JP6180152B2 - Absorption refrigerator - Google Patents

Description

  The present invention relates to an absorption refrigeration machine, and more specifically, enables further miniaturization of an exhaust heat recovery unit installed in the system to save energy, reduces the heat transfer area in the exhaust heat recovery unit, and reduces the absorption liquid. The present invention relates to an absorption refrigerator that suppresses the occurrence of drift in a heat recovery unit and avoids crystallization of an absorbing solution by local heating.

  In the absorption refrigerator, cold water and hot water can be taken out by changing the concentration of an absorption liquid circulating in the apparatus, for example, a lithium bromide aqueous solution. As shown in FIG. 36, the main structure of the double effect machine overlaps with the triple effect machine, as shown in FIG. 36, the evaporator 31 and the absorber 5, which form a container almost close to a vacuum, and the low temperature regenerator 2 of a container having a slightly higher pressure than those. And a condenser 3, for example, a high temperature regenerator 8 that forms a container having an internal pressure close to atmospheric pressure to obtain heat energy by burning city gas or the like with a burner. In this specification, in accordance with the description of JISB8622, the absorption refrigerator is "... an absorption refrigerator, an absorption chiller / heater and an absorption heat pump that constitutes a refrigeration cycle and cools or heats water ... The term “absorption chiller / heater” or “absorption heat pump” is not displayed.

  In the evaporator 31, the latent heat of evaporation is taken away by the refrigerant liquid 31w that has flowed down to the outer surface of the evaporator pipe 31p under high vacuum, and the cold water 32 flowing through the evaporator pipe is cooled. In the absorber 5, the refrigerant vapor 31s generated in the evaporator 31 is cooled by the cooling water 33w flowing through the absorber pipe 5p, so that it is absorbed by the absorbing liquid and the interior of the container is kept at a high vacuum. This figure is drawn with a triple effect machine, but for the time being, it is assumed that it is a double effect machine with a one-dot chain line added, and the explanation will be continued. In the low temperature regenerator 2, the refrigerant vapor 34 generated in the high temperature regenerator 8 is caused to flow to the low temperature regenerator pipe 2p, and the absorption liquid 35m is heated and concentrated by the latent heat to generate refrigerant vapor 36s. In the high temperature regenerator 8, the absorbing liquid 35n is heated and concentrated to generate the refrigerant vapor 34. In the condenser 3, the refrigerant vapor 36s evaporated in the low temperature regenerator 2 is cooled by the cooling water 33w flowing through the condenser pipe 3p, and is condensed and liquefied. The cooling water 33w that has been pumped by a cooling water pump (not shown) and circulated through the condenser pipe 3p via the absorber pipe 5p is circulated after being cooled by a cooling tower (not shown).

  In such an absorption refrigerator, not only cooling operation but also a cooling / heating switching valve (not shown) is opened and the refrigerant vapor 34 evaporated in the high temperature regenerator 8 is sent to the evaporator 31, and the refrigerant vapor 36 s is also generated in the low temperature regenerator 2. If it does, it will also send and heating operation can also be performed if the warm water which flows through the evaporator pipe | tube 31p is heated. In both cases of cooling and heating, in controlling the temperature of cold water or hot water, the heating amount in the high-temperature regenerator 8 is generally adjusted by a fuel control valve (not shown) based on the cold / hot water outlet temperature t. In addition, while warm water is produced | generated by the refrigerant | coolant vapor | steam which generate | occur | produced in the system, absorption liquid takes the same density | concentration change as the time of cooling, and circulates along the substantially equivalent path | route.

  In such an absorption refrigerator, energy saving is promoted based on the principle of double effect or triple effect, but in order to improve the heat exchange efficiency in the system, as shown in FIG. The heat exchanger 4, the intermediate temperature heat exchanger 22, and the high temperature heat exchanger 9 are installed. This high temperature heat exchanger preheats the absorbing liquid 35n toward the high temperature regenerator 8, and the high temperature absorbing liquid 8b derived from the high temperature regenerator 8 is used as the heat source.

  The intermediate temperature heat exchanger 22 preheats the absorption liquid 37a toward the intermediate temperature regenerator 21, and in the illustrated example, the absorption liquid 37b derived from the intermediate temperature regenerator 21 and the absorption liquid 8b exiting the high temperature heat exchanger 9 are low in temperature. It is used as a heat source on the way to the absorber 5 through the heat exchanger 4. The low temperature heat exchanger 4 preheats the absorption liquid 5a toward the low temperature regenerator 2, and in the illustrated example, the absorption liquid 2n derived from the low temperature regenerator 2 and the absorption liquid derived from the intermediate temperature heat exchanger 22 are used. The absorbing liquid 22a that has passed through the intermediate temperature heat exchanger 22 is used as a heat source while being returned to the absorber 5.

  By the way, it is often possible to further reduce the heating load in the regenerator by further heating the absorption liquid supplied to the intermediate temperature regenerator 21 and the high temperature regenerator 8. FIG. 36 shows a triple effect machine proposed in Japanese Patent Laid-Open No. 2003-214720, in which an exhaust gas heat exchanger 38 is provided in parallel with the intermediate temperature heat exchanger 22. In addition, although 39 added with the dashed-dotted line in the figure is also an exhaust gas heat exchanger, it replaces with the exhaust gas heat exchanger 38, and this is parallel with the high temperature heat exchanger 9. FIG. Such an example is disclosed in Japanese Patent Application Laid-Open No. 2004-125314.

  In the cycle flow as shown in FIG. 36, if a large amount of absorbing liquid (diluted liquid) is flowed to the exhaust gas heat exchanger as the exhaust heat recovery unit during the cooling operation, the temperature of the diluted liquid from the exhaust gas heat exchanger decreases, The amount of heat exchanged in the intermediate temperature heat exchanger or the high temperature heat exchanger is also reduced, so that the amount of heat recovered from the exhaust gas cannot be efficiently reflected in the performance improvement. Therefore, the exhaust gas temperature must be lowered in order to reduce the amount of liquid absorbed into the exhaust gas heat exchanger and increase the amount of heat recovered from the exhaust gas. For this reason, exhaust gas heat exchangers are inevitably large, and the use of high fin tubes or plate fin tubes contributes to the improvement of heat transfer efficiency. It contributes to the rising production costs. Furthermore, an increase in the size of the exhaust gas heat recovery device causes a drift of the solution in the vessel, and increases the risk of crystallization of the solution due to local heating.

  By the way, absorption refrigerators are often used in partial load operation. During this partial load operation, the temperature of the solution, which is the low temperature side fluid of the exhaust gas heat exchanger, is lowered along with the load factor, and as a result, the temperature is lowered to a temperature at which the exhaust gas is condensed. From the viewpoint of corrosion due to exhaust gas drain water, it is preferable to use stainless steel for the heat transfer tube. However, if stainless steel is used, there is a concern of stress corrosion cracking, and it is necessary to select a material with high corrosion resistance. Will increase costs.

  By the way, it is known that if the absorption pump is controlled by an inverter and a flow rate adjusting mechanism is added to the pipe that flows to the low-temperature regenerator, fine circulation control is possible, contributing to improved partial load efficiency. ing. However, the pipe to the medium-temperature regenerator or high-temperature regenerator side has a medium-temperature heat exchanger and exhaust gas heat exchanger in parallel, or a high-temperature heat exchanger and exhaust gas heat exchanger in parallel and branched. A two-line distribution form is assumed. Therefore, in the pipe flowing to the medium temperature regenerator or the high temperature regenerator, the distribution ratio between the exhaust gas heat exchanger and the medium temperature heat exchanger or the high temperature heat exchanger must be a distribution ratio according to the difference in the pipe resistance. . Note that, during the partial load operation, the circulation amount of the absorbing liquid decreases, so the flow rate in the exhaust gas heat exchanger also decreases, and the heat transfer performance tends to be remarkably reduced. As described above, the parallel arrangement further reduces the amount of feed to the exhaust gas heat exchanger and further reduces the flow velocity, resulting in a further decrease in heat transfer performance.

  Under such circumstances, if the balance of the circulation rate is lost due to pressure fluctuations and temperature fluctuations caused by sudden fluctuations in the coolant temperature or changes in the combustion amount, the solution starts to flash due to this effect, and the circulation rate hunts or becomes unstable. It tends to be a natural flow. In particular, during the heating operation in which the solution concentration is low and the in-cylinder pressure is low, the saturation temperature of the solution is low, and in the high-temperature regenerator line, both the high-temperature heat exchanger and the exhaust gas heat exchanger tend to flash.

