JP2001194026A - Absorption refrigerating machine, and cogeneration system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain an absorption refrigerating machine, and a cogeneration system which can follow up variation of load quickly and can be constituted at a low cost. SOLUTION: The cogeneration system CGS comprises a combination of a power generating unit 1 and an absorption refrigerating machine 10. The absorption refrigerating machine 10 comprises a thermometer T1 for measuring the temperature of chilled water in a chilled water outlet line L2, a first feed pump PRI for feeding refrigerant liquid RL pooled in an evaporator 20 into an absorber 30 through a refrigerant liquid line L30 while regulating the flow rate, and a controller 90 for controlling the first feed pump PR1 based on the measurement of the chilled water outlet thermometer T1. According to the arrangement, the absorption refrigerating machine 10 exhibits high follow-up performance to variation of load.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to an absorption refrigerator and a cogeneration system provided with the absorption refrigerator.

[0002]

2. Description of the Related Art Conventionally, as a technique belonging to such a field, a technique disclosed in Japanese Patent Application Laid-Open No. 8-296922 is known. The conventional absorption refrigerator described in this publication constitutes a cogeneration system together with a power generation unit including a power generator and a gas engine. This absorption refrigerator is a so-called double-effect absorption refrigerator, and has a high-pressure regenerator and a low-pressure regenerator as regenerators. The high-pressure regenerator uses exhaust gas discharged from the gas engine of the power generation unit as a heat source, and the low-pressure regenerator uses a cooling fluid (cooling water) that circulates around the gas engine of the power generation unit and recovers heat, and The refrigerant gas heated and vaporized by the regenerator is used as a heat source.

[0003]

The present invention is not limited to the absorption refrigerator incorporated in the cogeneration system described above.
In all absorption chillers, it is required to improve the ability to follow load fluctuations. For example, in a general absorption refrigerator, when a light load operation is performed such that the generated heat amount is set to, for example, 25% or less of the maximum time, the control time becomes longer, the followability is reduced, and stable operation is difficult. Problems have been pointed out. In addition, in the absorption chiller incorporated in the above-mentioned conventional cogeneration system, the exhaust gas discharged from the power generation unit is directly introduced into the high-pressure regenerator. As a result, it becomes necessary to adjust the amount of exhaust gas introduced into the high-pressure regenerator. In this case, an electromagnetic valve or the like corresponding to a high temperature and a large diameter may be used, but this increases the cost of the entire cogeneration system including the absorption refrigerator.

Accordingly, an object of the present invention is to provide an absorption refrigerator and a cogeneration system which can be configured at a low cost with high followability to load fluctuation.

[0005]

In the absorption refrigerator according to the present invention, the refrigerant vaporized by the evaporator is absorbed into the absorption solution by the absorber, and the absorption solution and the refrigerant are separated by the regenerator. In an absorption refrigerator in which the separated refrigerant is condensed in a condenser and then vaporized again in an evaporator, the absorption refrigerator is arranged so as to pass through the evaporator, and a chilled water line through which chilled water flows, and an evaporation of the chilled water line. Temperature measuring means for measuring the temperature of the chilled water at the outlet of the vessel, refrigerant feeding means capable of feeding the refrigerant liquid staying in the evaporator while adjusting the flow rate into the absorber, and based on the measurement values of the temperature measuring means. Control means for controlling the refrigerant supply means.

[0006] In this absorption refrigerator, the control means activates the refrigerant supply means at the time of load fluctuation such as when the required amount of cooling heat decreases during the cooling operation. Thus, the refrigerant liquid staying in the evaporator is introduced into the absorber by the refrigerant feeding means. Further, the control means controls (feedback control) the refrigerant feeding means based on the measurement value of the temperature measurement means. That is, the control means sends a predetermined operation signal to the refrigerant supply means so that the temperature at the evaporator outlet of the cold water becomes a desired temperature corresponding to the required amount of heat or the like. The refrigerant supply means adjusts the flow rate of the refrigerant liquid supplied from the evaporator to the absorber according to a signal received from the control means.

As described above, when the refrigerant liquid is supplied from the evaporator to the absorber by the refrigerant supply means, the absorbing solution inside the absorber is diluted according to the evaporator outlet temperature of the cold water. As a result, the internal pressure of the condenser decreases, the saturation temperature in the evaporator increases, and the amount of refrigerant evaporating on the surface of the heat transfer tube decreases, so the chilled water line arranged to pass through the evaporator The evaporator outlet temperature of the cold water flowing through the evaporator rises in accordance with the dilution amount of the absorbing solution in the absorber. As a result, it becomes possible to control the absorption refrigerator so as to follow the load fluctuation, that is, the change in the required heat quantity with high accuracy.

When the absorption chiller is incorporated into a cogeneration system, and the exhaust heat of the power generation unit is used by the regenerator, the amount of exhaust gas from the power generation unit supplied to the regenerator when the load fluctuates is controlled. Since a large-diameter and expensive vacuum solenoid valve or the like to be used can be dispensed with, the manufacturing cost of the absorption refrigerator can be reduced. In this case, the refrigerant supply means can supply the refrigerant liquid staying in the evaporator to the absorber via a solution return line for supplying the absorbent solution regenerated by the regenerator into the absorber. It may be constituted as.

Further, a second temperature measuring means for measuring the temperature of the chilled water is further provided at the evaporator inlet of the chilled water line, and the control means is controlled by the refrigerant based on the measured values of the temperature measuring means and the second temperature measuring means. It may be configured to control the feeding means. If such a configuration is adopted, the control means performs feedback control of the refrigerant supply means based on the temperature of the chilled water at the evaporator outlet of the chilled water line, and also measures the value measured by the second temperature measuring means, Feedforward control will be performed based on the temperature of the cold water at the evaporator inlet of the line. As a result, the ability to follow a load change can be further improved. In addition, when the flow rate of the chilled water is controlled from the facility such as a building according to the load fluctuation, the flow rate data of the chilled water is taken in, the calorie is obtained by a computer or the like, and the refrigerant supply is performed based on the obtained heat quantity. If the sending means is controlled, finer control becomes possible.

Further, the apparatus further comprises a second refrigerant feeding means capable of feeding the refrigerant gas vaporized by the high-pressure regenerator into the evaporator while adjusting the flow rate, and the control means based on the measured value of the temperature measuring means. Preferably, it controls the second refrigerant supply means.

[0011] This absorption chiller not only performs cooling operation,
It enables heating operation. When performing the heating operation of the absorption refrigerator, the control means stops the refrigerant gas from flowing from the high-pressure regenerator to the low-pressure regenerator within an allowable range of the internal pressure of the high-pressure regenerator, and controls the temperature measurement means. The refrigerant supply means is controlled based on the measured value. That is,
The control device sends a predetermined operation signal to the refrigerant supply means so that the temperature of the cold water (hot water) at the outlet of the evaporator becomes a desired temperature corresponding to a required heat amount or the like. The refrigerant feeding means adjusts the flow rate of the refrigerant flowing from the high-pressure regenerator to the evaporator according to the signal received from the control means. Thereby, the cold water (hot water) flowing through the cold water line (cold / hot water line) is heated by the refrigerant gas supplied from the high-pressure regenerator into the evaporator and the temperature thereof rises. The flowing hot water can be used for heating.

Further, the cooling water line, which is arranged so as to pass through the absorber and through which the cooling water flows, is connected to the absorber inlet and the absorber outlet of the cooling water line.
It is preferable that the control apparatus further includes a bypass unit that can change a flow rate of the cooling water flowing into the absorber outlet side, and the control unit controls the bypass unit based on a value measured by the temperature measuring unit.

[0013] In this absorption refrigerator, the control means activates the bypass means at the time of load fluctuation such as when the required heat quantity changes during the cooling operation or the heating operation. Thereby, the bypass unit connects the absorber inlet and the absorber outlet of the cooling water line. And the control means controls the bypass means based on the cold water temperature measured at the evaporator outlet of the cold water line (cold / hot water line). In other words, the control means sends a predetermined operation signal to the refrigerant supply means such that the temperature of the cold water (hot water) at the evaporator outlet becomes a desired temperature corresponding to the required amount of heat or the like. The bypass means changes the flow rate of the cooling water flowing into the absorber outlet according to the signal received from the control means.

As described above, when the flow rate of the cooling water flowing into the absorber outlet changes (increases), the cooling water flowing through the cooling water line (heat transfer tube) disposed inside the absorber during the cooling operation. Due to the change (decrease) in the flow rate of water, the flow velocity inside the heat transfer tube changes (decreases), and the heat transfer performance decreases. Then, the temperature difference at the outlet of the absorber becomes smaller, the temperature efficiency of the absorber as a heat exchanger decreases, and the amount of heat recovered by the cooling water flowing through the cooling water line changes (decreases). Thereby, while the amount of the refrigerant absorbed by the absorbing solution inside the absorber decreases, and the amount of the refrigerant gas generated in the evaporator decreases, the evaporator outlet temperature of the chilled water flowing through the chilled water line is: It will decrease according to the reduction of the refrigerant gas in the evaporator. As a result, it becomes possible to control the absorption refrigerator so as to accurately and stably follow a load change during the cooling operation, that is, a change in the required heat amount. Such a configuration is extremely useful for improving the followability and stability against load fluctuations when the absorption refrigerator is operated at a very light load, such as setting the generated heat amount to 15% or less of the maximum. It is valid.

