JP2017036856A - Waste heat input type absorption chiller heater and waste heat recovery amount control method thereof - Google Patents

Abstract

[PROBLEMS] To improve the stability of the entire system and the energy use efficiency. Cooling in which a regenerator 2, a condenser 3, an evaporator 4, an absorber 5, and cooling water for heat exchange in the absorber 5 and the condenser 3 are circulated through a cooling tower 6, respectively. The exhaust heat input type absorption chiller / heater 1 is provided with a water circulation channel 7 and recovers exhaust heat input from the exhaust heat supply source G to heat and regenerate the absorption liquid. A control unit 20 that controls the flow rate of the cooling water flowing through the passage 7 is provided, and the control unit 20 adjusts the exhaust heat recovery amount to a state in which the exhaust heat recovery amount is set with respect to the exhaust heat amount input from the exhaust heat supply source G. Control the flow rate of cooling water. [Selection] Figure 2

Description

  The present invention relates to an exhaust heat input type absorption chiller / heater and a method for controlling the amount of exhaust heat recovery.

  An absorption chiller / heater is a device that uses a refrigerant (water) and an absorbent (lithium bromide solution) to repeat refrigeration cycles of evaporation, absorption, regeneration, and condensation, and generate cold and hot water by heat exchange during that cycle. Widely used as air conditioning equipment for buildings. Also, the exhaust heat input type absorption chiller / heater that uses exhaust heat from the gas engine, etc., as the regeneration heat of the absorption liquid is a type of cogeneration system that is attracting attention as an air conditioning facility with a high energy-saving effect. (For example, refer to Patent Document 1 below).

  FIG. 1 shows an example of a conventional exhaust heat input type absorption chiller / heater. The waste heat input type absorption chiller / heater J1 regenerates and heats the absorbent by using the waste water generated by the gas engine G1. The exhaust hot water generated in the gas engine G1 is sent to the exhaust heat regenerator J2 in the exhaust heat input type absorption chiller / heater J1 through the exhaust hot water supply pipe P1, and heat exchange for heating the absorption liquid is performed. The exhaust heat is recovered. The exhaust hot water whose exhaust heat has been recovered by the exhaust heat regenerator J2 is returned to the gas engine G1 through the exhaust hot water return pipe P2 at a predetermined return temperature. The exhaust hot water supply pipe P1 and the exhaust hot water return pipe P2 are connected by a bypass pipe P3 via a three-way valve V. By controlling the opening and closing of the three-way valve V, the exhaust hot water sent to the exhaust heat regenerator J2. The amount of warm water and the ratio of the amount of warm water returned to the gas engine G1 without passing through the waste heat regenerator J2 are appropriately adjusted to maintain a constant return temperature of the warm water and maintain the stable operation of the gas engine G1. Yes.

Japanese Patent No. 3639885

  In recent years, the amount of exhaust heat recovery has increased due to the improvement in performance of the exhaust heat input type absorption chiller / heater. On the other hand, the efficiency of the gas engine which is the exhaust heat supply source of the exhaust heat input type absorption chiller / heater is also improved, and the amount of exhaust heat is reduced. As a result, a situation occurs in which the amount of exhaust heat recovered by the exhaust heat input type absorption chiller / heater exceeds the amount of exhaust heat from the gas engine. In this case, if the above-mentioned three-way valve control is performed in order to keep the return temperature of the exhaust hot water constant, the amount of exhaust heat recovered will fluctuate, and the refrigerating capacity of the exhaust heat input type absorption chiller / heater will only fluctuate. However, the return of the warm water via the bypass pipe is repeated intermittently, and the return temperature is not stable.

  If the desired heat cannot be recovered from the waste water as described above and the refrigeration capacity falls below the cooling load, a reheating operation with a gas burner may occur for heating and regeneration of the absorbent, or the temperature of the waste water will be regulated. If this happens, there is a concern that heat will be dissipated to the cooling tower wastefully with circulating cooling water. If such a situation occurs, it will be against the original purpose of the cogeneration system for effective use of energy. .

  This invention makes it an example of a subject to cope with such a problem. In other words, by controlling the recovered heat amount to the set state, the return temperature of the waste water is stabilized, the refrigeration capacity is stabilized, the additional cooking operation is suppressed, and the waste heat of the recovered waste heat is avoided. The purpose of the present invention is to effectively use energy, to improve the stability of the entire system and to improve the efficiency of energy use.

