JP2009097749A - Absorption type refrigerating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve efficiency of cold utilization-side device and to reduce initial costs and running costs of the entire refrigerating system by controlling a refrigerating capacity of an absorption type refrigerating device without depending on operating conditions at a cold utilization-side device side, in the absorption type refrigerating device driven by exhaust heat of an engine. <P>SOLUTION: A refrigerant absorbing capacity of an absorber is controlled to be reduced, and simultaneously a refrigerating capacity of the absorption type refrigerating device is reduced, when a temperature of a cooled fluid at an outlet of an evaporator becomes a set temperature calculated on the basis of an outside air temperature, or less. Further when the temperature becomes higher than the set temperature, the refrigerant absorbing capacity of the absorber is reduced, and simultaneously a refrigerating capacity of the absorption type refrigerating device is increased. According to this constitution, improvement of efficiency of the cold utilization-side device, and reduction of the initial costs and running costs of the entire refrigerating system can be combined though the refrigerating capacity of the absorption type refrigerating device is controlled without depending on the operating conditions at the cold utilization-side device side. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an absorption refrigeration apparatus driven by engine exhaust heat.

  The conventional air-cooled absorption refrigeration system is a direct air-cooling method in which the solution is cooled by air-cooling fins while absorbing the refrigerant vapor by the absorber, and the absorber absorbs the refrigerant vapor and cools the absorbed solution at the same time. Expansion of the gas-liquid interface is important for performance improvement. However, for that purpose, large-diameter heat transfer tubes for reducing the pressure loss of the refrigerant vapor absorbed by the solution flowing on the upper and lower absorber headers and the wall of the absorber heat transfer tube, and the large size of the refrigerant vapor communication tube with the evaporator are used. It is necessary to reduce the diameter of the device, and there is a great restriction on downsizing the device.

  On the other hand, the solution flowing into the absorber is supercooled by an air-cooled cooler, and the refrigerant heat is simply absorbed in the absorber, and the absorbed heat is removed by sensible heat of the supercooled solution (solution The separation cooling method is considered to be the most advantageous method for a small air-cooled absorption refrigeration apparatus because the absorber is made smaller than before.

  If this indirect air-cooled air-cooled absorption refrigeration system is driven by using exhaust heat from the engine, the size and cost of the apparatus can be reduced. It can be easily changed to a form to be converted to use, the effective use of exhaust heat is promoted, and it can be considered that it can greatly contribute to energy saving and CO2 reduction.

  By the way, as a conventional example of this indirect air cooling type air cooling absorption refrigeration apparatus, for example, there is one disclosed in Patent Document 1, but in this conventional example, an absorber is a type that sprays a solution. Although it is adopted, it is a conventional direct-fire method in which a solution is heated by a burner with a double-effect cycle, and there is no example using exhaust heat.

  Also, the compression refrigeration unit is driven by the engine, the absorption refrigeration unit is driven by the exhaust heat, and the refrigerant of the compression refrigeration unit is supercooled by the cold heat so that the performance of the compression refrigeration unit is improved. As a conventional example of a refrigeration system in which an absorption refrigeration apparatus and a compression refrigeration apparatus are combined, there are many examples such as that shown in Patent Document 2, for example.

JP-A-7-98163 JP-A-9-53864

  By the way, in a system in which an absorption refrigeration apparatus driven by exhaust heat of an engine is combined with a cold heat utilization side device that uses cold generated in the absorption refrigeration apparatus, for example, a compression refrigeration apparatus driven by an engine, In the conventional example described above, the refrigerant of the compression refrigeration apparatus is supercooled simply by the cold heat of the absorption refrigeration apparatus using the exhaust heat.

  However, in such a refrigeration system, when the outside air temperature decreases or when the compression refrigeration apparatus becomes a partial load, the refrigerant temperature (that is, condensation) at the condenser outlet of the compression refrigeration apparatus. In particular, when the decrease in the outside air temperature and the partial load of the compression refrigeration unit overlap, the decrease in the refrigerant temperature at the condenser outlet of the compression refrigeration unit increases. The evaporation temperature of the refrigeration apparatus or the temperature of the fluid to be cooled at the outlet of the evaporator (the refrigerant temperature of the compression refrigeration apparatus) also decreases, and the evaporation temperature or the temperature of the fluid to be cooled is a preset value (that is, the outside air temperature and the compression temperature). When the temperature is lower than the temperature value set based on the load of the refrigerating apparatus, the refrigerating capacity of the absorption refrigerating apparatus becomes an excessive state, and the refrigerant on the absorption refrigerating apparatus side is wasted. Become

  On the other hand, when the outside air temperature rises or when the load of the compression refrigeration apparatus increases, the refrigerant temperature at the condenser outlet of the compression refrigeration apparatus rises, so the evaporation temperature of the absorption refrigeration apparatus, or When the temperature of the fluid to be cooled at the outlet of the evaporator also rises and the evaporation temperature or the temperature of the fluid to be cooled rises above a preset value, the refrigeration capacity of the absorption refrigeration apparatus becomes insufficient. Therefore, it is necessary to quickly increase the refrigerating capacity.

  Therefore, in order to improve the efficiency of the compression refrigeration system and reduce the running cost without installing a large capacity exhaust heat driven absorption refrigeration system, respond to changes in the operating conditions on the compression refrigeration system side. Therefore, it is necessary to control the refrigeration capacity of the absorption refrigeration apparatus.

  In this case, the control of the refrigeration capacity of the absorption refrigeration apparatus is performed by detecting the operating conditions on the compression refrigeration apparatus side, for example, the outside air temperature and the refrigerant temperature (condensation temperature) on the outlet side of the condenser of the compression refrigeration apparatus, It is conceivable to use this to calculate the refrigeration capacity of the absorption refrigeration system (the refrigeration capacity required for the absorption refrigeration system) and control based on this, but according to such a control method, the absorption refrigeration system In addition to the conditions on the apparatus side, it is necessary to always detect the conditions on the compression refrigeration apparatus side, which complicates the control system and causes a cost increase. In particular, for example, a plurality of refrigeration systems combining an absorption refrigeration system and a compression refrigeration system exist in the same management area, and the refrigeration capacity of the absorption refrigeration system in each of these refrigeration systems is individually set on the compression refrigeration system side. When the control is performed in accordance with the operating conditions, the control system becomes more complicated, requires a lot of management costs, and further increases the cost.

  Accordingly, the present invention relates to an absorption refrigeration apparatus driven by exhaust heat of the engine, wherein the refrigeration capacity of the absorption refrigeration apparatus is set to the operating conditions on the cold heat utilization side equipment side that uses the cold generated by the absorption refrigeration apparatus. An object of the present invention is to provide an absorption refrigeration apparatus that can improve the efficiency of the cold energy utilization side device and reduce the initial cost and running cost of the entire refrigeration system by controlling without using the system. It is.

  In the present invention, the following configuration is adopted as a specific means for solving such a problem.

  In the first invention of the present application, a generator that operates in response to exhaust heat of the engine, a condenser, an evaporator that temporarily evaporates the refrigerant, a falling liquid film type absorber, and the absorber In an exhaust heat-driven absorption refrigeration apparatus having an air-cooled supercooler for supercooling an absorbing solution that enters, a refrigerant tank and a refrigerant electromagnetic valve are sequentially provided in the middle of a pipe from the condenser to the evaporator, while the absorber The refrigeration capacity of the absorption refrigeration system is controlled by changing the temperature of the supercooling solution flowing into the gas and / or the flow rate of the supercooling solution to control the refrigeration capacity of the absorption refrigeration system. When the temperature of the cooling fluid falls below the set temperature set based on the set temperature or the outside air temperature, the temperature of the supercooled solution flowing into the absorber and / or the flow rate of the supercooled solution is changed to Reduced refrigerant absorption capacity of absorber At the same time, the refrigerant solenoid valve is closed to reduce the amount of refrigerant flowing into the evaporator, thereby reducing the refrigeration capacity of the absorption refrigeration apparatus and storing the refrigerant from the condenser in the refrigerant tank. On the other hand, when the temperature is equal to or higher than the set temperature, the refrigerant absorption capacity of the absorber is increased by changing the temperature of the supercooling solution flowing into the absorber and / or the flow rate of the supercooling solution. At the same time, the refrigerant solenoid valve is opened, and the refrigerant stored in the refrigerant tank is caused to flow into the evaporator to increase the refrigerant flow rate, thereby increasing the refrigeration capacity of the absorption refrigeration apparatus. .

  According to such a configuration, the temperature of the supercooled solution flowing into the absorber and / or the flow rate of the supercooled solution is changed to increase or decrease the refrigerant absorption capacity of the absorber to control the refrigeration capacity of the absorption refrigeration apparatus. As a result, it is not affected by the load on the cold-use side device driven by the engine, so input control of exhaust heat is not particularly required when controlling the refrigerating capacity, and the cost is reduced by simplifying the control. Is possible.

  Further, when the temperature of the fluid to be cooled at the outlet of the evaporator becomes equal to or lower than the set temperature set based on the set temperature or the outside air temperature, the temperature and / or excess of the supercooled solution flowing into the absorber. Control is performed to change the flow rate of the cooling solution to reduce the refrigerant absorption capacity of the absorber, and at the same time, the refrigerant electromagnetic valve is closed to reduce the amount of refrigerant flowing into the evaporator, thereby reducing the refrigeration capacity of the absorption refrigeration apparatus Although the refrigeration capacity of the absorption refrigeration apparatus is simply controlled by the set temperature based on the set temperature or the outside air temperature, the refrigeration capacity of the absorption refrigeration apparatus is It is possible to cope with the degree of cooling demand on the side equipment side as much as possible, and both simplification of the control system and improvement in efficiency of the equipment on the side of cooling use can be achieved.

  Further, in this case, the amount of ineffective refrigerant on the absorption refrigeration apparatus side can be reduced by storing the refrigerant from the condenser in the refrigerant tank.

  On the other hand, when the temperature is equal to or higher than the set temperature, the refrigerant absorption capacity of the absorber is increased by changing the temperature of the supercooling solution flowing into the absorber and / or the flow rate of the supercooling solution. At the same time, the refrigerant solenoid valve is opened to allow the refrigerant stored in the refrigerant tank to flow into the evaporator to increase the refrigerant flow rate, thereby increasing the refrigeration capacity of the absorption refrigeration apparatus, thereby providing the cold heat utilization side device. As a result, the cold heat supply amount is increased, and the performance of the cold heat utilization side device is improved as compared with the normal state in which the above control is not performed.

  In addition, by controlling the refrigeration capacity of the absorption refrigeration apparatus according to the conditions on the absorption refrigeration apparatus side without depending on the conditions on the cold energy utilization side equipment side, the cost can be reduced by simplifying the control system. For example, when a plurality of refrigeration systems in which an absorption refrigeration apparatus and a cold energy utilization side device are combined exist in the same management area, the above effect becomes more remarkable.

