JP2003262421A - Method of operating multiple-effect absorption refrigerator and water heater/cooler for preventing corrosion of flue wall at partial load - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a flue from being corroded by an exhaust gas drain that may form in a high-temperature regenerator if the temperature of an absorbing solution drops during partial-load operation. <P>SOLUTION: During the partial-load operation, of the absorbing solution 1b whose temperature id lowered in advance by a low-temperature heat exchanger 6 before it is sprinkled by an absorber 1, an amount determined according to the exhaust gas temperature t<SB>e</SB>of the high-temperature regenerator 3 is supplied to a reservoir 1r of the absorber 1 without passing through the low-temperature heat exchanger 6. Thus, the absorbing solution sprinkled within the absorber 1 and collected in the reservoir 1r after absorbing refrigerant steam is heated by the absorbing solution 1b<SB>1</SB>supplied to the reservoir 1r, without the collected absorbing solution passing through the low-temperature heat exchanger 6, to elevate in advance the temperature of the absorbing solution 1a going to the low-temperature heat exchanger 6 from the absorber 1, so as to avoid the temperature drop of the absorbing solution 3a supplied to a high temperature regenerator 3 and control the temperature drop of high- temperature regenerator exhaust gas 29. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for preventing corrosion of a flue wall at a partial load in a multiple-effect absorption refrigerator / cooler / cooler / heater, and more particularly to a partial load operation regardless of cooling / heating operation. When the temperature becomes high, the temperature of the exhaust gas of the high temperature regenerator decreases due to the decrease in the temperature of the absorption liquid that is introduced into the high temperature regenerator, and the operation that can suppress the corrosion on the flue wall of the high temperature regenerator due to the exhaust gas drain caused It is about law.

[0002]

2. Description of the Related Art Absorption refrigerators, absorption chiller-heaters and the like are capable of taking out cold water or hot water by changing the concentration of an absorbing liquid circulating in the machine. For example, in a double-effect absorption refrigerating machine, as shown in FIG. 17, an evaporator 5 and an absorber 1 each consisting of a vacuum container, a low temperature regenerator 2 and a condenser 4 having a higher pressure than those, The burner 3A includes a high-temperature regenerator 3 that burns, for example, city gas to obtain heat energy.

In the evaporator 5, latent heat of vaporization is removed by the refrigerant liquid 5w flowing down to the outer surface of the evaporator pipe 5p under high vacuum, and the cold water 20 flowing through the evaporator pipe is cooled. Absorber 1
Then, the refrigerant vapor 5s generated in the evaporator 5 is replaced with the absorber pipe 1p.
By cooling with cooling water 9w flowing through the absorption liquid 1b
And the inside of the container is maintained at a high vacuum. In the low temperature regenerator 2, the refrigerant vapor 3 separated and evaporated in the high temperature regenerator 3
s is passed through the low temperature regenerator tube 2p and the latent liquid heats and concentrates the absorbing liquid 2m to separate and evaporate the refrigerant 2s. High temperature regenerator 3
Then, the absorption liquid 3m is heated and concentrated in a vacuum to form the refrigerant vapor 3s.
Generate. In the condenser 4, the refrigerant vapor 2s evaporated in the low temperature regenerator 2 is cooled by the cooling water 9w flowing in the condenser pipe 4p and condensed and liquefied. The cooling water 9w that has been pumped by the cooling water pump 9a and has flowed through the absorber pipe 1p and the condenser pipe 4p.
Is circulated after being cooled by a cooling tower (not shown).

In the operation of such an absorption refrigerator / cooler / heater, not only the cooling operation but also the refrigerant vapor evaporated in the high temperature regenerator 3 by opening the cooling / heating switching valves 21 ₃ and 21 ₂ as shown in FIG. 3s is sent to the evaporator 5, and if the low temperature regenerator 2 also generates the refrigerant vapor 2s, it is also sent to the evaporator pipe 5
Heating operation can be performed by heating the warm water 20 flowing through p. In either case of cooling or heating, when controlling the temperature of the cold water or the hot water 20, generally, the cold / hot water outlet temperature t
Based on the above, the heating amount in the high temperature regenerator 3 is adjusted by a fuel control valve (not shown).

By the way, in the above heating operation, it is not necessary to condense the refrigerant vapor 3s generated in the high temperature regenerator 3 and the refrigerant vapor 2s generated in the low temperature regenerator 2 in the condenser 4, and the refrigerant vapor in the absorber 1 as well. 5s (see Figure 17)
Need not be absorbed positively. The former can be easily understood from the fact that the short path conduit 3c shown in FIG. 18 is provided.

As described above, it is not necessary to condense the refrigerant vapor or absorb the refrigerant vapor at the time of heating because the refrigerant vapors 3s and 2s are not required.
Is used for heating the warm water 20 as it is. Therefore, in the evaporator 5, the refrigerant liquid 5w generated as a result of the refrigerant vapor exchanging heat with the hot water and condensing is increasing, and the refrigerant liquid 5w overflows from the refrigerant reservoir 5r and moves to the absorber 1 by itself. Therefore, although the dispersion pipe 1c of the absorber is used to return the absorption liquid from the low temperature heat exchanger 6 to the absorber 1, the dispersion is intended to absorb the refrigerant vapor generated in the evaporator into the absorption liquid. Not something to do.

