10 is provided at the upper end of the supercooling heat exchanger 2 for introducing the outside air Ao into the gap S. Outside air introduction plate. By doing so, the air temperature sent to the supercooling heat exchanger 2 is optimized by mixing the cooling air Ac sent from the air cooler 4 to the supercooling heat exchanger 2 and the outside air Ao. can do. Further, on the inlet side of the gap S, a flow rate adjusting mechanism 13 such as a damper is provided so that the cooling air Ac sent from the air cooler 2 to the supercooling heat exchanger 2 and the outside air Ao can be mixed at an arbitrary ratio. By providing, the cooling air Ac and the outside air Ao can be arbitrarily mixed, and the temperature of the air sent to the supercooling heat exchanger 2 can be easily optimized. Other configurations and operational effects are the same as those in the first reference example and the first embodiment, and thus the description thereof is omitted.

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

  In this case, a clearance S through which the outside air Ao can flow is provided between the air cooler 4 and the supercooling heat exchanger 2, and the cooling is sent from the air cooler 4 to the supercooling heat exchanger 2. It is comprised so that the air Ac and the external air Ao can be mixed. Further, at the inlet side of the gap S, a flow rate of a damper or the like is provided so that the cooling air Ac and the outside air Ao sent from the air cooler 4 to the supercooling heat exchanger 2 can be mixed at an arbitrary ratio. An adjustment mechanism 13 is provided. Reference numeral 9 is a connecting plate for connecting the air cooler 4 and the supercooling heat exchanger 2 via the gap S, and 10 is provided at the upper end of the supercooling heat exchanger 2 for introducing the outside air Ao into the gap S. Outside air introduction plate. By doing so, the air temperature sent to the supercooling heat exchanger 2 is optimized by mixing the cooling air Ac sent from the air cooler 4 to the supercooling heat exchanger 2 and the outside air Ao. can do. Further, on the inlet side of the gap S, a flow rate adjusting mechanism 13 such as a damper is provided so that the cooling air Ac sent from the air cooler 2 to the supercooling heat exchanger 2 and the outside air Ao can be mixed at an arbitrary ratio. By providing, the cooling air Ac and the outside air Ao can be arbitrarily mixed, and the temperature of the air sent to the supercooling heat exchanger 2 can be easily optimized.

Furthermore, in this case, the evaporator E is a refrigerant circulation system. That is, the liquid refrigerant Rw from the condenser C merges at the outlet side of the air cooler 4 in the refrigerant circulation circuit 3 in which the unevaporated refrigerant in the refrigerant pool 1 circulates in the heat transfer surface of the air cooler 4. The liquid refrigerant Rw branched from the inlet side of the air cooler 4 in the circulation circuit 3 is scattered from the upper part of the evaporator E to the heat transfer surface. In this case, in the case of the refrigerant circulation type evaporator E, since the refrigerant reservoir 1 is already attached, the configuration can be further simplified. Other configurations and operational effects are the same as those in the first reference example , and thus description thereof is omitted.

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

In this case, the refrigerant circuit 3 is provided with a cooling circuit 6 for sending the liquid refrigerant Rw in the refrigerant pool 1 to the air cooler 5 for cooling the cooling air Ac sent to the condenser C. The cooling circuit 6 is branched upstream of the air cooler 4 that cools the cooling air Ac sent to the supercooling heat exchanger 2 in the refrigerant circulation circuit 3. If it does in this way, a part of liquid refrigerant Rw of refrigerant pool 1 will be sent to air cooler 5 which cools cooling air Ac sent to condenser C, and it is for cooling sent to condenser C As a result of the accelerated temperature decrease of the air Ac, the condensation temperature also decreases, and the temperature of the heating source of the generator G can be further decreased. Other configurations and operational effects are the same as those in the first reference example and the first embodiment, and thus the description thereof is omitted.

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

  In this case, the refrigerant circuit 3 is provided with a cooling circuit 6 for sending the liquid refrigerant Rw in the refrigerant pool 1 to the air cooler 5 for cooling the cooling air Ac sent to the condenser C. The cooling circuit 6 is branched upstream of the air cooler 4 that cools the cooling air Ac sent to the supercooling heat exchanger 2 in the refrigerant circulation circuit 3. If it does in this way, a part of liquid refrigerant Rw of refrigerant pool 1 will be sent to air cooler 5 which cools cooling air Ac sent to condenser C, and it is for cooling sent to condenser C As a result of the accelerated temperature decrease of the air Ac, the condensation temperature also decreases, and the temperature of the heating source of the generator G can be further decreased.