JP 2003-214720 A JP 2004-125314 A

  The present invention has been made in view of the above-mentioned several problems, and its purpose is to make it difficult to cause a drift of the solution in the container in order to reduce the size of the exhaust heat recovery device in order to reduce the heat transfer area. Reduces the crystallization tendency of the solution due to heating, avoids drain water corrosion due to dew condensation of exhaust gas during partial load operation as much as possible, also reduces the circulation rate during partial load operation and branches by parallel pipes The heat transfer performance in the exhaust gas heat exchanger due to the flow can be suppressed, and the absorption liquid distribution ratio to the medium temperature heat exchanger and exhaust heat recovery unit, and the high temperature heat exchanger and exhaust heat recovery device To achieve a flow that is not controlled by pipe resistance, and to prevent the flushing of the solution and avoid the hunting of the fluid even if the circulation amount is unbalanced due to pressure fluctuation or temperature fluctuation in each regenerator line. It is to provide an absorption chiller an attempt is made to realize the Rukoto.

The present invention includes an absorber, a low temperature regenerator, a high temperature regenerator, a condenser, an evaporator, a low temperature heat exchanger that heats the absorption liquid from the absorber before sending it to the low temperature regenerator, Equipped with a high-temperature heat exchanger that heats and an exhaust heat recovery unit that heats the absorbing liquid using exhaust heat, and condensates the refrigerant vapor generated by heating the absorbing liquid to the evaporator pipe in the evaporator In the cooling operation in which cold water is obtained in the evaporator tube by vaporizing the condensate on the heat transfer surface, the absorption liquid generated by generating the refrigerant vapor and the high temperature heat exchanger are directed to the high temperature regenerator. The double-effect absorption chiller that absorbs the refrigerant vapor generated when cold water is obtained after passing through heat exchange with a low-temperature heat exchanger and places the absorber and the evaporator connected to it in a high vacuum Applies to For example, referring to FIG. 2, the feature is that the absorption liquid led out from the absorber 5 is in a pipe line toward the low temperature heat exchanger 4, and the branch pipe 6 is upstream of the low temperature heat exchanger 4. Branched. Using the retained heat of the refrigerant drain that is generated in the low temperature regenerator 2 and goes to the condenser 3, the low temperature regenerator 2 is heated by heating the absorption liquid that follows the branch pipe 6 among the absorption liquid that has been directed to the low temperature heat exchanger 4. A refrigerant drain heat exchanger 1 for a low-temperature regenerator that is fed to is provided. The liquid amount excluding the amount to be circulated as a heating source in the low temperature heat exchanger 4 of the absorbent solution delivered from the low-temperature regenerator 2 to the exhaust heat recovery device 7 is fed, its waste heat The recovery unit 7 is installed in the upstream line of the high-temperature heat exchanger 9 in which the absorption liquid flows toward the high-temperature regenerator 8, and is connected in series with the high-temperature heat exchanger 9.

For example, as shown in FIG. 7 , also in the triple effect absorption refrigerator, the absorption liquid led out from the absorber 5 is in a pipe line toward the low temperature heat exchanger 4, and the branch pipe 6 is upstream of the low temperature heat exchanger 4. Is branched. A refrigerant drain heat exchanger 1 for a low-temperature regenerator that heats the absorption liquid that is generated in the low-temperature regenerator 2 and that flows to the condenser 3 and heats the absorption liquid that follows the branch pipe 6 and sends it to the low-temperature regenerator 2. Provided. Then, the exhaust heat recovery device 15 is liquid volume delivered excluding the amount sent to the low temperature regenerator 2 of the absorbing liquid that has circulated the low temperature heat exchanger 4, exhaust heat recovery device 15 is absorbing liquid It is installed in the middle temperature upstream conduit in the flow towards the regenerator 21 heat exchanger 22, the temperature heat exchanger 22 in the their being connected in series.

In addition triple effect absorption refrigerating machine, for example, as shown in FIG. 4, the liquid amount excluding the amount that is sent to the low-temperature regenerator 2 of the absorbing liquid that has circulated cold heat exchanger 4 in the exhaust heat recovery device 7 is liquid volume delivered excluding the amount sent from the medium-temperature heat exchanger 22 to the intermediate temperature regenerator 21 further immediately before the exhaust heat recovery device 7 flow absorbing liquid toward the high-temperature regenerator 8 is a high temperature heat exchanger 9 Is connected to the high-temperature heat exchanger 9 in series.

  The high temperature regenerator 8 is a gas-fired type, and the exhaust heat recovery unit is an exhaust gas heat exchanger 7 through which the high temperature regenerator 8 exhaust gas is circulated.

  For example, as shown in FIG. 1 and FIG. 16, a pipe line that goes to the low-temperature regenerator 2 by mixing the absorption liquid flowing through the low-temperature heat exchanger 4 and the absorption liquid flowing through the low-temperature regenerator refrigerant drain heat exchanger 1. Alternatively, the system may be configured to include an external waste heat utilization heat exchanger 11 that introduces waste heat generated outside the system, heats the absorption liquid, and sends the absorption liquid to the low-temperature regenerator 2.

  According to the present invention, low-temperature regeneration is performed by heating the absorption liquid that follows the branch pipe provided upstream of the low-temperature heat exchanger by using the thermal energy of the refrigerant drain that is generated in the low-temperature regenerator and then goes to the condenser. Since the refrigerant drain heat exchanger for low-temperature regenerators to be sent to the regenerator is provided, the absorption liquid heated by the low-temperature regenerator and the absorption liquid heated by the refrigerant drain heat exchanger for low-temperature regenerators are sent to the low-temperature regenerator. can do. That is, since the refrigerant drain heat exchanger is provided, the solution temperature at the inlet of the low-temperature regenerator increases, and the amount of heat required for heating the absorption liquid in the low-temperature regenerator can be reduced accordingly. Since the heating source of the low-temperature regenerator is the refrigerant vapor from the high-temperature regenerator, the reduction in the amount of heating heat in the low-temperature regenerator reduces the burden of generating the refrigerant vapor in the high-temperature regenerator.

  Further, the heat transfer efficiency in the exhaust heat recovery device is remarkably improved by arranging the exhaust heat recovery device in front of the high temperature heat exchanger having a low temperature level and in series with the high temperature heat exchanger. In addition, the exhaust heat recovery unit having the same flow rate as the flow rate in the high-temperature heat exchanger increases the Reynolds number in the pipe and improves the heat transfer coefficient on the heat transfer surface. At least these two points work together to promote further downsizing of the exhaust heat recovery device. Special processing is required, and the number of expensive heat transfer tubes that require special materials and measures against corrosion are also reduced. This greatly reduces the manufacturing cost of the exhaust heat recovery unit.

  In order to reduce the heat transfer area, aiming at miniaturization of the exhaust heat recovery device, it is difficult to cause the drift of the solution in the vessel, and the possibility of liquid crystal deposition by local heating is reduced. Drain water corrosion based on dew condensation of exhaust gas during partial load operation can be avoided as much as possible. Furthermore, in the partial load state, a reduction in the heat transfer performance in the exhaust gas heat exchanger is prevented by reducing the amount of circulating fluid and avoiding the generation of branch flow. Since the absorption liquid distribution ratio to the high temperature heat exchanger and the exhaust heat recovery unit is not generated, a flow that is not controlled by the pipe resistance is achieved. Even if the balance is lost due to pressure fluctuations or temperature fluctuations, it is possible to prevent the solution from flushing and the occurrence of liquid quantity hunting.

In the high-temperature heat exchanger, a part of the mixed liquid of the absorbent flowing through the low-temperature heat exchanger and the absorbent flowing through the refrigerant drain heat exchanger for the low-temperature regenerator, that is, the amount sent to the low-temperature regenerator or liquid volume left so as to be fed, et al except, will be a part of the absorbing liquid which has flowed through only the low-temperature regenerator refrigerant drain heat exchanger is fed by mixed in the exhaust heat recovery device, The absorption liquid heating effect in the exhaust heat recovery device is improved, and the heat exchange load in the high temperature heat exchanger can be reduced. If the amount of circulating fluid or the liquid temperature from the high-temperature regenerator is suppressed, heating in the high-temperature regenerator can be suppressed and fuel consumption can be reduced.