For this reason, it is not necessary to flow the cooling water into the cooling water piping system 9 leading to the absorber pipe 1p and the condenser pipe 4p, and therefore the cooling water pump 9a is not operated during the heating operation. . Further, as shown in FIG. 17, it is not necessary to pump up and spray the refrigerant liquid 5w from the refrigerant reservoir 5r of the evaporator 5, and the refrigerant pump 5h is not operated. However, the absorption liquid takes about the same concentration change as during cooling while hot water is generated by the refrigerant vapor generated in the system,
There is no change in following the same route and circulating.

In such absorption refrigerators and the like, energy saving is being promoted based on the principle of double effect. However, in order to improve heat exchange efficiency in the system, as shown in FIG. A heat exchanger 6 and a high temperature heat exchanger 7 are installed. The high temperature heat exchanger 7 preheats the absorbing liquid 3a toward the high temperature regenerator 3, and the high temperature concentrated absorbing liquid 3b derived from the high temperature regenerator 3 is introduced as its heat source. The low temperature heat exchanger 6 preheats the absorption liquid 1a directed to the low temperature regenerator 2, and in the illustrated example, the absorption liquid 2b led out from the low temperature regenerator 2 and the concentrated absorption liquid 3b leaving the high temperature heat exchanger 7. _The absorbing liquid 1b obtained by merging with ₇ is used as a heat source while being returned to the absorber 1.

By the way, recently, in buildings and factories,
Cogeneration systems capable of heating and cooling privately by heating city gas have been increasingly introduced. As the power generation equipment, the engine is driven by the combustion of city gas to turn the generator, and as the cooling and heating equipment, the absorption chiller,
A water heater is used.

Since both facilities are common in that they use city gas as fuel, they can be grouped together as a cogeneration system. However, the significance of being an integrated facility is totally despite the fact that the power generation system and the heating and cooling system are different. The goal is to reduce city gas consumption. That is, the generation of exhaust heat is inevitable in the power generation equipment, but if this can be used not only in the cooling operation but also in the heating operation, the gas consumption in the cooling and heating equipment can be reduced.

Incidentally, in the gas engine, the cooling water after cooling the casing is about 80 to 90 ° C. Even if a large amount of this amount of exhaust heat is used, the heat energy possessed by the exhaust heat is not significant, and in the end, it can be used only for small-scale heating or hot water supply. However, in the absorption refrigerator / cooler / chiller / heater, since the concentration / dilution of the absorbing solution is a cycle, even the above-mentioned low-temperature waste heat can contribute to a certain extent for heating or evaporation of the absorbing solution. Attention is paid to this point.

An example of an absorption refrigerating machine / cooling / heating machine in a cogeneration system in which such a gas engine for power generation and an absorption refrigerating machine / cooling / heating machine are put together is proposed in Japanese Patent Laid-Open No. 11-237136. There is. The exhaust heat used here is, from the viewpoint of the absorption refrigerator / cooler / heater,
It is discharged from the heat source of the power generation system outside the system, and sensible heat / latent heat exchange is possible if it comes into contact with the absorbing liquid with a low temperature, and absorption refrigeration is achieved by recovering heat from the exhaust heat. It is possible to reduce the amount of heating required for water heaters and water heaters.

It is needless to say that it is desirable from the viewpoint of energy saving to take in the exhaust heat existing outside and effectively use it as a heat source. Recently, efforts have been made to further increase the efficiency of exhaust heat recovery, reduce the fuel consumption in absorption chillers and chiller-heaters as much as possible, and increase the gas reduction rate, and the expectations are increasing. ing.

[0014]

By the way, even if the above-mentioned waste heat water is used to save energy, whether it is a cooling operation or a heating operation, when it is a partial load operation of 50% or less, for example. However, the temperature of the exhaust gas emitted from the high temperature regenerator, which has heated the absorption liquid at a low temperature, may drop to 70 to 80 ° C, which is extremely low. In this way, when the exhaust gas becomes 100 ° C. or less, a part of the exhaust gas is often condensed on the wall surface of the flue (see reference numeral 3B in FIG. 17),
Carbon dioxide corrosion occurs when gas is fired, and sulfuric acid corrosion occurs when oil is fired.

This is because the heating amount in the high temperature regenerator is suppressed during the partial load operation. That is, in the cooling operation, the refrigerant vapor generated in the high temperature regenerator at the partial load becomes smaller than that at the full load, and the refrigerant liquid amount supplied to the evaporator decreases accordingly. Since the amount of refrigerant vapor generated in the evaporator and transferred to the absorber will be reduced, the cooling burden on the refrigerant vapor of the cooling water that is constantly flowed in the absorber pipe during cooling operation regardless of load fluctuations will be reduced. However, the absorption liquid sprayed to absorb the refrigerant vapor by that amount is cooled more strongly than during full load operation.