In order to achieve such an object, the present invention has the following configuration.
A regenerator that heats and regenerates the absorption liquid, a condenser that condenses and liquefies water vapor generated by heating and regeneration with heat exchange with cooling water, an evaporator that evaporates the liquefied water under low pressure, and vaporized water vapor An absorber that is condensed by heat exchange with the cooling water and absorbed by the absorption liquid, and a cooling water circulation passage that circulates the cooling water that exchanges heat with the absorber and the condenser through the cooling tower, respectively. An exhaust heat input type absorption chiller / heater that heats and regenerates the absorption liquid by recovering the exhaust heat input from the exhaust heat supply source, and the flow rate of the cooling water flowing through the cooling water circulation channel And a control unit that controls the flow rate of the cooling water so as to adjust the exhaust heat recovery amount to a set state with respect to the exhaust heat amount input from the exhaust heat supply source. Exhaust heat input type absorption chiller / heater characterized by

  The exhaust heat absorption type absorption chiller / heater of the present invention having such a feature stabilizes the return temperature of the exhaust water by controlling the flow rate of the circulating cooling water and controlling the recovered heat amount. To stabilize the refrigeration capacity. In addition, it is possible to effectively use energy by suppressing additional cooking operation and avoiding wasteful heat dissipation of recovered exhaust heat. Thereby, it is possible to improve the stability of the entire system including the exhaust heat recovery source and improve the energy utilization efficiency.

It is explanatory drawing which showed the example of the form of the waste heat input type absorption cold / hot water machine of a prior art. It is explanatory drawing which showed the structural example of the waste heat input type absorption cold / hot water machine which concerns on embodiment of this invention. 5 is a graph showing an example of the relationship between the cooling water flow rate and the exhaust heat recovery amount (the rated cooling water flow rate is 100%, and the exhaust heat recovery amount at that time is 1.0). It is explanatory drawing (control flow) which showed the example of control of the waste heat input type absorption cold / hot water machine which concerns on embodiment of this invention. It is explanatory drawing (control flow) which showed the example of control of the waste heat input type absorption cold / hot water machine which concerns on embodiment of this invention. It is explanatory drawing (control flow) which showed the example of control of the waste heat input type absorption cold / hot water machine which concerns on embodiment of this invention. It is explanatory drawing (control flow) which showed the example of control of the waste heat input type absorption cold / hot water machine which concerns on embodiment of this invention. It is explanatory drawing which showed the control effect of the waste heat input type absorption chiller / heater according to the embodiment of the present invention ((a) waste heat recovery amount when not controlling, (b) when controlling) Waste heat recovery amount).

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 2 shows an exhaust heat input type absorption chiller / heater 1 according to an embodiment of the present invention. The exhaust heat input type absorption chiller / heater 1 includes a regenerator 2, a condenser 3, an evaporator 4, and an absorber 5 as a basic configuration for executing a refrigeration cycle. Further, a cooling water circulation passage 7 for circulating cooling water through the cooling tower 6 is provided.

  In the regenerator 2, the absorption liquid (for example, lithium bromide solution) that has been diluted by absorbing the refrigerant (for example, water) is heated to evaporate the water that is the refrigerant to regenerate the absorption liquid to a high concentration. . The regenerator 2 may include a high-temperature regenerator and a low-temperature regenerator that use heating means such as a gas burner 2F in stages. The regenerated absorbent is sent to the absorber 5 through the absorbent pipe 8.

  In the condenser 3, water vapor generated by heating / regeneration in the regenerator 2 is condensed and liquefied by heat exchange with cooling water circulating in the cooling water circulation passage 7. Inside the condenser 3, a heat exchanging portion 7 </ b> A communicating with the cooling water circulation passage 7 is disposed.

  In the evaporator 4, the water liquefied in the condenser 3 is evaporated under a low pressure. In the evaporator 4, a heat exchange section 4 </ b> A of the cold water supply flow path is arranged, and the heat of water in the cold water supply flow path is taken away using the vaporization heat to generate cold water.

  In the absorber 5, the water vapor evaporated in the evaporator 4 is absorbed by the absorbent regenerated in the regenerator 2, and the absorbed heat is radiated by heat exchange with the cooling water circulating in the cooling water circulation passage 7. The absorption liquid diluted by absorbing water as the refrigerant is sent to the regenerator 2 through the absorption liquid pipe 8. Inside the absorber 5, a heat exchanging portion 7 </ b> B communicating with the cooling water circulation channel 7 is disposed.