  As the above synergistic effect, it is possible to improve the efficiency of the cold-use side equipment that uses the cold generated in the absorption refrigeration apparatus, and promote the reduction of the initial cost and running cost of the entire refrigeration system.

  In the absorption refrigeration apparatus according to the second invention of the present application, in the absorption refrigeration apparatus according to the first invention, the temperature when the refrigerant solenoid valve is opened from the closed state and the temperature when the refrigerant electromagnetic valve is opened from the closed state Are set to the same temperature or different temperatures, and the temperature is set to a preset value or a value set based on the outside air temperature.

  According to such a configuration, for example, when the set temperature when the refrigerant solenoid valve is opened from the closed to the closed temperature is set to the same temperature, control is performed as compared with the case where the set temperature is different. However, although the cost of the apparatus can be reduced, the solenoid valve is frequently opened and closed. Further, when the set temperature when the refrigerant solenoid valve is changed from open to closed and when the set temperature is changed from closed to open, for example, when the refrigerant electromagnetic valve is changed from open to closed (that is, to the refrigerant tank) When the set temperature at the start of refrigerant storage is set lower than the set temperature when the refrigerant solenoid valve is opened from the closed state (that is, the start of outflow of refrigerant stored in the refrigerant tank), the refrigeration capacity increases. Control is started earlier and a rapid increase in refrigeration capacity is realized.

  Also, by setting the temperature to a preset value or a value set based on the outside air temperature, for example, the temperature is set in consideration of the conditions on the absorption refrigeration equipment side or the conditions on the side of the cold energy utilization side. However, compared with the case of temperature control, the configuration of the control system for the refrigeration capacity of the absorption refrigeration apparatus is extremely simple, and the initial cost can be greatly reduced, and the speed of the refrigeration capacity can be controlled quickly. The If there is a possibility that the accuracy of the set value is insufficient, a value set based on the outside air temperature may be used.

  In the absorption refrigeration apparatus according to the third invention of the present application, in the absorption refrigeration apparatus according to the first or second invention, the opening and closing of the refrigerant solenoid valve is preset with the detected value of the evaporation temperature of the evaporator. Or a set value based on the outside air temperature, or a detected value of the temperature difference between the fluid to be cooled at the outlet and the inlet of the evaporator and a preset value or a set value based on the outside air temperature. It is characterized by doing.

  According to such a configuration, the opening and closing of the refrigerant solenoid valve is performed by the evaporation temperature of the evaporator or the temperature difference between the fluids to be cooled at the outlet and the inlet of the evaporator, and the conditions in the cold energy utilization side device are not related at all. Therefore, the opening and closing control of the refrigerant solenoid valve can be performed more quickly, and as a result, the absorption by reducing the evaporation capability of the evaporator by storing the refrigerant in the refrigerant tank with the refrigerant solenoid valve closed. Control of the refrigerating capacity of the refrigerating apparatus, and the refrigerating of the absorption refrigerating apparatus by increasing the evaporating capacity in the evaporator by opening the refrigerant solenoid valve and causing the refrigerant stored in the refrigerant tank to flow out to the evaporator side. Responsiveness of the increase control of the capacity is improved, and the refrigeration capacity can be precisely and quickly controlled.

  In the absorption refrigeration apparatus according to the fourth invention of the present application, in the absorption refrigeration apparatus according to the first, second, or third invention, a weir is provided in the refrigerant tank, and the dam is overflowed to evaporate the evaporation. The refrigerant flows into the evaporator, and the refrigerant flow rate to the evaporator is increased or decreased by opening or closing the refrigerant solenoid valve.

  According to such a configuration, at the time when the refrigerant solenoid valve is opened from the closed state, that is, at the time when the refrigerant stored after the refrigerant is stored in the refrigerant tank is flowed to the evaporator side, the refrigerant tank is always provided in the refrigerant tank. Since the refrigerant is stored, a sufficient amount of refrigerant is caused to flow to the evaporator side simultaneously with the opening operation of the refrigerant solenoid valve, and the increase control of the refrigerating capacity is performed more quickly and reliably. The effect becomes large when there are many start / stops.

  In the absorption refrigeration apparatus according to the fifth invention of the present application, in the absorption refrigeration apparatus according to the first, second, third, or fourth invention, the surplus refrigerant after the refrigerant tank is full, It is characterized in that it flows into the lower part of the evaporator or directly into the dilute solution reservoir of the absorber.

  According to such a configuration, surplus refrigerant is allowed to flow into the lower part of the evaporator or directly into the dilute solution pool of the absorber and mixed with the dilute solution in the dilute solution pool, so that the concentration of the absorbent solution Since the change can be suppressed, the solution crystal can be avoided without excessively concentrating the solution and by freezing the refrigerant in the evaporator or increasing the concentration in the generator.

  In the absorption refrigeration apparatus according to the sixth invention of the present application, in the absorption refrigeration apparatus according to the first, second, third, fourth, or fifth invention, the operation / stop of the absorption refrigeration apparatus is performed as described above. It is controlled by the solution temperature of the generator, and even if the engine is stopped, the refrigerant solenoid valve is closed if the solution temperature is equal to or higher than a predetermined temperature and the refrigerant tank has sufficient refrigerant storage capacity. If the absorption refrigeration apparatus is operated until the refrigerant tank is full, or only the solution pump is operated, and the solution temperature of the generator falls below the predetermined temperature, there is a margin in the refrigerant storage capacity of the refrigerant tank. However, the operation of the absorption refrigeration apparatus or the operation of the solution pump is stopped.

  According to such a configuration, even when the engine is stopped, the refrigerant is stored in the refrigerant tank when the refrigerant can be generated and the refrigerant can be stored in the refrigerant tank. The amount of the ineffective refrigerant can be reduced to effectively use the refrigerant, that is, the exhaust heat of the engine, and at the same time, it greatly contributes to the improvement in efficiency when the engine is started or the engine starts and stops frequently.

  In the absorption refrigeration apparatus according to the seventh invention of the present application, in the absorption refrigeration apparatus according to the first, second, third, fourth, fifth or sixth invention, from the refrigerant tank to the evaporator. Control of increase / decrease in the flow rate of the flowing refrigerant is performed by opening / closing a refrigerant flow control valve provided in the middle of the pipe from the refrigerant tank to the evaporator, or by allowing a weir provided in the refrigerant tank to flow over the refrigerant. What is made to flow in is characterized by being performed by opening and closing a refrigerant flow rate control valve provided in the middle of the pipe from the upstream portion of the weir to the evaporator.

  According to such a configuration, since the amount of refrigerant flowing into the evaporator can be finely increased / decreased, the control of the refrigeration capacity of the absorption refrigeration apparatus is made to correspond to the change in the load on the cold-use side device side. It can be precisely controlled.

  In the absorption refrigeration apparatus according to the eighth invention of the present application, in the absorption refrigeration apparatus according to the first, second, third, fourth, fifth, sixth or seventh invention, the air-cooled supercooler. The refrigerating capacity is controlled by changing the temperature of the supercooled solution flowing into the absorber according to the start / stop of the fan or the increase / decrease of the air volume.

  According to such a configuration, the control of the refrigerating capacity by changing the temperature of the supercooled solution can be performed very easily and quickly by making use of the characteristics of the indirect air cooling system and by the start / stop of the fan or the increase / decrease of the air volume. The capacity control range of the absorption refrigeration apparatus can be reduced to the minimum capacity, and as a result, the capacity of the cold energy utilization side equipment can be utilized to the limit.

  In the absorption refrigeration apparatus according to the ninth invention of the present application, in the absorption refrigeration apparatus according to the first, second, third, fourth, fifth, sixth or seventh invention, the air-cooled supercooler. The refrigerating capacity is controlled by changing the flow rate of the supercooled solution flowing into the absorber by a flow rate adjusting valve provided on the inlet side or the outlet side of the gas.

  According to such a configuration, the refrigeration capacity can be controlled very easily and quickly by adjusting the flow rate of the supercooled solution using the flow rate adjusting valve, so that the capacity control range of the absorption refrigeration system can be reduced to the minimum capacity. As a result, it becomes possible to use the capacity of the cold energy utilization side device to the limit.

  In the absorption refrigeration apparatus according to the tenth invention of the present application, in the absorption refrigeration apparatus according to the first, second, third, fourth, fifth, sixth or seventh invention, the refrigerant vapor is absorbed. Increase or decrease the flow rate of the solution pump that sucks and discharges the mixed solution of the diluted solution from the absorber and the concentrated solution that generates refrigerant vapor in the generator and whose temperature is reduced by heat exchange in the solution heat exchanger. It is characterized by controlling the refrigerating capacity.

  According to such a configuration, by increasing or decreasing the flow rate of the solution pump, the refrigeration capacity can be controlled easily and quickly, so that the capacity control range of the absorption refrigeration apparatus can be reduced to the minimum capacity, It becomes possible to use the capacity of the cold energy utilization side equipment to the limit.

  In the absorption refrigeration apparatus according to the eleventh invention of the present application, the generator that operates by receiving exhaust heat from the engine, the condenser, and the refrigerant accumulated in the lower refrigerant reservoir are circulated to the upper part by a refrigerant pump and dispersed. An exhaust heat driven absorption refrigeration apparatus comprising an evaporator to be evaporated, a falling liquid film type absorber, and an air-cooled supercooler for supercooling an absorbing solution entering the absorber, wherein the refrigerant reservoir of the evaporator The amount of the refrigerant is set to a constant amount, and the surplus refrigerant is allowed to flow into the dilute solution reservoir below the absorber, while the temperature of the supercooling solution flowing into the absorber and / or the flow rate of the supercooling solution is changed. It is assumed that the absorption capacity of the absorption refrigeration system is controlled by increasing or decreasing the capacity of the absorber, and the temperature of the fluid to be cooled at the outlet of the evaporator is set based on a preset set temperature or an outside air temperature When the temperature falls below The temperature of the supercooled solution flowing into the absorber and / or the flow rate of the supercooled solution is changed to reduce the refrigerant absorption capacity of the absorber, and at the same time, the refrigerant pump is stopped or circulated. The refrigerant flow rate is decreased, the refrigerant flow into the evaporator is stopped, or the refrigerant flow rate is decreased, thereby reducing the refrigeration capacity of the absorption refrigeration system, while the temperature is equal to or higher than the set temperature. In this case, the temperature of the supercooled solution flowing into the absorber and / or the flow rate of the supercooled solution is changed to increase the refrigerant absorption capacity of the absorber, and at the same time, the refrigerant pump is operated. Alternatively, control is performed to increase the refrigeration capacity of the absorption refrigeration system by increasing the flow rate of the circulating refrigerant and allowing the refrigerant to flow into the evaporator or increasing the amount of refrigerant flowing into the evaporator. .

