JP2003065628A - Absorption refrigerating machine, equipment using absorption refrigerating machine and gas turbine suction air cooling device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an absorption refrigerating machine which prevents cooled water from coming into a supercooled state even when a cooling load lessens sharply, and thus can safely stop an operation. SOLUTION: In the absorption refrigerating machine 1, refrigerant gas produced by evaporation of a liquid refrigerant spread on an evaporator tube (tube group) in an evaporator 10 is absorbed and dissolved in a solution in an absorber 20, a dilute solution coming out from the absorber 20 is regenerated as a high-temperature and high-density solution by heating and this high-density solution is returned to the absorber 20. In this machine, a steam control valve 3 is provided for steam piping 4 supplying steam for heating the dilute solution.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an absorption refrigerating machine, an equipment using the absorption refrigerating machine, and a gas turbine intake air cooling device using the absorption refrigerating machine, and more particularly, to a supercooling when a cooling load is sharply reduced. The present invention relates to a technology for protecting an absorption refrigerator.

[0002]

2. Description of the Related Art An absorption refrigerating machine is a refrigerating machine using water as a refrigerant, a lithium bromide solution as an absorbent and steam, exhaust gas, gas fuel or oil fuel as an energy source (heat source) for heating. This absorption refrigerator has an evaporator, an absorber, a regenerator, and a condenser as main members, and the inside of the evaporator and the absorber are kept in a high vacuum (absolute pressure of 6 to 7 mmHg). There is.

In this evaporator, the liquid refrigerant (water) sent from the refrigerant pump is sprayed toward a group of evaporator tubes through which cold water (for example, 12 ° C.) flows, so that the liquid refrigerant is heated. And becomes refrigerant vapor (gas). That is, since the evaporator is a high vacuum container, liquid water (refrigerant) boils at around 4 to 6 ° C. and evaporates and vaporizes.
For example, 12 ° C. cold water can be used as heat source water.

The cold water that has exchanged heat with the liquid refrigerant (water) is cooled by the latent heat of vaporization given to the liquid refrigerant (for example, becomes 7 ° C.) and then flows out from the evaporator to the cold water system.
The cold water whose temperature has been lowered (for example, to 7 ° C.) is sent to various cooling loads such as cooling devices in various plants such as cooling devices for buildings and intake cooling devices for gas turbines to be used as cold heat. To be done. In addition,
The cold water used as cold heat rises in temperature (for example, 12
℃) and again flow into the evaporator tube of the evaporator,
After that, it circulates through the cold water system.

On the other hand, in the absorber, the refrigerant vapor generated in the evaporator is absorbed by the lithium bromide solution. The lithium bromide solution which has absorbed water and has a low concentration (hereinafter referred to as "diluted lithium bromide solution") is collected at the bottom of the absorber. In this absorber, the latent heat of condensation when the refrigerant vapor is absorbed by the lithium bromide solution and changes from gas (water vapor) to liquid (water) and when the concentration of the lithium bromide solution absorbs water and becomes thin Since heat of dilution is generated, these heats are removed by cooling water (which is circulated in a system different from the above "cold water"). Since the lithium bromide solution has a partial vapor pressure of water lower than that of saturated vapor of water, it is highly hygroscopic and is a suitable substance for absorbing refrigerant vapor.

In the regenerator, the dilute solution of lithium bromide sent from the absorber is heated. Therefore, a part of the refrigerant in the dilute solution of lithium bromide is vaporized, and the solution is a concentrated lithium bromide solution (hereinafter, "concentrated solution of lithium bromide").
Will be called). The concentrated solution of lithium bromide whose concentration has been increased to the original state is sent to the absorber and absorbs the refrigerant vapor again. On the other hand, the evaporated refrigerant vapor is sent to the condenser.

In an actual machine, a double-effect absorption refrigerating machine having a regenerator arranged in two stages is used for the purpose of increasing thermal efficiency and reducing heating energy. In this double-effect absorption refrigerator, as a regenerator, the combustion gas obtained by burning the supplied fuel or the high temperature steam or exhaust gas is introduced as a heat source to heat the diluted solution of lithium bromide. And a low pressure regenerator that heats the dilute lithium bromide solution using the high temperature refrigerant vapor generated in the high pressure regenerator as a heating source.

Further, in the condenser, the refrigerant vapor sent from the regenerator is cooled by cooling water to be condensed and liquefied. The condensed water is supplied to the evaporator again as a liquid refrigerant (water).

As described above, in the absorption refrigerator, the refrigerant (water) is used.
Changes with water-steam-water (change of phase), and the lithium bromide solution changes with concentrated solution-dilute solution-concentrated solution (change of concentration). The absorption refrigerator cools during the above-described phase change (refrigerant) and concentration change (lithium bromide solution).
This is an apparatus for repeatedly producing the action of producing cold water by latent heat of vaporization of water and absorbing water vapor by the absorption capacity of a lithium bromide solution in a high vacuum closed system.

In such an absorption refrigerating machine, the heating amount is increased by increasing the supply amount of a heat source such as fuel or steam to be supplied to the high pressure regenerator, and the concentration of the lithium bromide solution is increased so that the absorption refrigerating device is discharged from the evaporator. You can lower the temperature of some cold water. On the contrary, the temperature of cold water flowing out of the evaporator is raised by reducing the heating amount by reducing the supply amount of the heat source such as fuel and steam supplied to the high-pressure regenerator and diluting the concentration of the lithium bromide solution. be able to. In this way, by adjusting the concentration of the lithium bromide solution, the temperature of the cold water is controlled and the temperature of the cold water flowing out of the evaporator is set to the set temperature (for example, 7 ° C).

Here, as an example of a device utilizing the cold heat of the absorption refrigerating machine described above, the structure of a gas turbine intake cooling device will be briefly described with reference to FIG. In the figure, reference numeral 1 is an absorption refrigerator, 3 is a steam control valve, 4 is steam piping, and 70
Is a gas turbine, 71 is a compressor, 72 is a turbine, 73
Is a combustor, 74 is an intake air cooler, 80 is a generator, 81 is an exhaust gas boiler, P4 is a cold water pump, and P5 is a cooling water pump. The gas turbine 70 burns fuel together with the intake air compressed by the compressor 71 in the combustor 73, and the combustor 7
The high temperature combustion gas generated in 3 is supplied between the moving blades and the stationary blades of the turbine 72 to be expanded, and the turbine 72 is rotated to obtain the shaft output. This gas turbine 7
0 has an intake air cooler 74 for improving the output, and receives cold water from the absorption refrigerator 1 as cold heat used in the intake air cooler 74.

[0012]

By the way, when stopping the operation of the above-mentioned absorption refrigerating machine, an operation stopping method of gradually narrowing down the heat source is generally adopted as compared with the conventional method. Therefore, it takes a certain amount of time before the absorption refrigerator is brought into the stopped state in which the cooling capacity is not generated. Such a conventional shutdown method does not pose any particular problem except that it takes a long time to complete the shutdown in normal operation.