On the other hand, during the heating operation, when the high-temperature refrigerant gas is supplied from the high-pressure regenerator to the evaporator, the high-temperature refrigerant gas also flows into the absorber communicating with the evaporator. In this case, when the flow rate of the cooling water flowing into the absorber outlet side is changed (increased) by the bypass means controlled by the control means, the flow rate of the cooling water flowing through the cooling water line disposed inside the absorber is changed. Changes (decreases). This allows
The amount of heat of the refrigerant gas collected by the cooling water in the absorber and radiated by the cooling tower or the like also changes. As a result, it becomes possible to control the absorption refrigerator so as to follow the load fluctuation during the heating operation, that is, the change in the required heat quantity with high accuracy.

Also in this case, a second temperature measuring means for measuring the temperature of the cold water is further provided at the evaporator inlet of the cold water line, and the control means is controlled based on the measured values of the temperature measuring means and the second temperature measuring means. , The bypass means may be controlled. If such a configuration is adopted, the control unit performs feedback control of the bypass unit based on the temperature of the chilled water at the evaporator outlet of the chilled water line, and measures the value measured by the second temperature measuring unit, that is, the chilled water line. The feedforward control is performed based on the temperature of the cold water at the evaporator inlet. As a result, the ability to follow a load change can be further improved. In addition, when the flow rate of the chilled water is controlled from the facility such as a building according to the load fluctuation, the flow rate data of the chilled water is taken in, the calorie is obtained by a computer or the like, and the refrigerant supply is performed based on the obtained heat quantity. If the sending means is controlled, finer control becomes possible.

According to a fourth aspect of the present invention, in the absorption refrigerator, the refrigerant vaporized in the evaporator is absorbed into the absorption solution by the absorber, and the absorption solution and the refrigerant are separated by the high-pressure regenerator and the low-pressure regenerator. In an absorption refrigerator in which the separated refrigerant is condensed in a condenser and then vaporized again in an evaporator, the absorption refrigerator is arranged so as to pass through the evaporator, and a chilled water line for circulating chilled water and an evaporation of the chilled water line Temperature measuring means for measuring the temperature of the chilled water at the outlet of the vessel, a refrigerant feeding means capable of feeding the refrigerant gas into the absorber while adjusting the flow rate and condensing the refrigerant gas passed through the low-pressure regenerator as a heat source, and a temperature measuring means. Control means for controlling the refrigerant supply means based on the measured value.

Also in this absorption chiller, the refrigerant supply means is operated by the control means at the time of load fluctuation such as when the required amount of cooling heat decreases during the cooling operation. Thereby, the refrigerant liquid condensed after passing through the low-pressure regenerator is introduced into the absorber. Further, the control means controls (feedback control) the refrigerant feeding means based on the measurement value of the temperature measuring means. That is, the control means sends a predetermined operation signal to the refrigerant supply means so that the temperature at the evaporator outlet of the cold water becomes a desired temperature corresponding to the required amount of heat or the like. The refrigerant supply means adjusts the flow rate of the refrigerant liquid supplied from the low-pressure regenerator to the absorber according to a signal received from the control means.

As described above, when the refrigerant liquid is supplied from the low-pressure regenerator to the absorber by the refrigerant supply means, the absorbing solution inside the absorber is diluted, and the amount of refrigerant gas generated in the evaporator decreases. I do. Therefore, the evaporator outlet temperature of the chilled water flowing through the chilled water line rises in accordance with the dilution amount of the absorbing solution in the absorber and the amount of the refrigerant gas reduced in the evaporator. As a result, it becomes possible to control the absorption refrigerator so as to accurately and stably follow a load change, that is, a change in a required heat amount. Such a configuration is extremely effective in improving the followability to a load change during a light load operation in which the amount of generated heat is set to, for example, 25% or less of the maximum.

In this case as well, the refrigerant supply means supplies the refrigerant liquid staying in the evaporator to the absorber via a solution return line for supplying the absorbing solution regenerated by the regenerator to the absorber. You may comprise as what can be transmitted. Further, a second temperature measuring means for measuring the temperature of the chilled water is further provided at the evaporator inlet of the chilled water line, and the control means is provided with a refrigerant feeding means based on the measured values of the temperature measuring means and the second temperature measuring means. Is preferably controlled. If such a configuration is adopted, the control unit performs feedback control of the refrigerant supply unit based on the temperature of the chilled water at the evaporator outlet of the chilled water line, and also measures the value of the second temperature measurement unit, that is,
Feedforward control is performed based on the temperature of the cold water at the evaporator inlet of the cold water line. As a result, the ability to follow a load change can be further improved.
In addition, when the flow rate of the chilled water is controlled from the facility such as a building according to the load fluctuation, the flow rate data of the chilled water is taken in, the calorie is obtained by a computer or the like, and the refrigerant supply is performed based on the obtained heat quantity. If the sending means is controlled, finer control becomes possible.

In the absorption refrigerator according to the present invention, the refrigerant vaporized by the evaporator is absorbed into the absorption solution by the absorber, the absorption solution is separated from the refrigerant by the regenerator, and the separated refrigerant is separated by the regenerator. In an absorption refrigerator, which is condensed in a condenser and then vaporized again in an evaporator, it is arranged so as to pass through the evaporator, and a chilled water line for flowing chilled water and a temperature of chilled water at an evaporator outlet of the chilled water line And a cooling water line for circulating cooling water, and a communication between an absorber inlet and an absorber outlet of the cooling water line, and an absorber. It is characterized by comprising bypass means capable of changing the flow rate of the cooling water flowing into the outlet side, and control means for controlling the bypass means based on a value measured by the temperature measuring means.

In the cogeneration system according to the present invention, the power generation unit and the absorption chiller are combined, and the power generation unit generates electric power and uses the exhaust heat of the power generation unit with the absorption chiller. After separating the absorbing solution and the refrigerant and condensing the separated refrigerant,
In a cogeneration system that obtains cold heat by vaporizing, an absorption refrigerator includes a condenser that condenses a refrigerant separated from an absorption solution, an evaporator that vaporizes the refrigerant condensed in the condenser, and a refrigerant that is vaporized in the evaporator. An absorber that absorbs into the absorbing solution, a high-pressure regenerator that heats the absorbing solution supplied from the absorber using exhaust gas discharged from the power generation unit as a heat source, a cooling fluid that flows through the power generation unit, and a refrigerant that is vaporized by the high-pressure regenerator A low-pressure regenerator that heats the absorbing solution supplied from the absorber using gas as a heat source, a chilled water line that is arranged to pass through the evaporator, and chilled water that circulates chilled water, and chilled water at the evaporator outlet of the chilled water line. Temperature measuring means for measuring the temperature of the refrigerant, refrigerant feeding means capable of feeding the refrigerant liquid staying in the evaporator into the absorber while adjusting the flow rate, and a temperature measuring means based on the measured value of the temperature measuring means. There are, characterized in that it comprises a control means for controlling the coolant feeding means.

[0023] Further, there is further provided a second refrigerant feeding means capable of feeding the refrigerant gas vaporized by the high-pressure regenerator into the evaporator while adjusting the flow rate, and the control means based on the measured value of the temperature measuring means. Preferably, it controls the second refrigerant supply means.

Further, the cooling water line, which is arranged so as to pass through the absorber and through which the cooling water flows, communicates with the absorber inlet and the absorber outlet of the cooling water line.
It is preferable that the control apparatus further includes a bypass unit that can change a flow rate of the cooling water flowing into the absorber outlet side, and the control unit controls the bypass unit based on a value measured by the temperature measuring unit.

According to a ninth aspect of the present invention, in the cogeneration system according to the present invention, a power generation unit and an absorption refrigerator are combined, and the power generation unit generates electric power and uses the exhaust heat of the power generation unit with the absorption refrigerator. After separating the absorbing solution and the refrigerant and condensing the separated refrigerant,
In a cogeneration system that obtains cold heat by vaporizing, an absorption refrigerator includes a condenser that condenses a refrigerant separated from an absorption solution, an evaporator that vaporizes the refrigerant condensed in the condenser, and a refrigerant that is vaporized in the evaporator. An absorber that absorbs into the absorbing solution, a high-pressure regenerator that heats the absorbing solution supplied from the absorber using exhaust gas discharged from the power generation unit as a heat source, a cooling fluid that flows through the power generation unit, and a refrigerant that is vaporized by the high-pressure regenerator A low-pressure regenerator that heats the absorbing solution supplied from the absorber using gas as a heat source, a chilled water line that is arranged to pass through the evaporator, and chilled water that circulates chilled water, and chilled water at the evaporator outlet of the chilled water line. Temperature measuring means for measuring the temperature of the refrigerant, and a refrigerant feeder capable of adjusting the flow rate of the refrigerant gas passing through the low-pressure regenerator as a heat source and supplying the refrigerant gas into the absorber while condensing the refrigerant gas. If, based on the measurement values of the temperature measuring means, and a controlling means for controlling the coolant feeding means.