  According to such a configuration, the temperature of the supercooled solution flowing into the absorber and / or the flow rate of the supercooled solution is changed to increase or decrease the refrigerant absorption capacity of the absorber to control the refrigeration capacity of the absorption refrigeration apparatus. As a result, it is not affected by the load on the cold-use side device driven by the engine, so input control of exhaust heat is not particularly required when controlling the refrigerating capacity, and the cost is reduced by simplifying the control. Is possible.

  In addition, when the temperature of the fluid to be cooled at the outlet of the evaporator becomes equal to or lower than the preset temperature calculated based on the preset temperature or the outside air temperature, the temperature and / or excess of the supercooled solution flowing into the absorber. Control is performed to change the flow rate of the cooling solution to reduce the refrigerant absorption capacity of the absorber, and at the same time, the refrigerant pump is stopped or the circulating refrigerant flow rate is reduced to prevent the refrigerant from flowing into the evaporator. By suspending or reducing the refrigerant inflow amount to reduce the refrigeration capacity of the absorption refrigeration system, the refrigeration capacity of the absorption refrigeration system is simply controlled by the set temperature based on the set temperature or the outside air temperature. Nevertheless, the refrigeration capacity of the absorption refrigeration apparatus can be made to correspond to the degree of cold demand on the cold-use side equipment side.

  Further, in this case, surplus refrigerant in the refrigerant reservoir below the evaporator flows into the dilute solution reservoir below the absorber and is mixed with the dilute solution in the dilute solution reservoir, thereby changing the concentration of the solution. Is suppressed.

  On the other hand, when the temperature is equal to or higher than the set temperature, the refrigerant absorption capacity of the absorber is increased by changing the temperature of the supercooling solution flowing into the absorber and / or the flow rate of the supercooling solution. At the same time, by performing control to increase the refrigeration capacity of the absorption refrigeration system by increasing the refrigerant flow rate that operates or circulates the refrigerant pump, the amount of cold supply to the cold-use side device increases, The performance of the cold energy utilization side device is improved as compared with the normal state in which the above control is not performed.

  In addition, by controlling the refrigeration capacity of the absorption refrigeration apparatus according to the conditions on the absorption refrigeration apparatus side without depending on the conditions on the cold energy utilization side equipment side, the cost can be reduced by simplifying the control system. For example, when a plurality of refrigeration systems in which an absorption refrigeration apparatus and a cold energy utilization side device are combined exist in the same management area, the above effect becomes more remarkable.

  As the above synergistic effect, it is possible to improve the efficiency of the cold-use side equipment that uses the cold generated in the absorption refrigeration apparatus, and promote the reduction of the initial cost and running cost of the entire refrigeration system.

  In the absorption refrigeration apparatus according to the twelfth invention of the present application, in the absorption refrigeration apparatus according to the eleventh invention, the temperature when the medium pump is stopped or the circulating refrigerant flow rate is decreased, and the medium The temperature when operating the pump or increasing the circulating refrigerant flow rate is set to the same or different temperature, and the temperature is set to a preset value or a value set based on the outside air temperature. It is a feature.

  According to such a configuration, for example, the temperature when the refrigerant pump is stopped or the circulating refrigerant flow rate is decreased and the temperature when the refrigerant pump is operated or the circulating refrigerant flow rate is increased are the same temperature. In this case, the control can be simplified and the cost of the apparatus can be reduced as compared with the case where the temperature is different, but the operation becomes complicated. Further, when the temperature when stopping the refrigerant pump or decreasing the circulating refrigerant flow rate and the temperature when operating the refrigerant pump or increasing the circulating refrigerant flow rate are different temperatures, for example, If the temperature when the refrigerant pump is stopped or the circulating refrigerant flow rate is decreased is set lower than the temperature when the refrigerant pump is operated or the circulating refrigerant flow rate is increased, The increase control of the capacity is started earlier, and the quick increase of the refrigerating capacity is realized.

  In addition, by setting the temperature to a preset value or a value set based on the outside air temperature, for example, the temperature is controlled in consideration of the conditions on the absorption refrigeration equipment side or the conditions on the side of the cold energy utilization side. Compared to the case, the configuration of the control system for the refrigeration capacity of the absorption refrigeration apparatus is extremely simple, the initial cost can be greatly reduced, and the quickness in the control of the refrigeration capacity is ensured. In addition, when there is a possibility that the accuracy of the preset set value is insufficient, the set value may be set based on the outside air temperature.

  In the absorption refrigeration apparatus according to the thirteenth invention of the present application, in the absorption refrigeration apparatus according to the eleventh or twelfth invention, the refrigerant pump is controlled to stop or circulate, and the refrigerant pump is reduced. The control of increasing the flow rate of the circulating refrigerant is performed by comparing the detected value of the evaporation temperature of the evaporator with a preset set value or a set value based on the outside air temperature, or at the outlet and inlet of the evaporator. This is performed by comparing the detected value of the temperature difference of the fluid to be cooled with a preset value or a preset value based on the outside air temperature.

  According to this configuration, the decrease control of the refrigerant flow rate at which the refrigerant pump is stopped or circulated, and the increase control of the refrigerant flow rate at which the refrigerant pump is operated or circulated are the evaporation temperature of the evaporator or the evaporation rate. This is performed by the temperature difference between the fluid to be cooled at the outlet and the inlet of the evaporator, and the conditions in the cold-use side equipment are not involved at all, so that the control can be performed more quickly, and as a result, the evaporation capacity of the evaporator can be increased. The responsiveness of the decrease control of the absorption capacity of the absorption refrigeration system by reducing the increase of the refrigeration capacity of the absorption refrigeration system by increasing the evaporation capacity of the evaporator improves the responsiveness of the refrigeration capacity. And quick control becomes possible.

  In the absorption refrigeration apparatus according to the fourteenth invention of the present application, in the absorption refrigeration apparatus according to the eleventh, twelfth or thirteenth invention, the absorption refrigeration apparatus is operated or stopped at the solution temperature of the generator. Even if the engine is stopped, the refrigerant solenoid valve is closed when the solution temperature is equal to or higher than a predetermined temperature and the refrigerant storage capacity of the refrigerant reservoir of the evaporator is sufficient. If the absorption refrigeration unit is operated until the refrigerant pool is full, or only the solution pump is operated, and the solution temperature of the generator falls below the predetermined temperature, there is a margin in the refrigerant storage capacity of the refrigerant pool. Is also characterized in that the operation of the absorption refrigeration apparatus or the operation of the solution pump is stopped.

  According to such a configuration, even if the engine is stopped, the refrigerant is stored in the refrigerant reservoir when the refrigerant can be generated and the refrigerant can be stored in the refrigerant reservoir. Thus, the amount of the ineffective refrigerant can be reduced to effectively use the refrigerant, that is, the exhaust heat of the engine, and at the same time, it greatly contributes to the efficiency improvement at the start.

  In the absorption refrigeration apparatus according to the fifteenth aspect of the present invention, in the absorption refrigeration apparatus according to the eleventh, twelfth, thirteenth, or fourteenth aspect, a refrigerant tank is provided in the middle of the piping from the condenser to the evaporator. And a refrigerant solenoid valve are sequentially provided, and when the absorption refrigeration apparatus is in operation and the refrigerant pump is stopped, the refrigerant solenoid valve is closed to collect refrigerant in the refrigerant tank, while the evaporator below the evaporator is When the amount of refrigerant in the refrigerant pool decreases, the refrigerant electromagnetic valve is opened, and the refrigerant in the refrigerant tank is replenished to the refrigerant pool.

  According to this configuration, when the absorption refrigeration apparatus is in operation and the refrigerant pump is stopped, that is, liquid refrigerant is generated in the condenser, the refrigeration required for the absorption refrigeration apparatus. In the case where the capacity is low and the refrigerant pump is stopped and the refrigerant is not supplied to the evaporator, the liquid refrigerant from the condenser is in an excess state. It is possible to reduce the amount of the invalid refrigerant as much as possible.

  On the other hand, when the amount of refrigerant in the refrigerant pool at the lower part of the evaporator decreases, that is, when the refrigerating capacity of the absorption refrigeration apparatus is required to increase, the temperature of the supercooled solution flowing into the absorber and / or the supercooled solution In the case where the refrigerant absorption capacity of the absorber is increased to increase the refrigerant absorption capacity, the refrigerant pump is operated accordingly, the refrigerant amount in the refrigerant reservoir is reduced, and replenishment of the refrigerant is required. As the refrigerant in the refrigerant tank is replenished in the refrigerant reservoir, the amount of refrigerant circulated to the evaporator further increases as compared with the case where such refrigerant replenishment is not performed, and the absorption refrigeration apparatus As a result, it becomes easy to control the refrigeration capacity of the absorption refrigeration apparatus to correspond to changes in the operating conditions of the cold-use equipment.

  In the absorption refrigeration apparatus according to the sixteenth invention of the present application, in the absorption refrigeration apparatus according to the eleventh, twelfth, thirteenth, fourteenth or fifteenth invention, a fan provided in the air-cooled supercooler is provided. The refrigeration capacity is controlled by changing the temperature of the supercooled solution flowing into the absorber according to start / stop or increase / decrease of air volume.

  According to such a configuration, the control of the refrigerating capacity by changing the temperature of the supercooled solution can be performed very easily and quickly by making use of the characteristics of the indirect air cooling system and by the start / stop of the fan or the increase / decrease of the air volume. The capacity control range of the absorption refrigeration apparatus can be reduced to the minimum capacity, and as a result, the capacity of the cold energy utilization side equipment can be utilized to the limit.

  In the absorption refrigeration apparatus according to the seventeenth invention of the present application, in the absorption refrigeration apparatus according to the eleventh, twelfth, thirteenth, fourteenth or fifteenth invention, an inlet side or an outlet side of the air-cooled supercooler. The refrigeration capacity is controlled by changing the flow rate of the supercooled solution flowing into the absorber by a flow rate adjusting valve provided in the above.

  According to such a configuration, the refrigeration capacity can be controlled very easily and quickly by adjusting the flow rate of the supercooled solution using the flow rate adjusting valve, so that the capacity control range of the absorption refrigeration system can be reduced to the minimum capacity. As a result, it becomes possible to use the capacity of the cold energy utilization side device to the limit.

  In the absorption refrigeration apparatus according to the eighteenth invention of the present application, in the absorption refrigeration apparatus according to the eleventh, twelfth, thirteenth, fourteenth, or fifteenth invention, the rare gas from the absorber that has absorbed refrigerant vapor. Control the refrigeration capacity by increasing or decreasing the flow rate of the solution pump that draws and discharges the mixed solution of the solution and the concentrated solution that generates refrigerant vapor in the generator and whose temperature is reduced by heat exchange in the solution heat exchanger. It is characterized by doing.