However, when the cooling load is suddenly reduced, for example, when the chilled water pump is stopped due to a disaster such as an earthquake, the operation speed of the absorption chiller cannot keep up and the chilled water may be overcooled. Such supercooling is performed in a pipe of a cold water system that circulates cold water,
There is a problem of freezing cold water. In particular, the tube (tube group) in the evaporator receives a large amount of supercooling and, in addition to being advantageous in terms of heat exchange efficiency, a tube with a relatively small diameter is used. There is a concern that cold water is likely to freeze, and once frozen, expanded cold water (ice) causes tube rupture.

Also, in a cooling device of various plants such as a device that uses cold water supplied from an absorption refrigerator as a cold heat source, for example, a cooling device of various plants such as an intake air cooling device of a gas turbine (see FIG. 10), a trip of a gas turbine or the like occurs. If the cooling load suddenly decreases, the stop speed of the absorption refrigerator cannot keep up,
It is conceivable that the supercooled state will occur as when the cold water pump is stopped as described above. Therefore, there is a concern that the tube of the absorption refrigerator may be ruptured due to a trouble that occurs on the cooling load side such as a trip of the gas turbine. Such supercooling is
A cooling device in which the cooling capacity and the cooling load of the absorption refrigerator are closer to 1: 1, in other words, a cooling device in which the cooling water supplied by one absorption refrigerator is used by one cooling device is more likely to occur. is there.

From the above background, the development of an absorption refrigerating machine capable of preventing cold water from becoming supercooled even when the cooling load is suddenly reduced or the cooling load is suddenly removed has been developed. desired.

The present invention has been made in view of the above circumstances. A first object of the present invention is absorption refrigeration that can be safely stopped without the cold water being overcooled even if the cooling load is suddenly reduced. To provide a machine. A second object of the present invention is to install equipment using an absorption refrigerating machine that is not damaged by overcooling even when the cooling load is suddenly reduced due to a trouble such as a trip of a gas turbine.
Another object of the present invention is to provide a gas turbine intake air cooling device using an absorption refrigerator.

[0017]

The present invention adopts the following means in order to solve the above problems. The absorption refrigerating machine according to claim 1 absorbs and dissolves a refrigerant gas formed by evaporating a liquid refrigerant dispersed in a tube group in an evaporator into a solution in the absorber, and heats a dilute solution discharged from the absorber. Regeneration as a high-temperature high-concentration solution by this, in the absorption refrigerator to return the high-concentration solution to the absorber, characterized in that an emergency shutoff means is provided in the supply system of the heat source for heating the dilute solution. is there.

According to such an absorption refrigerating machine, since the emergency shutoff means is provided in the supply source of the heat source, the regeneration from the dilute solution to the high-concentration solution for absorbing and dissolving the refrigerant gas in the absorber is stopped. . For this reason, the concentration of the solution in the absorber decreases and the refrigerant gas cannot be absorbed, so that the evaporated refrigerant gas is saturated and further evaporation and vaporization of the liquid refrigerant is stopped. Therefore, supercooling of cold water can be prevented.

In the absorption refrigerating machine according to the first aspect, it is preferable that an emergency shutoff valve for receiving the emergency stop signal and closing the supply system is adopted as the emergency shutoff means, whereby the supply of the heat source is instantaneously performed. In addition, it can be surely shut off. (Claim 2)

Further, in the absorption refrigerating machine according to the first or second aspect, upon receiving the emergency stop signal, the refrigerant pump provided in the refrigerant distribution system for supplying the liquid refrigerant to the evaporator can be stopped. Preferably, this stops the supply of the liquid refrigerant to the evaporator, so that the cooling of the cold water due to the evaporation of the liquid refrigerant cannot be performed, and therefore the supercooling can be prevented more reliably. Note that crystallization can be prevented by heating the portion where the high-concentration solution flows with a heater. (Claim 3)

Further, in the absorption refrigerating machine according to the third aspect, upon receiving the emergency stop signal, cooling water is supplied to the solution pump and the absorber provided in the solution circulation system for supplying the dilute solution to the heating section. It is preferable to stop at least one of the cooling water pumps to be supplied, which limits the refrigerant gas absorption capacity in the absorber, so that supercooling can be prevented more reliably. In addition, when both the solution pump and the cooling water pump are stopped, the prevention of supercooling becomes more reliable as compared with the case where either one of them is stopped. (Claim 4)

In the absorption refrigerating machine according to the fifth aspect of the present invention, the dilute solution discharged from the absorber is obtained by absorbing and dissolving the refrigerant gas formed by the evaporation of the liquid refrigerant dispersed in the tube group in the evaporator into the solution in the absorber. Is regenerated as a high-temperature high-concentration solution by heating, and the high-concentration solution is returned to the absorber in an absorption refrigerator,
It is characterized in that the cold water system in which the cold water that flows through the inside of the tube group in the evaporator and exchanges heat is circulated is provided with the heat capacity increasing means of the cold water.

According to such an absorption refrigerator, since the heat capacity increasing means for the chilled water is provided, the chilled water temperature decreasing speed after the operation is stopped becomes slow, and the supercooling occurs until the operation is stopped. Can be prevented.

In the absorption refrigerator according to the fifth aspect of the present invention, it is preferable that the heat capacity increasing means is a cushion tank, so that a desired heat capacity can be easily increased by setting the tank capacity. The cushion tank can also be used as a cold heat storage tank. (Claim 6)

In the absorption refrigerating machine according to the seventh aspect, the dilute solution discharged from the absorber is obtained by absorbing and dissolving the refrigerant gas formed by the evaporation of the liquid refrigerant dispersed in the tube group in the evaporator into the solution in the absorber. Is regenerated as a high-temperature high-concentration solution by heating, and the high-concentration solution is returned to the absorber in an absorption refrigerator,
It is characterized in that a cold water system in which cold water that flows inside the tube group in the evaporator and exchanges heat is circulated, is provided with means for preventing supercooling of the cold water that operates upon receiving an emergency stop signal.

According to such an absorption refrigerating machine, since the cooling water system is provided with the supercooling preventing means which operates upon receiving the emergency stop signal, the supercooling preventing means is instantaneously operated to prevent the supercooling of the cold water. be able to.