According to a tenth aspect of the present invention, in the cogeneration system, a power generation unit and an absorption refrigerator are combined, and the power generation unit generates electric power and uses the exhaust heat of the power generation unit with the absorption refrigerator. In the cogeneration system that separates the absorption solution and the refrigerant and condenses the separated refrigerant, and then vaporizes to obtain cold heat, the absorption refrigerator has a condenser that condenses the refrigerant separated from the absorption solution. The evaporator evaporates the refrigerant condensed in the condenser, the absorber evaporates the refrigerant vaporized in the evaporator into an absorption solution, and heats the absorption solution supplied from the absorber using exhaust gas discharged from the power generation unit as a heat source. A high-pressure regenerator, and an absorption solution supplied from an absorber using the cooling fluid flowing through the power generation unit and the refrigerant gas vaporized by the high-pressure regenerator as heat sources. A low-pressure regenerator that is arranged to pass through the evaporator, a chilled water line that circulates chilled water, a temperature measurement unit that measures the temperature of the chilled water at the evaporator outlet of the chilled water line, and a passage that passes through the absorber. The cooling water line for flowing the cooling water, and the communication between the absorber inlet and the absorber outlet of the cooling water line,
It is characterized by comprising bypass means capable of changing the flow rate of cooling water flowing into the outlet side of the absorber, and control means for controlling the bypass means based on a value measured by the temperature measuring means.

In the absorption refrigerator according to the present invention, the refrigerant vaporized by the evaporator is absorbed into the absorption solution by the absorber, the absorption solution is separated from the refrigerant by the regenerator, and the separated refrigerant is separated by the regenerator. In an absorption refrigeration and heating machine that condenses with a condenser and then vaporizes again with an evaporator to obtain cooling water for cooling or hot water for heating, it is arranged so as to pass through the evaporator, and the cold water or hot water flows. A hot / cold water line, a temperature measuring means for measuring the temperature of cold water or hot water at the evaporator outlet of the cold / hot water line, and a first capable of feeding the refrigerant liquid retained in the evaporator into the absorber while adjusting the flow rate. Refrigerant supply means, a second refrigerant supply means capable of supplying the refrigerant gas vaporized by the high-pressure regenerator into the evaporator while adjusting the flow rate, and a first refrigerant supply means based on the measurement value of the temperature measurement means. A system for controlling the refrigerant supply means or the second refrigerant supply means Characterized in that it comprises a means.

In this case, the cooling water line, which is arranged so as to pass through the absorber and communicates the cooling water, communicates between the absorber inlet and the absorber outlet of the cooling water line, and the absorber outlet side And a bypass unit that can change a flow rate of the cooling water flowing into the control unit.
It is preferable that the bypass unit is controlled based on the measurement value of the temperature measuring unit.

[0029]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of an absorption refrigerator and a cogeneration system according to the present invention will be described below in detail with reference to the drawings.

FIG. 1 is a perspective view showing a first embodiment of a cogeneration system (hereinafter referred to as "CGS") according to the present invention, and FIG. 2 is a system diagram of the cogeneration system shown in FIG. The cogeneration system CGS (hereinafter, simply referred to as “CGS”) shown in these drawings is configured by combining the power generation unit 1 and the absorption refrigerator (absorption refrigerator / heater) 10 into one body. , 500 KW, the total length is about 5 m and the total width is about 2 m. Therefore, the CGS is configured to be extremely compact, and is suitable for use in buildings, offices, factories, and the like for in-house power generation and the like.

As shown in FIG. 2, the power generation unit 1 has a generator 2 and a gas engine 3 for driving the generator 2. A cooling jacket (not shown) is provided in the gas engine 3, and cooling water EW (cooling fluid) supplied from the cooling tower 4 via a cooling water line is circulated in the jacket. . The cooling water EW that cools the gas engine 3 as the prime mover that drives the generator 2 by flowing through the jacket portion as described above, together with the exhaust gas EG discharged from the gas engine 3 and the absorption refrigerator 10
On the side it is used as a heat source for concentrating the absorbing solution as working fluid. In addition, a diesel engine, a gasoline engine, a micro gas turbine, or the like can be applied as a prime mover that drives the generator 2.
A fuel cell can be applied as the power generation unit 1.

The absorption refrigerator 10 performs a refrigerating operation by an absorption cycle in which water is used as a refrigerant R and a lithium bromide solution or the like is used as an absorption solution Y. That is, the absorption refrigerator 10 includes the evaporator 20, the absorber 30, the high-pressure regenerator 40 and the low-pressure regenerator 50 as the regenerator, and the condenser 60, which constitute the absorption cycle. And
A low-temperature refrigerant liquid (water) RL condensed in the condenser 60 is vaporized in the evaporator 20 to perform a freezing (refrigeration and heating) operation. In the absorption refrigerator 10, the refrigerant R may be ammonia, the absorption solution Y may be water, the refrigerant R may be TFE, the absorption solution Y may be E181, or the like. It is also possible to configure a cycle using a refrigerant system as a medium.

As shown in FIG. 2, the evaporator 20 and the absorber 3
0 shares the same shell SL1 (high vacuum vessel). A heat transfer tube 21 is disposed in the evaporator 20, and the heat transfer tube 21 is provided with cold water W through a cold water inlet line L <b> 1.
1 is supplied. The cold water W1 flowing through the heat transfer tube 21 is discharged to the outside via the cold water outlet line L2. These cold water inlet line L1, heat transfer tube 21, and cold water outlet line L
2 constitutes a cold water line arranged to pass through the inside of the evaporator 20 (shell SL1). Refrigerant liquid RL is sprayed onto heat transfer pipe 21 via spray pipe 22, and the sprayed refrigerant liquid RL takes vaporization latent heat from cold water W <b> 1 flowing through heat transfer pipe 21 to be vaporized.

Thus, the cold water W1 flows into the heat transfer tube 21 at a temperature of, for example, 12 ° C., is cooled, and then is discharged at a temperature of, for example, 5 ° C. or 7 ° C. through the cold water outlet line L2. . The refrigerant gas (water vapor) RG vaporized by depriving the latent heat of vaporization from the cold water W1 flows into the absorber 30 side.
Further, the cold water W1 flowing out of the evaporator 20 is used for cooling of a building or the like, and the cold water W1 used for cooling or the like is heated to a temperature of, for example, 12 ° C., and is introduced into the evaporator 20 again. . The evaporator 20 is provided with a refrigerant pump (not shown). The refrigerant pump RL pumps the refrigerant liquid RL from the inside of the evaporator 20, and the pumped refrigerant liquid RL is connected to a refrigerant line (not shown). Spray tube 22
And is sprayed toward the heat transfer tube 21.

Similarly, the heat transfer tube 31 is also provided inside the absorber 30.
Is arranged. Cooling water W2 is supplied to the heat transfer tube 31 via a cooling water line L3, and the absorbing solution Y is sprayed to the heat transfer tube 31 via a spray tube 32.
Since the sprayed absorption solution Y absorbs the refrigerant gas RG flowing into the absorber 30 side, its concentration decreases, and the diluted absorption solution Y having the reduced concentration is collected at the bottom of the absorber 30. The heat generated in the absorber 30 is recovered by the cooling water W2 flowing in the heat transfer tube 21. The absorber 30 is provided with a solution pump (not shown), and the solution pump pumps up the absorbing solution Y from inside the absorber 30. The pumped absorption solution Y is sprayed toward the heat transfer tube 31 via a solution line (not shown) and the spray tube 32.

Absorption solution Y collected at the bottom of absorber 30
Is pumped by the solution pump PY and the low-temperature heat exchanger 7
0, solution line L4, high temperature heat exchanger 75, solution line L
5 to the high-pressure regenerator 40. The high-pressure regenerator 40 uses exhaust gas EG discharged from the gas engine 3 of the power generation unit 1 as a heat source. Note that the high-pressure regenerator 40 may additionally include another heat source using gas, heavy oil, kerosene, steam, or the like as fuel. A heat transfer tube 41 (including a flat heat transfer material) is disposed inside the high-pressure regenerator 40. The heat transfer tube 41 is connected to the gas engine 3 of the power generation unit 1 via an exhaust gas line L6.
The exhaust gas EG discharged from is supplied as a heat source. Further, the exhaust gas EG flowing through the heat transfer tube 41 is discharged out of the system via the exhaust gas line L7 and the duct 5. As a result, the absorption solution Y supplied to the high-pressure regenerator 40 deprives the heat of the exhaust gas EG via the heat transfer tube 41 and rises in temperature, so that a part of the absorbed refrigerant R is vaporized. As a result, the concentration of the absorbing solution Y in the high-pressure regenerator 40 increases.

The absorption solution Y heated to a high concentration by the high-pressure regenerator 40 is supplied to the solution line L8, the high-temperature heat exchanger 75,
Solution line L9, low temperature heat exchanger 70, solution line L10
Is supplied to the scatter tube 32 through the tub and is scattered toward the heat transfer tube 31 in the absorber 30. On the other hand, the refrigerant gas RG vaporized in the high-pressure regenerator 40 is supplied as a heat source to the low-pressure regenerator 50 via the refrigerant line L11. That is, the heat transfer tube 51 is disposed in the low-pressure regenerator 50, and the refrigerant line L11 is connected to a fluid inlet of the heat transfer tube 51.

The low-pressure regenerator 50 includes, in addition to the refrigerant gas RG vaporized in the high-pressure regenerator 40,
The cooling water EW that has cooled the gas engine 3 is also used as a heat source. That is, the heat transfer tube 52 is disposed in the low-pressure regenerator 50, and the cooling water EW flowing out of the jacket of the gas engine 3 is supplied to the fluid inlet of the heat transfer tube 52 via the cooling water line L12. Pumped by pump PW. The cooling water EW flowing through the heat transfer tube 51 is returned to the cooling tower 4 via the cooling water line L13, and is reused for cooling the gas engine 3.