  According to such a configuration, by increasing or decreasing the flow rate of the solution pump, the refrigeration capacity can be controlled easily and quickly, so that the capacity control range of the absorption refrigeration apparatus can be reduced to the minimum capacity, It becomes possible to use the capacity of the cold energy utilization side equipment to the limit.

  As a result of the above, according to the absorption refrigeration apparatus of the present invention, the refrigeration capacity of the absorption refrigeration apparatus is not based on the operating conditions on the cold heat utilization side equipment side using the cold generated by the absorption refrigeration apparatus, By controlling based on the conditions on the absorption refrigeration apparatus side, it is possible to achieve both the improvement of the efficiency of the cold energy utilization side device and the reduction of the initial cost and running cost of the entire refrigeration system.

  Hereinafter, the present invention will be specifically described based on preferred embodiments.

I: First Embodiment FIG. 1 shows a refrigeration system according to a first embodiment of the present invention. This refrigeration system is configured by combining an absorption refrigeration apparatus Z driven by exhaust heat and a compression refrigeration apparatus X as a cold heat utilization side device.

The absorption refrigeration apparatus Z employs water (H ₂ O) as a refrigerant, lithium bromide (LiBr) as an absorption liquid, and an exhaust heat-driven air-cooled absorption refrigeration apparatus that uses exhaust hot water as a heating source. In the heat exchanger 1a, the absorption dilute solution is heated with exhaust warm water to generate the refrigerant vapor and the absorption concentrated solution, and the refrigerant vapor flowing from the generator 1 through the pipe 51 is condensed. The refrigerant to be cooled and the fluid to be cooled (that is, the refrigerant that is discharged from the condenser 23 of the compression refrigeration apparatus X described below) inside the refrigerant liquid flowing in from the condenser 2 through the pipe line 52 are contained inside. The evaporator 3 that is sprayed on the plate surface of the flowing plate heat exchanger 3a to evaporate it transiently, and the downflow that absorbs the refrigerant vapor generated in the evaporator 3 to generate an absorption diluted solution To the liquid film type absorber 4 and the generator 1 A solution heat exchanger 5 for exchanging heat in the plate heat exchanger 5a between the absorbing diluted solution flowing in through the passage 53 and the absorbing concentrated solution flowing out from the generator 1 through the conduit 54; There is provided a fan 7 for introducing a mixed solution of an absorption concentrated solution and an absorption dilute solution in a dilute solution reservoir 16 provided in the lower part of the absorber 4 through a pipe 55 and supercooling it to flow into the absorber 4. And an air-cooled solution cooler 6 and a solution pump 9 for allowing the absorbed dilute solution from the absorber 4 to flow into the generator 1 through the solution heat exchanger 5.

  Here, the evaporator 3 and the absorber 4 are housed in an integral housing 15, and the unevaporated refrigerant flowing down to the lower part of the evaporator 3 flows through the bottom wall of the housing 15 as it is. It flows into the dilute solution reservoir 16 provided at the lower part of the slag and is mixed with the absorbed dilute solution in the dilute solution reservoir 16. As a result, the solution concentration is prevented from greatly changing due to an increase or decrease in the amount of refrigerant generated in the generator 1.

  Further, the middle of the pipe line 52 connecting the condenser 2 and the evaporator 3 and the evaporator 3 are connected by a bypass pipe line 64. The bypass pipe 64 is provided with the refrigerant tank 14 and the refrigerant solenoid valve 10 sequentially from the upstream side. Therefore, when the refrigerant electromagnetic valve 10 is closed, the refrigerant is stored in the refrigerant tank 14, while when the refrigerant electromagnetic valve 10 is opened, the refrigerant stored in the refrigerant tank 14 is supplied to the evaporator 3 side. Is done.

  The compression refrigeration apparatus X is configured by connecting a compressor 21, an evaporator 22, a condenser 23, an expansion valve 24, and a four-way valve 25 that are driven by an engine 26 through a pipeline. Then, the liquid refrigerant condensed and flowing out in the condenser 23 flows into the plate heat exchanger 3a of the evaporator 3 on the absorption refrigeration apparatus Z side from the lower end side through the pipe 61, The refrigerant flows out from the upper end side to the evaporator 22 side through the pipe line 62. At that time, it is supercooled in the plate heat exchanger 3a of the evaporator 3 of the absorption refrigeration apparatus.

  In order to drive the absorption refrigeration apparatus Z using the exhaust water of the engine 26 of the compression refrigeration apparatus X as a heat source, the cooling water circulation system of the engine 26 and the heat exchanger 1a of the generator 1 are connected to each other by a pipe. 57 and 58 are connected.

  The refrigeration system configured as described above operates as follows.

  First, in the compression refrigeration apparatus X, the compressor 26 of the compression refrigeration apparatus X is driven by the engine 26, and the gas refrigerant discharged from the compressor 21 is condensed in the condenser 23 to be liquid refrigerant. In addition, the liquid refrigerant is further supercooled in the evaporator 3 on the absorption refrigeration apparatus Z side, and the supercooled refrigerant is evaporated in the evaporator 22 to cool the room. In this case, the refrigeration capacity can be improved by supercooling the liquid refrigerant from the condenser 23.

  On the other hand, in the absorption refrigeration apparatus Z, the generator 1 receives the hot water from the engine 26, and the generator 1 heats the absorption dilute solution from the absorber 4 to generate refrigerant vapor and the absorption concentrated solution. . The refrigerant vapor generated in the generator 1 is condensed in the air-cooled condenser 2 provided with a fan 8 to be a liquid refrigerant.

  Here, the liquid refrigerant from the condenser 2 flows into the upper part of the evaporator 3 through each of the pipe line 52 and the bypass pipe line 64 when the refrigerant solenoid valve 10 is open. Is done. Further, when the refrigerant solenoid valve 10 is in a closing operation, a part of the liquid refrigerant from the condenser 2 flows into the upper part of the evaporator 3 through the conduit 52, and the other part of the liquid refrigerant. The refrigerant is stored in the refrigerant tank 14. Accordingly, the amount of liquid refrigerant flowing into the evaporator 3 increases when the refrigerant solenoid valve 10 is opened and decreases when the refrigerant solenoid 10 is closed.

  The liquid refrigerant that has flowed into the upper portion of the evaporator 3 is evenly spread from the spreader (not shown) to the upper portion of the plate heat exchanger 3a and flows down along the surface of the heat exchanger 3a. Evaporate in the middle to generate refrigerant vapor. At this time, the refrigerant on the compression refrigeration apparatus X side flowing in the plate heat exchanger 3a is supercooled by the heat of evaporation.

  On the other hand, in the absorber 4, the absorption dilute solution supercooled in the air-cooled supercooler 6 is evenly spread from the spreader (not shown) to the plate 4a and flows down along the plate 4a. The refrigerant vapor from the evaporator 3 is absorbed to form an absorbing diluted solution, which is stored in the diluted solution reservoir 16.

  In the dilute solution reservoir 16, if there is an absorbed dilute solution that has absorbed the refrigerant vapor in the absorber 4 and an unevaporated refrigerant that has not evaporated in the evaporator 3 and has flowed down, The mixed solution is stored, and the mixed solution is supplied to the generator 1 side by the solution pump 9. At this time, in the solution heat exchanger 5, heat recovery is performed by heat exchange between the absorption diluted solution from the absorber 4 side and the absorption concentrated solution generated in the generator 1.

  In the absorption refrigeration apparatus Z, the refrigeration capacity is increased or decreased by adjusting the absorption capacity in the absorber 4. That is, by increasing the absorption capacity of the absorber 4 and increasing the absorption of refrigerant vapor into the absorption diluted solution, the evaporation capacity in the evaporator 3 (that is, the supercooling capacity for the refrigerant on the compression refrigeration apparatus X side). As a result, the refrigerating capacity of the absorption refrigeration apparatus Z as a whole is enhanced.

  By the way, as described above, the refrigeration capacity of the compression refrigeration apparatus X varies depending on the degree of supercooling of the refrigerant discharged from the condenser 23, and the refrigeration capacity increases as the degree of supercooling increases. Therefore, in terms of improving the capacity of the compression refrigeration apparatus X, the refrigerant on the compression refrigeration apparatus X side needs to be supercooled as much as possible by the cold heat of the absorption refrigeration apparatus Z. What is necessary is just to combine the absorption refrigeration apparatus Z of the capability which can achieve the supercooling temperature corresponding to the refrigerating capacity of the refrigeration apparatus X.

  However, when the outside air temperature decreases or when the compression refrigeration apparatus becomes a partial load, the refrigerant temperature (that is, the condensation temperature) at the condenser outlet of the compression refrigeration apparatus decreases. When the drop in temperature and the partial load of the compression refrigeration unit overlap, the drop in refrigerant temperature at the condenser outlet of this compression refrigeration unit increases, so the evaporation temperature of the absorption refrigeration unit or the evaporator The temperature of the fluid to be cooled at the outlet (the refrigerant temperature of the compression refrigeration system) also decreases, and the evaporation temperature or the temperature of the fluid to be cooled is a preset value or a set value based on the outside air temperature (that is, the outside air temperature and the compression refrigeration system). If the temperature is lower than the temperature value set based on the load of the absorption refrigeration system, the refrigeration capacity of the absorption refrigeration apparatus becomes excessive, and the refrigerant on the absorption refrigeration apparatus side is wasted.

  On the other hand, when the outside air temperature rises or when the load of the compression refrigeration apparatus increases, the refrigerant temperature at the condenser outlet of the compression refrigeration apparatus rises, so the evaporation temperature of the absorption refrigeration apparatus or the evaporator When the temperature of the fluid to be cooled at the outlet of the refrigerant rises and the evaporating temperature or the temperature of the fluid to be cooled rises above a preset value or a set value based on the outside air temperature, the refrigeration capacity of the absorption refrigeration apparatus is reduced. Since the state becomes insufficient, it is necessary to increase the refrigerant cooling rate to the evaporator at the same time as increasing the supercooling temperature or the supercooling flow rate of the solution flowing into the absorber and increasing the refrigeration capacity quickly.

  Therefore, in order to improve the efficiency of the compression refrigeration system and reduce the running cost without installing a large capacity exhaust heat driven absorption refrigeration system, respond to changes in the operating conditions on the compression refrigeration system side. Therefore, it is necessary to control the refrigeration capacity of the absorption refrigeration apparatus.