In the absorption refrigerating machine according to claim 7, the supercooling preventing means includes an indirect heat exchanger for exchanging heat between the heat source for heating the dilute solution and the cold water, and the indirect heat source for the heat source. It is preferable that the system is provided with a normally-closed opening / closing valve that is opened in response to the emergency stop signal and is provided in a system that is introduced into the heat exchanger. Cooling can be prevented. (Claim 8)

In the absorption refrigerating machine according to claim 7, as the supercooling preventing means, there is a mixing pipe line consisting of a forward path and a return path connecting the cold water system and the cooling water system supplied to the absorber. It is preferable to employ a cold water / cooling water mixing circuit having a normally-closed on-off valve that is provided on each of the forward path and the return path and that opens when receiving the emergency stop signal. Supercooling of the cold water can be prevented by mixing the cooling water of. (Claim 9)

In the absorption refrigerating machine according to the tenth aspect of the invention, the dilute solution discharged from the absorber is obtained by absorbing and dissolving the refrigerant gas formed by the evaporation of the liquid refrigerant dispersed in the tube group in the evaporator into the solution in the absorber. Is regenerated as a high-temperature high-concentration solution by heating
In the absorption refrigerator for returning the high-concentration solution to the absorber, at least two or more means are selected from the heat capacity increasing means according to claim 6 and the supercooling preventing means according to claim 8 or 9. It is characterized by having annexed.

According to such an absorption refrigerator, the cooling water supercooling prevention function can be ensured by taking advantage of the respective advantages of the heat capacity increasing means and the supercooling prevention means in consideration of the installation location and cost. Can be obtained.

A facility using the absorption refrigerator according to claim 11 is a facility using an absorption refrigerator as a device for supplying at least cold water, and the absorption refrigerator according to any one of claims 1 to 10 is used. It is characterized by being configured and equipped. According to the equipment using such an absorption refrigerator, it is possible to prevent supercooling in the absorption refrigerator and provide equipment with high reliability.

A gas turbine intake air cooling device according to a twelfth aspect of the present invention is an intake air conditioner for cooling the intake air of a gas turbine with the absorption refrigerator according to any one of the first to tenth aspects and the cold water introduced from the absorption refrigerator. It is characterized in that it is configured by including:

According to such a gas turbine intake air cooling device, overcooling can be prevented even when the cooling load such as a gas turbine trip is suddenly reduced, so that the reliability of the device can be improved. In this case, it is preferable to employ a gas turbine trip signal as the emergency stop signal, and thereby reliable processing / operation can be instantaneously performed to prevent supercooling. (Claim 13)

[0034]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of an absorption refrigerator and a gas turbine intake air cooling system using the same according to the present invention will be described below with reference to the drawings. FIG. 2 shows a schematic configuration example of the absorption refrigerator 1 having a double-effect type. However, the absorption refrigerator according to the present invention may be a single-effect type. In FIG. 2, the evaporator 10 and the absorber 20 are
It is configured in the same shell (high vacuum container). A group of evaporator tubes 11 is arranged in the evaporator 10. Cold water W1 is supplied to the evaporator tube 11 via a cold water inlet line L1, and the evaporator tube 11
The cold water W1 flowing through is discharged to the outside through the cold water outlet line L2. Further, the refrigerant (water) R pumped up by the refrigerant pump P1 via the refrigerant line L11 is sprayed toward the evaporator tube 11. Dispersed refrigerant R
Is a refrigerant vapor r by taking latent heat from the cold water W1 flowing in the evaporator tube 11 and evaporating it. The refrigerant vapor r passes through the gas-liquid separator 12 and flows into the absorber 20 side.

The cold water W1 enters the evaporator 10 at a temperature of, for example, 12 ° C., is cooled by the evaporator tube 11, and is discharged from the evaporator 10 at a temperature of, for example, 7 ° C.
The 7 ° C. cold water W1 that emerges from the cold water outlet line L2 is used as cold heat for cooling the building, for the process of the factory, and for cooling the gas turbine intake air. The temperature of the chilled water W1 that has been subjected to a cooling load such as building cooling rises, for example, 12 °
And the temperature again reaches the evaporator 10.

On the other hand, inside the absorber 20, the absorber tube 2
1 is arranged. Cooling water W2 is supplied to the absorber tube 21 via a cooling water line L3. Then, the concentrated lithium bromide solution Y1 pumped by the solution pump P2 via the solution line L21 is sprayed toward the absorber tube 21. For this reason, the sprayed concentrated lithium bromide solution Y1 absorbs the refrigerant vapor r flowing into the absorber 20 side, and the concentration thereof becomes thin. The diluted lithium bromide solution Y3 having a reduced concentration is collected at the bottom of the absorber 20. The heat generated in the absorber 20 is cooled by the cooling water W2 flowing in the absorber tube 21.

The diluted lithium bromide solution Y3 collected at the bottom of the absorber 20 is pumped by the solution pump P3,
It is supplied to the high pressure regenerator 40 via the valve V5, the low temperature heat exchanger 30, the solution line L22, the high temperature heat exchanger 31, and the solution line L23.

The high-pressure regenerator 40 is a lithium bromide dilute solution Y.
3 has a function of evaporating a part of the refrigerant to increase the concentration by heating 3. The heat source for heating used here includes burner heating for burning high temperature steam or exhaust gas, or fuel gas or fuel oil. In the illustrated example, the furnace cylinder and the heat transfer tube are housed in the case and a burner is installed. In this high-pressure regenerator 40, the gas line L
By supplying the fuel gas G through the valve 31, the valve V21, and the fuel control valve V22, the fuel gas G burns to heat the diluted lithium bromide solution Y3. The diluted lithium bromide solution Y3 supplied to the high-pressure regenerator 40 is heated by the burner, and a part of the refrigerant is evaporated and vaporized to become a solution Y2 in lithium bromide having a medium concentration. The solution Y2 in lithium bromide is supplied to the low pressure regenerator 50 through the solution line L24 and the high temperature heat exchanger 31.

On the other hand, the refrigerant vapor r evaporated in the high pressure regenerator 40 is supplied to the low pressure regenerator tube 51 of the low pressure regenerator 50 via the refrigerant line L12, and further to the condenser 60 via the refrigerant line L13. Is supplied to. The low pressure regenerator 50 and the condenser 60 are configured in the same shell.

In this low pressure regenerator 50, the solution line L2
The solution Y2 in lithium bromide is supplied via 4 and the dilute lithium bromide solution Y3 branched from the solution line L22 via the solution line L25 is sprayed toward the low pressure regenerator tube 51. In this low pressure regenerator 50,
The solutions Y2 and Y3 are heated by the low pressure regenerator tube 51, a part of the refrigerant is evaporated to further increase the concentration of the solution, and the high concentration lithium bromide concentrated solution Y1 is converted into the low pressure regenerator 50.
Collected at the bottom of the. This concentrated lithium bromide solution Y1 is
It is again supplied to the absorber 20 by the solution pump P2.

The condenser 60 has a cooling water line L4.
A condenser tube 61 to which the cooling water W2 is supplied is arranged. In the condenser 60, the high pressure regenerator 40 evaporates and the refrigerant line L12 and the low pressure regenerator tube 51
And the refrigerant vapor r supplied through the refrigerant line L13 and the refrigerant vapor r that has evaporated in the low pressure regenerator 50 and has flowed into the condenser 60 side are cooled and condensed in the condenser tube 61, It becomes the refrigerant (water) R. The refrigerant R is sent to the evaporator 10 via the refrigerant line L14 due to gravity and the pressure difference. Refrigerant R collected at the bottom of the evaporator 10.
Is sprayed toward the evaporator tube 11 again via the refrigerant line L11 by the refrigerant pump P1.