Furthermore, in this case, the evaporator E is a refrigerant circulation system. That is, the liquid refrigerant Rw from the condenser C merges at the outlet side of the air cooler 4 in the refrigerant circulation circuit 3 in which the unevaporated refrigerant in the refrigerant pool 1 circulates in the heat transfer surface of the air cooler 4. The liquid refrigerant Rw branched from the inlet side of the air cooler 4 in the circulation circuit 3 is scattered from the upper part of the evaporator E to the heat transfer surface. In this case, in the case of the refrigerant circulation type evaporator E, since the refrigerant reservoir 1 is already attached, the configuration can be further simplified. Other configurations and operational effects are the same as those in the first reference example , and thus description thereof is omitted.

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

In this case, a clearance S through which the outside air Ao can flow is provided between the air cooler 4 and the supercooling heat exchanger 2, and the cooling is sent from the air cooler 4 to the supercooling heat exchanger 2. It is comprised so that the air Ac and the external air Ao can be mixed. Further, at the inlet side of the gap S, a flow rate of a damper or the like is provided so that the cooling air Ac and the outside air Ao sent from the air cooler 4 to the supercooling heat exchanger 2 can be mixed at an arbitrary ratio. An adjustment mechanism 13 is provided. Reference numeral 9 is a connecting plate for connecting the air cooler 4 and the supercooling heat exchanger 2 via the gap S, and 10 is provided at the upper end of the supercooling heat exchanger 2 for introducing the outside air Ao into the gap S. Outside air introduction plate. The refrigerant circulation circuit 3 is additionally provided with a cooling circuit 6 for sending the liquid refrigerant Rw in the refrigerant reservoir 1 to the air cooler 5 for cooling the cooling air Ac sent to the condenser C. The cooling circuit 6 is branched upstream of the air cooler 4 that cools the cooling air Ac sent to the supercooling heat exchanger 2 in the refrigerant circulation circuit 3. By doing so, the air temperature sent to the supercooling heat exchanger 2 is optimized by mixing the cooling air Ac sent from the air cooler 4 to the supercooling heat exchanger 2 and the outside air Ao. In addition, a part of the liquid refrigerant Rw in the refrigerant reservoir 1 is sent to the air cooler 5 that cools the cooling air Ac sent to the condenser C, and the cooling sent to the condenser C As a result of the temperature decrease of the working air Ac being accelerated, the condensation temperature is also decreased, and the temperature of the heating source of the generator G can be further decreased. Further, on the inlet side of the gap S, a flow rate adjusting mechanism 13 such as a damper is provided so that the cooling air Ac sent from the air cooler 2 to the supercooling heat exchanger 2 and the outside air Ao can be mixed at an arbitrary ratio. By providing, the cooling air Ac and the outside air Ao can be arbitrarily mixed, and the temperature of the air sent to the supercooling heat exchanger 2 can be easily optimized. Other configurations and operational effects are the same as those in the first reference example , and thus description thereof is omitted.

Seventh Embodiment FIG. 8 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to a seventh embodiment of the present invention.

  In this case, a clearance S through which the outside air Ao can flow is provided between the air cooler 4 and the supercooling heat exchanger 2, and the cooling is sent from the air cooler 4 to the supercooling heat exchanger 2. It is comprised so that the air Ac and the external air Ao can be mixed. Further, at the inlet side of the gap S, a flow rate of a damper or the like is provided so that the cooling air Ac and the outside air Ao sent from the air cooler 4 to the supercooling heat exchanger 2 can be mixed at an arbitrary ratio. An adjustment mechanism 13 is provided. Reference numeral 9 is a connecting plate for connecting the air cooler 4 and the supercooling heat exchanger 2 via the gap S, and 10 is provided at the upper end of the supercooling heat exchanger 2 for introducing the outside air Ao into the gap S. Outside air introduction plate. The refrigerant circulation circuit 3 is additionally provided with a cooling circuit 6 for sending the liquid refrigerant Rw in the refrigerant reservoir 1 to the air cooler 5 for cooling the cooling air Ac sent to the condenser C. The cooling circuit 6 is branched upstream of the air cooler 4 that cools the cooling air Ac sent to the supercooling heat exchanger 2 in the refrigerant circulation circuit 3. By doing so, the air temperature sent to the supercooling heat exchanger 2 is optimized by mixing the cooling air Ac sent from the air cooler 4 to the supercooling heat exchanger 2 and the outside air Ao. In addition, a part of the liquid refrigerant Rw in the refrigerant reservoir 1 is sent to the air cooler 5 that cools the cooling air Ac sent to the condenser C, and the cooling sent to the condenser C As a result of the temperature decrease of the working air Ac being accelerated, the condensation temperature is also decreased, and the temperature of the heating source of the generator G can be further decreased. Further, on the inlet side of the gap S, a flow rate adjusting mechanism 13 such as a damper is provided so that the cooling air Ac sent from the air cooler 4 to the supercooling heat exchanger 2 and the outside air Ao can be mixed at an arbitrary ratio. By providing, the cooling air Ac and the outside air Ao can be arbitrarily mixed, and the temperature of the air sent to the supercooling heat exchanger 2 can be easily optimized.