Although not limited to partial load operation, cooling is performed when the temperature of the cooling water supplied to the absorber pipe is extremely low, such as 10 ° C., or when the cooling water circulates at about 32 ° C. during operation. The water may be only 22 ° C., for example, at the time of start-up, and the above-mentioned situation occurs even when this low-temperature cooling water is supplied.

On the other hand, even in the heating operation, when the refrigerant vapor generated in the high temperature regenerator decreases due to the partial load, the amount of refrigerant vapor supplied to the evaporator decreases. Cooling water does not flow into the absorber pipe, but the amount of refrigerant vapor moving from the evaporator and the amount of high-temperature refrigerant liquid flowing from the liquid reservoir of the evaporator are reduced, so absorption in the liquid reservoir of the absorber is reduced. The liquid temperature also becomes lower than that during full load operation. The same is true during cooling operation, but if the temperature of the absorption liquid introduced from the absorber to the low-temperature heat exchanger becomes low, the concentrated absorption liquid returned to the low-temperature heat exchanger will also cool more strongly than during full load operation. As a result, the temperature of the absorbing liquid sprinkled in the absorber also drops.

As described above, when the partial load is reached, the temperature of the absorbing liquid in the absorber liquid reservoir is lowered, and when the absorbing liquid having a low temperature is sent to the low temperature heat exchanger, it is discharged from the low temperature heat exchanger and then regenerated at low temperature. Whether it is sent to the high temperature regenerator through the regenerator or directly supplied to the high temperature regenerator, it remains lower than that at the full load operation even when reaching the high temperature regenerator. In the high temperature regenerator, combustion is suppressed because of partial load,
Generates refrigerant vapor with a small amount of combustion. Since the temperature of the absorbing liquid is low, the amount of energy consumed for heating the absorbing liquid is large, and the thermal energy taken out by the exhaust gas is small. This lowers the temperature of the exhaust gas.

The present invention has been made in view of the above-mentioned circumstances, and an object thereof is to utilize even the heat of heat existing outside the system of the absorption refrigerator / cooler / cooler, particularly low temperature exhaust heat, to utilize the refrigerant. Even if the steam is generated to reduce the burden of steam generation in the low-temperature regenerator and, in turn, to significantly reduce the gas consumption in the high-temperature regenerator, the absorbed liquid temperature during partial load operation Prevents flue wall corrosion during partial load in a multiple-effect absorption refrigerator / cooler / heater that prevents the flue from being corroded by the exhaust gas drain due to the temperature drop of the exhaust gas from the high temperature regenerator It is to provide a driving method.

[0020]

SUMMARY OF THE INVENTION The present invention is directed to an absorbing liquid introduced into the absorber, a low temperature regenerator, a high temperature regenerator, a condenser, an evaporator and an absorber and returned to the absorber as a heat source. Low temperature heat exchanger that preheats, the high temperature heat exchanger that preheats the absorbing liquid that is introduced from the high temperature regenerator as a heat source and that goes to the high temperature regenerator, the absorber pipe of the absorber and the condenser pipe of the condenser Absorption provided with a cooling water piping system, in which hot water introduced from outside the system and a hot water heat exchanger that exchanges heat with all or part of the absorption liquid that is derived from the absorber and heated in the low temperature heat exchanger It is applied to the operation method in refrigerators and chiller-heaters. As for the feature, referring to FIG. 1,
When the partial load operation is performed regardless of the cooling operation or the heating operation, the exhaust gas temperature t _e of the high temperature regenerator 3 in the absorbing liquid 1b that is previously cooled in the low temperature heat exchanger 6 in preparation for the spraying in the absorber 1 The liquid amount determined based on the low temperature heat exchanger 6
Is supplied to the liquid reservoir 1r of the absorber 1 without passing through. Then, the absorption liquid that is sprayed in the absorber 1 and absorbs the refrigerant vapor and collects in the liquid reservoir 1r is heated by the absorption liquid 1b ₁ supplied to the liquid reservoir 1r without passing through the low temperature heat exchanger 6. By raising the temperature of the absorption liquid 1a from the absorber 1 toward the low temperature heat exchanger 6 in advance, the temperature drop of the absorption liquid 3a supplied to the high temperature regenerator 3 is avoided, and the temperature of the high temperature regenerator exhaust gas 29 is lowered. This is the operation method to prevent corrosion of the flue wall during partial load so that it can be suppressed.

In the cooling water piping system 9, the cooling water 9 is used during the cooling operation.
w is made to flow from the condenser pipe 4p toward the absorber pipe 1p, and due to the cooling water having a low temperature before flowing through the absorber pipe, the saturated pressure in the condenser 4 is passed through the absorber pipe 1p and then the condenser. The saturation pressure generated in the condenser 4 is set to be lower than the saturation pressure generated by the cooling water flowing into the pipe 4p.

As shown in FIG. 12, the multi-effect absorption refrigerator / cooler / heater may not be provided with a hot water heat exchanger.