In the absorption refrigerator 1 described above, the valves V1, V2, V3 and V4 are closed (shown in black in the figure) during the cooling operation, and the valves V5 and V are shown.
11, V12, V13, and V14 are open (shown in outline in the figure). Further, the absorption refrigerator 1 can also be operated in heating (heating cold water), but since it is not related to the present invention, description of operation during heating operation will be omitted.

Now, an embodiment in which the absorption refrigerator 1 having the above-described structure is used for cooling a gas turbine intake air, that is, an embodiment of a gas turbine intake air cooling device will be described below with reference to the drawings. <First Embodiment> In the first embodiment shown in FIG. 1, reference numeral 70 in the drawing denotes a gas turbine, 71 denotes a compressor, and 7
2 is a turbine, 73 is a combustor, 74 is an intake air cooler, 80
Is a generator, 81 is an exhaust gas boiler, P4 is a cold water pump, P
5 is a cooling water pump. The gas turbine 70 burns the fuel together with the intake air compressed by the compressor 71 in the combustor 73, supplies the generated high-temperature combustion gas between the moving blades and the stationary blades of the turbine 72, and expands it to obtain a shaft output. It is designed to be used. This shaft output is converted into electric power by driving the generator 80, for example.

Further, since the combustion gas after working in the turbine 72 still has a large amount of heat energy, it is sent to the exhaust gas boiler 81 and the amount of heat retained therein is reused.
That is, in the exhaust gas boiler 81, the turbine 72
The steam is generated by heating the water with the heat energy held by the combustion gas discharged from the steam, and this steam is used for the operation of a steam turbine (not shown), or the high pressure regeneration of the absorption refrigerator 1 is performed. The dilute solution of lithium bromide Y3 is supplied to the vessel 40 as a heat source for heating, so that the waste heat of the combustion gas is effectively used. The combustion gas whose temperature has been lowered by being used for generating steam in the exhaust gas boiler 81 is released to the atmosphere after being subjected to appropriate treatment such as removal of harmful components as necessary.

The gas turbine intake air cooling device shown in FIG. 1 is provided for the purpose of increasing the density by cooling the intake air (air) supplied to the compressor 71, and consequently improving the output and performance of the gas turbine 70. Intake air cooler 74
It is equipped with. This intake air cooler 74 is used in the absorption refrigerator 1.
Is supplied with cold water W1 cooled by
By exchanging heat between the cold water W1 flowing in and the intake air,
The intake air temperature supplied to the compressor 71 is lowered. Cold water W1
Circulates in the pipe line connecting the evaporator 10 and the intake air cooler 74 by the operation of the cold water pump P4. That is, the cold water W1 cooled in the evaporator 10 and having a low temperature cools the intake air in the intake air cooler 74 to rise in temperature, and the evaporator 10 is cooled again.
Repeat the temperature change of returning to and cooling.

In the absorption refrigerator 1 shown, the high pressure regenerator 4 is used.
At 0, high temperature steam is used as a heat source for heating the lithium bromide dilute solution Y3. The steam supplied to the high-pressure regenerator 40 may be supplied from the exhaust gas boiler 81 or may be supplied from another system (not shown), both of which include a steam shutoff valve 2 and a steam control valve 3. Four
It is designed to pass through.

Here, the one steam shutoff valve 2 can be selected from two positions, that is, a fully open position and a fully closed position, and is normally set to the fully open position. The steam shutoff valve 2 functions as an emergency shutoff means that instantly fully closes the steam pipe 4 that is a heat source supply system, for example, in response to an emergency stop signal of the absorption refrigerator 1 It is an emergency shutoff valve that can be fully closed. Further, the other steam control valve 3 has a function of appropriately adjusting the valve opening degree according to the load of the absorption refrigerator 1 and controlling the amount of steam supplied to the high pressure regenerator 40. That is, when the cooling load of the absorption refrigerator 1 is large, the valve opening of the steam control valve 3 is increased to increase the supply amount of steam, and conversely, when the cooling load is small,
The valve opening is reduced to reduce the amount of steam supplied.
In the illustrated example, the opening degree of the steam control valve 3 is controlled according to the temperature of the cold water W1 detected by the temperature detecting means 5.

The emergency stop signal for operating the above-described steam shutoff valve 2 from full open to full close includes cooling such as when the chilled water pump P4 is stopped due to an earthquake or when the gas turbine 70 is tripped. There is a signal that is output when a situation is detected in which the load suddenly decreases or disappears. In the illustrated example, the steam shutoff valve 2 can be instantaneously closed by a trip signal output from the gas turbine 70. In addition to such a trip signal, the cold water temperature detected by a cold water inlet line L1, cold water outlet line L2 or a temperature sensor (not shown) installed at an appropriate position in the pipe group 74a has become a low temperature below a predetermined value. It is also possible to adopt the signal output in some cases. Needless to say, the temperature of the cold water detected by the temperature detecting means 5 for the cold water W1 described above can be used in addition to newly providing a dedicated temperature sensor.

With such a configuration, even if the gas turbine 70 trips and the cooling load sharply decreases, the trip signal is received to instantly fully close the steam shutoff valve 2 to stop the steam supply of the heat source and cool water. Can be prevented. That is, when the cooling load of the intake air cooler 74 disappears due to the trip of the gas turbine 70, the supply of the heat source is stopped and the lithium bromide Y3 cannot be concentrated. Therefore, the concentration of the solution in the absorber 20 is reduced. Becomes lower and the refrigerant gas cannot be absorbed. Therefore, the evaporator 10
Since the refrigerant gas evaporated in Saturates in Saturation and further evaporation or vaporization of the liquid refrigerant is suppressed or stopped, the cooling capacity of the cold water W1 in the evaporator 10 decreases in a relatively short time.
Therefore, it is possible to prevent the cooling water W1 from continuing to be cooled on the absorption refrigerating machine 1 side to be in a supercooled state, so that the cold water W1 freezes in the evaporator tube 11 in the evaporator 10 and the tube ruptures. It is possible to avoid such a situation.

Further, in the above description, the steam shutoff valve 2 is urgently shut off by the trip of the gas turbine 70. However, even when the chilled water pump P4 becomes inoperable in an emergency such as an earthquake, If it is used as a safety device for preventing tube breakage, the same effect can be obtained. Needless to say, the above-described steam cutoff valve 2 can be applied not only to the gas turbine intake air cooling device but also to a cooling device and a cooling device for various plants.