Even in the triple effect absorption refrigerator of claim 2 or claim 3, it is possible to further reduce the size of the exhaust heat recovery unit installed in the system to save energy more than the double effect machine, and recover the exhaust heat. Reduction of the heat transfer area in the chamber and generation of drift in the exhaust heat recovery chamber of the absorption liquid are suppressed, and crystallization of the absorption liquid due to local heating is suppressed. Of course, as in the case of a double effect machine, the refrigerant drain heat exchanger for the low temperature regenerator can increase the solution temperature at the inlet of the low temperature regenerator, and the heating source of the low temperature regenerator is the refrigerant vapor that has passed from the high temperature regenerator through the medium temperature regenerator. Therefore, a reduction in the amount of heating heat in the low temperature regenerator reduces the burden of generating refrigerant vapor in the high temperature regenerator. In addition, since the logarithmic average temperature difference can be increased or the Reynolds number in the pipe can be improved, the heat transfer rate on the heat transfer surface can be improved, and the exhaust heat recovery device can be reduced in size and cost.

Exhaust heat recovery device is disposed on the upstream side pipe passage of the medium temperature heat exchanger, in a case which is connected in series with the medium-temperature heat exchanger, the miniaturization of exhaust heat recovery system in order to contemplate the reduction of heat transfer area In order to reduce the possibility of crystallization of the solution due to local heating, it is difficult to cause the drift of the solution in the vessel. Drain water corrosion based on dew condensation of exhaust gas during partial load operation can be avoided as much as possible. The absorption liquid distribution ratio to the intermediate temperature heat exchanger and the exhaust heat recovery unit is not generated, a flow that is not controlled by the pipe resistance can be achieved, and the hunting of the liquid amount can be avoided.

Exhaust heat recovery device is disposed on the upstream side pipe of the high temperature heat exchanger, even when it is connected in series with the high temperature heat exchanger, the miniaturization of exhaust heat recovery system in order to contemplate the reduction of heat transfer area In order to reduce the possibility of crystallization of the solution due to local heating, it is difficult to cause the drift of the solution in the vessel. Drain water corrosion based on dew condensation of exhaust gas during partial load operation can be avoided as much as possible. Absorption liquid distribution ratio between the high- temperature heat exchanger and the exhaust heat recovery unit is not generated, a flow that is not controlled by pipe resistance can be achieved, and liquid amount hunting can be avoided.

  If the high-temperature regenerator is a gas-fired type, the exhaust heat generated during combustion can be introduced into the exhaust heat recovery device, and the retained heat energy can be recovered and utilized.

  External waste that heats the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator by the waste heat generated outside the system, and sends the absorbed liquid to the low-temperature regenerator If the heat-utilizing heat exchanger is provided, the absorption liquid temperature can be supplied to the low-temperature regenerator in a state where the absorption liquid temperature is also increased by the external energy, and heating by the refrigerant drain in the low-temperature regenerator can be reduced. As a result, the generation load of the refrigerant vapor in the high-temperature regenerator is also reduced.