Referring to FIG. 8, a desired amount of absorbing liquid 1b, which is previously cooled in low temperature heat exchanger 6, is passed through low temperature heat exchanger 6 in preparation for spraying in absorber 1 as shown in FIG. Instead of supplying the liquid to the liquid reservoir 1r of the absorber 1, the amount of liquid determined based on the exhaust gas temperature t _e of the high temperature regenerator 3 does not pass through the low temperature heat exchanger 6 of the evaporator 5. Supply to the liquid reservoir 5r. Then, the absorbing liquid that is sprayed in the absorber 1 and absorbs the refrigerant vapor and collects in the liquid reservoir 1r is supplied to the liquid reservoir 5r of the evaporator 5 without passing through the low temperature heat exchanger 6 and then the absorber 1r. Of the absorption liquid 3a supplied to the high temperature regenerator 3 by raising the temperature of the absorption liquid 1a directed from the absorber 1 to the low temperature heat exchanger 6 in advance by raising the temperature by the absorption liquid flowing into the liquid reservoir 1r of Avoid the decline,
The temperature drop of the high temperature regenerator exhaust gas 29 can be suppressed. In addition, as shown in FIG. 11, not only the absorbing liquid may be supplied to the evaporator 5, but the absorbing liquid may be simultaneously sent to the absorber 1.

As shown in FIG. 16, during heating operation, the exhaust gas temperature t of the high temperature regenerator 3 of the absorbing liquid 3b introduced into the high temperature heat exchanger 7 before directly or indirectly returning to the low temperature heat exchanger 6. _The amount of liquid determined based on _e is supplied to at least one of the liquid reservoirs 1r and 5r of the absorber 1 and the evaporator 5 without passing through the high temperature heat exchanger 7. Also in this case, the occurrence of corrosion in the flue 3B of the high temperature regenerator during heating partial load operation can be suppressed.

[0025]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a flue wall corrosion prevention operation method under partial load in a multiple-effect absorption refrigerator / cooler / heater according to the present invention will be described in detail with reference to the drawings showing the embodiment. Explained. FIG. 1 shows an absorber 1, a low temperature regenerator 2,
A high temperature regenerator 3, a condenser 4, an evaporator 5, a low temperature heat exchanger 6 for preheating the absorbing liquid 1a toward the low temperature regenerator 2, and a high temperature heat exchanger 7 for preheating the absorbing liquid 3a toward the high temperature regenerator 3. The structure of the double effect absorption refrigerator / cooler / heater 10 is shown. By the way, a pool boiling type heat exchange device is adopted for the low temperature regenerator 2, and the refrigerant vapor 3s generated in the high temperature regenerator 3 is received by the regenerator tube 2p as a heating source, and the regenerator tube is buried in the absorbing liquid 2m. A vapor space 2a for temporarily storing the refrigerant vapor 2s and leading it to the condenser 4 is secured above.

The function and action are as described in the section "Prior Art", and the same reference numerals as those in FIG. In the high temperature regenerator 3, hot gas obtained by burning city gas by the burner 3A is used as a heating source.
The refrigerant vapor 3s generated in the high temperature regenerator 3 is introduced into the low temperature regenerator 2 as a heating source. The absorbing liquid (concentrated absorbing liquid) 3b derived from the high temperature regenerator 3 is introduced into the high temperature heat exchanger 7 as a heat source, and the absorbing liquid 1b returned to the absorber 1 is introduced into the low temperature heat exchanger 6 as a heat source. It The same applies to the point that a cooling water piping system 9 is provided, which connects the absorber pipe 1p of the absorber 1 and the condenser pipe 4p of the condenser 4.

In this example, the absorption refrigerator / cooler / heater 10 is placed in an environment where exhaust heat of 83 to 95 ° C. exists outside the system. That is, as with the high temperature regenerator 3, a gas engine (smallly shown in FIG. 3) 12 that burns city gas to obtain power is installed, and the equipment of the absorption refrigerator / cooler / heater 10 is installed by the gas engine 12. When it is installed together with a power generation facility for driving the power generator 13, the heat energy held by the exhaust heat water after cooling the gas engine is to be positively utilized. In FIG. 3, numeral 14 shown at the gas engine 12 is a cooling tower for heat radiation, 15 is an exhaust gas heat exchanger,
Reference numeral 8 is a three-way switching valve.

Returning to FIG. 1, the absorption chiller / cooler / heater system is provided with waste heat hot water 12a, which is gas engine cooling water, and absorption liquid 1a derived from the absorber 1 through the low temperature heat exchanger 6. The exhaust heat hot water heat exchanger 8 for heat exchange is installed at a position higher than the low temperature regenerator 2. In this example, this waste heat hot water heat exchanger 8
A pool boiling heat exchange device is adopted in the same manner as the low temperature regenerator 2 to temporarily store the refrigerant vapor 8s generated from the absorbing liquid 8m that comes into contact with the exhaust heat hot water pipe 8p, and also the space for the vapor of the low temperature regenerator 2 A vapor reservoir 8a is secured which can be led to the condenser 4 via 2a. In addition, a passage 8b for leading the absorption liquid 8m in the exhaust heat hot water heat exchanger 8 to the low temperature regenerator 2 is also provided. By the way, in this example,
The passage 8b also functions as a transfer path of the refrigerant vapor 8s to the low temperature regenerator 2.