On the other hand, the low-temperature heat exchanger 70 and the high-temperature heat exchanger 7
5 is branched from the solution line L4 downstream of the high-temperature heat exchanger 75, and the inside of the low-pressure regenerator 50 is connected to the absorber 3 via the solution line L14.
From 0 a dilute absorption solution Y is supplied. Low pressure regenerator 50
The absorption solution Y supplied to the inside takes heat from the high-temperature refrigerant gas RG via the heat transfer tube 51 and from the cooling water EW heated via the heat transfer tube 52 to raise the temperature. Thereby, the refrigerant R dissolved in the absorbing solution Y is vaporized and the concentration of the absorbing solution Y is increased. The absorption solution Y having a high concentration is
It is collected at the bottom of the low-pressure regenerator 50 and flows out of the solution line L15. The solution line L15 is connected to the high-temperature heat exchanger 7
5 and the low-temperature heat exchanger 70, and as a result, the absorbing solution Y collected at the bottom of the low-pressure regenerator 50 flows into the solution line L15, the solution line L9, and the low-temperature heat exchanger 70. , Spraying pipe 32 through solution line L10
And is sprayed toward the heat transfer tube 31 in the absorber 30.

For the solution line L4, a flow regulating valve FV0 is provided between the branch point of the solution line L14 and the high temperature heat exchanger 75. By changing the opening of the flow control valve FV0, the flow rate of the absorption solution Y supplied from the absorber 30 to the high-pressure regenerator 40 and the flow rate of the absorption solution Y supplied from the absorber 30 to the low-pressure regenerator 50 are appropriately adjusted. Can be set.

The refrigerant gas RG vaporized in the low-pressure regenerator 50
Is introduced into the condenser 60 via the refrigerant line L16. Similarly, the refrigerant gas RG that has passed through the low-pressure regenerator 50 as a heat source after being vaporized by the high-pressure regenerator 40 is introduced into the condenser 60 via the refrigerant line L17. A heat transfer tube 61 is disposed inside the condenser 60, and a fluid inlet of the heat transfer tube 61 has a cooling water line L <b> 1 connected to a fluid outlet of the heat transfer tube 31 disposed in the absorber 30.
Cooling water W2 is supplied via 8. Therefore, the condenser 6
The high-pressure refrigerant gas RG that has flowed into the coolant tube 0 is cooled and condensed through the heat transfer tube 61 to become a low-temperature refrigerant liquid (water) RL.
The refrigerant liquid RL is supplied to the distribution pipe 22 via the refrigerant line L19 due to a pressure difference and a gravity difference between the inside of the condenser 60 and the inside of the evaporator 20, and is dispersed to the heat transfer tube 21 in the evaporator 20. You. Note that the condenser 60 may be configured to share the same shell as the low-pressure regenerator 50.

Here, not only the absorption chiller incorporated in the cogeneration system as described above, but also the absorption chiller in general, it is required to improve the followability to the load fluctuation. For example, in a general absorption refrigerator, during a light load operation in which the generated heat is set to, for example, 25% or less of the maximum, the control time becomes longer, and the stability and followability are reduced. Problems such as inoperability have been pointed out.
In view of this point, the absorption chiller 10 is provided with various refrigerant feeding systems as described below in order to improve the followability to the load fluctuation at low cost.

First, as shown in FIG. 1, a refrigerant liquid line L3 connecting the evaporator 20 side and the absorber 30 side in the shell SL1 is provided below the shell SL1 of the evaporator 20 and the absorber 30.
0 is connected. In the middle of the refrigerant liquid line L30, a first feed pump PR1 and a first gate valve GV1 are sequentially arranged from the evaporator 20 side to the absorber 30 side. The first feed pump PR1 is configured as a so-called inverter pump, and is connected to the control device 90 as shown in FIG. Further, the first gate valve GV1 is a remote control valve of an electromagnetic type or the like, and is connected to the control device 90 similarly to the first feed pump PR1.

As a result, the liquid reservoir of the evaporator 20 and the liquid reservoir of the absorber 30 can communicate with each other via the refrigerant liquid line L30, and the first gate valve GV1 is controlled via the controller 90.
Is opened and the first feed pump PR1 is operated, the refrigerant liquid RL staying in the evaporator 20 can be fed into the absorber 30 while adjusting the flow rate. That is,
The refrigerant liquid line L30 including the first feed pump PR1 and the first gate valve GV1 is connected to the refrigerant liquid RL staying in the evaporator 20.
Functions as a refrigerant supply means capable of supplying the refrigerant into the absorber 30 while adjusting the flow rate.

It should be noted that a pump other than an inverter pump may be used as the first feed pump PR1. In this case, a flow regulating valve is provided downstream of the first feed pump PR1. It is sufficient to provide a bypass line for circulating the refrigerant liquid RL when the refrigerant liquid is not supplied.

Further, a refrigerant liquid line L31 is branched from the refrigerant liquid line L30 between the first feed pump PR1 and the first gate valve GV1. This refrigerant liquid line L31 has a second gate valve GV2 on the way, and
Merges with the solution line L10 communicating with. Second gate valve G
V2 is a remote control valve of an electromagnetic type or the like, and is connected to the control device 90. As a result, the first
If the gate valve GV1 is closed and the second gate valve GV2 is opened and the first feed pump PR1 is operated, the evaporator 20
While adjusting the flow rate of the refrigerant liquid RL staying in the
Can be fed into the absorber 30 via

That is, the first feed pump PR1 and the first feed pump PR1
The refrigerant liquid line L30 including the gate valve GV1 and the refrigerant liquid line L31 including the second gate valve GV2 are connected to a high-pressure regenerator 40.
And the absorbing solution Y regenerated by the low-pressure regenerator 50
0 (solution line L1)
The refrigerant liquid RL staying in the evaporator 20 functions as a refrigerant supply means that can supply the refrigerant liquid RL staying in the evaporator 20 to the absorber 30 via the spray pipe 32 and the spray pipe 32).

Further, a refrigerant liquid line L32 is branched from the middle of the refrigerant line L19 connecting the condenser 60 and the evaporator 20, and the refrigerant liquid line L32 is connected to the first gate valve GV1 and the first feed. The refrigerant liquid line L30 merges with the pump PR1. In this refrigerant liquid line L32,
From the condenser 60 to the evaporator 20, a third gate valve GV3,
The second feed pump PR2 and the fourth gate valve GV4 are arranged in order. The second feed pump PR2 is also configured as a so-called inverter pump, and is connected to the control device 90 as shown in FIG. Further, the third gate valve GV3 and the fourth gate valve GV4 are remote control valves of an electromagnetic type or the like, and are connected to the control device 90. Further, the refrigerant liquid line L32 has an orifice OF1 arranged on the outlet side of the third gate valve GV3.

As a result, the second gate valve GV2 is closed via the control device 90, and the first gate valve GV1 and the third gate valve GV are closed.
By opening V3 and the fourth gate valve GV4 and operating the second feed pump PR2, the refrigerant liquid RL staying in the condenser 60 can be fed into the absorber 30.
That is, the second feed pump PR2, the third gate valve GV3,
The refrigerant liquid line L32 including the fourth gate valve GV4, a part of the refrigerant liquid line L30 including the first gate valve GV1, and the second gate valve GV2 are connected to the refrigerant liquid RL staying in the condenser 60.
Functions as a refrigerant supply means capable of supplying the refrigerant into the absorber 30.

Further, a refrigerant liquid line L33 is branched from the refrigerant liquid line L32 on the upstream side of the fourth gate valve GV4. This refrigerant liquid line L33 is
It has a gate valve GV5 and merges with the solution line L10 communicating with the spray tube 32. The fifth gate valve GV5 is also a remote control valve of an electromagnetic type or the like, and is connected to the control device 90. As a result, the fourth gate valve GV4 is closed via the control device 90, the third gate valve GV3 and the fifth gate valve GV5 are opened, and the second feed pump PR2 is operated.
While adjusting the flow rate of the refrigerant liquid RL staying in the spray pipe 3
2 can be fed into the absorber 30.

That is, the refrigerant liquid line L3 including the second feed pump PR2, the third gate valve GV3, and the fourth gate valve GV4.
2 and the refrigerant liquid line L33 including the fifth gate valve GV5 are connected to a solution return line (solution line L10) for supplying the absorbing solution Y regenerated by the high-pressure regenerator 40 and the low-pressure regenerator 50 into the absorber 30. And, it functions as a refrigerant supply means capable of supplying the refrigerant liquid RL staying in the condenser 60 into the absorber 30 via the spray pipe 32).

Further, after being vaporized in the high-pressure regenerator 40, the refrigerant line L34 passes from the low-pressure regenerator 50 as a heat source for heating, and a refrigerant line L34 for guiding the condensed refrigerant liquid RL to the condenser 60. Forked. Refrigerant line L
Reference numeral 34 has a first flow control valve FV1 on the way, and its tip is connected to the absorber 30 side above the shell SL1. The first flow control valve FV1 is also configured as a remote control valve, and is connected to the control device 90 as shown in FIG. An orifice OF2 is arranged near the absorber inlet of the refrigerant line L34.