Cycle flow chart of a double effect absorption refrigerating machine provided with the high-temperature heat exchanger liquid amount excluding the amount that is sent to the low-temperature regenerator is fed out of the absorption liquid has flowed through the low temperature heat exchanger from the intake Osamuki . In the absorption refrigerator according to claim 1 of the present invention, the mixed liquid of the absorption liquid that has flowed from the absorber through the low-temperature heat exchanger and the absorption liquid that has flowed through the refrigerant drain heat exchanger for the low-temperature regenerator to the low-temperature regenerator. The cycle flow figure of the double effect absorption refrigerating machine which comprises the high temperature heat exchanger with which a part of absorption liquid sent and sent from a low-temperature regenerator is sent. Out of the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger from the absorber and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount of liquid excluding the amount sent to the low-temperature regenerator is delivered. A double-effect absorption chiller equipped with a high-temperature heat exchanger, and the exhaust gas heat exchanger is also supplied with a part of the absorption liquid flowing only through the refrigerant drain heat exchanger for low-temperature regenerators. Cycle flow diagram. Absorbed liquid that has passed through the low-temperature heat exchanger from the absorber is sent to the low-temperature regenerator after the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger from the absorber and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator. The cycle flow figure of the triple effect absorption refrigerating machine provided with the high temperature heat exchanger to which the liquid quantity except the quantity sent to the low temperature regenerator and the quantity sent to the medium temperature regenerator is fed. Triple effect absorption with a high-temperature heat exchanger to which the amount of liquid excluding the amount sent to the low-temperature regenerator and the amount sent to the medium-temperature regenerator out of the absorbent flowing through the low-temperature heat exchanger from the absorber Cycle flow diagram of a type refrigerator. The cycle flow figure of the triple effect absorption refrigerating machine which comprised the intermediate temperature heat exchanger to which the liquid quantity except the quantity sent to the low temperature regenerator is sent among the absorption liquid which distribute | circulated the low temperature heat exchanger from the absorber. Absorbed liquid that has passed through the low-temperature heat exchanger from the absorber is sent to the low-temperature regenerator after the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger from the absorber and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator. The cycle flow figure of the triple effect absorption refrigerating machine which comprised the intermediate temperature heat exchanger to which the liquid quantity except the quantity sent to the low-temperature regenerator is sent. From the absorber, a mixture of the absorption liquid that has passed through the low-temperature heat exchanger and the absorption liquid that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator is sent to the low-temperature regenerator and from a part of the absorption liquid that flows out of the low-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine which equipped with the high temperature heat exchanger with which the liquid quantity except the quantity sent to the intermediate temperature heat exchanger was sent. A mixture of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator is sent to the low-temperature regenerator, and part of the absorption liquid flowing out from the low-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine which comprises the intermediate temperature heat exchanger supplied. A mixture of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator is sent to the low-temperature regenerator, and part of the absorption liquid flowing out from the low-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine which comprises the intermediate temperature heat exchanger supplied. A mixture of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator is sent to the low-temperature regenerator, and part of the absorption liquid flowing out from the low-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine provided with the high temperature heat exchanger with which a part of absorption liquid sent out to an intermediate temperature regenerator and flowing out from an intermediate temperature regenerator is sent. Out of the mixed liquid of the absorption liquid that has flowed from the absorber through the low-temperature heat exchanger and the absorption liquid that has flowed through the refrigerant drain heat exchanger for the low-temperature regenerator, the liquid amount excluding the amount sent to the low-temperature regenerator goes to the medium-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine provided with the high temperature heat exchanger with which a part of absorption liquid which is sent out and flows out from an intermediate temperature regenerator is sent. Out of the mixed liquid of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount sent to the low-temperature regenerator and the amount sent to the medium-temperature regenerator It is equipped with a high-temperature heat exchanger to which the amount of liquid excluding the refrigerant is fed, and the exhaust gas heat exchanger is also fed with a part of the absorption liquid that has circulated only through the refrigerant drain heat exchanger for low-temperature regenerators. Fig. 3 is a cycle flow diagram of a triple effect absorption refrigerator. Out of the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger from the absorber and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount of liquid excluding the amount sent to the low-temperature regenerator is delivered. A triple-effect system that has an intermediate temperature heat exchanger, and the exhaust gas heat exchanger is fed to the intermediate temperature heat exchanger with a part of the absorbent flowing through only the refrigerant drain heat exchanger for the low temperature regenerator. Cycle flow diagram of absorption refrigerator. Out of the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger from the absorber and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount of liquid excluding the amount sent to the low-temperature regenerator is delivered. Triple effect absorption refrigeration machine equipped with an intermediate temperature heat exchanger, and the exhaust gas heat exchanger is also supplied with a part of the absorption liquid flowing only through the refrigerant drain heat exchanger for the low temperature regenerator Cycle flow diagram. Triple effect absorption with a high-temperature heat exchanger to which the amount of liquid excluding the amount sent to the low-temperature regenerator and the amount sent to the medium-temperature regenerator out of the absorbent flowing through the low-temperature heat exchanger from the absorber Cycle flow diagram of a type refrigerator. Triple effect absorption with a high-temperature heat exchanger to which the amount of liquid excluding the amount sent to the low-temperature regenerator and the amount sent to the medium-temperature regenerator out of the absorbent flowing through the low-temperature heat exchanger from the absorber Cycle flow diagram of a type refrigerator. Out of the mixed liquid of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount sent to the low-temperature regenerator and the amount sent to the medium-temperature regenerator It is equipped with a high-temperature heat exchanger to which the amount of liquid excluding the refrigerant is fed, and the exhaust gas heat exchanger is also fed with a part of the absorption liquid that has circulated only through the refrigerant drain heat exchanger for low-temperature regenerators. Fig. 3 is a cycle flow diagram of a triple effect absorption refrigerator. Out of the mixed liquid of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount sent to the low-temperature regenerator and the amount sent to the medium-temperature regenerator It is equipped with a high-temperature heat exchanger to which the amount of liquid excluding the refrigerant is fed, and the exhaust gas heat exchanger is also fed with a part of the absorption liquid that has circulated only through the refrigerant drain heat exchanger for low-temperature regenerators. Fig. 3 is a cycle flow diagram of a triple effect absorption refrigerator. A mixture of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator is sent to the low-temperature regenerator, and part of the absorption liquid flowing out from the low-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine provided with the high temperature heat exchanger with which a part of absorption liquid sent out to an intermediate temperature regenerator and flowing out from an intermediate temperature regenerator is sent. From the absorber, a mixture of the absorption liquid that has passed through the low-temperature heat exchanger and the absorption liquid that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator is sent to the low-temperature regenerator and from a part of the absorption liquid that flows out of the low-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine which equipped with the high temperature heat exchanger with which the liquid quantity except the quantity sent to the intermediate temperature heat exchanger was sent. Out of the mixed liquid of the absorption liquid that has flowed from the absorber through the low-temperature heat exchanger and the absorption liquid that has flowed through the refrigerant drain heat exchanger for the low-temperature regenerator, the liquid amount excluding the amount sent to the low-temperature regenerator goes to the medium-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine provided with the high temperature heat exchanger with which a part of absorption liquid which is sent out and flows out from an intermediate temperature regenerator is sent. Out of the mixed liquid of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount sent to the low-temperature regenerator and the amount sent to the medium-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine which equipped with the high temperature heat exchanger with which the liquid quantity except for is supplied. Out of the mixed liquid of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount sent to the low-temperature regenerator and the amount sent to the medium-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine which equipped with the high temperature heat exchanger with which the liquid quantity except for is supplied. High-temperature heat exchange in which the amount of liquid excluding the amount sent to the intermediate-temperature regenerator is supplied from the mixed liquid of the absorption liquid distributed through the intermediate-temperature heat exchanger and the absorption liquid distributed through the refrigerant drain heat exchanger for the intermediate-temperature regenerator Cycle flow of a triple effect absorption refrigeration machine in which the exhaust gas heat exchanger is supplied with a part of the absorption liquid that has passed through only the refrigerant drain heat exchanger for the medium temperature regenerator. Figure. The cycle flow figure of the triple effect absorption refrigerating machine which comprised the intermediate temperature heat exchanger to which the liquid quantity except the quantity sent to the low temperature regenerator is sent among the absorption liquid which distribute | circulated the low temperature heat exchanger from the absorber. The cycle flow figure of the triple effect absorption refrigerating machine which comprised the intermediate temperature heat exchanger to which the liquid quantity except the quantity sent to the low temperature regenerator is sent among the absorption liquid which distribute | circulated the low temperature heat exchanger from the absorber. A mixture of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator is sent to the low-temperature regenerator, and part of the absorption liquid flowing out from the low-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine which comprises the intermediate temperature heat exchanger supplied. A mixture of the absorption liquid flowing through the low-temperature heat exchanger from the absorber and the absorption liquid flowing through the refrigerant drain heat exchanger for the low-temperature regenerator is sent to the low-temperature regenerator, and part of the absorption liquid flowing out from the low-temperature regenerator The cycle flow figure of the triple effect absorption refrigerating machine which comprises the intermediate temperature heat exchanger supplied. An intermediate temperature heat exchanger to which the amount of liquid excluding the amount sent from the absorber to the low temperature regenerator and the amount sent to the refrigerant drain heat exchanger for the intermediate temperature regenerator is supplied. The cycle flow figure of the equipped triple effect absorption refrigerator. Out of the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger from the absorber and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount of liquid excluding the amount sent to the low-temperature regenerator is delivered. A triple-effect system that has an intermediate temperature heat exchanger, and the exhaust gas heat exchanger is fed to the intermediate temperature heat exchanger with a part of the absorbent flowing through only the refrigerant drain heat exchanger for the low temperature regenerator. Cycle flow diagram of absorption refrigerator. Out of the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger from the absorber and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount of liquid excluding the amount sent to the low-temperature regenerator is delivered. A triple-effect system that has an intermediate temperature heat exchanger, and the exhaust gas heat exchanger is fed to the intermediate temperature heat exchanger with a part of the absorbent flowing through only the refrigerant drain heat exchanger for the low temperature regenerator. Cycle flow diagram of absorption refrigerator. Out of the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger from the absorber and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount of liquid excluding the amount sent to the low-temperature regenerator is delivered. Triple effect absorption refrigeration machine equipped with an intermediate temperature heat exchanger, and the exhaust gas heat exchanger is also supplied with a part of the absorption liquid flowing only through the refrigerant drain heat exchanger for the low temperature regenerator Cycle flow diagram. Out of the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger from the absorber and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount of liquid excluding the amount sent to the low-temperature regenerator is delivered. Triple effect absorption refrigeration machine equipped with an intermediate temperature heat exchanger, and the exhaust gas heat exchanger is also supplied with a part of the absorption liquid flowing only through the refrigerant drain heat exchanger for the low temperature regenerator Cycle flow diagram. Out of the mixed liquid of the absorbent that has passed through the low-temperature heat exchanger from the absorber and the absorbent that has passed through the refrigerant drain heat exchanger for the low-temperature regenerator, the amount of liquid excluding the amount sent to the low-temperature regenerator is delivered. Triple effect absorption refrigeration machine equipped with an intermediate temperature heat exchanger, and the exhaust gas heat exchanger is also supplied with a part of the absorption liquid flowing only through the refrigerant drain heat exchanger for the low temperature regenerator Cycle flow diagram. The cycle flow figure of the absorption refrigerating machine as a prior art in which the exhaust gas heat exchanger was installed.

  Below, the absorption refrigerator which concerns on this invention is demonstrated in detail based on a specific cycle flow. In both double-effect and triple-effect machines, energy saving is achieved by further reducing the size of the exhaust heat recovery unit, for example, the exhaust gas heat exchanger, reducing the heat transfer area in the exhaust gas heat exchanger, and the exhaust gas heat exchanger for absorbing liquid It aims at suppressing the occurrence of internal drift and avoiding crystallization of the absorbing solution by local heating. First, a dual effect absorption refrigerator will be described. Since the configuration of the entire refrigerator has been described with reference to FIG. 36, the same reference numerals are given here and description thereof is omitted. Since the presence or absence of pumps excluding the rare liquid pump 13 and the refrigerant pump 14 often varies depending on the model, the description is omitted as much as possible.

In the present invention, a refrigerant drain heat exchanger 1 is first introduced as shown in FIGS . This uses the retained heat of the refrigerant drain that is generated in the low-temperature regenerator 2 and then goes to the condenser 3, and after a part of the absorption liquid that goes to the low-temperature heat exchanger 4 is divided and heated, it is sent to the low-temperature regenerator 2. To do. For this reason, a branch pipe 6 is provided on the upstream side immediately before the low-temperature heat exchanger in the pipe line where the absorbing liquid derived from the absorber 5 is directed to the low-temperature heat exchanger 4, and the refrigerant drain heat exchanger 1 is connected to the branch pipe. The absorption liquid to be traced can be heated. This refrigerant drain heat exchanger is for a low temperature regenerator, and is referred to as a low temperature regenerator refrigerant drain heat exchanger in order to distinguish it from a refrigerant drain heat exchanger for a medium temperature regenerator described in FIG. In the description, it is often abbreviated as a refrigerant drain heat exchanger.