<Second Embodiment> In the second embodiment shown in FIG. 3, reference numeral 70 in the drawing is a gas turbine, 71 is a compressor, 72 is a turbine, 73 is a combustor, 74 is an intake air cooler, 80 is a generator, 81 is an exhaust gas boiler, P4 is a cold water pump, and P5 is a cooling water pump. In this embodiment, as in the first embodiment described above, the high pressure regenerator 40 is used.
In, the high temperature steam is used as a heat source for heating the diluted lithium bromide solution Y3. The steam supplied to the high-pressure regenerator 40 may be supplied from the exhaust gas boiler 81 or may be supplied from another system (not shown), and both flow through the steam pipe 4 equipped with the steam control valve 3. Has become. That is, in this embodiment, the steam shutoff valve 2 is not provided in the steam pipe 4, and therefore the steam control valve 3 is configured to function as an emergency shutoff means similar to the steam emergency shutoff valve 2. There is.

Even with such a configuration, the gas turbine 7
When 0 is tripped and the cooling load is rapidly reduced, the steam control valve 3 is instantly fully closed upon receiving the trip signal, and the steam supply of the heat source can be stopped to prevent the supercooling of the cold water.
That is, when the cooling load of the intake air cooler 74 disappears due to the trip of the gas turbine 70, the supply of the heat source is stopped and the lithium bromide Y3 cannot be concentrated. Therefore, the cooling of the cold water W1 in the evaporator 10 is stopped. Capacity declines in a relatively short time. Therefore, it is possible to prevent the cooling water W1 from continuing to be cooled on the absorption refrigerating machine 1 side to be in a supercooled state, so that the cold water W1 freezes in the evaporator tube 11 in the evaporator 10 and the tube ruptures. It is possible to avoid such a situation.

In the above description, the steam control valve 3 is fully closed by the trip of the gas turbine 70 to shut off the supply of steam in an emergency. However, the chilled water pump P4 cannot be operated in an emergency such as an earthquake. In the case of, for example, if it is used as a safety device for preventing tube breakage, the same operation and effect can be obtained. Furthermore, the above-described steam control valve 3 can be used for cooling devices and various plants in addition to the gas turbine intake cooling device. It goes without saying that it can also be applied to the above cooling device.

<Third Embodiment> In the third embodiment shown in FIG. 4, reference numeral 70 in the drawing is a gas turbine, 71 is a compressor, 72 is a turbine, 73 is a combustor, 74 is an intake air cooler, 80 is a generator, 81 is an exhaust gas boiler, P4 is a cold water pump, and P5 is a cooling water pump. In this embodiment, as in the first embodiment described above, the high pressure regenerator 40 is used.
In, the high temperature steam is used as a heat source for heating the diluted lithium bromide solution Y3. The steam supplied to the high-pressure regenerator 40 may be supplied from the exhaust gas boiler 81 or may be supplied from another system (not shown), both of which include a steam shutoff valve 2 and a steam control valve 3. Four
It is designed to pass through.

Further, in this embodiment, the above-mentioned first
Similar to the embodiment described above, when the emergency stop signal is received, not only the steam cutoff valve 2 is fully closed to stop the supply of steam but also the operation of the refrigerant pump P1 is stopped. Refrigerant pump P1
Is for supplying a liquid refrigerant (water) R to the evaporator 10 and spraying it toward the evaporator tube 11. When the refrigerant pump P1 is stopped, the supply of the refrigerant R to the evaporator 10 is stopped, so that the cold water W resulting from the evaporation and vaporization of the refrigerant R is generated.
1 can not be cooled.

Therefore, both the heating and concentration of the dilute lithium bromide solution Y3 in the high-pressure regenerator 40 and the spraying of the refrigerant R in the evaporator 10 are stopped, so that the concentration of the solution in the absorber 20 decreases and the refrigerant gas is discharged. Can no longer be absorbed,
In the evaporator 10, the refrigerant R that evaporates and vaporizes is lost. For this reason, the refrigerant gas evaporated in the evaporator 10 is saturated, and since the liquid refrigerant is not scattered and there is no new evaporation and vaporization, the cooling capacity of the cold water W1 in the evaporator 10 can be more reliably achieved in a shorter time. Can be lowered.
As a result, it is possible to reliably prevent the cooling water W1 from continuing to be cooled on the absorption refrigerating machine 1 side to be in a supercooled state, so that the cooling water W1 freezes in the evaporator tube 11 in the evaporator 10. It is possible to avoid a situation in which the tube ruptures. When the refrigerant pump P1 is stopped, crystallization may occur in a line in which a high-concentration lithium bromide solution flows. Therefore, it is preferable to prevent the temperature from lowering to the crystal temperature by heating the heater, for example.

<Fourth Embodiment> In the fourth embodiment shown in FIG. 5, reference numeral 70 in the drawing is a gas turbine, 71 is a compressor, 72 is a turbine, 73 is a combustor, 74 is an intake air cooler, 80 is a generator, 81 is an exhaust gas boiler, P4 is a cold water pump, and P5 is a cooling water pump. In this embodiment, in addition to the above-described third embodiment, when the emergency stop signal is received, the solution pump P3 or the cooling water pump P5.
Is configured to be stopped.

That is, in this embodiment, as in the first embodiment described above, not only is the steam shutoff valve 2 fully closed to stop the supply of steam when an emergency stop signal is received, but the refrigerant pump In addition to stopping the operation of P1, both or both of the solution pump P3 and the cooling water pump P5 are similarly stopped. Solution pump P3
Is provided in the solution circulation system in order to supply the diluted solution of lithium bromide Y3 in the absorber 20 to the high temperature regenerator 40 which serves as a heating unit. When the solution pump P3 is stopped, the lithium bromide dilute solution Y3 in the absorber 20 cannot be heated and concentrated. The cooling water pump P5 is
It is provided to supply the cooling water W2 to the absorber 20, and when this pump stops, the latent heat of condensation and the heat of dilution cannot be removed.

Therefore, both the heating and concentration of the dilute solution of lithium bromide Y3 in the high-pressure regenerator 40 and the spraying of the refrigerant R in the evaporator 10 are stopped, so that the concentration of the solution in the absorber 20 decreases and the refrigerant gas is discharged. Can no longer be absorbed,
In the evaporator 10, the refrigerant R that evaporates and vaporizes is lost. Furthermore, if the circulation of the dilute solution of lithium bromide Y3 is stopped, the solution heated and concentrated by preheating is not supplied to the absorber 11, and if the supply of the cooling water W2 is stopped, the temperature is reduced. The rise suppresses absorption of the refrigerant gas.