Furthermore, in this case, the evaporator E is a refrigerant circulation system. That is, the liquid refrigerant Rw from the condenser C merges at the outlet side of the air cooler 4 in the refrigerant circulation circuit 3 in which the unevaporated refrigerant in the refrigerant pool 1 circulates in the heat transfer surface of the air cooler 4. The liquid refrigerant Rw branched from the inlet side of the air cooler 4 in the circulation circuit 3 is scattered from the upper part of the evaporator E to the heat transfer surface. In this case, in the case of the refrigerant circulation type evaporator E, since the refrigerant reservoir 1 is already attached, the configuration can be further simplified. Other configurations and operational effects are the same as those in the first reference example , and thus description thereof is omitted.

Eighth Embodiment FIG. 9 shows an absorption refrigeration cycle in an absorption refrigeration apparatus according to an eighth embodiment of the present invention.

  In this case, a clearance S through which the outside air Ao can flow is provided between the air cooler 4 and the supercooling heat exchanger 2, and the cooling is sent from the air cooler 4 to the supercooling heat exchanger 2. It is comprised so that the air Ac and the external air Ao can be mixed. Further, at the inlet side of the gap S, a flow rate of a damper or the like is provided so that the cooling air Ac and the outside air Ao sent from the air cooler 4 to the supercooling heat exchanger 2 can be mixed at an arbitrary ratio. An adjustment mechanism 13 is provided. Reference numeral 9 is a connecting plate for connecting the air cooler 4 and the supercooling heat exchanger 2 via the gap S, and 10 is provided at the upper end of the supercooling heat exchanger 2 for introducing the outside air Ao into the gap S. Outside air introduction plate. The refrigerant circulation circuit 3 is also provided with a cooling circuit 6 for sending the liquid refrigerant Rw in the refrigerant reservoir 1 to the air cooler 5 for cooling the cooling air Ac sent to the condenser C. A gap S through which the outside air Ao can flow is provided between the condenser 5 and the condenser C so that the cooling air Ac sent from the air cooler 5 to the condenser C can be mixed with the outside air Ao. Has been. Furthermore, a flow rate adjusting mechanism 14 such as a damper is provided on the inlet side of the gap S so that the cooling air Ac and the outside air Ao sent from the air cooler 5 to the condenser C can be mixed at an arbitrary ratio. Is provided. Reference numeral 11 is a connecting plate for connecting the air cooler 5 and the condenser C through the gap S, and 12 is an outside air introduction plate provided to introduce the outside air Ao into the gap S at the upper end of the condenser C. The cooling circuit 6 is branched on the upstream side of the air cooler 4 that cools the cooling air Ac sent to the supercooling heat exchanger 2 in the refrigerant circulation circuit 3. By doing so, the air temperature sent to the supercooling heat exchanger 2 is optimized by mixing the cooling air Ac sent from the air cooler 4 to the supercooling heat exchanger 2 and the outside air Ao. In addition, a part of the liquid refrigerant Rw in the refrigerant reservoir 1 is sent to the air cooler 5 that cools the cooling air Ac sent to the condenser C, and the cooling sent to the condenser C As a result of the temperature decrease of the working air Ac being accelerated, the condensation temperature is also decreased, and the temperature of the heating source of the generator G can be further decreased. Moreover, the air temperature sent to the condenser C can be optimized by mixing the cooling air Ac sent from the air cooler 5 to the condenser C and the outside air Ao. Further, on the inlet side of the gap S, a damper is provided so that the cooling air Ac and the outside air Ao sent from the air coolers 4 and 5 to the supercooling heat exchanger 2 and the condenser C can be mixed at an arbitrary ratio. By providing the flow rate adjusting mechanisms 13 and 14, etc., it is possible to easily mix the cooling air Ac and the outside air Ao, and easily optimize the air temperature sent to the supercooling heat exchanger 2 and the condenser C. Can be

Other configurations and operational effects are the same as those in the first reference example , and thus description thereof is omitted.