  An exhaust gas heat exchanger 7 as an exhaust heat recovery unit is installed in a cycle line in which such a refrigerant drain heat exchanger 1 is provided. This is a high temperature heat generated by the flow of the absorbent toward the high temperature regenerator 8. It is located in the upstream line just before the exchanger and is in series with the high temperature heat exchanger. In this example, the exhaust gas heat exchanger 7 saves energy by recovering the stored energy of the combustion exhaust gas (high temperature regenerator exhaust gas) discharged from the gas-fired high temperature regenerator. If it is installed, the boiler exhaust gas may be introduced, and if the absorption chiller forms a cogeneration system, exhaust gas / heated water from the engine or turbine shall be used. You can also.

In the example of FIG. 1 , the above-described high-temperature heat exchanger 9 is supplied with the amount of liquid excluding the amount sent from the absorber 5 to the low-temperature regenerator 2 out of the absorbent flowing through the low-temperature heat exchanger 4. Be paid. The exhaust liquid heat exchanger 7 is not supplied with the absorption liquid flowing through the refrigerant drain heat exchanger 1, but as described above, the exhaust gas heat exchanger 7 and the high-temperature heat exchanger 9 are connected in series. 36, there is no distribution of the absorption liquid to the high-temperature heat exchanger 9 and the exhaust gas heat exchanger 7 as shown in FIG. 36, and a series of flows that eliminates the shunt flow governed by the pipe resistance is achieved. Therefore, the heat transfer efficiency in the exhaust gas heat exchanger 7 disposed on the upstream side of the high temperature heat exchanger 9 having a low temperature level is increased. This can be said to be a result of a large logarithm average temperature difference.

  In more detail, if the amount of heat heated by the exhaust gas heat exchanger is the same because of the series flow as described above, that is, the amount of heat for recovering the exhaust gas from 200 ° C. to 100 ° C., for example, is the same. For example, the heat exchanger outlet temperature decreases as the liquid amount increases. Therefore, the exhaust gas heat exchanger inevitably has a large logarithmic average temperature difference. Considering that Q = K × A × ΔTm (where Q is the amount of exchange heat, K is the overall heat transfer coefficient, A is the heat transfer area, and ΔTm is the logarithm average temperature difference), the heat transfer coefficient in the pipe is improved. As a result, the K value tends to increase, and ΔTm also increases as the solution side outlet temperature decreases. That is, it can be understood that if K and ΔTm are increased in order to obtain the necessary exchange heat quantity Q, the necessary heat transfer area A can be reduced.

  As described above, the same amount of liquid as the circulation amount in the high-temperature heat exchanger 9 also flows in the exhaust gas heat exchanger 7, but this increases the Reynolds number in the exhaust gas heat exchanger, The generation of active turbulence improves the heat transfer coefficient at the heat transfer surface. The synergistic effect due to the large logarithmic average temperature difference and the improvement of the heat transfer surface heat transfer coefficient enables the number of heat transfer tube groups to be reduced, and promotes further downsizing of the exhaust gas heat exchanger. In addition to the need for special processing, the introduction of expensive heat transfer tubes that require the use of special materials such as SUS and countermeasures against corrosion can be reduced, greatly contributing to the cost reduction of exhaust gas heat exchanger production.

Although the absorbing liquid that has circulated only refrigerant drain heat exchanger 1 is not fed into the exhaust gas heat exchanger 7 in FIG. 2, the absorbent solution and the refrigerant drain heat exchanger 1 which has flowed through the low temperature heat exchanger 4 The amount of liquid excluding the absorption liquid circulated as a heating source in the low-temperature heat exchanger 4 out of the absorption liquid sent from the low-temperature regenerator to the mixed liquid with the distributed absorption liquid Is different from the above example in that is fed to the high temperature heat exchanger 9 through the exhaust gas heat exchanger 7 .

  In any cycle flow, since the retained heat of the refrigerant drain that is generated by the low temperature regenerator 2 and goes to the condenser 3 is used, the absorption liquid heated by the low temperature heat exchanger 4 is supplied to the low temperature regenerator 2. And the absorption liquid heated with the refrigerant | coolant drain heat exchanger 1 is sent. The refrigerant drain heat exchanger increases the solution temperature at the inlet of the low-temperature regenerator, and the amount of input heat necessary for heating the absorption liquid in the low-temperature regenerator is accordingly reduced. Since the heat source of the low temperature regenerator 2 is the refrigerant vapor 34 from the high temperature regenerator 8, the burden of generating the refrigerant vapor in the high temperature regenerator 8 is reduced.

  In order to reduce the heat transfer area, the exhaust gas heat exchanger 7 is aimed to be miniaturized so as not to cause the drift of the solution in the vessel, and the possibility of liquid crystal deposition due to local heating is drastically reduced. Drain water corrosion due to condensation of exhaust gas during partial load operation is also avoided as much as possible. Furthermore, at the time of this partial load, the pump discharge rate according to the inverter control is reduced, that is, the absorption fluid circulation rate is reduced, and the generation of branch flow is avoided by serializing the exhaust gas heat exchanger according to the present invention with the high temperature heat exchanger. In combination with this, the reduction of the Reynolds number in the pipe is suppressed. As a result, a decrease in heat transfer performance in the exhaust gas heat exchanger is suppressed. Even if the circulation amount is unbalanced due to pressure fluctuations or temperature fluctuations, the solution is flushed or hunting of the liquid amount is naturally suppressed. By the way, as mentioned above, downsizing by reducing the number of tube group stages brings about a reduction in pressure loss without causing a decrease in the gas side heat transfer coefficient. Lead to Therefore, it is possible to introduce a case where the user has only gas equipment that is classified as a low-pressure gas supply section. That is, it is possible to introduce an absorption refrigeration machine not only for users who have only intermediate pressure supply or higher pressure supply facilities, but regardless of the size of the gas supply facilities. This means that the absorption refrigerator according to the present invention also has a very practical advantage of making it easier to remove installation restrictions.

  FIG. 3 is a cycle flow in which a part of the absorbent that has circulated only through the refrigerant drain heat exchanger 1 is also mixed and fed to the exhaust gas heat exchanger 7. That is, the high-temperature heat exchanger 9 is sent from the absorber 5 to the low-temperature regenerator 2 out of the mixed liquid of the absorbent flowing through the low-temperature heat exchanger 4 and the absorbent flowing through the refrigerant drain heat exchanger 1. The amount of liquid excluding the amount is fed. Thus, even though the absorption liquid that has circulated through the refrigerant drain heat exchanger 1 is only a part, the absorption liquid that does not rely only on heating in the low-temperature heat exchanger 4 is introduced into the exhaust gas heat exchanger 7. Improve the absorption liquid heating effect in the exhaust gas heat exchanger. As a result, the heat exchange load in the high temperature heat exchanger 9 can be reduced, and the amount of circulating fluid and the liquid temperature from the high temperature regenerator in the low temperature heat exchanger 4 can be suppressed. Contributes to savings in consumption.

  Unlike FIG. 3 and FIG. 2, the heat exchanger 11 using an outside waste heat is attached to the cycle flow in FIG. This is because the absorption liquid flowing through the low-temperature heat exchanger 4 and the absorption liquid flowing through the refrigerant drain heat exchanger 1 are mixed and interposed in a pipe line toward the low-temperature regenerator 2 to introduce waste heat generated outside the system. The absorbent is heated to deliver the absorbent to the low temperature regenerator 2. The absorbing liquid can be supplied to the low-temperature regenerator 2 in a state where the temperature is also increased by the energy outside the system, and heating by the refrigerant drain in the low-temperature regenerator 2 is also reduced. Of course, the generation load of the refrigerant vapor 34 in the high temperature regenerator 8 is also reduced. The extraneous waste heat utilization heat exchanger 11 is provided as necessary, and is omitted in FIGS. 2 and 3, but may be provided in the same manner if necessary. The heat source can be various hot fluids or solar energy.