  In the exhaust heat input type absorption chiller / heater 1, exhaust heat from an exhaust heat supply source G such as a gas engine is input and used for heating and regeneration of the absorption liquid. Exhaust hot water generated by the exhaust heat supply source G is sent into the exhaust heat input type absorption chiller / heater 1 through the exhaust hot water supply pipe 11, and the absorption liquid pipe 8 through which the absorption liquid circulates by the absorption liquid pump 17 It is supplied to the exhaust heat regenerator 10 for heat exchange. The exhaust hot water from which the exhaust heat has been recovered by the exhaust heat regenerator 10 is returned to the exhaust heat supply source G such as a gas engine through the exhaust hot water return pipe 12 having the return pump 12P.

  Two bypass pipes 13 and 15 are provided between the exhaust hot water supply pipe 11 and the exhaust hot water return pipe 12, and the bypass pipe 13 communicates with the exhaust hot water return pipe 12 via the first three-way valve 14. The bypass pipe 15 communicates with the exhaust hot water return pipe 12 via the second three-way valve 16. The first three-way valve 14 and the second three-way valve 16 are appropriately controlled in order to stably operate the exhaust heat supply source G.

  The cooling water circulation channel 7 passes through the cooling tower 6 and communicates with the heat exchanging part 7B in the absorber 5 and the heat exchanging part 7A in the condenser 3, and close to the cooling tower 6 as necessary. Are provided with a bypass channel 7C and a cooling water three-way valve 7D. And the control part 20 which controls the flow volume of the cooling water which flows through the cooling water circulation flow path 7 is provided. The control unit 20 includes a circulation pump 21 that can variably control the output, an inverter 22 that drives the circulation pump 21, and a control device 23 that controls the output of the circulation pump 21 by controlling the inverter 22.

  A control operation of the control unit 20 will be described. The control unit 20 controls the flow rate of the cooling water so that the exhaust heat amount input from the exhaust heat supply source G is adjusted to a state where the exhaust heat recovery amount recovered by the exhaust heat regenerator 10 is set. . As shown in FIG. 3, the exhaust heat recovery amount can be adjusted by the cooling water flow rate flowing through the cooling water circulation passage 7. FIG. 3 shows the change in the amount of exhaust heat recovered when the cooling water flow rate is changed, with the cooling water flow rate at the rated operation of the circulation pump 21 being 100% and the exhaust heat recovery amount at that time being 1.0. ing. As shown in the figure, the amount of exhaust heat recovery can be adjusted to decrease or increase by decreasing or increasing the cooling water flow rate. When the cooling water flow rate is increased, the amount of heat exchanged in the condenser 3 and the absorber 5 can be increased, so that the energy absorption of the refrigeration cycle can be increased and the exhaust heat recovery amount can be increased. Conversely, when the cooling water flow rate is reduced, the energy absorption of the refrigeration cycle is reduced, so that the amount of exhaust heat recovery can be reduced.

  The control unit 20 includes temperature measuring means for measuring the input temperature T1 of the exhaust warm water input from the exhaust heat supply source G and the return temperature T2 of the exhaust warm water, and the input temperature T1 and the return temperature T2 measured by the temperature measurement means. The cooling water flow rate is controlled based on one or both of the above. Further, a temperature measuring means for measuring the absorbing liquid temperature (absorbing liquid temperature in the high temperature regenerator) T3 in the regenerator 2 is provided, and the cooling water flow rate is controlled based on the absorbing liquid temperature T3 measured by the temperature measuring means. To do.

  As temperature measuring means, a temperature sensor 11T for measuring the input temperature T1 is provided in the exhaust hot water supply pipe 11, a temperature sensor 12T for measuring the return temperature T2 is provided in the exhaust hot water return pipe 12, and a regenerator (high temperature regenerator) 2 is provided. Are provided with temperature sensors 2T for measuring the absorption liquid temperature T3, the measurement signals of the temperature sensors 2T, 11T, and 12T are input to the control device 23, and the inverter 22 is controlled by the control signal output by the control device 23. The circulation pump 21 is controlled via

  A specific control operation of the control unit 20 will be described with reference to the control flow shown in FIGS. In the example shown in FIG. 4, the flow rate of the cooling water is controlled so that the measured return temperature T2 becomes the set temperature Ta, and the measured absorption liquid temperature T3 avoids crystallization of the absorption liquid. When the set temperature Tn is exceeded, the flow rate of the cooling water is controlled to the maximum flow rate as a safety measure.