By the way, the exhaust heat water 12a introduced into the exhaust heat water pipe 8p of the exhaust heat heat water heat exchanger 8 has a temperature of 83 to 95 ° C.
Is preferred. For example, when such a temperature cannot be obtained with the gas engine cooling water alone, the exhaust gas heat exchanger 15 (see FIG. 3) is used so that the cooling water can be heated by the exhaust gas of the gas engine such as 300 to 600 ° C. It suffices to provide it so that exhaust heat having a high temperature can be supplied as heat exchange water. Of course, hot water that has just been heat-exchanged with exhaust gas may be used without being particular about engine cooling water. In short, if the heat having the above-mentioned temperature exists in the form of hot water outside the system of the absorption refrigerator / cooler / heater, it can be used as the externally generated hot water.

The above description is the addition of the exhaust heat / hot water heat exchanger 8 to the multiple effect absorption refrigerator / cooler / heater shown in FIG. 17 and the operation of the exhaust heat / hot water heat exchanger 8. The details of the effects will be described later, and the points directly related to the present invention will be described below. That is, a branch pipe 25 is provided in the pipe line through which the absorbing liquid 1b goes to the low temperature heat exchanger 6, and the tip of the branch pipe 25 faces the liquid reservoir 1r of the absorber.
Then, for example, a flow rate control valve 26 is interposed in this branch pipe, and the temperature sensor 2 attached to the flue 3B of the high temperature regenerator 3
The opening degree can be adjusted according to the level of the exhaust gas temperature detected by 7.

A controller 28 is separately installed to adjust the opening. Information about whether combustion in the high temperature regenerator corresponds to a high load state by taking in an opening signal of a fuel control valve (not shown) that adjusts the heating amount in the high temperature regenerator 3 to the controller. Is obtained. If the combustion state is now high, the controller 28 may instruct some control based on the temperature signal from the temperature sensor 27, but ignores it for the control according to the present invention, and the flow control valve The flow control valve is kept closed without outputting a command signal to the switch 26.

When the information that the high temperature regenerator 3 is not in the high combustion state is input, the controller 28 causes the temperature sensor 27 to operate.
The control according to the present invention is made to function on the basis of the temperature signal from. PID calculation and the like are performed based on inputs such as how much the combustion state is and the temperature of the exhaust gas 29, and the partial flow rate of the absorbing liquid 1b before the low temperature heat exchanger 6 is determined according to the result. It The controller 28 calculates an opening degree corresponding to the flow rate and outputs a command signal to the flow rate control valve 26 in order to realize the divided flow rate.

When such an operation is performed during the partial load operation, the low temperature heat exchanger 6 is prepared for the spraying in the absorber 1 regardless of whether it is the cooling operation of FIG. 1 or the heating operation of FIG.
The amount of liquid of the absorbing liquid 1b which has been cooled in advance in accordance with the exhaust gas temperature t _e of the high temperature regenerator 3 is directly supplied to the liquid reservoir 1r of the absorber without passing through the low temperature heat exchanger 6. Like

By doing so, the absorbing liquid 1 scattered in the absorber 1 absorbs the refrigerant vapor and collects in the liquid reservoir 1r.
a is heated by the absorption liquid 1b ₁ supplied to the liquid reservoir without passing through the low temperature heat exchanger 6, and the temperature of the absorption liquid 1a directed from the absorber 1 to the low temperature heat exchanger 6 must be raised in advance. You can As a result, a large temperature drop of the absorbent 3a supplied to the high temperature regenerator 3 can be avoided, the temperature drop of the high temperature regenerator exhaust gas 29 can be suppressed, and the cause of corrosion of the flue 3B can be removed. Like It should be noted that the temperature transition of the absorbing liquid under cooling partial load can be easily understood by comparing it with a multi-effect absorption refrigerator / cooler / heater having a configuration before the present invention is applied. The multi-effect absorption refrigerator / cooler / heater 10A shown in FIG. 12, which does not have the hot water heat exchanger 8 and has a simple structure to be described later, will be described as an example.

Incidentally, in sending the absorbing liquid to the liquid reservoir 1r of the absorber, an on / off control valve may be employed instead of the flow rate control valve. In that case, the controller 28 may perform on / off time control. Although FIG. 1 shows the cooling operation, even if it is said that the control is performed based on the exhaust gas temperature t _e , the controller 28 is suitable for the cooling partial load, but the heating operation of FIG. Needless to say, the control suitable for each is individually performed.

This type of multi-effect absorption refrigerator / cooler / heater 1
0 is the cooling water 9w of the cooling water piping system 9 as shown in FIG.
Is passed through the absorber pipe 1p by the cooling water pump 9a and then flowed to the condenser pipe 4p. This takes the same idea as the case shown in FIG. On the other hand, in FIG. 1, the cooling water 9w is caused to flow from the condenser pipe 4p of the condenser 4 toward the absorber pipe 1p of the absorber 1 by the pump 9b. Eg 3
In the case of FIG. 3, the cooling water of 2 ° C. passes through the absorber 1 and the condenser 4
Although the temperature rises to about 36 ° C. at the time when the temperature reaches, the cooling effect in the condenser 4 is increased by the amount not consumed in the absorber 1 if it is first introduced into the condenser 4 as shown in FIG. As a result, the saturation pressure in the condenser 4 is generated in the condenser 4 by the cooling water having a low temperature before flowing through the absorber tube 1p and flowing into the condenser tube 4p after flowing through the absorber tube 1p. It can be kept below the saturation pressure.