When the first flow control valve FV1 is opened via the control device 90, the flow rate of the high-temperature refrigerant liquid RL flowing out of the heat transfer pipe 51 of the low-pressure regenerator 50 is adjusted while the temperature of the high-temperature refrigerant liquid RL is controlled by the condenser 60. Can be fed into the absorber 30 without excessively decreasing. That is, the refrigerant line L including the first flow control valve FV1 and the orifice OF2
34 is a low-pressure regenerator 50 after vaporization in the high-pressure regenerator 40.
High-temperature refrigerant liquid R that has passed as a heat source for heating and condensed
It functions as a refrigerant feeding means that can adjust the flow rate of L and feed it into the absorber 30.

A refrigerant line L35 branches off from a refrigerant line L11 for supplying the refrigerant gas RG vaporized by the high-pressure regenerator 40 to the low-pressure regenerator 50 as a heat source. In this case, as shown in FIG. 1, the refrigerant line L11 is provided with a sixth gate valve (cooling / heating switching valve) GV6, and the refrigerant line L35 is provided on the upstream side of the sixth gate valve GV6 from the refrigerant line L11. Forked. The refrigerant line L35 is provided with a second flow control valve FV which is a remote control valve on the way.
2, the tip of which is located at the evaporator 20 above the shell SL1.
Connected to the side. The second flow control valve FV2 is also connected to the control device 90. An orifice OF3 is arranged near the evaporator inlet of the refrigerant line L35.

By closing the sixth gate valve GV6 and opening the second flow control valve FV2 via the control device 90, the evaporator can adjust the flow rate of the refrigerant gas RG vaporized by the high-pressure regenerator 40 while controlling the flow rate. 20 can be fed. That is, the second flow control valve FV2 and the orifice O
The refrigerant line L35 including F3 functions as a refrigerant supply unit capable of supplying the refrigerant gas RG vaporized by the high-pressure regenerator 40 into the evaporator 20 while adjusting the flow rate.

In addition, a three-way bypass valve VX is provided for the cooling water line including the heat transfer tube 31 and the cooling water lines L3 and L18 disposed in the absorber 30.
The bypass three-way valve VX is remotely controllable by the control device 90 and is capable of adjusting the flow rate of the fluid flowing into the two outlet ports, and the inlet port is connected to the cooling water line L3. Also, one outlet port of the bypass three-way valve VX is connected to the absorber inlet of the cooling water line, that is, the heat transfer tube 31, and the other outlet port is connected to the absorber outlet of the cooling water line via a pipe.
That is, it is connected to the junction of the heat transfer tube 21 and the cooling water line L18. The bypass three-way valve VX functions as a bypass unit that connects the absorber inlet and the absorber outlet of the cooling water line and changes the flow rate of the cooling water flowing into the absorber outlet side.

On the other hand, a chilled water inlet line L1, which constitutes a chilled water line arranged to pass through the evaporator 20,
Of the heat transfer tube 21 and the cold water outlet line L2, the cold water outlet line L2 is provided with a cold water outlet thermometer T1. As shown in FIG. 3, the cold water outlet thermometer T1 is connected to the control device 90, and measures the temperature of the cold water W1 flowing through the cold water line at the evaporator outlet (exit of the heat transfer tube 21). Is given to the control device 90.
Similarly, a cold water inlet thermometer T2 is connected to the cold water inlet line L1.
Is provided. The chilled water inlet thermometer T2 measures the temperature of the chilled water W1 flowing through the chilled water line at the evaporator inlet (the inlet of the heat transfer tube 21), and gives a signal indicating the measured value to the control device 90.

The solution line L8 connected to the high-pressure regenerator 40 is provided with a high re-outlet thermometer T3. This high re-outlet thermometer T3 is connected to the control device 90 via a signal line as shown in FIG. 3, and measures the temperature of the absorbing solution Y returned from the high-pressure regenerator 40 to the absorber 30. A signal indicating the measured value is provided to the control device 90.
Further, the high pressure regenerator 40 is provided with a high internal pressure gauge P for measuring the internal pressure. As shown in FIG. 3, the high pressure internal pressure gauge P is connected to a control device 90 via a signal line, and measures the internal pressure of the high pressure regenerator 40 to control a signal indicating a measured value. To the device 90. The exhaust gas line L7 for discharging the exhaust gas EG from the high-pressure regenerator 40 is provided with an exhaust gas thermometer T4. The exhaust gas thermometer T4 is also connected to the control device 90 via a signal line as shown in FIG. 3, and measures the temperature of the exhaust gas passing through the high-pressure regenerator 40 and outputs a signal indicating the measured value to the control device. Give to 90.

In addition, the high-pressure regenerator 40 and the low-pressure regenerator 5
A solution line L10 for returning the absorption solution Y from 0 to the absorber 30 is provided with an absorption inlet densitometer X.
As shown in FIG. 3, the absorption inlet concentration meter X is connected to the control device 90 via a signal line, and measures the concentration of the absorption solution Y returned to the absorber 30 at the inlet of the absorber 30,
A signal indicating the measured value is provided to the control device 90. Note that, instead of the absorption inlet concentration meter X, a pressure gauge, a thermometer, and an arithmetic unit (CPU 91) for calculating the concentration of the absorption solution Y based on the measured values of the pressure gauge and the thermometer may be used. It is possible. Thereby, the absorption refrigerator 10 and the CGS
Can be configured at low cost.

As shown in FIG. 3, the control unit 90 includes a CPU 91 for performing various arithmetic processes, a ROM 92 for storing programs for control and arithmetic processes in advance, a RAM 93 for storing various data for control and arithmetic operations, and the like. It is composed of Note that a sequencer may be used as the control device 90. The above-mentioned cold water outlet thermometer T1, cold water inlet thermometer T
2. The high re-outlet thermometer T3, the exhaust gas thermometer T4, the high re-inside pressure gauge P, and the absorption inlet concentration meter X measure the cold water temperature, solution temperature, exhaust gas temperature, inside pressure, and solution concentration at the respective locations. Then, a signal indicating the measured value is transmitted to the control device 90 (CP
U91). The control device 90 controls the cold water outlet thermometer T
1. Perform predetermined arithmetic processing based on signals received from the cold water inlet thermometer T2, the high re-outlet thermometer T3, the exhaust gas thermometer T4, the high re-inside pressure gauge P, and the absorption inlet concentration meter X. Feed pumps PR1 and PR2, gate valves GV1 to GV
V6, and controls the respective flow control valves FV1 and FV2 and the bypass three-way valve VX.

In the absorption chiller 10 configured as described above, the above-described refrigerant supply system is appropriately operated at the time of a load change or the like. This eliminates the need to control the amount of exhaust gas of the power generation unit 1 supplied as a heat source to the high-pressure regenerator 40 by using a large-diameter and expensive solenoid valve or the like, thereby reducing the manufacturing cost of the absorption refrigerator 10. It becomes possible.

Next, with reference to FIGS. 4 to 6, an operation method of the absorption refrigerator 10 constituting the above-described CGS when the load is changed will be described.

Normally, during the operation of the absorption refrigerator 10, only the sixth gate valve GV6 among the above-mentioned gate valves GV1 to GV6 is open, and the respective flow control valves FV1 and FV2 are closed. The bypass three-way valve VX is set to connect the cooling water line L3 and the heat transfer tube 31, and the feed pumps PR1 and PR2 are stopped. In addition, cold water outlet thermometer T1, cold water inlet thermometer T2, high re-outlet thermometer T
3. From the exhaust gas thermometer T4, the high pressure inside pressure gauge P, and the absorption inlet concentration meter X, signals indicating the respective measured values are sent to the control device 90 (CPU 91).

On the other hand, when a load change occurs during the operation of the absorption refrigerator 10, for example, when the required amount of cooling heat decreases during the cooling operation, the control device 90 is not provided with load setting means (not shown). For example, a command signal indicating that control corresponding to the load change should be started is given. In response to this, the control device 90 opens the first gate valve GV1 and activates the first feed pump PR1. When the first feed pump PR1 is operated, the refrigerant liquid RL staying in the evaporator 20
Is supplied to the inside of the absorber 30 via a refrigerant liquid line L30 shown by a white line in FIG.

When the first feed pump PR1 is operated, the control device 90 (CPU 91) performs feedback control of the first feed pump PR1 based on the measurement value of the cold water outlet thermometer T1, and also controls the cold water inlet thermometer. The first feed pump PR1 is feedforward controlled based on the measured value of T2. In other words, the control device 90 gives a predetermined operation signal to the first feed pump PR1 so that the temperature of the cold water W1 at the evaporator outlet becomes a desired temperature according to the required amount of heat and the like, and at the same time, the cold water W1 at the evaporator inlet. A predetermined operation signal is given to the first feed pump PR1 so that the temperature becomes a desired temperature corresponding to a required heat amount or the like. Thereby, the first feed pump PR1 adjusts the flow rate of the refrigerant liquid RL to be fed from the evaporator 20 to the absorber 30 according to the signal received from the control device 90.

As described above, when the refrigerant liquid RL is fed from the evaporator 20 to the absorber 30 by the first feed pump PR1, the absorbing solution Y inside the absorber 30 becomes the evaporator outlet temperature of the cold water W1. Will be diluted accordingly. This allows
As the internal pressure of the absorber 30 increases, the saturation temperature in the evaporator 20 increases, and the evaporator outlet of the chilled water W1 flowing through the chilled water line (heat transfer tube 21) arranged to pass through the evaporator 20. The temperature will also increase in accordance with the dilution amount of the absorbing solution Y in the absorber 30. At this time, by reducing the flow rate of the chilled water, the total amount of heat can be reduced while maintaining the chilled water temperature as it is. As described above, the absorption refrigerator 10 can be controlled so as to follow load fluctuations, that is, changes in the required heat quantity with high accuracy.