  In this case, the control of the refrigeration capacity of the absorption refrigeration apparatus is performed by detecting the operating conditions on the compression refrigeration apparatus side, for example, the outside air temperature and the refrigerant temperature (condensation temperature) on the outlet side of the condenser of the compression refrigeration apparatus, It is conceivable to use this to calculate the refrigeration capacity of the absorption refrigeration system (the refrigeration capacity required for the absorption refrigeration system) and control based on this, but according to such a control method, the absorption refrigeration system In addition to the conditions on the apparatus side, it is necessary to always detect the conditions on the compression refrigeration apparatus side, which complicates the control system and causes a cost increase. In particular, for example, a plurality of refrigeration systems combining an absorption refrigeration system and a compression refrigeration system exist in the same management area, and the refrigeration capacity of the absorption refrigeration system in each of these refrigeration systems is individually set on the compression refrigeration system side. When the control is performed in accordance with the operating conditions, the control system becomes more complicated, requires a lot of management costs, and further increases the cost.

  Accordingly, the present invention relates to an absorption refrigeration apparatus driven by exhaust heat of the engine, wherein the refrigeration capacity of the absorption refrigeration apparatus is set to the operating conditions on the cold heat utilization side equipment side that uses the cold generated by the absorption refrigeration apparatus. By controlling without relying on it, the efficiency of the cold energy utilization side device is improved, and the initial cost and running cost of the entire refrigeration system are reduced.

  In order to realize such control, in this embodiment, the refrigerant absorption capacity of the absorber 4 is increased or decreased by changing the temperature of the supercooled solution flowing into the absorber 4, so that the absorption refrigeration apparatus Z When the temperature of the fluid to be cooled at the outlet of the evaporator 3 is equal to or lower than a preset temperature set based on a preset preset temperature or an outside air temperature under such a configuration, At the same time as controlling the temperature of the supercooled solution flowing into the absorber 4 to reduce the refrigerant absorption capacity of the absorber 4, the refrigerant solenoid valve 10 is closed and the amount of refrigerant flowing into the evaporator 3 is closed. Is reduced to reduce the refrigerating capacity of the absorption refrigeration apparatus Z, and the refrigerant from the condenser 2 is stored in the refrigerant tank 14.

  Further, when the temperature becomes equal to or higher than the set temperature, the temperature of the supercooled solution flowing into the absorber 4 is changed to reduce the refrigerant absorption capacity of the absorber 4, and at the same time, the refrigerant solenoid valve 10 is opened, and the refrigerant stored in the refrigerant tank 14 is caused to flow into the evaporator 3 to increase the refrigerant flow rate, thereby increasing the refrigeration capacity of the absorption refrigeration apparatus Z.

  Specifically, a temperature sensor 18 is provided on the outlet side of the evaporator 3 to detect the refrigerant temperature at the outlet of the evaporator 3 (that is, the refrigerant subcooling temperature on the compression refrigeration apparatus X side). However, when it is based on the outside air temperature, an outside air temperature sensor 20 is provided to detect the outside air temperature at the same time.

  Here, the set temperature is set as the outlet temperature in the evaporator 3 from the condensation temperature in the condenser 23 of the compression refrigeration apparatus X and the temperature that can be supercooled by the refrigeration capacity of the absorption refrigeration apparatus Z. In the case of setting based on the outside air temperature detected by the outside air temperature sensor 20, in the condenser 23 of the compression refrigeration apparatus X corresponding to the outside air temperature A condensing temperature is predicted, a predetermined supercooling temperature is calculated from the predicted condensing temperature and the refrigerating capacity of the absorption refrigeration apparatus Z at the outside air temperature, and an outlet temperature in the evaporator 3 is obtained. It is set as a set temperature for controlling the refrigeration capacity of the device Z. However, the setting lower limit value of the outlet temperature of the evaporator 3 needs to be a value considering the freezing of the refrigerant.

  Then, the outlet temperature of the evaporator 3 detected by the temperature sensor 18 is compared with the set temperature. When the outlet temperature of the evaporator 3 is lower than the set temperature, the refrigerating capacity of the absorption refrigeration apparatus Z is excessive. On the contrary, if the outlet temperature of the evaporator 3 is higher than the set temperature, the refrigerating capacity of the absorption refrigeration apparatus Z is insufficient and the required supercooling temperature cannot be secured. The control to increase is performed.

  Specific control of the refrigeration capacity of the absorption refrigeration apparatus Z is as follows.

  That is, when the temperature of the refrigerant at the outlet of the evaporator 3 (the refrigerant temperature of the compression refrigeration apparatus X) becomes equal to or lower than the set temperature calculated based on the set temperature or the outside air temperature, the air-cooled supercooler 6 The refrigerant absorption capacity of the absorber 4 can be increased by changing the temperature of the supercooled solution circulating in the air-cooled supercooler 6 by the start and stop of the fan 7 provided in the air or by increasing or decreasing the air volume of the fan 7. Simultaneously with the control to decrease, the refrigerant solenoid valve 10 is closed to reduce the amount of refrigerant flowing into the evaporator 3, thereby reducing the refrigeration capacity of the absorption refrigeration apparatus Z. As a result, the refrigeration capacity of the absorption refrigeration apparatus Z is made to correspond as much as possible to the degree of supercooling of the compression refrigeration apparatus X while being in a control mode that does not take into account the conditions on the compression refrigeration apparatus X side. be able to. In this case, the amount of inactive refrigerant on the absorption refrigeration apparatus Z side can be reduced by storing the refrigerant (excess refrigerant) from the condenser 2 in the refrigerant tank 14.

  On the other hand, when the temperature is equal to or higher than the set temperature, the temperature of the supercooled solution flowing into the absorber 4 is changed to reduce the refrigerant absorption capacity of the absorber 4, and at the same time, the refrigerant electromagnetic valve 10 is opened, the refrigerant stored in the refrigerant tank 14 is caused to flow into the evaporator 3, and the refrigerant flow rate is increased to increase the refrigeration capacity of the absorption refrigeration apparatus Z, thereby controlling the compression refrigeration apparatus. The supercooling temperature of the refrigerant of X increases, and the performance of the compression refrigeration apparatus X is improved compared to the normal state where the above control is not performed.

  Furthermore, the refrigerant is stored in the refrigerant tank 14 not only when the engine 26 is in operation and the refrigerant electromagnetic valve 10 is in a closed operation, but also when the operation of the engine 26 is stopped. That is, even when the engine 26 is in a stopped state, if the solution temperature of the generator 1 is equal to or higher than a predetermined temperature and the refrigerant storage capacity of the refrigerant tank 14 has a margin, the refrigerant electromagnetic valve 10 is closed. The refrigerant is stored in the refrigerant tank 14 by operating the absorption refrigeration apparatus Z until the refrigerant tank 14 is full or operating only the solution pump 9. If the solution temperature of the generator 1 is equal to or lower than the predetermined temperature, even if the refrigerant storage capacity of the refrigerant tank 14 is sufficient, the operation of the absorption refrigeration apparatus Z is stopped, or the solution pump 6 is stopped, and the storage of the refrigerant in the refrigerant tank 14 is stopped.

  According to such a configuration, even when the engine 26 is stopped, the refrigerant is stored in the refrigerant tank 14 when the refrigerant can be generated and the refrigerant can be stored in the refrigerant tank 14. Therefore, the amount of the ineffective refrigerant can be reduced to effectively use the refrigerant, that is, the exhaust heat of the engine.

  As a synergistic effect, the efficiency of the compression refrigeration apparatus X can be improved and the refrigeration can be achieved despite the fact that the refrigeration capacity of the absorption refrigeration apparatus is controlled without being based on the operating conditions on the compression refrigeration apparatus X side. The initial cost and running cost of the entire system can be reduced at the same time.

  In this embodiment, the set temperature when the refrigerant electromagnetic valve 10 is changed from open to closed and the set temperature when the refrigerant electromagnetic valve 10 is changed from closed to open are set to the same temperature, but the present invention is limited to this. Instead, it can be at a different temperature. For example, when the refrigerant electromagnetic valve 10 is opened to closed (that is, the refrigerant starts to be stored in the refrigerant tank 14), the set temperature is set when the refrigerant electromagnetic valve 10 is opened from the closed (that is, the refrigerant tank 14). When the temperature is set to be lower than the set temperature of the refrigerant stored in the refrigerant, the increase control of the refrigerating capacity is started earlier, and a quick increase of the refrigerating capacity is realized.

  Further, the piping 52 from the condenser 2 to the evaporator 3 can be omitted and simplified, and in this case, the refrigerant supplied to the evaporator 3 is only when the solenoid valve 10 is open, Although the refrigerant can be used more effectively, it is necessary to control the electromagnetic valve 10 more complicatedly.

II: Second Embodiment FIG. 2 shows a refrigeration system according to a second embodiment of the present invention. This refrigeration system has the same basic configuration as that of the refrigeration system according to the first embodiment, and is configured by combining an exhaust heat-driven absorption refrigeration apparatus Z and a compression refrigeration apparatus X.

And the point that the refrigerating system concerning this embodiment differs from the refrigerating system concerning the 1st embodiment of the above,
The refrigerant tank 14 is provided with a weir 14a, and among the liquid refrigerant from the condenser 2, the liquid refrigerant that has overflowed the weir 14a is caused to flow into the evaporator 3 side through a pipe 64. ,
The capacity of the absorber 4 is adjusted by adjusting the opening degree of the flow rate adjusting valve 11 provided on the upstream side of the air-cooled supercooler 6 or the flow rate adjusting valve 12 provided on the downstream side and adjusting the flow rate of the solution pump 9. The point is that the temperature is adjusted by controlling the temperature of the supercooled solution circulating in the air-cooled supercooler 6.

  Here, the operational effects peculiar to the above differences are as follows.

  The refrigeration tank 14 is provided with a weir 14a, and among the liquid refrigerant from the condenser 2, the liquid refrigerant that has overflowed the weir 14a is caused to flow into the evaporator 3 side via the pipe line 52. Thus, when the refrigerant solenoid valve 10 is opened, that is, when the refrigerant stored in the refrigerant tank 14 flows to the evaporator 3 side, the refrigerant tank 14 is always full of refrigerant. Therefore, it is not necessary to store the refrigerant in the refrigerant tank at the time of starting or the like, and a sufficient amount of refrigerant is caused to flow toward the evaporator 3 at the same time when the refrigerant electromagnetic valve 10 is opened. This is done more quickly and reliably.

  By adjusting the capacity of the absorber 4 by adjusting the opening degree of the flow rate adjusting valve 11 or the flow rate adjusting valve 12 and adjusting the flow rate of the solution pump 9, it is very easy to control the refrigerating capacity of the absorption refrigeration apparatus Z. And since it can be performed quickly, the capacity control range of the absorption refrigeration apparatus Z can be reduced to the minimum capacity, and as a result, the capacity of the compression refrigeration apparatus X can be utilized to the limit.

  In addition, although the said refrigerant | coolant electromagnetic valve 10 is set as the structure which opens or closes the said bypass pipe line 64, in other embodiment, this can also be replaced with the refrigerant | coolant flow control valve which can adjust flow volume. In the case of such a configuration, the amount of refrigerant flowing into the evaporator can be controlled more or less finely as compared with the case of the refrigerant solenoid valve 10, so that the refrigerating capacity of the absorption refrigeration apparatus Z can be increased. The control can be more precisely controlled in accordance with the load change on the compression refrigeration apparatus X side.