  A description will be given along the control flow of FIG. After the operation is started (step S10), the flow rate of the cooling water is set to a predetermined flow rate (step S11), and the return temperature T2 is measured at a predetermined time interval (step S12). Further, the absorption liquid temperature T3 in the regenerator 2 (high temperature regenerator) is measured at a predetermined time interval (step S13). Then, it is determined whether or not T3> Tn (step S14). If T3> Tn, the absorption liquid temperature T3 exceeds the set temperature Tn that avoids crystallization of the absorption liquid. The water flow rate is set to the maximum (step S14a), and the process proceeds to step S12. If T3> Tn, it is determined whether T2 = Ta (step S15). If T2 = Ta, the process proceeds to step S12 without changing the flow rate. If T2 = Ta, it is determined whether or not T2 <Ta (step S16). If T2 <Ta, cooling water per hour is used to reduce the exhaust heat recovery amount by decreasing the cooling flow rate. The flow rate change dG / dt = (T2-Ta) R is controlled (step S16a). If T2 <Ta, the cooling flow rate is increased and the exhaust heat recovery amount is increased, so that dG / dt = n ( T2-Ta) R is controlled (step S17). R is a constant and can be determined according to the heat capacity of the cooling water of the exhaust heat input type absorption chiller / heater 1, and n is a constant larger than 1 and can be determined according to the characteristics of the air conditioner. it can. Thereafter, if necessary, it is determined whether or not there is a driving prohibition signal (step S18). If there is no driving prohibition signal, the operation is continued (step S12), and if there is a driving prohibition signal, the operation is stopped (step S19).

  In the example shown in FIG. 5, the flow rate of the cooling water is controlled so that the temperature difference between the measured charging temperature T1 and the return temperature T2 becomes the set temperature difference Tb, and the measured absorption liquid temperature T3. When the temperature exceeds a set temperature Tn that avoids crystallization of the absorbing liquid, the flow rate of the cooling water is controlled to the maximum flow rate for safety measures.

  A description will be given along the control flow of FIG. Steps S20, S21, S23, S24, S24a, S28, and S29 are the same as steps S10, S11, S13, S14, S14a, S18, and S19 in the flow shown in FIG. In this example, in step S22, a temperature difference ΔT (= T1−T2) between the charging temperature T1 and the return temperature T2 is measured at a predetermined time interval, and in step S25, it is determined whether ΔT = Tb, and ΔT If = Tb, the process proceeds to step S22 without changing the flow rate. If ΔT = Tb is not satisfied, it is determined whether ΔT <Tb (step S26). If ΔT <Tb is not satisfied, the cooling water per hour is decreased in order to reduce the exhaust heat recovery amount by decreasing the cooling flow rate. The flow rate change dG / dt = (Tb−ΔT) R is controlled (step S26a), and if ΔT <Tb, in order to increase the cooling flow rate and increase the amount of exhaust heat recovery, dG / dt = n ( Tb−ΔT) R is controlled (step S27). R is a constant and can be determined according to the heat capacity of the cooling water of the exhaust heat input type absorption chiller / heater 1, and n is a constant larger than 1 and can be determined according to the characteristics of the air conditioner. it can.

  In the example shown in FIG. 6, when the time change rate of the measured charging temperature T1 (or return temperature T2) is positive, the flow rate of the cooling water is increased to control the charging temperature T1 (or return temperature T2). When the rate of time change is negative, the flow rate of cooling water is controlled to decrease, and when the measured absorption liquid temperature T3 exceeds the set temperature Tn to avoid crystallization of the absorption liquid, safety measures are taken. Therefore, the flow rate of cooling water is controlled to the maximum flow rate.