Since the condenser 4 is connected to the steam reservoir 8a of the exhaust heat hot water heat exchanger 8 through the steam space 2a of the low temperature regenerator 2 and the passage 8b, the exhaust heat hot water heat exchanger 8 is provided. Has almost the same pressure as the condenser 4. As can be seen from this, if the pressure in the condenser 4 is low, the pressure in the exhaust heat hot water heat exchanger 8 is also reduced, and the vaporization can be promoted in the exhaust heat hot water heat exchanger even at a low temperature.

That is, in the exhaust heat hot water heat exchanger 8, the absorption liquid 8m is caused to recover latent heat of the exhaust heat hot water under the low saturation pressure of the condenser 4 in the vapor reservoir 8a, whereby the refrigerant vapor 8s. The generation load of the refrigerant vapor 2s in the low temperature regenerator 2 can be reduced by generating the. By promoting the generation of latent heat in this way, the amount of heat exchange can be increased. This is the regenerator tube 2 of the low temperature regenerator 2.
This means that the amount of the refrigerant vapor 3s from the high temperature regenerator 3 introduced into p can be reduced, and eventually the amount of gas consumed by the burner 3A can be reduced.

FIG. 1 shows, as just described, the cooling water piping system 9
The idea which is generally considered to be unsuitable for flowing the cooling water 9w from the condenser pipe 4p toward the absorber pipe 1p has been introduced.
Although it is described in Japanese Patent No. 48147, it is performed only in a very special case.

Generally, the cooling water is flowed from the absorber to the condenser for the following reasons. Both the absorber and the condenser are safe to come with cool cooling water. However, providing two cooling water systems such as one system for the absorber and one system for the condenser causes an increase in equipment cost. Therefore, as described above, the cooling water system of one system serves to cool the absorber and the condenser.

Therefore, if the cooling water returned from the cooling tower is made to flow from the condenser, the cooling water whose temperature has been raised in the condenser is introduced into the absorber, and the temperature of the absorbing liquid in the absorber becomes higher. . This reduces the refrigerant absorption capacity, that is, the absorption performance. On the other hand, in the condenser in which the cooling water having a high temperature is introduced when flowing from the absorber to the condenser, the condensation performance is slightly lowered. Both have advantages and disadvantages, but from the viewpoint of the efficiency of the absorption refrigerator, it is possible to keep the absorption performance of the absorber from flowing from the absorber to the condenser so that it is special. The cooling system in which the cooling water flows from the condenser to the absorber is not adopted except in such a case.

Nevertheless, although the flow is reversed in FIG. 1, this is because if the degree of cooling in the condenser is increased when an exhaust heat hot water heat exchanger utilizing exhaust heat is provided. The generation of steam is promoted, which in turn can reduce the load of refrigerant vapor generation in the low-temperature regenerator and high-temperature regenerator, and even if there is a decrease in absorption performance in the absorber, sufficient gas consumption is required to compensate for it. We believe that we will be able to bring significant reductions.

More specifically, when cooling water is flowed from the absorber to the condenser as shown in FIG. 3, the temperature corresponding to the saturation pressure in the condenser is, for example, 36.5 ° C. For example, when the flow is reversed as shown in FIG. 1, the temperature can be 33.0 ° C. The former saturation pressure is 57 to 62 mmHg
While the latter is 46 to 51 mmH
It becomes g. Considering that the temperature of the absorbing liquid 1a from the absorber 1 coming into the waste heat hot water heat exchanger 8 through the low temperature heat exchanger 6 is 71 to 81 ° C., the inlet temperature of the waste heat hot water heat exchanger 8 is considered. Of 90 ° C. and the outlet temperature of 80 ° C., a logarithmic average temperature difference of 5.5 to 6.0 ° C. can be achieved. According to this, as compared with that of 4.0 to 4.5 ° C. when flowing from the absorber to the condenser, a remarkably good heat exchange rate is obtained.

If the pressure of the exhaust heat / hot water heat exchanger 8 can be lowered in this manner, the saturation temperature is lowered and the exhaust heat can be recovered as latent heat at a low temperature. Here, it is omitted to show the heat balance in the case where the cooling water is flowed from the absorber to the condenser, and vice versa, but the refrigerant vapor generation amount in the high temperature regenerator is reduced or the temperature is slightly lowered. As a result, the amount of combustion in the latter high temperature regenerator can be greatly reduced as compared with the former.

In the former case (FIG. 3), even if the gas reduction rate of 10% is achieved as compared with the case where the exhaust heat / hot water heat exchanger is not provided, the heat transfer area is the same as that case. Nevertheless, in the latter case (in the case of FIG. 1), it reaches as much as 25%, and eventually the latter achieves a gas reduction rate of 2.5 times that of the former case. This teaches that even if the current heat transfer area is maintained, it is possible to introduce a waste heat hot water heat exchanger and its effect will be prominently exhibited, and it does not significantly increase ancillary costs. It also makes it easier to modify the equipment.