  Since the structure and the effect other than the above are the same as those in the case of the first embodiment, here, after attaching the same reference numerals to the respective structural members in FIG. The corresponding explanation in the first embodiment is used, and the explanation here is omitted.

III: Third Embodiment FIG. 3 shows a refrigeration system according to a third embodiment of the present invention. This refrigeration system is configured by combining an exhaust heat driven absorption refrigeration apparatus Z and a compression refrigeration apparatus X.

The absorption refrigeration apparatus Z employs water (H ₂ O) as a refrigerant, lithium bromide (LiBr) as an absorption liquid, and an exhaust heat-driven air-cooled absorption refrigeration apparatus that uses exhaust hot water as a heating source. In the heat exchanger 1a, the absorption dilute solution is heated with exhaust warm water to generate the refrigerant vapor and the absorption concentrated solution, and the refrigerant vapor flowing from the generator 1 through the pipe 51 is condensed. The refrigerant 2 to be cooled and the refrigerant liquid flowing from the condenser 2 through the pipe 52 to the lower refrigerant reservoir 17 by the refrigerant pump 13 provided in the pipe 63 (that is, the following description) Of the compressor refrigeration apparatus X) is circulated to the upper side of the plate heat exchanger 3a flowing inside, the evaporator 3 for spraying on the plate surface and evaporating it, and the above Refrigerant steam generated in the evaporator 3 , A falling film type absorber 4 that absorbs water to generate a diluted absorption solution, an absorbed diluted solution that flows into the generator 1 through a line 53, and an absorbed concentrated solution that flows out of the generator 1 through a line 54 Of the solution heat exchanger 5 that exchanges heat in the plate heat exchanger 5 a, the absorption concentrated solution from the solution heat exchanger 5, and the absorption diluted solution in the diluted solution reservoir 16 provided below the absorber 4 An air-cooled solution cooler 6 provided with a fan 7 that causes the solution to flow through the pipe line 55 and supercools it to flow into the absorber 4, and the solution heat exchange between the absorption diluted solution from the absorber 4 It comprises a solution pump 9 that flows into the generator 1 via a vessel 5.

  Here, the evaporator 3 and the absorber 4 are housed in an integral casing 15, and the refrigerant overflowing from the refrigerant reservoir 17 provided at the lower part of the evaporator 3 is allowed to flow through the bottom wall of the casing 15. It flows into the dilute solution reservoir 16 provided at the lower part of the absorber 4 and is mixed with the dilute absorbent solution in the dilute solution reservoir 16. As a result, it is possible to prevent the solution concentration from greatly changing due to the increase or decrease in the amount of refrigerant generated in the generator 1, and to avoid refrigerant freezing in the evaporator and crystallization of the solution in the generator due to excessive concentration.

  The compression refrigeration apparatus X is configured by connecting a compressor 21, an evaporator 22, a condenser 23, an expansion valve 24, and a four-way valve 25 that are driven by an engine 26 through a pipeline. Then, the liquid refrigerant condensed and flowing out in the condenser 23 flows into the plate heat exchanger 3a of the evaporator 3 on the absorption refrigeration apparatus Z side from the lower end side through the pipe 61, The refrigerant flows out from the upper end side to the evaporator 22 side through the pipe line 62. At that time, it is supercooled in the plate heat exchanger 3a of the evaporator 3 of the absorption refrigeration apparatus.

  In order to drive the absorption refrigeration apparatus Z using the exhaust water of the engine 26 of the compression refrigeration apparatus X as a heat source, the cooling water circulation system of the engine 26 and the heat exchanger 1a of the generator 1 are connected to each other by a pipe. 57 and 58 are connected.

  The refrigeration system configured as described above operates as follows.

  First, in the compression refrigeration apparatus X, the compressor 26 of the compression refrigeration apparatus X is driven by the engine 26, and the gas refrigerant discharged from the compressor 21 is condensed in the condenser 23 to be liquid refrigerant. In addition, the liquid refrigerant is further supercooled in the evaporator 3 on the absorption refrigeration apparatus Z side, and the supercooled refrigerant is evaporated in the evaporator 22 to cool the room. In this case, the refrigeration capacity can be improved by supercooling the liquid refrigerant from the condenser 23.

  On the other hand, in the absorption refrigeration apparatus Z, the generator 1 receives the hot water from the engine 26, and the generator 1 heats the absorption dilute solution from the absorber 4 to generate refrigerant vapor and the absorption concentrated solution. . The refrigerant vapor generated in the generator 1 is condensed in the air-cooled condenser 2 provided with a fan 8 to be a liquid refrigerant.

  Here, the liquid refrigerant from the condenser 2 flows into the refrigerant reservoir 17 provided at the lower part of the evaporator 3 through the pipe line 52. The refrigerant flowing into the refrigerant reservoir 17 is circulated to the upper side of the plate heat exchanger 3a of the evaporator 3 by the refrigerant pump 13, and a spreader ( (Not shown) is sprayed evenly and evaporates while flowing down along the surface of the heat exchanger 3a to generate refrigerant vapor. At this time, the refrigerant on the compression refrigeration apparatus X side flowing in the plate heat exchanger 3a is supercooled by the heat of evaporation.

  On the other hand, in the absorber 4, the absorption dilute solution supercooled in the air-cooled supercooler 6 is evenly sprayed from the sprayer (not shown) to the plate 4a and flows down along the plate 4a. The refrigerant vapor from the evaporator 3 is absorbed to form an absorbing diluted solution, which is stored in the diluted solution reservoir 16.

  In the dilute solution reservoir 16, there is a mixed solution composed of an absorbed dilute solution that has absorbed refrigerant vapor in the absorber 4 and an unevaporated refrigerant that flows in when the amount of refrigerant accumulated in the refrigerant reservoir 17 exceeds the amount stored in the evaporator 3. While being stored, this mixed solution is supplied to the generator 1 side by the solution pump 9. At this time, in the solution heat exchanger 5, heat recovery is performed by heat exchange between the absorption diluted solution from the absorber 4 side and the absorption concentrated solution generated in the generator 1, and the diluted solution Increase the temperature to decrease the temperature of the concentrated solution.

  In the absorption refrigeration apparatus Z, the refrigeration capacity is increased or decreased by adjusting the absorption capacity in the absorber 4. That is, by increasing the absorption capacity of the absorber 4 and increasing the absorption of refrigerant vapor into the absorption diluted solution, the evaporation capacity in the evaporator 3 (that is, the supercooling capacity for the refrigerant on the compression refrigeration apparatus X side). As a result, the refrigerating capacity of the absorption refrigeration apparatus Z as a whole is enhanced.

  By the way, as described above, the refrigeration capacity of the compression refrigeration apparatus X varies depending on the degree of supercooling of the refrigerant discharged from the condenser 23, and the refrigeration capacity increases as the degree of supercooling increases. Therefore, in terms of improving the capacity of the compression refrigeration apparatus X, the refrigerant on the compression refrigeration apparatus X side needs to be supercooled as much as possible by the cold heat of the absorption refrigeration apparatus Z. What is necessary is just to combine the absorption refrigeration apparatus Z of the capability which can achieve the supercooling temperature corresponding to the refrigerating capacity of the refrigeration apparatus X.

  However, when the outside air temperature decreases or when the compression refrigeration apparatus becomes a partial load, the refrigerant temperature (that is, the condensation temperature) at the condenser outlet of the compression refrigeration apparatus decreases. When the drop in temperature and the partial load of the compression refrigeration unit overlap, the drop in refrigerant temperature at the condenser outlet of this compression refrigeration unit increases, so the evaporation temperature of the absorption refrigeration unit or the evaporator The temperature of the fluid to be cooled at the outlet (the refrigerant temperature of the compression refrigeration system) also decreases, and the evaporation temperature or the temperature of the fluid to be cooled is set in advance or a value set based on the outside air temperature (that is, the outside air temperature and the compression temperature). When the temperature is lower than the temperature value set based on the load of the refrigerating apparatus, the refrigerating capacity of the absorption refrigerating apparatus becomes an excessive state, and the refrigerant on the absorption refrigerating apparatus side is wasted. Become.

  On the other hand, when the outside air temperature rises or when the load of the compression refrigeration apparatus increases, the refrigerant temperature at the condenser outlet of the compression refrigeration apparatus rises, so the evaporation temperature of the absorption refrigeration apparatus or the evaporator When the temperature of the fluid to be cooled at the outlet of the refrigerant also rises and the evaporating temperature or the temperature of the fluid to be cooled rises above a preset value or a value set based on the outside air temperature, Since the refrigeration capacity becomes insufficient, it is necessary to increase the refrigeration capacity rapidly by increasing the supercooling temperature or the supercooling flow rate of the solution flowing into the absorber and at the same time increasing the refrigerant flow rate to the evaporator.

  Therefore, in order to improve the efficiency of the compression refrigeration system and reduce the running cost without installing a large capacity exhaust heat driven absorption refrigeration system, respond to changes in the operating conditions on the compression refrigeration system side. Therefore, it is necessary to control the refrigeration capacity of the absorption refrigeration apparatus.

  In this case, the control of the refrigeration capacity of the absorption refrigeration apparatus is performed by detecting the operating conditions on the compression refrigeration apparatus side, for example, the outside air temperature and the refrigerant temperature (condensation temperature) on the outlet side of the condenser of the compression refrigeration apparatus, It is conceivable to use this to calculate the refrigeration capacity of the absorption refrigeration system (the refrigeration capacity required for the absorption refrigeration system) and control based on this, but according to such a control method, the absorption refrigeration system In addition to the conditions on the apparatus side, it is necessary to always detect the conditions on the compression refrigeration apparatus side, which complicates the control system and causes a cost increase. In particular, for example, a plurality of refrigeration systems combining an absorption refrigeration system and a compression refrigeration system exist in the same management area, and the refrigeration capacity of the absorption refrigeration system in each of these refrigeration systems is individually set on the compression refrigeration system side. When the control is performed in accordance with the operating conditions, the control system becomes more complicated, requires a lot of management costs, and further increases the cost.

  Accordingly, the present invention relates to an absorption refrigeration apparatus driven by exhaust heat of the engine, wherein the refrigeration capacity of the absorption refrigeration apparatus is set to the operating conditions on the cold heat utilization side equipment side that uses the cold generated by the absorption refrigeration apparatus. By controlling without relying on it, the efficiency of the cold energy utilization side device is improved, and the initial cost and running cost of the entire refrigeration system are reduced.