In the absorption chiller 10, the first feed pump PR1 is feedback-controlled based on the temperature of the chilled water W1 at the evaporator outlet (chilled water outlet line L2) of the chilled water line, and evaporates the chilled water line. Since the feedforward control is performed based on the temperature of the chilled water W1 at the vessel inlet (the chilled water inlet line L1), the ability to follow a load change is further improved.

Further, the control device 90 closes the first gate valve GV1 at a predetermined timing, and then controls the second gate valve GV1.
V2 is opened and the first feed pump PR1 is operated. Thus, the refrigerant liquid RL staying in the evaporator 20
Is supplied into the absorber 30 through the refrigerant liquid line L31, the solution line L10, and the spray pipe 32 shown in FIG. 4 by the first feed pump PR1 while the flow rate is adjusted. You. As a result, it is possible to directly dilute the absorbing solution Y sprayed into the absorber 30 from the spraying pipe 32, so that it is possible to further improve the ability to follow a load change.

When the absorption refrigerator 10 is operated in a light load state in which the amount of generated heat is set to, for example, 25% or less of the maximum, the control corresponding to the light load should be started from a load setting means (not shown). Is issued to the control device 90. In response to this, the control device 90 closes each of the gate valves GV1 to GV5 and the second flow control valve FV2, stops each of the feed pumps PR1 and PR2, and then stops the first flow control valve FV1. Release. When the first flow control valve FV1 is opened, the heat transfer tube 5 of the low-pressure regenerator 50 is opened.
The refrigerant liquid RL that condenses after passing through 1 is supplied to the inside of the absorber 30 via a refrigerant line L34 indicated by a white line in FIG.

When the first flow control valve FV1 is opened, the control device 90 (CPU 91) performs feedback control of the opening of the first flow control valve FV1 based on the measurement value of the chilled water outlet thermometer T1 and also controls the chilled water. Based on the measured value of the inlet thermometer T2, the opening of the first flow control valve FV1 is feedforward controlled. That is, the control device 90 controls the cold water W
An operation signal indicating the degree of opening such that the temperature at the evaporator outlet of the first evaporator becomes a desired temperature according to the required heat amount or the like is given to the first flow control valve FV1, and the temperature of the cold water W1 at the evaporator inlet is the required heat amount or the like. To the first flow control valve FV1. As a result, the opening of the first flow control valve FV1 is adjusted according to the signal received from the control device 90.

As described above, when the refrigerant liquid RL condensed after passing through the low-pressure regenerator 50 via the first flow control valve FV1 is supplied to the absorber 30, the absorbing solution Y inside the absorber 30 becomes It is diluted according to the evaporator outlet temperature of the cold water W1. In this case, since the refrigerant liquid RL to be introduced into the condenser 60 is taken out from the low-pressure regenerator 50, the amount of the refrigerant liquid generated in the condenser 60 is also reduced. Therefore, the evaporator outlet temperature of the chilled water W1 flowing through the chilled water line increases according to the dilution amount of the absorbing solution Y in the absorber 30 and the amount of the refrigerant liquid RL reduced in the condenser 60. Accordingly, even during a light load operation in which the generated heat amount is set to, for example, 25% or less of the maximum time, the absorption refrigerator 10 is configured to follow the load fluctuation, that is, the change in the required heat amount with high accuracy. It becomes possible to control.

The first flow control valve FV1 is connected to the chilled water W at the evaporator outlet (chilled water outlet line L2) of the chilled water line.
Feedback control based on the temperature of
Since feedforward control is performed based on the temperature of the chilled water W1 at the evaporator inlet (chilled water inlet line L1) of the chilled water line, the ability to follow load fluctuations is further improved.

When the refrigerant liquid RL is supplied from the low-pressure regenerator 50 to the absorber 30, the refrigerant line L34 and the solution line L10 are connected, and the refrigerant liquid RL from the low-pressure regenerator 50 is absorbed from the spray tube 32. It may be configured to be introduced into the vessel 30 (see a two-dot chain line in FIG. 5). Under such a configuration, since the high-temperature refrigerant liquid RL can be introduced into the spray tube 32, it is effective in preventing the absorption solution Y from freezing in the spray tube 32.

Further, when the absorption refrigerator 10 is operated in a very light load state in which the amount of generated heat is set to, for example, 15% or less of the maximum during the cooling operation, the load setting means (not shown) can handle the light load. A command signal to start the performed control is issued to control device 90. In response to this, the control device 90 closes each of the gate valves GV1 to GV5 and each of the flow rate adjustment valves FV1 and FV2, stops each of the feed pumps PR1 and PR2, and then stops the bypass three-way valve VV.
X is given an operation signal to switch the flow direction of the cooling water W2 to the absorber outlet side (the cooling water line L18 side) of the cooling water line. The bypass three-way valve VX connects the absorber inlet and the absorber outlet of the cooling water line.

The controller 90 feedback-controls the opening of the bypass three-way valve VX based on the measurement value of the chilled water outlet thermometer T1, and controls the bypass three-way valve VX based on the measurement value of the chilled water inlet thermometer T2. Feed-forward control of the opening of VX is performed. That is, the control device 90 provides the bypass three-way valve VX with an operation signal indicating an opening degree such that the temperature of the cold water W1 at the evaporator outlet becomes a desired temperature corresponding to the required heat amount and the like, and the evaporator inlet of the cold water W1. Is given to the bypass three-way valve VX indicating the degree of opening such that the temperature at becomes the desired temperature corresponding to the required amount of heat. The bypass three-way valve VX adjusts its opening degree, that is, the flow rate of the cooling water W2 circulated to the absorber outlet side, according to the signal received from the control device 90.

As a result, the flow rate of the cooling water W2 flowing from the cooling water line L3 to the absorber outlet side increases,
Since the flow rate of the cooling water W2 flowing in the heat transfer tube 31 disposed inside the heat transfer tube 31 decreases, the amount of heat recovered by the cooling water W2 flowing in the heat transfer tube 31 decreases. Therefore, the amount of the refrigerant R absorbed by the absorbing solution Y inside the absorber 30 decreases, and the amount of the refrigerant liquid RL generated in the condenser 60 decreases, so that the evaporation of the chilled water W1 flowing through the chilled water line evaporates. The outlet temperature of the vessel is reduced according to the amount of the refrigerant liquid reduced in the condenser 60. As a result,
It becomes possible to control the absorption refrigerator 10 so as to follow the load fluctuation during the cooling operation, that is, the change in the required heat quantity with high accuracy.

Also in this case, the bypass three-way valve VX
Is feedback-controlled based on the temperature of the chilled water W1 at the evaporator outlet of the chilled water line (chilled water outlet line L2), and is feedforward based on the temperature of the chilled water W1 at the evaporator inlet of the chilled water line (chilled water inlet line L1). Since the control is performed, the followability to the load fluctuation is further improved.

On the other hand, the absorption refrigerator 10 enables not only the cooling operation but also the heating operation. When the absorption chiller 10 performs the heating operation, a command signal indicating that the heating operation should be started is issued to the control device 90 from a load setting unit (not shown) or the like. In response, the control device 90
Are the gate valves GV1 to GV5 and the second flow control valve F
V2 is closed and each feed pump PR1, PR2
Is stopped, and as shown in FIG. 6, the sixth gate valve GV
6 is closed and the second flow control valve FV2 is opened.

When the sixth gate valve GV6 is closed, the flow of the high-temperature refrigerant gas RG from the high-pressure regenerator 40 to the low-pressure regenerator 50 is stopped. When the second flow control valve FV2 is opened, the high-pressure regenerator 40 is opened.
The high-temperature refrigerant gas RG vaporized in the evaporator 20 (shell S) through a refrigerant line L35 indicated by an outline in FIG.
L1).

Further, the control device 90 controls the cold water outlet thermometer T
Based on the measured value of 1, the opening of the second flow control valve FV2 is feedback-controlled, and based on the measured value of the cold water inlet thermometer T2, the opening of the second flow control valve FV2 is feedforward controlled. That is, the control device 90
An operation signal indicating the degree of opening such that the temperature of the cold water (actually, hot water) W1 at the evaporator outlet attains a desired temperature corresponding to the required amount of heat or the like is given to the second flow control valve FV2, and the evaporator of the cold water W1 An operation signal indicating the degree of opening such that the temperature at the inlet becomes a desired temperature according to the required amount of heat or the like is given to the second flow control valve FV2.

The second flow control valve FV 2 adjusts its opening degree, that is, the flow rate of the refrigerant gas RG supplied to the evaporator 30 from the high-pressure regenerator 40, in accordance with a signal received from the control device 90. As a result, the chilled water line (heat transfer tube 21)
Water flowing through the evaporator 20 from the high-pressure regenerator 40
Since the temperature is increased by being heated by the refrigerant gas RG fed into the inside, the cold water W1 (hot water) flowing out from the cold water line can be used for heating.