Here, the behavior of the exhaust heat / hot water heat exchanger 8 will be briefly described. In the example of FIG. 1, the exhaust heat hot water heat exchanger 8 is installed at a position higher than the low temperature regenerator 2. 32 ° C. cooling water was introduced into the condenser 4 and
If it is derived at 4 ° C, the average temperature is 33 ° C, and the saturation pressure at that time is around 50 mmHg. This condenser pressure also reaches the vapor reservoir 8a of the exhaust heat / hot water heat exchanger 8 through the low temperature regenerator 2 and the passage 8b.

The temperature of the absorbing liquid entering the waste heat hot water heat exchanger 8 from the low temperature heat exchanger 6 is slightly lower than 80 ° C. When the waste heat hot water is supplied at 90 ° C., the waste heat in the waste heat hot water heat exchanger is exhausted. Hot water pipe 8p
The absorbing liquid that comes into contact with the liquid is vaporized under the saturation pressure. That is, latent heat is taken from the exhaust heat water to generate refrigerant vapor from the absorbing liquid. The waste heat hot water heat exchanger 8 is supplied by the absorbing liquid 1a successively introduced from the low temperature heat exchanger 6 to the waste heat hot water heat exchanger 8.
The absorbing liquid 8m overflows from the inside, and is guided to the low temperature regenerator 2 through the passage 8b.

Even if the condenser 4 and the waste heat hot water heat exchanger 8 are said to have the same pressure, since the refrigerant is condensed in the condenser, the condenser pressure is a little, but the low temperature regenerator 2 and the exhaust heat are discharged. Lower than the hot water heat exchanger 8. Therefore, the refrigerant vapor 8s generated in the waste heat hot water heat exchanger 8 moves to the condenser 4 along the low temperature regenerator 2 and the passage 8b. If refrigerant vapor is generated in the exhaust heat hot water heat exchanger 8 in this manner, the refrigerant vapor generation load in the low temperature regenerator 2 is reduced as described above. The behavior of the absorption refrigerator / cooler / heater after that follows the explanation at the beginning.

By the way, in FIG. 1, it has been explained that the exhaust heat hot water heat exchanger 8 is of a pool boiling type in which the vapor reservoir 8a is secured above the exhaust heat hot water pipe 8p immersed in the absorbing liquid 8m. However, not limited to this, the exhaust heat hot water heat exchanger may have a falling liquid film type structure like the evaporator 5 and the absorber 1. That is, even if the exhaust hot water pipe to which the absorbing liquid is sprayed and the vapor reservoir occupy substantially the same space, the function thereof is not different from that of the pool boiling type.

The above-mentioned exhaust heat hot water heat exchanger 8 does not necessarily have to be positioned above the low temperature regenerator 2. For example, if the pump 16 is provided as shown in FIG. 3, the exhaust heat hot water heat exchanger 8 may be installed below the low temperature regenerator 2. Since only the absorbing liquid 8m flows through the passage 8d in which the pump 16 is interposed, a new vapor passage 8e for sending the generated refrigerant vapor 8s to the low temperature regenerator 2 is required. Thus, two of the passage 8d and the passage 8e may be provided toward the low temperature regenerator 2, but the passage 8d and the passage 8e cannot be shared like the passage 8b (see FIG. 1). In consideration of the above, the passage 8f may be provided instead of the passage 8e for direct transfer to the condenser 4.

Incidentally, although the notation of FIG. 3 is different from that of FIG. 1, it is the same as that of FIG. 1 except for the position of the exhaust heat / hot water heat exchanger 8 and the flow direction of the cooling water. It indicates that it is a reverse flow type absorption refrigerator / cooler / heater. As a matter of course, the present invention is not limited to the configuration of FIG. 1 and can be applied to FIG. Incidentally, in any of the configurations, when the temperature of the exhaust heat water is low, it is not preferable to exchange heat with the absorbing liquid, and the three-way switching valve 18 provided in the exhaust heat water passage is provided.
It should be possible to prevent the introduction of hot waste water by.

FIG. 4 shows an example in which the present invention is applied to a parallel flow type absorption refrigerator / cooler / cooler. In the figure, only the example in which the exhaust heat hot water heat exchanger 8 is placed below the low temperature regenerator 2 is shown, and an example corresponding to FIG. 1 is not shown.
In this parallel flow type, the low temperature heat exchanger 6
Part of the absorbing liquid 1a derived from the exhaust heat hot water heat exchanger 8
To the low temperature regenerator 2 and the remaining portion 3a ₁ is the high temperature heat exchanger 7
It is made to flow to the high temperature regenerator 3 through the both in parallel. Needless to say, the exhaust heat / hot water heat exchanger 8 is installed in the path toward the low temperature regenerator 2 because it is intended to reduce the refrigerant vapor generation in the low temperature regenerator 2. In that respect, it is not different from FIG. 1 and FIG.