  In order to realize such control, in this embodiment, the refrigerant absorption capacity of the absorber is improved by changing the temperature of the supercooled solution flowing into the absorber using the characteristics of the indirect air-cooled absorption type. The refrigeration capacity of the absorption refrigeration apparatus is controlled by increasing and decreasing, and under such a configuration, the temperature of the fluid to be cooled at the outlet of the evaporator 3 is equal to or lower than a set temperature set based on a set temperature or an outside air temperature. In this case, the temperature of the supercooled solution flowing into the absorber 4 is changed to control to reduce the refrigerant absorption capacity of the absorber 4, and at the same time, the refrigerant pump 13 is stopped or circulated. The refrigerant flow rate is decreased to stop the refrigerant flow into the evaporator 3 or to reduce the refrigerant flow amount, thereby reducing the refrigeration capacity of the absorption refrigeration apparatus Z.

  When the temperature becomes equal to or higher than the set temperature, the temperature of the supercooled solution flowing into the absorber 4 is changed to increase the refrigerant absorption capacity of the absorber 4, and at the same time, the refrigerant pump 13 Is controlled to increase the refrigeration capacity of the absorption refrigeration apparatus Z by increasing the flow rate of refrigerant circulating or increasing the flow rate of refrigerant into the evaporator 3 or increasing the amount of refrigerant flowing into the evaporator 3. .

  Specifically, a temperature sensor 18 is provided on the outlet side of the evaporator 3 to detect the refrigerant temperature at the outlet of the evaporator 3 (that is, the refrigerant subcooling temperature on the compression refrigeration apparatus X side). However, when it is based on the outside air temperature, an outside air temperature sensor 20 is provided to detect the outside air temperature at the same time.

  Here, the set temperature is set as the outlet temperature in the evaporator 3 from the condensation temperature in the condenser 23 of the compression refrigeration apparatus X and the temperature that can be supercooled by the refrigeration capacity of the absorption refrigeration apparatus Z. When the set temperature is set based on the outside air temperature detected by the outside air temperature sensor 20, the condensation of the compression refrigeration apparatus X corresponding to the outside air temperature is controlled. A condensation temperature in the evaporator 23 is predicted, a predetermined supercooling temperature is calculated from the predicted condensation temperature and the refrigerating capacity at the outside air temperature of the absorption refrigeration apparatus Z, and an evaporator outlet temperature in the evaporator 3 is obtained. This is set as a set temperature for controlling the refrigeration capacity of the absorption refrigeration apparatus Z. However, the setting lower limit value of the outlet temperature of the evaporator 3 is a value in consideration of freezing of the refrigerant.

  Then, the outlet temperature of the evaporator 3 detected by the temperature sensor 18 is compared with the set temperature. When the outlet temperature of the evaporator 3 is lower than the set temperature, the refrigerating capacity of the absorption refrigeration apparatus Z is excessive. On the contrary, if the outlet temperature of the evaporator 3 is higher than the set temperature, the refrigerating capacity of the absorption refrigeration apparatus Z is insufficient and the required supercooling temperature cannot be secured. The control to increase is performed.

  Specific control of the refrigeration capacity of the absorption refrigeration apparatus Z is as follows.

  That is, when the temperature of the refrigerant at the outlet of the evaporator 3 (the refrigerant temperature of the compression refrigeration apparatus X) becomes equal to or lower than the set temperature set based on the set temperature or the outside air temperature, the air-cooled supercooler 6 is turned on. Decreasing the refrigerant absorption capacity of the absorber 4 by changing the temperature of the supercooled solution circulating in the air-cooled supercooler 6 by starting and stopping the fan 7 provided or by increasing or decreasing the air volume of the fan 7 At the same time, the refrigerant flow into the evaporator 3 is stopped or the refrigerant flow amount is decreased to reduce the refrigerating capacity of the absorption refrigeration apparatus Z. As a result, the refrigeration capacity of the absorption refrigeration apparatus Z is made to correspond as much as possible to the degree of supercooling of the compression refrigeration apparatus X while being in a control mode that does not take into account the conditions on the compression refrigeration apparatus X side. be able to. In this case, surplus refrigerant in the refrigerant reservoir 17 below the evaporator 3 flows into the diluted solution reservoir 16 below the absorber 4 and is mixed with the diluted solution in the diluted solution reservoir 16, thereby Changes in the concentration of the solution are suppressed.

  On the other hand, when the temperature is equal to or higher than the set temperature, the temperature of the supercooled solution flowing into the absorber 4 is changed to reduce the refrigerant absorption capacity of the absorber 4, and at the same time, the refrigerant pump 13 By increasing the flow rate of refrigerant circulating or increasing the refrigeration capacity of the absorption refrigeration apparatus Z, the supercooling temperature of the refrigerant of the compression refrigeration apparatus X increases, and the compression type The performance of the refrigeration apparatus X is improved as compared with the normal state where the above control is not performed.

  As a synergistic effect as described above, the efficiency of the compression refrigeration apparatus can be improved and the refrigeration system in spite of controlling the refrigeration capacity of the absorption refrigeration apparatus without being based on the operating conditions on the compression refrigeration apparatus X side. The overall initial cost and running cost can be reduced at the same time.

  In this embodiment, the temperature when the refrigerant pump 13 is stopped or circulated and the refrigerant flow rate is decreased, and the temperature when the refrigerant pump 13 is operated or circulated is increased. Although it is set as the same temperature, this invention is not limited to this, It can also be set as a different temperature. For example, when the temperature when the refrigerant pump 13 is stopped or the flow rate of the circulating refrigerant is decreased and the temperature when the refrigerant pump 13 is operated or the circulating flow rate of the refrigerant is increased are different from each other, For example, when the temperature when the refrigerant pump 13 is stopped or when the circulating refrigerant flow rate is decreased is set lower than the temperature when the refrigerant pump 13 is operated or the circulating refrigerant flow rate is increased First, the increase control of the refrigerating capacity is started earlier, and a quick increase of the refrigerating capacity is realized.

IV: Fourth Embodiment FIG. 4 shows a refrigeration system according to a fourth embodiment of the present invention. This refrigeration system has the same basic configuration as the refrigeration system according to the third embodiment, and is configured by combining an exhaust heat driven absorption refrigeration apparatus Z and a compression refrigeration apparatus X.

  The difference between the refrigeration system according to this embodiment and the refrigeration system according to the third embodiment is that, in the third embodiment, in the absorption refrigeration apparatus Z, the liquid refrigerant from the condenser 2 is changed. The entire amount is allowed to flow into the refrigerant reservoir 17 provided in the lower part of the evaporator 3 through the pipe 52, whereas in the fourth embodiment, in the middle of the pipe 52 in the fourth embodiment. The refrigerant tank 14 and the refrigerant electromagnetic valve 10 are provided, and the refrigerant electromagnetic valve 10 is closed so that the refrigerant can be stored in the refrigerant tank 14, and the refrigerant electromagnetic valve 10 is opened to open the refrigerant tank. The refrigerant stored in 14 flows into the refrigerant reservoir 17 side.

  With this configuration, for example, when the absorption refrigeration apparatus Z is in operation and the refrigerant pump 13 is stopped, that is, liquid refrigerant is generated in the condenser 2, When the refrigerating capacity required for the refrigerating apparatus Z is low and the refrigerant pump 13 is stopped and the refrigerant is not supplied to the evaporator 3, the liquid refrigerant from the condenser 2 is in an excess state. Therefore, by storing this surplus refrigerant in the refrigerant tank 14, the amount of ineffective refrigerant can be reduced as much as possible, and the exhaust heat of the engine can be used effectively.

  On the other hand, when the amount of refrigerant in the refrigerant reservoir 17 below the evaporator 3 decreases, that is, an increase in the refrigerating capacity of the absorption refrigeration apparatus Z is required, the refrigerant pump 13 is operated accordingly, When the amount of refrigerant in the refrigerant reservoir 17 decreases and refrigerant replenishment is required, the refrigerant in the refrigerant tank 14 is supplemented in the refrigerant reservoir, so that such refrigerant replenishment is performed. Compared to the case where there is no refrigerant, the amount of refrigerant circulating to the evaporator 3 is further increased, and the response to the increase in the refrigerating capacity of the absorption refrigeration apparatus Z is improved. This makes it easy to control the capacity to correspond to changes in the operating conditions of the compression refrigeration apparatus X.

  In addition, since the structure and the effect other than the above are the same as in the case of the third embodiment, the same reference numerals are given to the respective constituent members in FIG. 4 corresponding to the respective constituent members in FIG. Thus, the corresponding explanation in the third embodiment is used, and the explanation here is omitted.

V: Fifth Embodiment FIG. 5 shows a refrigeration system according to a fifth embodiment of the present invention. This refrigeration system also has the same basic configuration as the refrigeration system according to the third embodiment, and is configured by combining an exhaust heat driven absorption refrigeration apparatus Z and a compression refrigeration apparatus X.

  The difference between the refrigeration system according to this embodiment and the refrigeration system according to the third embodiment is that, in the third embodiment, the absorption refrigeration apparatus Z has a refrigerant absorption capacity of the absorber 4. In contrast to the control performed by adjusting the temperature of the supercooled solution circulating in the air-cooled supercooler 6, in the fifth embodiment, the control of the refrigerant absorption capacity of the absorber 4 is performed as follows: This is a point that is performed by adjusting the flow rate of the supercooled solution circulating through the air-cooled supercooler 6.

  That is, in the fifth embodiment, a flow rate adjusting valve 11 is provided on the inlet side of the air-cooled supercooler 6 or a flow rate adjusting valve 12 is provided on the outlet side, and the flow rate adjusting valve 11 or the flow rate adjusting valve 12 The flow rate of the supercooled solution flowing into the absorber 4 is changed. Further, the flow rate of the supercooled solution flowing into the absorber 4 is changed by increasing or decreasing the flow rate of the solution pump 9.

  In this way, the absorption of the supercooled solution flowing into the absorber 4 is controlled by increasing / decreasing the flow rate by adjusting the opening of each flow rate adjusting valve 11 or flow rate adjusting valve 12 and adjusting the flow rate of the solution pump 9. The refrigerant absorption capacity of the container 4, and thus the refrigeration capacity of the absorption refrigeration apparatus Z can be performed very easily and quickly, and as a result, the capacity control range of the absorption refrigeration apparatus Z is reduced to the minimum capacity. As a result, the capacity of the compression refrigeration apparatus X can be utilized to the limit.

  Since the structure and the effect other than the above are the same as in the case of the third embodiment, the same reference numerals are given to the respective structural members in FIG. 5 corresponding to the respective structural members in FIG. The corresponding explanation in the third embodiment is used, and the explanation here is omitted.

  In each of the above embodiments, the case where the compression refrigeration apparatus X is employed as an example of the cold heat utilization side equipment utilizing the cold generated on the absorption refrigeration apparatus Z side is shown. It is not limited to the device X.