  Next, the case of a triple effect absorption refrigerator will be described. As shown in FIG. 4, an intermediate temperature regenerator 21 and an intermediate temperature heat exchanger 22 that heats the absorption liquid directed to the intermediate temperature regenerator are added. In some cases, a medium temperature regenerator refrigerant drain heat exchanger 23 shown in FIG. Installed. In any case, the refrigerant drain heat exchanger 1 for the low-temperature regenerator described above is still provided, and the absorption liquid that follows the branch pipe 6 immediately before the low-temperature heat exchanger 4 is heated and sent to the low-temperature regenerator 2. The exhaust gas heat exchanger 7 is installed in an upstream pipe line immediately before the high temperature heat exchanger in which the absorbent flows toward the high temperature regenerator 8, and is in series with the high temperature heat exchanger 9, or in FIG. The exhaust gas heat exchanger 15 is installed in the upstream pipe line immediately before the intermediate temperature heat exchanger 22 in which the absorption liquid flows toward the intermediate temperature heat exchanger 21, and is in series with the intermediate temperature heat exchanger. In these triple effect machines, the heat exchanger 11 utilizing the extraneous waste heat described with reference to FIG. 1 can be attached, and therefore, in FIG. 16, the cycle flow is added. Of course, it goes without saying that a heat exchanger using waste heat outside the system can be attached as necessary in any of the above-mentioned drawings of the triple effect machine and those to be mentioned later. Regardless of the presence or absence of a heat exchanger using waste heat outside the system, the effect similar to that of the double effect machine described above is also exhibited in the case of this triple effect machine.

  I will repeat it a little, but I will describe the effect. The refrigerant drain heat exchanger for the low temperature regenerator can increase the solution temperature at the inlet of the low temperature regenerator, and the heating source of the low temperature regenerator is the refrigerant vapor that has passed through the medium temperature regenerator from the high temperature regenerator. Reduction reduces the burden of refrigerant vapor generation in the high-temperature regenerator. In addition, since the logarithmic average temperature difference can be increased and the Reynolds number in the pipe can be improved, the heat transfer coefficient on the heat transfer surface can be improved, and the exhaust gas heat exchanger can be reduced in size and cost. It becomes. If the exhaust gas heat exchanger installed in the system to save energy can be further reduced in size, the heat transfer area in the exhaust gas heat exchanger will be reduced, the internal drift of the absorption liquid will be suppressed, and the absorption liquid crystal by local heating will be suppressed. There is also very little analysis. It is also possible to avoid drain water corrosion based on exhaust gas dew condensation during partial load operation as much as possible. Since the absorption liquid distribution ratio to the intermediate temperature heat exchanger and the exhaust gas heat exchanger is not generated, a flow that is not controlled by the pipe resistance is achieved, and the generation of liquid hunting is minimized.

  First, it sees from FIG. 4 and FIG. 5 in which the refrigerant | coolant drain heat exchanger 23 (for example, refer FIG. 16) for intermediate temperature regenerators is not provided. In these cycle flows, to the high temperature heat exchanger 9, the amount sent from the absorber 5 through the low temperature heat exchanger 4 to the low temperature regenerator 2 and the amount sent to the medium temperature regenerator 21. The amount of liquid excluding is delivered. Although the absorption liquid which circulated only through the refrigerant drain heat exchanger 1 is not fed to the exhaust gas heat exchanger 7, it goes without saying that the energy saving effect by the refrigerant drain heat exchanger 1 is exhibited. In FIG. 4, the absorption liquid flowing through the exhaust gas heat exchanger 7 does not flow through the intermediate temperature heat exchanger 22. In FIG. 5, the absorption liquid flowing through the exhaust gas heat exchanger 7 flows through the intermediate temperature heat exchanger 22. Has become.

  6 and 7 show that the intermediate temperature heat exchanger 22 is in series with the exhaust gas heat exchanger 15. The exhaust gas heat exchanger 15 is supplied with an amount of liquid excluding the amount sent from the absorber 5 to the low-temperature regenerator 2 out of the absorbent flowing through the low-temperature heat exchanger 4. In FIG. 6, the absorption liquid that has flowed through the exhaust gas heat exchanger 15 is sent out in parallel to the intermediate temperature heat exchanger 22 and the high temperature heat exchanger 9, and in FIG. 7, the absorption liquid that has flowed through the exhaust gas heat exchanger 15 is medium temperature heat. It passes through the exchanger 22 and is sent to the intermediate temperature regenerator 21 and the high temperature heat exchanger 9 arranged in series therewith.

  In FIG. 8, the exhaust gas heat exchanger 7 in series with the high-temperature heat exchanger 9 includes a mixture of an absorption liquid flowing from the absorber 5 through the low-temperature heat exchanger 4 and an absorption liquid flowing through the refrigerant drain heat exchanger 1. The liquid is sent to the low temperature regenerator 2, and from the amount of liquid excluding the absorption liquid circulated as a heating source in the low temperature heat exchanger 4 from the absorbed liquid flowing out from the low temperature regenerator, the liquid is sent to the intermediate temperature heat exchanger 22. The amount of liquid excluding the measured amount is fed.

  In the example of FIGS. 9 and 10, the intermediate temperature heat exchanger 22 is in series with the exhaust gas heat exchanger 15. In these, the mixed liquid of the absorption liquid that has flowed through the low-temperature heat exchanger 4 and the absorption liquid that has flowed through the refrigerant drain heat exchanger 1 is sent from the absorber 5 to the low-temperature regenerator 2 and flows out from the low-temperature regenerator 2. The amount of liquid excluding the absorbent that is circulated as a heating source in the low-temperature heat exchanger 4 is sent to the exhaust gas heat exchanger 15.

  In FIG. 11, the high-temperature heat exchanger 9 is in series with the exhaust gas heat exchanger 7. To the exhaust gas heat exchanger, a mixed liquid of the absorption liquid flowing through the low-temperature regenerator 2 and the absorption liquid flowing through the refrigerant drain heat exchanger 1 is sent to the low-temperature regenerator 2 and flows out from the low-temperature regenerator. Among them, the amount of liquid excluding the absorption liquid circulated as a heating source in the low-temperature heat exchanger 4 is sent to the intermediate temperature regenerator 21, and the absorption liquid flowing out from the intermediate temperature regenerator 21 is heated in the intermediate temperature heat exchanger 22. The liquid quantity except the absorption liquid circulated as a source is supplied.

  FIG. 12 also shows a series configuration of the high-temperature heat exchanger 9 and the exhaust gas heat exchanger 7, which is composed of the absorption liquid flowing through the low-temperature heat exchanger 4 and the absorption liquid flowing through the refrigerant drain heat exchanger 1. Of the mixed liquid, the liquid amount excluding the amount sent to the low temperature regenerator 2 is sent to the intermediate temperature regenerator 21 and circulates as a heating source in the intermediate temperature heat exchanger 22 among the absorbing liquid flowing out from the intermediate temperature regenerator 21. The amount of liquid excluding the absorbed liquid is fed.

  Also in FIG. 13, the exhaust gas heat exchanger 7 is configured in series with the high temperature heat exchanger 9. For this purpose, of the mixed liquid of the absorbent flowing through the low temperature heat exchanger 4 and the absorbent flowing through the refrigerant drain heat exchanger 1, the amount sent to the low temperature regenerator 2 and the medium temperature regenerator 21 were sent. The amount of liquid excluding the amount is fed. 6, 7, 8, 9, 10, and 11 as well as FIG. 12 described above, the absorbed liquid that has circulated only through the refrigerant drain heat exchanger 1 for a low-temperature regenerator is an exhaust gas heat exchanger. 7 and 15 are not sent.

  By the way, FIG.14 and FIG.15 is an example of the cycle flow which should be mentioned specially. This is because the middle temperature heat exchanger 22 is in series with the exhaust gas heat exchanger 15. This is the amount of liquid excluding the amount sent to the low temperature regenerator 2 out of the mixed liquid of the absorbent flowing through the low temperature heat exchanger 4 and the absorbing liquid flowing through the refrigerant drain heat exchanger 1. . In this case, a part of the absorbent that has circulated only through the refrigerant drain heat exchanger 1 is also mixed and fed to the exhaust gas heat exchanger 15. Thereby, the absorption liquid heating effect in the exhaust gas heat exchanger 15 is improved, and the heat exchange load in the intermediate temperature heat exchanger 22 is reduced. If the circulating fluid amount or the liquid temperature from the high temperature regenerator 8 can be suppressed, heating in the high temperature regenerator 8 can be saved and fuel consumption can be suppressed.