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

  In this case, a clearance S through which the outside air Ao can flow is provided between the air cooler 4 and the supercooling heat exchanger 2, and the cooling is sent from the air cooler 4 to the supercooling heat exchanger 2. It is comprised so that the air Ac and the external air Ao can be mixed. Further, at the inlet side of the gap S, a flow rate of a damper or the like is provided so that the cooling air Ac and the outside air Ao sent from the air cooler 4 to the supercooling heat exchanger 2 can be mixed at an arbitrary ratio. An adjustment mechanism 13 is provided. Reference numeral 9 is a connecting plate for connecting the air cooler 4 and the supercooling heat exchanger 2 via the gap S, and 10 is provided at the upper end of the supercooling heat exchanger 2 for introducing the outside air Ao into the gap S. Outside air introduction plate. The refrigerant circulation circuit 3 is also provided with a cooling circuit 6 for sending the liquid refrigerant Rw in the refrigerant reservoir 1 to the air cooler 5 for cooling the cooling air Ac sent to the condenser C. A gap S through which the outside air Ao can flow is provided between the condenser 5 and the condenser C so that the cooling air Ac sent from the air cooler 5 to the condenser C can be mixed with the outside air Ao. Has been. Furthermore, a flow rate adjusting mechanism 14 such as a damper is provided on the inlet side of the gap S so that the cooling air Ac and the outside air Ao sent from the air cooler 5 to the condenser C can be mixed at an arbitrary ratio. Is provided. Reference numeral 11 is a connecting plate for connecting the air cooler 5 and the condenser C through the gap S, and 12 is an outside air introduction plate provided to introduce the outside air Ao into the gap S at the upper end of the condenser C. The cooling circuit 6 is branched on the upstream side of the air cooler 4 that cools the cooling air Ac sent to the supercooling heat exchanger 2 in the refrigerant circulation circuit 3. By doing so, the air temperature sent to the supercooling heat exchanger 2 is optimized by mixing the cooling air Ac sent from the air cooler 4 to the supercooling heat exchanger 2 and the outside air Ao. In addition, a part of the liquid refrigerant Rw in the refrigerant reservoir 1 is sent to the air cooler 5 that cools the cooling air Ac sent to the condenser C, and the cooling sent to the condenser C As a result of the temperature decrease of the working air Ac being accelerated, the condensation temperature is also decreased, and the temperature of the heating source of the generator G can be further decreased. Moreover, the air temperature sent to the condenser C can be optimized by mixing the cooling air Ac sent from the air cooler 5 to the condenser C and the outside air Ao. Further, on the inlet side of the gap S, a damper is provided so that the cooling air Ac and the outside air Ao sent from the air coolers 4 and 5 to the supercooling heat exchanger 2 and the condenser C can be mixed at an arbitrary ratio. By providing the flow rate adjusting mechanisms 13 and 14, etc., it is possible to easily mix the cooling air Ac and the outside air Ao, and easily optimize the air temperature sent to the supercooling heat exchanger 2 and the condenser C. Can be

Furthermore, in this case, the evaporator E is a refrigerant circulation system. That is, the liquid refrigerant Rw from the condenser C merges at the outlet side of the air cooler 4 in the refrigerant circulation circuit 3 in which the unevaporated refrigerant in the refrigerant pool 1 circulates in the heat transfer surface of the air cooler 4. The liquid refrigerant Rw branched from the inlet side of the air cooler 4 in the circulation circuit 3 is scattered from the upper part of the evaporator E to the heat transfer surface. In this case, in the case of the refrigerant circulation type evaporator E, since the refrigerant reservoir 1 is already attached, the configuration can be further simplified. Other configurations and operational effects are the same as those in the first reference example , and thus 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.

It is an absorption refrigerating cycle in the absorption refrigeration apparatus concerning the 1st reference example of this invention. 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 a solution cycle diagram in the absorption refrigeration apparatus concerning the conventional absorption refrigeration apparatus, the 1st reference example of this invention, and each embodiment. It is an absorption refrigeration cycle of a conventional indirect air-cooled absorption refrigeration apparatus including a refrigerant transient evaporator. It is an absorption refrigeration cycle of a conventional indirect air-cooled absorption refrigeration apparatus including a refrigerant circulation evaporator.