1 is a system diagram of an absorption refrigeration apparatus according to a first embodiment of the present invention. It is a system diagram of an absorption refrigeration apparatus according to a second embodiment of the present invention. It is a system diagram of the absorption refrigeration apparatus which concerns on 3rd Embodiment of this invention. It is a system diagram of an absorption refrigeration apparatus according to a fourth embodiment of the present invention. FIG. 10 is a system diagram of an absorption refrigeration apparatus according to a fifth embodiment of the present invention.

Explanation of symbols

1 ·· Generator 2 ·· Condenser 3 ·· Evaporator 4 ··· Absorber 5 ·· Solution heat exchanger 6 ·· Air-cooled supercooler 7 ·· Fan 8 ·· Fan 9 ·· Solution pump 10 ··· Refrigerant solenoid valve 11 .. Flow rate adjustment valve 12 .. Flow rate adjustment valve 14 .. Refrigerant tank 14a .. Weir 15 .. Housing 16 .. Diluted solution reservoir 17 .. Refrigerant reservoir 18 .. Temperature sensor 20. 21 ・ ・ Compressor 22 ・ ・ Evaporator 23 ・ ・ Condenser 24 ・ ・ Expansion valve 25 ・ ・ Four-way valve 26 ・ ・ Engine 30 ・ ・ Controller X ・ ・ Compression refrigeration equipment (cold heat utilization side equipment)
Z .. Absorption refrigeration equipment

Claims (18)

A generator that operates in response to engine exhaust heat, a condenser, an evaporator that temporarily evaporates refrigerant, a falling liquid film type absorber, and air cooling that supercools the absorbing solution entering the absorber An exhaust heat-driven absorption refrigeration apparatus equipped with a supercooler,
While sequentially providing a refrigerant tank and a refrigerant solenoid valve in the middle of the pipe from the condenser to the evaporator,
By changing the temperature of the supercooling solution flowing into the absorber and / or the flow rate of the supercooling solution, the capacity of the absorber is increased or decreased to control the refrigeration capacity of the absorption refrigeration apparatus,
The temperature of the supercooled solution flowing into the absorber and / or the supercooled solution when the temperature of the fluid to be cooled at the outlet of the evaporator is equal to or lower than the set temperature set based on the set temperature or the outside air temperature. In order to reduce the refrigerant absorption capacity of the absorption refrigeration system by closing the refrigerant electromagnetic valve and reducing the amount of refrigerant flowing into the evaporator. While storing the refrigerant from the condenser in the refrigerant tank,
When the temperature is equal to or higher than the set temperature, the temperature of the supercooled solution flowing into the absorber and / or the flow rate of the supercooled solution is changed to increase the refrigerant absorption capacity of the absorber, An absorption type wherein control is performed to increase the refrigeration capacity of the absorption refrigeration system by opening the refrigerant solenoid valve and causing the refrigerant stored in the refrigerant tank to flow into the evaporator to increase the flow rate of the refrigerant. Refrigeration equipment.   The temperature when the refrigerant solenoid valve is changed from open to closed and the temperature when the refrigerant solenoid valve is changed from closed to open are set to the same temperature or different temperatures, and the temperature is set based on a preset set value or an outside air temperature. The absorption refrigeration apparatus according to claim 1, wherein   The refrigerant solenoid valve is opened or closed by comparing the detected value of the evaporation temperature of the evaporator with a preset value or a set value set based on the outside air temperature, or to be cooled at the outlet and inlet of the evaporator. 3. The absorption refrigeration apparatus according to claim 1, wherein the detection is performed by comparing a detected value of the temperature difference of the fluid with a preset set value or a set value set based on an outside air temperature.   A dam is provided in the refrigerant tank, the refrigerant is allowed to flow into the evaporator through the weir, and the refrigerant flow rate to the evaporator is increased or decreased by opening or closing the refrigerant electromagnetic valve. The absorption refrigeration apparatus according to claim 1, 2 or 3.   The surplus refrigerant after the refrigerant tank is full is allowed to flow into the lower part of the evaporator or directly into the dilute solution reservoir of the absorber. Absorption refrigeration equipment. The operation / stop of the absorption refrigeration system shall be controlled by the solution temperature of the generator,
Even if the engine is in a stopped state, if the solution temperature is equal to or higher than a predetermined temperature and the refrigerant storage capacity of the refrigerant tank is sufficient, the refrigerant electromagnetic valve is closed and the absorption tank is used until the refrigerant tank is full. Operate the refrigeration unit or operate only the solution pump,
If the solution temperature of the generator is equal to or lower than the predetermined temperature, the operation of the absorption refrigeration apparatus or the operation of the solution pump is stopped even if the refrigerant storage capacity of the refrigerant tank has a margin. 6. The absorption refrigeration apparatus according to claim 1, 2, 3, 4 or 5.   Control of increase / decrease in the flow rate of the refrigerant flowing from the refrigerant tank to the evaporator is performed by opening / closing a refrigerant flow control valve provided in the middle of a pipe from the refrigerant tank to the evaporator, or overflowing a weir provided in the refrigerant tank. The refrigerant flowing into the evaporator is performed by opening and closing a refrigerant flow rate control valve provided in the middle of a pipe from the upstream portion of the weir to the evaporator. The absorption refrigeration apparatus according to 2, 3, 4, 5 or 6.   The refrigeration capacity is controlled by changing the temperature of the supercooled solution flowing into the absorber according to the start / stop of a fan provided in the air-cooled supercooler or the increase / decrease of the air volume. The absorption refrigeration apparatus according to 3, 4, 5, 6 or 7.   The refrigeration capacity is controlled by changing the flow rate of the supercooled solution flowing into the absorber by a flow rate adjusting valve provided on the inlet side or the outlet side of the air-cooled supercooler. The air-cooled absorption refrigeration apparatus according to 3, 4, 5, 6 or 7.   A solution pump that sucks and discharges a mixed solution of a dilute solution from the absorber that has absorbed refrigerant vapor and a concentrated solution that generates refrigerant vapor in the generator and whose temperature is reduced by heat exchange in the solution heat exchanger. The absorption refrigeration apparatus according to claim 1, wherein the refrigeration capacity is controlled by increasing or decreasing the flow rate of the refrigeration. A generator that operates in response to the exhaust heat of the engine, a condenser, an evaporator that circulates and evaporates the refrigerant accumulated in the refrigerant reservoir in the lower part by means of a refrigerant pump, and a falling liquid film type absorber , An exhaust heat driven absorption refrigeration apparatus comprising an air-cooled supercooler for supercooling the absorbent solution entering the absorber,
While the capacity of the refrigerant reservoir of the evaporator is set to a constant amount, excess refrigerant flows into the dilute solution reservoir below the absorber,
By changing the temperature of the supercooling solution flowing into the absorber and / or the flow rate of the supercooling solution, the capacity of the absorber is increased or decreased to control the refrigeration capacity of the absorption refrigeration apparatus,
The temperature of the supercooled solution flowing into the absorber and / or the supercooled solution when the temperature of the fluid to be cooled at the outlet of the evaporator is equal to or lower than the set temperature set based on the set temperature or the outside air temperature. The flow rate of the refrigerant is changed to reduce the refrigerant absorption capacity of the absorber, and at the same time, the refrigerant pump is stopped or the circulating refrigerant flow rate is reduced to stop the flow of the refrigerant into the evaporator. While reducing the refrigeration capacity of the absorption refrigeration system by reducing the inflow of refrigerant or
When the temperature is equal to or higher than the set temperature, control is performed to increase the refrigerant absorption capacity of the absorber by changing the temperature of the supercooled solution flowing into the absorber and / or the flow rate of the supercooled solution. At the same time, the control for increasing the refrigeration capacity of the absorption refrigeration apparatus by increasing the flow rate of the refrigerant operating or circulating the refrigerant pump and causing the refrigerant to flow into the evaporator or increasing the amount of refrigerant flowing in. An absorption refrigeration apparatus characterized in that   The temperature for stopping the refrigerant pump or decreasing the circulating refrigerant flow rate and the temperature for operating the refrigerant pump or increasing the circulating refrigerant flow rate are the same or different temperatures. The absorption refrigeration apparatus according to claim 11, wherein the temperature is set to a preset value or a value set based on an outside air temperature.   The refrigerant pump stop control or circulating refrigerant flow decrease control, and the refrigerant pump operation or circulating refrigerant flow increase control are performed with a detection value of the evaporator evaporation temperature and a preset set value or Contrast with the set value set based on the outside air temperature, or the detected value of the temperature difference of the fluid to be cooled at the outlet and the inlet of the evaporator and the set value set based on the preset set value or the outside air temperature The absorption refrigeration apparatus according to claim 11, wherein the absorption refrigeration apparatus is performed in comparison with the above. The operation / stop of the absorption refrigeration system shall be controlled by the solution temperature of the generator,
Even when the engine is stopped, if the solution temperature is equal to or higher than a predetermined temperature and the refrigerant storage capacity of the refrigerant pool of the evaporator is sufficient, the refrigerant solenoid valve is closed and the refrigerant pool is full. Operate the absorption refrigeration system until it becomes, or operate only the solution pump,
The operation of the absorption refrigeration apparatus or the operation of the solution pump is stopped even if there is a margin in the refrigerant storage capacity of the refrigerant reservoir when the solution temperature of the generator is equal to or lower than the predetermined temperature. Item 14. The absorption refrigeration apparatus according to item 11, 22 or 13.   A refrigerant tank and a refrigerant electromagnetic valve are sequentially provided in the pipeline from the condenser to the evaporator, and the refrigerant electromagnetic valve is closed when the absorption refrigeration apparatus is in operation and the refrigerant pump is stopped. 12. The refrigerant is stored in the refrigerant tank, while the refrigerant electromagnetic valve is opened to replenish the refrigerant in the refrigerant tank when the amount of refrigerant in the refrigerant reservoir below the evaporator decreases. , 12, 13 or 14. Absorption refrigeration apparatus.   13. The refrigeration capacity is controlled by changing the temperature of the supercooled solution flowing into the absorber according to the start / stop of a fan provided in the air-cooled supercooler or the increase / decrease of the air volume. The absorption refrigeration apparatus of Claim 13, 14, or 15.   The refrigeration capacity is controlled by changing the flow rate of the supercooled solution flowing into the absorber by a flow rate adjusting valve provided on the inlet side or the outlet side of the air-cooled supercooler. The air-cooled absorption refrigeration apparatus according to 13, 14 or 15.   A solution pump that sucks and discharges a mixed solution of a dilute solution from the absorber that has absorbed refrigerant vapor and a concentrated solution that generates refrigerant vapor in the generator and whose temperature is reduced by heat exchange in the solution heat exchanger. The absorption refrigeration apparatus according to claim 11, wherein the refrigeration capacity is controlled by increasing or decreasing the flow rate of the refrigeration.

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