For this reason, the refrigerant gas evaporated in the evaporator 10 is saturated, and the liquid refrigerant is no longer scattered, and there is no new evaporation and vaporization. Therefore, the cold water W1 in the evaporator 10 is not used.
The cooling capacity of can be reduced more reliably in a shorter time. That is, the absorption of the refrigerant vapor in the absorber 20 is limited, and the internal pressure does not fall to the saturation pressure of the freezing temperature, so that the supercooling of cold water can be more reliably avoided. As a result, it is possible to reliably prevent the cooling water W1 from continuing to be cooled on the absorption refrigerating machine 1 side to be in a supercooled state, so that the cooling water W1 freezes in the evaporator tube 11 in the evaporator 10. It is possible to avoid a situation in which the tube ruptures.

<Fifth Embodiment> In the fifth embodiment shown in FIG. 6, reference numeral 70 in the drawing is a gas turbine, 71 is a compressor, 72 is a turbine, 73 is a combustor, 74 is an intake air cooler, 80 is a generator, 81 is an exhaust gas boiler, 90 is a cushion tank, P4a is the first chilled water pump, and P4b is the second.
Cold water pump, P5 is a cooling water pump. In this embodiment, the cold water inlet line L1 and the cold water outlet line L2 (cold water system) in which the cold water that flows through the inside of the evaporator tube (tube group) 11 inside the evaporator 10 and is heat-exchanged (cooled) circulates, A cushion tank 90 is provided as a heat capacity increasing means. By providing the cushion tank 90, the amount of cold water circulating in the cold water system is increased by the tank capacity. The cushion tank 90 is provided with a partition plate inside or as a separate structure, and
0a and a low temperature tank 90b.

From the tube group 74a of the intake air cooler 74 to the evaporator 1
The cold water inlet line for returning the cold water to the evaporator tube 11 of No. 0 is L by interposing the cushion tank 90.
It is divided into 1a and L1b. One cold water inlet line L1a is a line for temporarily guiding the cold water whose temperature has risen due to intake air cooling to the high temperature tank 90a and storing it. The cold water stored in the high temperature tank 90a is cooled by the cold water inlet line L.
It is supplied to the evaporator tube 11 by the first cold water pump P4a installed in 1b.

The cold water outlet line for supplying cold water from the evaporator tube 11 of the evaporator 10 to the pipe group 74a of the intake air cooler 74 is also divided into L2a and L2b by interposing a cushion tank 90. One cold water outlet line L2a temporarily cools the cold water that has cooled through the evaporator tube 11 to a low temperature tank 90b.
It is a line that leads to and stores. The cold water stored in the low temperature tank 90b is supplied to the pipe group 7 of the intake cooler 74 by the second cold water pump P4b installed in the cold water outlet line L2b.
4a.

That is, since the amount of cold water circulating in the cold water system is greatly increased in accordance with the capacity of the cushion tank 90, the heat capacity is increased by the increase in the amount of water and the temperature change is reduced. In other words, even if the cooling load sharply decreases due to a trip of the gas turbine 70 or the like, the temperature decrease rate of the cold water becomes gentle due to the increase in the amount of water. Therefore, it takes a long time for the cold water flowing in the evaporator tube 11 to be in a supercooled state and to be frozen. For example, the supercooling may be caused before the operation stop of the absorption refrigerator 1 is completed. It becomes possible to prevent the tube from bursting. By adopting the cushion tank 90 as the heat capacity increasing means, a desired heat capacity can be easily increased by adjusting the tank capacity, and the low temperature tank 90b of the cushion tank 90 can be used as a cold heat storage tank. You can also

<Sixth Embodiment> In the sixth embodiment shown in FIG. 7, reference numeral 70 in the drawing is a gas turbine, 71 is a compressor, 72 is a turbine, 73 is a combustor, 74 is an intake air cooler, 80 is a generator, 81 is an exhaust gas boiler, 90 is a cushion tank, P4 is a cold water pump, and P5 is a cooling water pump. In this embodiment, the cold water inlet line L1 or the cold water outlet line L2 (cold water system) where the cold water that flows through the inside of the evaporator tube (tube group) 11 in the evaporator 10 and is heat-exchanged (cooled) circulates, A cushion tank 90 is provided as a heat capacity increasing means. By providing the cushion tank 90, the amount of cold water circulating in the cold water system is increased by the tank capacity.

In the illustrated embodiment, the cushion tank 90 is provided in the cold water inlet line for returning the cold water from the pipe group 74a of the intake air cooler 74 to the evaporator tube 11 of the evaporator 10, and this cold water inlet line is provided with a cushion. Tank 9
It is divided into L1a and L1b by interposing 0. One cold water inlet line L1a is a line for temporarily guiding the cold water whose temperature has risen due to intake air cooling to the high temperature tank 90a and storing it. The cold water stored in the high temperature tank 90a is supplied to the evaporator tube 11 by the first cold water pump P4 installed in the cold water inlet line L1b. Although the cushion tank 90 is installed on the cold water inlet line in the illustrated embodiment, it may be installed on the cold water outlet line L2 side.

Even with such a configuration, the amount of cold water circulating in the cold water system greatly increases in accordance with the capacity of the cushion tank 90, so that the heat capacity increases by the increase in the amount of water and the temperature change decreases. In other words, even if the cooling load sharply decreases due to a trip of the gas turbine 70 or the like, the temperature decrease rate of the cold water becomes gentle due to the increase in the amount of water. Therefore, the evaporator tube 11
It takes a long time for the cold water flowing in the inside to become supercooled and to be frozen, and for example, before the operation stop of the absorption refrigerator 1 is completed, the tube rupture caused by the supercooling is prevented. Will be able to prevent. By adopting the cushion tank 90 as the heat capacity increasing means, a desired heat capacity can be easily increased by adjusting the tank capacity, and the cushion tank 9 can be used.
0 can also be used as a cold heat storage tank.

<Seventh Embodiment> In the seventh embodiment shown in FIG. 8, reference numeral 70 in the drawing is a gas turbine, 71 is a compressor, 72 is a turbine, 73 is a combustor, 74 is an intake air cooler, 80 is a generator, 81 is an exhaust gas boiler, 95 is an indirect heat exchanger, 96 is a steam branch pipe, 97 is an opening / closing valve, P4 is a cold water pump, and P5 is a cooling water pump. In this embodiment, the steam branch pipe 96 is branched from the steam pipe 4 on the upstream side of the steam control valve 3, and the steam branch pipe 96 is provided with a supercooling prevention means. This supercooling prevention means is provided with an on-off valve 97 that closes in response to an emergency stop signal, and an indirect heat exchanger 95 that heats cold water with steam of a heat source.

The indirect heat exchanger 95 is the cold water inlet line L1.
The cold water flowing in the pipe group 95a connected to the heat exchanger is for exchanging heat with the high temperature steam introduced from the steam pipe 4, and has a function of heating the cold water by the heat of the steam to raise the temperature. With such a configuration, even if the cooling load on the intake air cooler 74 is suddenly reduced due to a trip of the gas turbine 70, the cold water supplied to the evaporator 10 is heated by the indirect heat exchanger 95. Supercooling can be prevented. In other words, when the emergency stop signal is output and the cooling load sharply decreases, the indirect heat exchanger 95 is configured to perform heating to an extent corresponding to the decreased cooling load. It is possible to prevent the cold water flowing in the evaporator tube 11 from becoming supercooled and freezing.