  Next, FIG. 16 and FIG. 17 in which the refrigerant drain heat exchanger 23 for the intermediate temperature regenerator is provided will be seen. In these cycle flows, the refrigerant drain heat exchanger 23 is in a pipe line where the absorbing liquid is directed to the intermediate temperature heat exchanger 22, and a branch pipe 24 is provided upstream of the intermediate temperature heat exchanger 22, and the intermediate temperature regeneration is performed. Using the retained heat of the refrigerant drain that is generated in the condenser 21 and goes to the refrigerant drain heat exchanger 1 for the low-temperature regenerator, the absorption liquid that follows the branch pipe 24 provided on the upstream side of the intermediate-temperature heat exchanger is heated to the intermediate-temperature regenerator 21. To be sent. Needless to say, the intermediate temperature regenerator 21 is supplied with the absorption liquid heated by the intermediate temperature heat exchanger 22 and the absorption liquid heated by the refrigerant drain heat exchanger 23 installed on the intermediate temperature regenerator side. The solution temperature at the inlet becomes higher, and the amount of heat required for heating the absorbing solution in the intermediate temperature regenerator can be reduced accordingly. Since the heating source of the intermediate temperature regenerator 21 is the refrigerant vapor from the high temperature regenerator 8, the reduction in the amount of heating heat in the intermediate temperature regenerator 21 reduces the burden of generating refrigerant vapor in the high temperature regenerator. This also applies to the cycle flows of FIGS. 18, 19, 20, 21, 21, 22, 23, 24, and 25.

  16 and 17, the amount of liquid excluding the amount sent to the low-temperature regenerator 2 and the amount sent to the intermediate-temperature regenerator 21 out of the absorbent flowing through the low-temperature heat exchanger 4 from the absorber 5 is high. It is fed to the heat exchanger 9. Although the absorption liquid which circulated only through the low-temperature regenerator refrigerant drain heat exchanger 1 is not fed to the exhaust gas heat exchanger 7, it goes without saying that the energy-saving effect of the low-temperature regenerator refrigerant drain heat exchanger 1 is exhibited. In FIG. 16, the absorption liquid flowing through the exhaust gas heat exchanger 7 does not flow through the intermediate temperature heat exchanger 22. In FIG. 17, the absorption liquid flowing through the exhaust gas heat exchanger 7 flows through the intermediate temperature heat exchanger 22. It is an absorption liquid.

  In FIG. 26 and FIG. 27, the heat exchanger in series with the exhaust gas heat exchanger 15 is the intermediate temperature heat exchanger 22. These exhaust gas heat exchangers are supplied with an amount of liquid excluding the amount sent from the absorber 5 to the low-temperature regenerator 2 out of the absorbent flowing through the low-temperature heat exchanger 4. In FIG. 26, the absorption liquid flowing through the exhaust gas heat exchanger 15 is sent out in parallel to the intermediate temperature heat exchanger 22 and the high temperature heat exchanger 9, and in FIG. 27, the absorption liquid flowing through the exhaust gas heat exchanger 15 is intermediate temperature heat exchange. It is sent to the intermediate temperature regenerator 21 and the high temperature heat exchanger 9 arranged in series therewith through the vessel 22.

  In FIG. 21 mentioned above, the refrigerant | coolant which distribute | circulated the low-temperature heat exchanger 4 from the absorber 5 and the refrigerant | coolant drain heat exchanger 1 for low-temperature regenerators distribute | circulate to the high-temperature heat exchanger 9 in series with the exhaust gas heat exchanger 7. The mixed liquid with the absorbed liquid is sent to the low-temperature regenerator 2, and the amount of liquid excluding the absorbed liquid circulated as a heating source in the low-temperature heat exchanger 4 out of the absorbed liquid flowing out from the low-temperature regenerator 2 The liquid amount excluding the amount sent to the heat exchanger 22 is fed.

  In the examples of FIGS. 28 and 29, the intermediate temperature heat exchanger 22 is in series with the exhaust gas heat exchanger 15. In these exhaust gas heat exchangers, a mixed liquid of the absorption liquid flowing through the low-temperature heat exchanger 4 and the absorption liquid flowing through the refrigerant drain heat exchanger 1 is sent from the absorber 5 to the low-temperature regenerator 2, and the low temperature The liquid amount excluding the absorption liquid circulated as a heating source in the low-temperature heat exchanger 4 out of the absorption liquid flowing out from the regenerator 2 is fed.

  18, 19, 23, and 24 also have a series configuration with the high-temperature heat exchanger 9. That is, among the mixed liquid of the absorbent flowing through the low-temperature heat exchanger 4 and the absorbent flowing through the low-temperature regenerator refrigerant drain heat exchanger 1, the amount sent to the low-temperature regenerator 2 and the medium-temperature regenerator 21 The amount of liquid excluding the measured amount is being fed.

  In FIG. 20, the high-temperature heat exchanger 9 is in series with the exhaust gas heat exchanger 7. In the exhaust gas heat exchanger 7, the absorption liquid and the refrigerant drain heat exchanger 1 that have circulated through the low-temperature heat exchanger 4 are circulated. The mixed liquid with the absorbed liquid is sent to the low-temperature regenerator 2, and the amount of liquid excluding the absorbed liquid circulated as a heating source in the low-temperature heat exchanger 4 out of the low-temperature regenerator 2 is recovered at the medium temperature. The amount of liquid excluding the absorption liquid circulated as a heating source in the intermediate temperature heat exchanger 22 out of the absorption liquid sent out to the vessel 21 and flowing out from the intermediate temperature regenerator 21 is supplied.

  FIG. 22 also shows a series configuration with the high-temperature heat exchanger 9, which is a low temperature of the mixed liquid of the absorbent flowing through the low-temperature heat exchanger 4 and the absorbent flowing through the refrigerant drain heat exchanger 1. The amount of liquid excluding the amount sent to the regenerator 2 is sent to the intermediate temperature regenerator 21, and the absorption liquid circulated as a heating source in the intermediate temperature heat exchanger 22 is removed from the absorption liquid flowing out from the intermediate temperature regenerator 21. The amount of liquid is fed to the exhaust gas heat exchanger 7.

  20 and 22, a mixed liquid of the absorbing liquid flowing through the intermediate temperature heat exchanger 22 and the absorbing liquid flowing through the intermediate temperature regenerator refrigerant drain heat exchanger 23 is sent to the intermediate temperature regenerator 21, and the intermediate temperature regenerator The amount of liquid excluding the absorbing liquid as the heating source in the intermediate temperature heat exchanger 22 out of the absorbing liquid flowing out from the 21 is supplied to the high temperature heat exchanger 9.

  FIG. 30 shows that the amount of liquid excluding the amount sent to the low-temperature regenerator 2 and the amount sent to the refrigerant drain heat exchanger 23 for the medium-temperature regenerator among the absorbent flowing through the low-temperature heat exchanger 4 is being fed. The warm heat exchanger 22 is in series with the exhaust gas heat exchanger 15. In any cycle flow of the triple effect machine described above, the absorption liquid that has circulated only through the low-temperature regenerator refrigerant drain heat exchanger 1 is not supplied to the exhaust gas heat exchangers 7 and 15.

  It should be noted that FIGS. 31, 32, 33, 34, and 35 are the intermediate temperature heat exchanger 22 in series with the exhaust gas heat exchanger 15. This is because the amount of liquid excluding the amount sent to the low-temperature regenerator 2 out of the mixed liquid of the absorbent flowing through the low-temperature heat exchanger 4 and the absorbent flowing through the refrigerant drain heat exchanger 1 is the exhaust gas heat exchanger. 15 is sent. In this case, a part of the absorption liquid flowing through only the refrigerant drain heat exchanger 1 is also mixed and fed to the exhaust gas heat exchanger. Thereby, the absorption liquid heating effect in the exhaust gas heat exchanger 15 is improved, and the heat exchange load in the intermediate temperature heat exchanger 22 located downstream can be reduced. If the amount or temperature of the circulating fluid from the high temperature regenerator 8 is suppressed, heating in the high temperature regenerator can be saved and fuel consumption can be suppressed.