1 is a refrigerant reservoir 2 is a supercooling heat exchanger 3 is a refrigerant circulation circuit 4, 5 is an air cooler 6 is a cooling circuit 7, 8 is a cooling fan 13, 14 is a flow rate adjusting mechanism (damper)
A is an absorber C is a condenser E is an evaporator G is a generator Lc is an absorbing solution (concentrated solution)
Ld is dilute solution Pl is solution pump Pr is refrigerant pump Rs is refrigerant vapor Rw is liquid refrigerant S is gap Ac is cooling air Ao is outside air X is cooling means

Claims (8)

Generator (G), condenser (C) for condensing and liquefying refrigerant vapor (Rs) obtained from generator (G), and vaporizing and condensing liquid refrigerant (Rw) condensed and liquefied by condenser (C) The evaporator (E) to be evaporated and the refrigerant vapor (Rs) evaporated by the evaporator (E) are absorbed by the concentrated solution (Lc) obtained by the generator (G) and supplied to the generator (G). An absorber (A) that generates the supplied dilute solution (Ld) is provided, and the absorbent solution (Ld) cooled by the air-cooled supercooling heat exchanger (2) is sent to the absorber (A). In the absorption refrigeration apparatus configured as described above, a refrigerant reservoir for storing an unevaporated portion of the liquid refrigerant (Rw) spread on the heat transfer surface of the evaporator (E) is provided below the evaporator (E). (1) is provided for cooling the liquid refrigerant (Rw) in the refrigerant pool (1) sent to the supercooling heat exchanger (2). In order to use as a cooling heat source air (Ac), the cooling air of the liquid refrigerant (Rw) of the refrigerant reservoir (1) is sent to the through coolant pump (Pr) supercooling heat exchanger (2) ( Ac) while attached to the feed Kyusuru refrigerant circuit air cooler for cooling (4) (3) Tona Ru cooling means (X), and liquid refrigerant from said condenser (C) and (Rw), the The non-evaporated refrigerant in the refrigerant pool (1) joins at the outlet side of the air cooler (4) in the refrigerant circulation circuit (3) circulating in the heat transfer surface of the air cooler (4), and the refrigerant circulation Absorption characterized in that the liquid refrigerant (Rw) branched from the inlet side of the air cooler (4) in the circuit (3) is sprayed on the heat transfer surface from the upper part of the evaporator (E). Type refrigeration equipment. A gap (S) through which outside air (Ao) can flow is provided between the air cooler (4) and the supercooling heat exchanger (2), and the supercooling from the air cooler (4). heat exchanger (2) to the cooling air sent (Ac) and outside air (Ao) and the absorption type refrigerating apparatus according to claim 1, characterized by being configured so as to mix. A flow rate adjusting mechanism (such as a damper) so that the cooling air (Ac) sent from the air cooler (4) to the supercooling heat exchanger (2) and the outside air (Ao) can be mixed at an arbitrary ratio. 13. The absorption refrigeration apparatus according to claim 2, wherein 13) is provided. As the condenser (C), an air-cooled condenser is adopted, and in the refrigerant circulation circuit (3), the liquid refrigerant (Rw) of the refrigerant reservoir (1) is sent to the condenser (C). The absorption refrigeration apparatus according to any one of claims 1, 2, and 3 , further comprising a cooling circuit (6) for sending liquid to an air cooler (5) for cooling air (Ac). A gap (S) through which outside air (Ao) can flow is provided between the air cooler (5) and the condenser (C), and the air cooler (5) is sent to the condenser (C). The absorption refrigeration apparatus according to claim 4, wherein the cooling air (Ac) and the outside air (Ao) are mixed. A flow rate adjusting mechanism (14) such as a damper is provided so that the cooling air (Ac) sent from the air cooler (5) to the condenser (C) and the outside air (Ao) can be mixed at an arbitrary ratio. The absorption refrigeration apparatus according to claim 5, wherein The generator according to claim 1, 2, 3, 4, characterized in that using the waste heat as a heat source (G), 5 Contact and 6 absorption refrigerating apparatus according to any one claim of. The absorption refrigeration apparatus according to claim 7, wherein solar heat is used as the exhaust heat.

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