  A description will be given along the control flow of FIG. Steps S30, S31, S33, S34, S34a, S38, and S39 are the same as steps S10, S11, S13, S14, S14a, S18, and S19 in the flow shown in FIG. In this example, the time change rate dT1 / dt (or dT2 / dt) of the charging temperature T1 (or return temperature T2) is measured at a predetermined time interval in step S32, and dT1 / dt = 0 (or in step S35). It is determined whether or not dT2 / dt = 0). If dT1 / dt = 0 (or dT2 / dt = 0), the flow proceeds to step S32 without changing the flow rate. If dT1 / dt = 0 (or dT2 / dt = 0), it is determined whether dT1 / dt> 0 (or dT2 / dt> 0) (step S36), and dT1 / dt> 0 (or dT2). / Dt> 0), the cooling water flow rate change per time dG / dt = dT1 / dt · R (or dG / dt = dT2 / dt) in order to reduce the exhaust heat recovery amount by reducing the cooling flow rate. (R) is controlled (step S36a), and if dT1 / dt> 0 (or dT2 / dt> 0), dG / dt = n in order to increase the amount of exhaust heat recovery by increasing the cooling flow rate. DT1 / dt · R (or dG / dt = n · dT2 / dt · R) is controlled (step S37). R is a constant and can be determined according to the heat capacity of the cooling water of the exhaust heat input type absorption chiller / heater 1, and n is a constant larger than 1 and can be determined according to the characteristics of the air conditioner. it can.

  In the example shown in FIG. 7, the flow rate of the cooling water is controlled so that the exhaust heat recovery amount becomes equal to the exhaust heat amount input from the exhaust heat supply source G, and the measured absorption liquid temperature T3 is the absorption liquid. When the temperature exceeds a set temperature Tn that avoids crystallization, the flow rate of the cooling water is controlled to the maximum flow rate for safety measures.

  A description will be given along the control flow of FIG. Steps S40, S41, S43, S44, S44a, S48, and S49 are the same as steps S10, S11, S13, S14, S14a, S18, and S19 in the flow shown in FIG. In this example, in step S42, the exhaust heat recovery amount (Qc) is estimated from the coolant temperature / flow rate, the load, and the characteristic diagram at predetermined time intervals. In step S24, it is determined whether or not Qc = Qe (Qe is the amount of exhaust heat (set value) from the exhaust heat supply source G). If Qc = Qe, the flow rate is not changed. The process proceeds to S42. If Qc = Qe, it is determined whether or not Qc <Qe (step S46). If Qc <Qe, the cooling water per hour is used to reduce the exhaust heat recovery amount by decreasing the cooling flow rate. The flow rate change dG / dt = (Qc−Qe) R is controlled (step S46a). If Qc <Qe, the cooling flow rate is increased to increase the exhaust heat recovery amount, so that dG / dt = n ( Qc-Qe) R is controlled (step S47). R is a constant and can be determined according to the heat capacity of the cooling water of the exhaust heat input type absorption chiller / heater 1, and n is a constant larger than 1 and can be determined according to the characteristics of the air conditioner. it can.

  FIG. 8 shows the control effect of the control unit 20. When the control of the control unit 20 is not performed, as shown in FIG. 8A, when the cooling load varies, the amount of exhaust heat recovered in the exhaust heat input type absorption chiller / heater 1 varies accordingly. If the exhaust heat recovery amount increases from the input exhaust heat amount from the exhaust heat supply source G, the control of the first three-way valve 14 and the second three-way valve 16 is likely to cause hunting, and the system operation is unstable. And the inconvenience that the efficiency of energy use decreases. On the other hand, when the control as described above is performed by the control unit 20, as shown in FIG. 8B, the input exhaust amount from the exhaust heat supply source G and the exhaust heat input type, regardless of the change in the cooling load. The amount of exhaust heat recovered by the absorption chiller / heater 1 can always be matched. As a result, the system operation can be stabilized, and the energy utilization efficiency can be increased.

  The effect of the exhaust heat input type absorption chiller / heater 1 according to the embodiment of the present invention will be described more specifically. First, the refrigeration capacity is reduced by suppressing the hunting of the first three-way valve 14 and the second three-way valve 16. Is stabilized. Moreover, since the additional cooking operation of the backup gas burner in the regenerator 2 is suppressed, the gas consumption is reduced. In addition, since the flow rate of cooling water can be reduced by controlling the amount of exhaust heat recovered, the cooling power for cooling water can be reduced compared to the conventional technology that circulates cooling water at a constant flow rate. This also makes it possible to operate with high energy-saving effect.

  As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, the specific configuration is not limited to these embodiments, and the design can be changed without departing from the scope of the present invention. Is included in the present invention. In particular, the absorption chiller / heater type itself can be used for various types of cycles, including single-effect cycle, double-effect cycle, triple-effect cycle, reverse flow, parallel flow, and series flow. can do.