  In FIG. 18 and FIG. 25, a part of the absorbent that has circulated only through the refrigerant drain heat exchanger 23 for the medium temperature regenerator is also mixed and fed to the high temperature heat exchanger 9. The exhaust gas heat exchanger 7 in series with the high-temperature heat exchanger 9 has an intermediate temperature out of the mixed liquid of the absorbent that has passed through the intermediate-temperature heat exchanger 22 and the absorbent that has passed through the refrigerant drain heat exchanger 23 for the intermediate-temperature regenerator. The liquid amount excluding the amount sent to the regenerator 21 is fed. A high-temperature absorption liquid can be sent to the high-temperature heat exchanger using the retained heat of the refrigerant drain generated in the medium-temperature regenerator. Similarly, a high temperature absorbent can be sent to the medium temperature regenerator. Also in these cycle flows, the solution temperature at the inlet of the intermediate temperature regenerator becomes higher, and the amount of heat required for heating the absorption liquid in the intermediate temperature regenerator 21 can be reduced accordingly. Since the heating source of the intermediate temperature regenerator 21 is the refrigerant vapor from the high temperature regenerator 8, the reduction in the amount of heating heat in the intermediate temperature regenerator greatly reduces the burden of generating refrigerant vapor in the high temperature regenerator. Since the absorption liquid heating effect in the exhaust gas heat exchanger 7 is improved and the heat exchange load in the intermediate temperature heat exchanger is reduced, the amount of circulating fluid or the liquid temperature from the high temperature regenerator can be suppressed, and in the high temperature regenerator Heating can be saved and fuel consumption can be reduced. On the other hand, the solution temperature at the inlet of the high-temperature regenerator is further increased through the high-temperature heat exchanger 9, and the amount of heat required for heating the absorbent in the high-temperature regenerator 8 can be reduced accordingly. Since the heating source of the high-temperature heat exchanger 9 is the high-temperature concentrated liquid returned from the high-temperature regenerator, the reduction in heating in the high-temperature regenerator greatly reduces the fuel consumption burden in the high-temperature regenerator.

  DESCRIPTION OF SYMBOLS 1 ... Refrigerant drain heat exchanger, 2 ... Low temperature regenerator, 3 ... Condenser, 4 ... Low temperature heat exchanger, 5 ... Absorber, 6 ... Branch pipe of upstream branch of low temperature heat exchanger, 7, 15 ... Waste heat Recovery unit (exhaust gas heat exchanger), 8 ... high temperature regenerator, 9 ... high temperature heat exchanger, 11 ... external waste heat utilization heat exchanger, 21 ... medium temperature regenerator, 22 ... medium temperature heat exchanger, 23 ... medium temperature regeneration Refrigerant drain heat exchanger for equipment, 24 ... Branch pipe just before the medium temperature heat exchanger, 31 ... Evaporator, 34 ... Refrigerant vapor.

Claims (5)

Absorber, low-temperature regenerator, high-temperature regenerator, condenser, evaporator, low-temperature heat exchanger that heats the absorption liquid from the absorber before sending it to the low-temperature regenerator, and heats the absorption liquid toward the high-temperature regenerator It is equipped with a high-temperature heat exchanger, an exhaust heat recovery device that heats the absorbing liquid using exhaust heat, and the refrigerant vapor condensate generated by heating the absorbing liquid is sprayed on the evaporator pipe in the evaporator, In the cooling operation in which cold water is obtained in the evaporator tube by vaporizing the condensate on the heat transfer surface, the absorption liquid generated by generating the refrigerant vapor and the high temperature heat exchanger The double-effect absorption chiller that absorbs the refrigerant vapor generated when cold water is obtained after passing through heat exchange with a low-temperature heat exchanger and places the absorber and the evaporator connected to it in a high vacuum In
A refrigerant drain led out from the absorber is in a pipe line to the low-temperature heat exchanger, a branch pipe is provided upstream of the low-temperature heat exchanger, the refrigerant drain generated in the low-temperature regenerator and going to the condenser A refrigerant drain heat exchanger for a low-temperature regenerator that heats the absorption liquid that follows the branch pipe out of the absorption liquid that has been directed to the low-temperature heat exchanger and sends it to the low-temperature regenerator,
Wherein the exhaust heat recovery device is liquid volume delivered excluding the amount to be circulated as a heating source in the low temperature heat exchanger of the absorption liquid fed from the low-temperature regenerator, the exhaust heat recovery device is absorbing liquid Is installed in the upstream line of the high-temperature heat exchanger in a flow toward the high-temperature regenerator, and is connected in series with the high-temperature heat exchanger. Absorber, low temperature regenerator, medium temperature regenerator, high temperature regenerator, condenser, evaporator, low temperature heat exchanger that heats the absorption liquid from the absorber before sending it to the low temperature regenerator, absorption toward the medium temperature regenerator An intermediate temperature heat exchanger for heating the liquid, a high temperature heat exchanger for heating the absorption liquid toward the high temperature regenerator, and an exhaust heat recovery unit for heating the absorption liquid using exhaust heat, and heating the absorption liquid In the cooling operation in which the condensate of the generated refrigerant vapor is sprayed on the evaporator tube in the evaporator, and cold water is obtained in the evaporator tube by vaporizing the condensate on the heat transfer surface, the refrigerant vapor is generated. The absorption liquid generated by this is exchanged with the absorption liquid directed to the 11 regenerator with the high-temperature heat exchanger, and after passing through at least the low-temperature heat exchanger, the refrigerant vapor generated when cold water is obtained is absorbed and absorbed. So that the vacuum chamber and the evaporator In the triple effect absorption refrigerating machine is,
A refrigerant drain led out from the absorber is in a pipe line to the low-temperature heat exchanger, a branch pipe is provided upstream of the low-temperature heat exchanger, the refrigerant drain generated in the low-temperature regenerator and going to the condenser A refrigerant drain heat exchanger for a low-temperature regenerator that heats the absorption liquid that follows the branch pipe and sends it to the low-temperature regenerator is provided,
Wherein the exhaust heat recovery device liquid amount excluding the amount that is sent to the low-temperature regenerator of the absorption liquid has flowed through the low temperature heat exchanger is fed, the exhaust heat recovery device is temperature regenerator medium is absorbing liquid the heading is installed upstream pipe immediately before the previous SL in heat exchanger flows, the absorption chiller being characterized in that connected in series to the middle temperature heat exchanger. Absorber, low temperature regenerator, medium temperature regenerator, high temperature regenerator, condenser, evaporator, low temperature heat exchanger that heats the absorption liquid from the absorber before sending it to the low temperature regenerator, absorption toward the medium temperature regenerator An intermediate temperature heat exchanger for heating the liquid, a high temperature heat exchanger for heating the absorption liquid toward the high temperature regenerator, and an exhaust heat recovery unit for heating the absorption liquid using exhaust heat, and heating the absorption liquid In the cooling operation in which the condensate of the generated refrigerant vapor is sprayed on the evaporator tube in the evaporator, and cold water is obtained in the evaporator tube by vaporizing the condensate on the heat transfer surface, the refrigerant vapor is generated. The absorption liquid generated by this is exchanged with the absorption liquid directed to the 11 regenerator with the high-temperature heat exchanger, and after passing through at least the low-temperature heat exchanger, the refrigerant vapor generated when cold water is obtained is absorbed and absorbed. So that the vacuum chamber and the evaporator In the triple effect absorption refrigerating machine is,
A refrigerant drain led out from the absorber is in a pipe line to the low-temperature heat exchanger, a branch pipe is provided upstream of the low-temperature heat exchanger, the refrigerant drain generated in the low-temperature regenerator and going to the condenser A refrigerant drain heat exchanger for a low-temperature regenerator that heats the absorption liquid that follows the branch pipe and sends it to the low-temperature regenerator is provided,
In the exhaust heat recovery unit, the amount sent from the intermediate temperature heat exchanger to the intermediate temperature regenerator is further excluded from the amount of the liquid that has passed through the low temperature heat exchanger excluding the amount sent to the low temperature regenerator. liquid volume is fed, the exhaust heat recovery device is disposed on the upstream side pipe immediately before the high temperature heat exchanger flow absorbing liquid toward the high-temperature regenerator, the high-temperature heat exchanger are connected in series Absorption type refrigerator characterized by that. The high-temperature regenerator is a type-fired gas, said exhaust heat recovery device is claimed in any one of claims 1 to 3, characterized in that exhaust gas heat exchanger for circulating the high-temperature regenerator flue gas Absorption refrigerator. Absorption heat generated outside the system is introduced into a pipe line that is mixed with the absorption liquid that has flowed through the low-temperature heat exchanger and the absorption liquid that has flowed through the refrigerant drain heat exchanger for the low-temperature regenerator and goes to the low-temperature regenerator. the absorption liquid is heated, as claimed in any one of claims 1 to 4 out of the system for utilizing waste heat heat exchanger for delivering the absorbent solution to the low temperature generator is characterized in that it is interposed Absorption refrigerator.