<Eighth Embodiment> In the eighth embodiment shown in FIG. 9, reference numeral 70 in the drawing is a gas turbine, 71 is a compressor, 72 is a turbine, 73 is a combustor, 74 is an intake air cooler, 80 is a generator, 81 is an exhaust gas boiler, L1 is a cold water inlet line, L2 is a cold water outlet line, 100 is a cooling water supply pipe line, 101 is a cooling water return pipe line, 102 and 103 are opening / closing valves, P4 is a cold water pump, P5 is a cooling water pump.
In this embodiment, the cooling water supply pipeline 1 is provided from the outlet pipe 104 of the cooling water W2 flowing out from the absorber 20 and the condenser 60.
00 is branched and joined to the cold water inlet line L1. The cooling water supply conduit 100 is provided with a normally-closed on-off valve 102 that opens when receiving an emergency stop signal. Further, the cooling water return pipe line 101 branched from the cold water outlet line L2 joins the inlet pipe 105 of the cooling water W2. The cooling water return pipe line 101 is provided with a normally-closed on-off valve 103 that opens when receiving an emergency stop signal.

That is, the supercooling prevention means of this embodiment is a cold water system consisting of a cold water inlet line L1 and a cold water outlet line L2, and a cooling water system through which cooling water W2 used for cooling the inside of the absorber 20 flows. And a cooling water supply pipeline (outward) 100 and a cooling water return pipeline (return) 101, and a cooling water supply pipeline (outgoing) 100 and a cooling water return pipeline (return) 101. Normally closed on-off valves 102, 1 which are respectively provided in the
03 is a cold water / cooling water mixing circuit. This chilled water / cooling water mixing circuit mixes the chilled water having a temperature higher than that of the chilled water with the chilled water system by opening the opening / closing valves 102 and 103 when the emergency stop signal is output, and is cooled by the evaporator 10. It has a function of increasing the temperature of cold water to prevent supercooling. That is, by using the cold water / cooling water mixing circuit, a simulated load for cooling cold water can be formed. In addition, the cooling water return line 101
Is for returning to the cooling water system by the amount of the cooling water joined to the closed-circuit cold water system for circulating the cold water.

With such a configuration, the gas turbine 7
Even if the cooling load in the intake air cooler 74 is suddenly reduced due to a trip of 0, the cooling water having a high temperature joins the cooling water cooled in the evaporator 10, so that the temperature of the entire cooling water rises. Overcooling can be prevented. In other words, when the emergency stop signal is output and the cooling load sharply decreases, the cooling water temperature is increased by mixing with the cooling water having a temperature higher than that of the cooling water.
It is possible to prevent the cold water flowing in the evaporator tube 11 from becoming supercooled and freezing.

By the way, the above-described fifth embodiment (see FIG. 6)
Either the first embodiment or the sixth embodiment (see FIG. 7), the seventh embodiment (see FIG. 8) and the eighth embodiment (see FIG. 9) may be independently adopted. Of course, this is possible, but they may be appropriately combined depending on the situation such as the installation location. The cushion tank 90 of the fifth and sixth embodiments requires a relatively large installation space, and thus is difficult to adopt when the installation place is limited. In the eighth embodiment, the installation space is the smallest and the cost is low, but after mixing the cold water and the cooling water, it is necessary to replace the cold water system with pure cold water. In the seventh embodiment, the required installation space is between those of the fifth and sixth embodiments and the eighth embodiment, and the cold water need not be replaced. Therefore, in consideration of these characteristics, the optimum combination may be selected for the actual installation place.

As described above, according to the absorption refrigerator of the present invention and the gas turbine intake air cooling system using the same,
Even if the cooling load of the absorption chiller 1 suddenly decreases, such as when the chilled water pump P4 stops due to the occurrence of a disaster such as an earthquake, or when the gas turbine trips or the like, the chilled water is supercooled. It becomes possible to prevent. Therefore, the evaporator tube 11 does not freeze and break due to supercooling, and the absorption refrigerator 1
The operation of can be stopped safely and surely. Further, the absorption refrigerating machine of the present invention described above can be applied to various equipments configured to receive the supply of cold water or the like by the absorption refrigerating machine in addition to the gas turbine intake air cooling device.

The configuration of the present invention is not limited to the above-described embodiment, and the present invention is applied to an absorption refrigerator having a configuration using other heat source such as exhaust gas instead of steam, which deviates from the gist of the present invention. It can be appropriately changed within the range not to do.

[0076]

According to the absorption refrigerating machine, the equipment using the absorption refrigerating machine, and the gas turbine intake air cooling device of the present invention, the following effects can be obtained. (1) According to the absorption refrigerating machine of claim 1, since the supply source of the heat source is provided with the emergency shutoff means, the supply of the heat source is stopped when an emergency stop is required, and the refrigerant gas is diluted from the dilute solution into the absorber. The regeneration (heating / concentration) to a high-concentration solution that absorbs and dissolves is stopped. For this reason, the concentration of the solution in the absorber decreases and the refrigerant gas cannot be absorbed, so that the evaporated refrigerant gas is saturated and further evaporation and vaporization of the liquid refrigerant is stopped. Therefore, it is possible to prevent the cold water from freezing due to supercooling and damage to the evaporator tube and the like, which is very effective in improving the reliability of the apparatus.

(2) According to the absorption chiller of the fifth aspect, since the heat capacity increasing means for the chilled water is provided, the chilled water temperature decrease rate after the operation is stopped becomes slow, and the operation is stopped before the operation is completed. Supercooling can be prevented from occurring.
Therefore, it is possible to prevent the cold water from freezing due to supercooling and damage to the evaporator tube and the like, which is very effective in improving the reliability of the apparatus.

(3) According to the absorption refrigerating machine of the seventh aspect, since the cooling water system is provided with the supercooling preventing means which operates upon receiving the emergency stop signal, the supercooling preventing means is instantaneously operated to cool the cold water. Supercooling can be prevented. Therefore, it is possible to prevent the cold water from freezing due to supercooling and damaging the evaporator tube or the like, which is a great effect in improving the reliability of the apparatus.

(4) According to the absorption refrigerating machine of claim 10, the heat capacity increasing means of claim 6 or claim 8 or 9 is provided.
At least two or more of the listed means for preventing overcooling were selected and installed together, so consider the installation location, cost, etc.
By utilizing the respective advantages of the heat capacity increasing means and the supercooling prevention means, it is possible to more surely obtain the optimum supercooling prevention function of the cold water at the installation place.