1: Exhaust heat input type absorption chiller / heater, 2: Regenerator, 2F: Gas burner,
3: Condenser, 4: Evaporator,
5: Absorber, 6: Cooling tower, 7: Cooling water circulation channel, 8: Absorption liquid piping,
7A, 7B: heat exchange section, 7C: bypass flow path, 7D: cooling water three-way valve,
10: Waste heat regenerator, 11: Waste hot water supply piping,
12: Waste hot water return pipe, 12P: Return pump,
13, 15: Bypass piping, 14: First three-way valve, 16: Second three-way valve,
17: Absorbent pump.
20: control unit, 21: circulation pump, 22: inverter, 23: control device,
2T, 11T, 12T: temperature sensor (temperature measuring means),
G: Waste heat supply source (gas engine)

Claims (9)

A regenerator that heats and regenerates the absorption liquid, a condenser that condenses and liquefies water vapor generated by heating and regeneration with heat exchange with cooling water, an evaporator that evaporates the liquefied water under low pressure, and vaporized water vapor An absorber that is condensed by heat exchange with the cooling water and absorbed by the absorption liquid, and a cooling water circulation passage that circulates the cooling water that exchanges heat with the absorber and the condenser through the cooling tower, respectively. An exhaust heat input type absorption chiller / heater that heats and regenerates the absorbing liquid by recovering the exhaust heat input from the exhaust heat supply source,
A control unit for controlling the flow rate of the cooling water flowing through the cooling water circulation channel;
The exhaust heat input type, wherein the control unit controls the flow rate of the cooling water so as to adjust the exhaust heat recovery amount to a set state with respect to the exhaust heat amount input from the exhaust heat supply source. Absorption type hot and cold water machine. Comprising a temperature measuring means for measuring the return temperature of the exhaust hot water supplied from the exhaust heat supply source,
The exhaust heat input type absorption chiller / heater according to claim 1, wherein the controller controls the flow rate of the cooling water so that the return temperature measured by the temperature measuring unit becomes a set temperature. . Temperature measuring means for measuring the temperature and return temperature of the exhaust water supplied from the exhaust heat supply source, respectively,
2. The exhaust heat according to claim 1, wherein the controller controls the flow rate of the cooling water so that a temperature difference between an input temperature and a return temperature measured by the temperature measuring unit becomes a set temperature difference. Input type absorption chiller / heater. Comprising a temperature measuring means for measuring the temperature at which the exhaust hot water supplied from the exhaust heat supply source is measured;
The control unit controls to increase the flow rate of the cooling water when the time change rate of the input temperature measured by the temperature measuring unit is positive, and when the time change rate of the input temperature is negative, 2. The exhaust heat input type absorption chiller / heater according to claim 1, wherein the cooling water flow rate is controlled to decrease. Comprising a temperature measuring means for measuring the return temperature of the exhaust hot water supplied from the exhaust heat supply source,
The control unit controls to increase the flow rate of the cooling water when the time change rate of the return temperature measured by the temperature measuring unit is positive, and when the time change rate of the return temperature is negative, 2. The exhaust heat input type absorption chiller / heater according to claim 1, wherein the cooling water flow rate is controlled to decrease.   The exhaust heat input type absorption according to claim 1, wherein the control unit controls the flow rate of the cooling water so that an exhaust heat recovery amount becomes equal to an exhaust heat amount input from the exhaust heat supply source. Type hot and cold water machine. Comprising temperature measuring means for measuring the temperature of the absorbent in the regenerator,
The controller is configured to control the flow rate of the cooling water to a maximum set flow rate when the temperature of the absorbent measured by the temperature measuring unit exceeds a set temperature that avoids crystallization of the absorbent. The exhaust heat input type absorption chiller / heater according to any one of claims 1 to 6. By repeating the refrigeration cycle of evaporation / absorption / regeneration / condensation, circulating cooling water for heat exchange in absorption and condensation, and recovering the exhaust heat input from the exhaust heat source for heating / regeneration of the absorption liquid A waste heat recovery amount control method for an exhaust heat input type absorption chiller / heater to perform,
By adjusting the flow rate of the cooling water, the exhaust heat input type absorption chiller / heater is adjusted to a state in which the exhaust heat recovery amount is set with respect to the exhaust heat amount input from the exhaust heat supply source Waste heat recovery amount control method.   The exhaust heat recovery amount control of the exhaust heat input type absorption chiller / heater according to claim 8, wherein the flow rate of the cooling water is controlled so that the exhaust heat recovery amount matches the exhaust heat amount. Method.

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