When the refrigerant gas RG is supplied from the high-pressure regenerator 40 to the absorber 30, the refrigerant line L35 and the solution line L10 are connected, and the refrigerant gas RG from the high-pressure regenerator 40 is absorbed from the spray tube 32. It may be configured to be introduced into the vessel 30 (see a two-dot chain line in FIG. 6). Under such a configuration, the high temperature refrigerant gas RG is
2 can be introduced into the spray pipe 32 at a location where crystals are most likely to be generated, that is, a solution line L1 through which a low-temperature concentrated solution flows and a concentrated solution line within the low-temperature heat exchanger 70 where rare crystals are generated. Heating can be performed via the solution line L4. Therefore, it is effective in preventing or canceling the freezing of the absorbing solution Y.

If a load change (reduction in required heat quantity) occurs during such a heating operation, the control unit 90
Sets the flow direction of the cooling water W2 relative to the bypass three-way valve VX to the absorber outlet side of the cooling water line (the cooling water line L18
Side). This allows
The bypass three-way valve VX connects the absorber inlet and the absorber outlet of the cooling water line. The control device 90 feedback-controls the opening degree of the bypass three-way valve VX based on the measurement value of the chilled water outlet thermometer T1, and opens the bypass three-way valve VX based on the measurement value of the chilled water inlet thermometer T2. Feed forward control the degree.

That is, the control device 90 sends an operation signal indicating an opening degree at which the temperature of the cold water W1 at the evaporator outlet reaches a desired temperature corresponding to the required heat quantity or the like.
And an operation signal indicating an opening degree such that the temperature of the cold water W1 at the inlet of the evaporator becomes a desired temperature corresponding to the required amount of heat or the like to the bypass three-way valve VX. This allows
The bypass three-way valve VX adjusts its opening degree, that is, the flow rate of the cooling water W2 circulated to the absorber outlet side, according to the signal received from the control device 90.

In this case, when the high-temperature refrigerant gas RG is supplied from the high-pressure regenerator 40 to the evaporator 20, the high-temperature refrigerant gas RG also flows into the absorber 30 communicating with the evaporator 20.
Further, when the flow rate of the cooling water W2 flowing into the absorber outlet side (cooling water line L18) is reduced, the flow rate of the cooling water W2 flowing through the heat transfer pipe 31 disposed inside the absorber 30 increases. Then, the cooling water W2 is passed through the absorber 30 (shell SL1) and condensed by passing the cooling water W2, so that the heat quantity of the refrigerant gas RG discharged from the cooling tower also increases. Therefore, by controlling the bypass three-way valve VX during the heating operation, it becomes possible to control the absorption refrigerator 10 so as to follow load fluctuations, that is, changes in the required heat quantity with high accuracy.

In the absorption refrigerator 10 incorporated in the CGS, the concentration of the absorption solution Y in the solution line L10 is monitored by the absorption inlet densitometer X. Therefore, in the absorption refrigerator 10, the absorption inlet concentration meter X
It is also possible to perform a so-called crystallization prevention operation of diluting when the concentration approaches the concentration at which the absorption solution Y is crystallized, based on the measured value of. In this case, the refrigerant liquid RL in the evaporator 20
Alternatively, the refrigerant liquid RL from the low-pressure regenerator 50 may be supplied to the inside of the absorber 30 or to the spray tube 32. Further, after the high-pressure regenerator 40 is stopped, the refrigerant liquid R
L may be fed to the inside of the absorber 30 or to the scatter tube 32. In particular, since the refrigerant liquid RL in the condenser 60, the refrigerant liquid RL from the low-pressure regenerator 50, and the refrigerant gas RG from the high-pressure regenerator 40 have high temperatures, it is effective in preventing crystallization of the absorption solution Y. And the high temperature refrigerant liquid R
If L or the like is introduced into the evaporator 20, it is possible to effectively prevent the refrigerant R and the cold water W1 in the heat transfer tube 21 from freezing in the evaporator 20. If such a refrigerant liquid RL or the like is fed to the spray tube 32, the cold water W1
It is possible to extremely effectively prevent the freezing phenomenon in the evaporator 20 (heat transfer tube 21), which easily freezes.

In addition, in the absorption refrigerator 10, the temperature of the absorbing solution Y at the high pressure regenerator outlet measured by the high re-outlet thermometer T3 and the temperature of the high pressure regenerator 40 measured by the high re-internal pressure gauge P are measured. Based on the internal pressure, the evaporator 20
The refrigerant liquid RL in the condenser, the refrigerant liquid RL in the condenser 60, the refrigerant liquid RL from the low-pressure regenerator 50, or the refrigerant gas RG from the high-pressure regenerator 40 are supplied to the inside of the absorber 30 or to the spray pipe 32. By sending the solution, the solution temperature of the high-pressure regenerator 40 can be lowered to the corrosion limit temperature or lower, and the corrosion of the shell SL1 and the like can be prevented.

In the absorption refrigerator 10, the temperature of the absorbing solution Y at the outlet of the high pressure regenerator measured by the high re-outlet thermometer T3 and the temperature of the exhaust gas EG at the outlet of the high pressure regenerator measured by the exhaust gas thermometer T4. The refrigerant liquid RL in the evaporator 20, the refrigerant liquid RL in the condenser 60, the refrigerant liquid RL from the low-pressure regenerator 50, or the refrigerant gas RG from the high-pressure regenerator 40 is By feeding inside or to the spray tube 32, so-called overload can also be prevented.

Further, in the absorption refrigerator 10, the chilled water W1 at the evaporator outlet is measured by the chilled water outlet thermometer T1.
And the refrigerant liquid RL in the evaporator 20 and the refrigerant liquid RL in the condenser 60, based on the temperature of the exhaust gas EG measured at the outlet of the high-pressure regenerator measured by the exhaust gas thermometer T4.
The refrigerant liquid RL from the low-pressure regenerator 50 or the high-pressure regenerator 4
By supplying the refrigerant gas RG from 0 to the inside of the absorber 30 or to the spray tube 32, it is also possible to shorten the start / stop time of each device.

[0090]

The absorption chiller and the cogeneration system according to the present invention are configured as described above, and have the following effects. That is, by feeding the refrigerant liquid staying in the evaporator or the condenser, the refrigerant liquid condensed after passing through the low-pressure regenerator, or the refrigerant gas vaporized by the high-pressure regenerator into the absorber while adjusting the flow rate. In addition, it is possible to realize an absorption refrigerator and a cogeneration system which have high follow-up performance with respect to load fluctuation and operation controllability and can be configured at low cost.

[Brief description of the drawings]

FIG. 1 is a perspective view showing a cogeneration system according to the present invention.

FIG. 2 is a system diagram of the cogeneration system shown in FIG.

FIG. 3 is a control block diagram of an absorption refrigerator incorporated in the cogeneration system shown in FIG.

FIG. 4 is a system diagram for explaining an operation method of the absorption chiller incorporated in the cogeneration system shown in FIG. 1 when a load changes.

FIG. 5 is a system diagram for explaining an operation method when the load of the absorption refrigerator incorporated in the cogeneration system shown in FIG. 1 changes.

FIG. 6 is a system diagram for describing a heating operation method of the absorption refrigerator incorporated in the cogeneration system shown in FIG.

[Explanation of symbols]

CGS: Cogeneration system, 1: Power generation unit, 2: Generator, 3: Gas engine, 4: Cooling tower, 5:
Duct, 10: absorption refrigerator, 20: evaporator, 21: heat transfer tube (cold water line), 22: spray tube, 30: absorber, 30
... evaporator, 31 ... heat transfer tube (cooling water line), 32 ... spray tube, 40 ... high pressure regenerator, 41 ... heat transfer tube, 50 ... low pressure regenerator, 51, 52 ... heat transfer tube, 60 ... condenser, 61 ... Heat transfer tube, 70 ... low temperature heat exchanger, 75 ... high temperature heat exchanger, 90 ...
Control device, EG: exhaust gas, EW: cooling water (cooling fluid),
FV0: Flow control valve, FV1: First flow control valve, FV2
... Second flow control valve, GV1, GV2, GV3, GV4
GV5, GV6: gate valve, VX: bypass three-way valve, L1
... Cold water inlet line (cold water line), L2 ... Cold water outlet line (cold water line), L3, L18 ... Cooled water line, L
8, L10: solution line, L11, L17, L19: refrigerant line, L30, L31, L32, L33: refrigerant liquid line, L34, L35: refrigerant line, OF1, OF2
OF3: orifice, P: high pressure inside the pressure gauge, PR1: first feed pump, PR2: feed pump, PW: feed pump, PY: solution pump, R: refrigerant, RG: refrigerant gas, R
L: refrigerant liquid, SL1: shell, SL2: shell, T1 ...
Chilled water outlet thermometer, T2: Chilled water inlet thermometer, T3: High re-outlet thermometer, T4: Exhaust gas thermometer, X: Absorption inlet concentration meter,
W1: cold water, W2: cooling water, Y: absorbing solution.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Akihiro Kawada 2-1-1, Shinhama, Arai-machi, Takasago City, Hyogo Prefecture Inside the Takasago Research Laboratory, Mitsubishi Heavy Industries, Ltd. (72) Inventor Takayuki Irie 2-1-1, Araimachi, Takarai City, Hyogo Prefecture No. 1 Inside the Mitsubishi Heavy Industries, Ltd. Takasago Research Laboratory (72) Inventor Shoji Watanabe 2-1-1, Araimachi Shinhama, Takasago City, Hyogo Prefecture Inside the Mitsubishi Heavy Industries, Ltd. Takasago Research Laboratory (72) Inventor Masayoshi Toyofuku Araimachi Niihama, Takasago City, Hyogo Prefecture 2-1-1, Mitsubishi Heavy Industries, Ltd. Takasago Research Laboratory (72) Inventor Kazuki Wajima 2-1-1, Araimachi Shinhama, Takasago City, Hyogo Prefecture Mitsubishi Heavy Industries, Ltd. Takasago Research Laboratory F-term (reference) 3L093 BB11 BB26 EE04 EE11 EE14 EE17 EE25 GG01 GG02 GG07 HH08 HH15 JJ02 JJ06 KK03