(5) According to the equipment using the absorption refrigerating machine according to claim 11, since the equipment is constructed by including the absorption refrigerating machine according to any one of claims 1 to 10, the trouble may occur. Even if the refrigeration load is suddenly reduced, it is possible to prevent overcooling in the absorption refrigerator and provide highly reliable equipment.

(6) According to the gas turbine intake air cooling device of the twelfth aspect, the absorption refrigerating device of any one of the first to tenth aspects and the intake air cooling of the gas turbine by the cold water introduced from the absorption refrigerating device. Since the intake air cooler for performing the above is provided, it is possible to prevent overcooling even when the cooling load such as a gas turbine trip suddenly decreases, and improve the reliability of the device. In this case, if a gas turbine trip signal is adopted as the emergency stop signal, reliable processing / operation can be instantaneously performed to prevent supercooling.

[Brief description of drawings]

FIG. 1 is a configuration diagram showing a first embodiment of an absorption refrigerator and a gas turbine intake air cooling device using the same according to the present invention.

FIG. 2 is a configuration diagram showing a detailed configuration example of an absorption refrigerator.

FIG. 3 is a configuration diagram showing a second embodiment of an absorption refrigerator according to the present invention and a gas turbine intake air cooling device using the same.

FIG. 4 is a configuration diagram showing a third embodiment of an absorption refrigerator according to the present invention and a gas turbine intake air cooling device using the same.

FIG. 5 is a configuration diagram showing a fourth embodiment of an absorption refrigerator according to the present invention and a gas turbine intake air cooling device using the same.

FIG. 6 is a configuration diagram showing a fifth embodiment of an absorption refrigerator according to the present invention and a gas turbine intake air cooling device using the same.

FIG. 7 is a configuration diagram showing a sixth embodiment of an absorption refrigerator according to the present invention and a gas turbine intake air cooling device using the same.

FIG. 8 is a configuration diagram showing a seventh embodiment of an absorption refrigerator and a gas turbine intake air cooling device using the same according to the present invention.

FIG. 9 is a configuration diagram showing an eighth embodiment of an absorption refrigerator and a gas turbine intake air cooling device using the same according to the present invention.

FIG. 10 is a diagram showing a configuration example of a conventional absorption refrigerator and a gas turbine intake air cooling device using the same.

[Explanation of symbols]

1 absorption refrigerator 2 Steam shutoff valve (emergency shutoff means) 3 Steam control valve 4 steam piping 10 evaporator 20 absorber 30 low temperature heat exchanger 40 high-pressure regenerator 50 low pressure regenerator 60 condenser 70 gas turbine 74 Intake air cooler 90 Cushion tank (means for increasing heat capacity) 95 Indirect heat exchanger (supercooling prevention means) 96 steam branch pipe 97, 102, 103 open / close valve 100 cooling water supply line 101 Cooling water return line P1 refrigerant pump P2, P3 solution pump P4 cold water pump P5 cooling water pump

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) F25B 15/00 F25B 15/00 Z 306 306A 306D 49/04 49/04

Claims (13)

[Claims] 1. A refrigerant gas formed by evaporating a liquid refrigerant dispersed in a tube group in an evaporator is absorbed and dissolved in a solution in an absorber,
In an absorption refrigerator that regenerates a high-temperature high-concentration solution by heating the diluted solution that has exited the absorber and returns the high-concentration solution to the absorber, an emergency cutoff is provided to a supply system of a heat source that heats the diluted solution. An absorption refrigerating machine comprising means. 2. The absorption refrigerator according to claim 1, wherein the emergency shutoff means is an emergency shutoff valve that closes the supply system in response to an emergency stop signal. 3. The absorption refrigerating machine according to claim 1 or 2, wherein upon receipt of the emergency stop signal, a refrigerant pump provided in a refrigerant distribution system for supplying the liquid refrigerant to the evaporator is stopped. . 4. In response to the emergency stop signal, at least one of a solution pump provided in a solution circulation system for supplying the diluted solution to a heating unit and a cooling water pump for supplying cooling water to the absorber is stopped. The absorption refrigerator according to claim 3, wherein the absorption refrigerator is a refrigerator. 5. A refrigerant gas formed by evaporating a liquid refrigerant dispersed in a tube group in an evaporator is absorbed and dissolved in a solution in an absorber,
In the absorption refrigerator in which the dilute solution discharged from the absorber is heated to be regenerated as a high-temperature high-concentration solution, and the high-concentration solution is returned to the absorber, heat is exchanged by flowing inside the tube group in the evaporator. An absorption refrigerating machine, characterized in that the cold water system in which the cold water is circulated is provided with a means for increasing the heat capacity of the cold water. 6. The absorption refrigerator according to claim 5, wherein the heat capacity increasing means is a cushion tank. 7. A refrigerant gas formed by evaporating a liquid refrigerant dispersed in a tube group in an evaporator is absorbed and dissolved in a solution in an absorber,
In the absorption refrigerator in which the dilute solution discharged from the absorber is heated to be regenerated as a high-temperature high-concentration solution, and the high-concentration solution is returned to the absorber, heat is exchanged by flowing inside the tube group in the evaporator. An absorption refrigerating machine, characterized in that the cold water system in which the cold water is circulated is provided with means for preventing the supercooling of the cold water which operates upon receiving an emergency stop signal. 8. The supercooling prevention means is provided in an indirect heat exchanger for exchanging heat between a heat source for heating the dilute solution and the cold water, and a system for introducing the heat source into the indirect heat exchanger. 8. The absorption refrigerator according to claim 7, further comprising a normally-closed on-off valve which is opened upon receipt of the emergency stop signal. 9. The supercooling prevention means is provided in each of the forward and backward paths, and the mixing pipeline including the forward and backward paths that connect the cold water system and the cooling water system to be supplied to the absorber. 8. The absorption refrigerator according to claim 7, which is a cold water / cooling water mixing circuit including a normally-closed open / close valve that opens when receiving an emergency stop signal. 10. A high-temperature high temperature solution is obtained by absorbing and dissolving a refrigerant gas, which is formed by evaporating a liquid refrigerant dispersed in a tube group in an evaporator, into a solution in the absorber, and heating the dilute solution discharged from the absorber. In an absorption refrigerating machine that is regenerated as a concentrated solution and returns this highly concentrated solution to the absorber, at least two or more are selected from the heat capacity increasing means according to claim 6 and the supercooling preventing means according to claim 8 or 9. An absorption chiller characterized in that the means of selecting is installed together. 11. An equipment using an absorption refrigerator as a device for supplying at least cold water, comprising the absorption refrigerator according to any one of claims 1 to 10. Equipment using a machine. 12. An absorption refrigerating machine according to any one of claims 1 to 10, and an intake cooler for cooling intake air of a gas turbine with cold water introduced from the absorption refrigerating machine. Characteristic gas turbine intake air cooling device. 13. The gas turbine intake air cooling device according to claim 12, wherein the emergency stop signal is a gas turbine trip signal.