Claims (12)

[Claims] 1. A refrigerant vaporized by an evaporator is absorbed by an absorption solution by an absorber, the absorption solution and the refrigerant are separated by a regenerator, and the separated refrigerant is condensed by a condenser and then recondensed by an evaporator. In an absorption refrigerator for vaporizing, a chilled water line arranged to pass through the evaporator and circulating chilled water; a temperature measuring unit for measuring a temperature of chilled water at an evaporator outlet of the chilled water line; Refrigerant supply means capable of supplying the inside of the absorber while adjusting the flow rate of the refrigerant liquid staying in the vessel, and control means for controlling the refrigerant supply means based on a measurement value of the temperature measurement means. An absorption refrigerator comprising: 2. The apparatus according to claim 1, further comprising: a second refrigerant supply unit configured to supply the refrigerant gas vaporized by the high-pressure regenerator to the evaporator while adjusting a flow rate of the refrigerant gas. The absorption refrigerator according to claim 1, wherein the second refrigerant supply unit is controlled based on a value. 3. A cooling water line, which is arranged to pass through the absorber and through which cooling water flows, communicates an absorber inlet and an absorber outlet of the cooling water line, and the absorber A bypass unit configured to change a flow rate of the cooling water flowing into the outlet side, wherein the control unit controls the bypass unit based on a measurement value of the temperature measurement unit. 1 or 2
2. The absorption refrigerator according to 1. 4. The refrigerant vaporized by the evaporator is absorbed by the absorption solution by the absorber, the absorption solution and the refrigerant are separated by the high-pressure regenerator and the low-pressure regenerator, and the separated refrigerant is condensed by the condenser. Then, in an absorption refrigerator that is vaporized again by an evaporator, a chilled water line that is arranged to pass through the evaporator and circulates chilled water, and a temperature at which the temperature of the chilled water is measured at an evaporator outlet of the chilled water line. Measuring means, a refrigerant feeding means capable of feeding the inside of the absorber while adjusting the flow rate of the refrigerant gas passed through the low-pressure regenerator as a heat source and condensing the refrigerant gas, based on a measurement value of the temperature measuring means, A control unit for controlling a refrigerant feeding unit. 5. The refrigerant vaporized by the evaporator is absorbed by the absorption solution in the absorber, the absorption solution and the refrigerant are separated by the regenerator, and the separated refrigerant is condensed by the condenser, and then again by the evaporator. In the absorption refrigerator to be vaporized, a chilled water line arranged to pass through the evaporator and circulating chilled water; a temperature measuring means for measuring a chilled water temperature at an evaporator outlet of the chilled water line; A cooling water line that is disposed so as to pass through the inside of the vessel, and allows the cooling water to flow therethrough, and connects the absorber inlet and the absorber outlet of the cooling water line, and the cooling water flowing into the absorber outlet side. An absorption refrigerator comprising: a bypass unit that can change a flow rate; and a control unit that controls the bypass unit based on a measurement value of the temperature measurement unit. 6. A power generation unit and an absorption refrigerator are combined, and the power generation unit generates electric power, and the absorption refrigerator uses an exhaust heat of the power generation unit to separate an absorption solution and a refrigerant. Then, after condensing the separated refrigerant, in a cogeneration system that obtains cold heat by vaporizing, the absorption refrigerator includes a condenser that condenses the refrigerant separated from the absorption solution, and a condenser that condenses in the condenser. An evaporator for vaporizing the refrigerant, an absorber for absorbing the refrigerant vaporized by the evaporator into an absorbing solution, and a high-pressure regeneration for heating the absorbing solution supplied from the absorber using exhaust gas discharged from the power generation unit as a heat source. A low-pressure heating device that heats the absorbing solution supplied from the absorber using the cooling fluid flowing through the power generation unit and the refrigerant gas vaporized by the high-pressure regenerator as heat sources. A pressure regenerator, a chilled water line arranged to pass through the inside of the evaporator, and a chilled water line for flowing chilled water; a temperature measuring means for measuring the temperature of the chilled water at an evaporator outlet of the chilled water line; Refrigerant supply means capable of supplying the refrigerant liquid staying in the absorber while adjusting the flow rate thereof, and control means for controlling the refrigerant supply means based on a measurement value of the temperature measurement means. Cogeneration system characterized by the following. 7. The apparatus according to claim 1, further comprising a second refrigerant supply unit capable of supplying the refrigerant gas vaporized by the high-pressure regenerator into the evaporator while adjusting a flow rate of the refrigerant gas, wherein the control unit performs measurement by the temperature measurement unit. The cogeneration system according to claim 6, wherein the second refrigerant supply means is controlled based on the value. 8. A cooling water line, which is arranged so as to pass through the inside of the absorber and through which cooling water flows, communicates an inlet and an outlet of the cooling water line with the absorber, and the absorber A bypass unit configured to change a flow rate of the cooling water flowing into the outlet side, wherein the control unit controls the bypass unit based on a measurement value of the temperature measurement unit. 6 or 7
The cogeneration system according to 1. 9. A power generation unit and an absorption refrigerator are combined, and the power generation unit generates electric power, and the absorption refrigerator uses an exhaust heat of the power generation unit to separate an absorption solution and a refrigerant. Then, after condensing the separated refrigerant, in a cogeneration system that obtains cold heat by evaporating, the absorption refrigerator includes: a condenser that condenses the refrigerant separated from the absorption solution; and a condenser that condenses in the condenser. An evaporator for evaporating the refrigerant, an absorber for absorbing the refrigerant vaporized by the evaporator into an absorbing solution, and a high-pressure regeneration for heating the absorbing solution supplied from the absorber using exhaust gas discharged from the power generation unit as a heat source. And a heater for heating the absorbing solution supplied from the absorber using the cooling fluid flowing through the power generation unit and the refrigerant gas vaporized by the high-pressure regenerator as heat sources. A pressure regenerator, a chilled water line arranged to pass through the evaporator, and circulating chilled water; a temperature measuring means for measuring the temperature of the chilled water at an evaporator outlet of the chilled water line; and the low-pressure regenerator A refrigerant supply unit capable of supplying the inside of the absorber while adjusting the flow rate and condensing the refrigerant gas passed as a heat source, and controlling the refrigerant supply unit based on a measurement value of the temperature measurement unit. And a cogeneration system. 10. A power generation unit and an absorption refrigerator are combined, and the power generation unit generates electric power, and the absorption refrigerator uses an exhaust heat of the power generation unit to separate an absorption solution and a refrigerant. Then, after condensing the separated refrigerant, in a cogeneration system that obtains cold heat by vaporizing, the absorption refrigerator includes a condenser that condenses the refrigerant separated from the absorption solution, and a condenser that condenses in the condenser. An evaporator for vaporizing the refrigerant, an absorber for absorbing the refrigerant vaporized by the evaporator into an absorbing solution, and a high-pressure regeneration for heating the absorbing solution supplied from the absorber using exhaust gas discharged from the power generation unit as a heat source. Heating the absorption solution supplied from the absorber using the cooling fluid flowing through the power generation unit and the refrigerant gas vaporized by the high-pressure regenerator as heat sources. A low-pressure regenerator, a chilled water line that is arranged to pass through the evaporator, and circulates chilled water; a temperature measuring unit that measures the temperature of the chilled water at an evaporator outlet of the chilled water line; Are arranged so as to pass through, a cooling water line for flowing the cooling water, and communicating the absorber inlet and the absorber outlet of the cooling water line, the flow rate of the cooling water flowing into the absorber outlet side A cogeneration system comprising: a bypass unit that can be changed; and a control unit that controls the bypass unit based on a measurement value of the temperature measurement unit. 11. A refrigerant vaporized by an evaporator is absorbed by an absorption solution by an absorber, and the absorption solution and the refrigerant are separated by a regenerator.
After the separated refrigerant is condensed in the condenser, it is vaporized again in the evaporator to obtain cold water for cooling or hot water for heating, and is arranged so as to pass through the evaporator. A cold / hot water line through which cold water or hot water flows, a temperature measuring means for measuring the temperature of the cold or hot water at the evaporator outlet of the cold / hot water line, and the absorption while adjusting the flow rate of the refrigerant liquid retained in the evaporator. A first refrigerant feeding means capable of feeding into the vessel, a second refrigerant feeding means capable of feeding into the evaporator while adjusting a flow rate of the refrigerant gas vaporized by the high-pressure regenerator, and the temperature An absorption refrigeration / heating machine comprising: a control unit that controls the first refrigerant supply unit or the second refrigerant supply unit based on a measurement value of a measurement unit. 12. A cooling water line through which cooling water flows, the cooling water line being arranged to pass through the absorber, an absorber inlet and an absorber outlet of the cooling water line communicate with each other, and the absorber A bypass unit configured to change a flow rate of the cooling water flowing into the outlet side, wherein the control unit controls the bypass unit based on a measurement value of the temperature measurement unit. 12. The absorption refrigerating and heating machine according to 11.