In FIG. 5, a part of the absorbing liquid 8m of the exhaust heat hot water heat exchanger 8 is transferred to the low temperature regenerator 2 and the rest 3a ₂ is transferred to the high temperature heat exchanger 7. FIG. 6 shows that the absorption liquids 1a and 3a ₁ discharged from the low temperature heat exchanger 6 are sent to the exhaust heat hot water heat exchanger 8 and the high temperature heat exchanger 7, and the absorption liquid 8 discharged from the exhaust heat hot water heat exchanger 8
This is a different example of the parallel flow type in which m is transferred to the low temperature regenerator 2 and the absorbing liquid 8m ₁ is transferred to the high temperature heat exchanger 7.

In FIG. 7, the absorbent is not sent from the exhaust heat / hot water heat exchanger 8 to the low temperature regenerator 2, but only the concentrated absorbent 3b ₇ passing through the high temperature regenerator 3 and the high temperature heat exchanger 7 is supplied to the low temperature regenerator 2. It is an example of a series flow type absorption refrigerator / cooler / heater that is supplied with. Even in this case, the exhaust heat / hot water heat exchanger 8 generates the refrigerant vapor 8s, thereby reducing the refrigerant vapor generation amount in the low temperature regenerator 2. Although all the examples in FIGS. 4 to 7 are shown only during the cooling operation, there is no difference from FIG. 2 during the heating operation. In either case, when the exhaust gas temperature falls below the allowable level during the partial load operation, the control valve 26 of the branch pipe 25 operates by receiving a signal from the controller 28 to send the absorbing liquid having a high temperature to the absorber 1, thereby lowering the low temperature heat. The temperature of the absorbing liquid 1a led out to the exchanger 6 is adjusted so as not to drop undesirably.

FIG. 8 shows an example in which a branch pipe 31 is provided in the pipe line through which the absorbing liquid 1b goes to the low temperature heat exchanger 6 as in FIG.
The tip is facing the liquid reservoir 5r of the evaporator 5. The flow control valve 26 is interposed in this branch pipe, and the controller 28 is controlled by the exhaust gas temperature t _e detected by the temperature sensor 27 attached to the flue 3B of the high temperature regenerator 3 depending on the level of the exhaust gas temperature t _e.
The point that the opening degree can be adjusted by receiving a command from is the same as the above-mentioned example. In the case of this example, the evaporator 5
Liquid 1b that has not been cooled in low temperature heat exchanger 6 toward
_{In fact} , sending ₁ is nothing but supplying the absorbing liquid 1b ₁ indirectly to the liquid reservoir 1r of the absorber.

To add some explanation, it is not preferable to supply the absorbing liquid having a high temperature to the liquid reservoir 5r of the evaporator 5 during the cooling operation. This is because when the high temperature absorbing liquid 1b ₁ is mixed with the refrigerant liquid accumulated in the liquid reservoir 5r, the vaporizing action of the liquid pumped up and dispersed by the refrigerant pump 5h is diminished, and the latent heat thereof causes the evaporator pipe 5p to flow. This is because the ability to cool the cold water 20 flowing will decrease. However, since the operation is carried out with a partial load, there is no particular problem in that respect even if the cooling capacity is deteriorated. If the cooling capacity is too low, consideration may be given to the control setting so that the opening degree of the flow rate control valve 26 is slightly narrowed in advance.

FIG. 9 shows the heating operation. During the heating operation, the operation of the refrigerant pump 5h is usually stopped. This is also mentioned in the section of the prior art. But,
When the branch pipe 31 faces the evaporator 5, the absorption liquid 1b ₁
When the refrigerant liquid whose temperature has risen due to the mixing of the above is pumped up by the refrigerant pump 5h as shown in FIG. 10, the refrigerant vapor 3 is discharged during high load operation including full load operation.
Not only s and 8s, but the high temperature refrigerant liquid sprayed by the spray pipe 5c flows down on the outer surface of the evaporator pipe 5p, and the heating degree of the hot water 20 flowing therein causes the refrigerant vapor to drift in the evaporator 5. Compared to the case of only, it is dramatically improved, for example, 60 ℃
It will also be possible to obtain hot water that reaches the maximum level and to increase the heating capacity.

In addition, since the absorption liquid 1b ₁ is supplied to the evaporator 5, the total concentration of the absorption liquid in the absorber 1 is lowered, whereby the absorption liquid saturation temperature is lowered and the exhaust heat hot water heat exchange is performed. It is also possible to promote the latent heat recovery action in the device 8, and energy saving can be largely achieved in the heating operation of the absorption chiller / cooler / heater. Since the details thereof are described in Japanese Patent Application No. 2002-8238 by the same applicant, further description will be omitted here.

As can be seen from the above description, the branch pipe 31
If the absorption liquid 1b ₁ can be supplied to the evaporator 5 via the air conditioner, an undesired temperature decrease of the absorption liquid toward the high temperature regenerator 3 can be avoided during low load heating, while the evaporator can be heated during high load heating. It also brings about the effect of two birds with one stone, which can increase the amount of heat exchange at. Even in the configuration of FIG. 8 in which the absorbing liquid is supplied to the evaporator, the direction of the cooling water 9w in the cooling water piping system 9 may be as shown in FIG. Further, the parallel flow type shown in FIGS. 4 to 6 can be used, or the series flow type shown in FIG. 7 can be used.

FIG. 1 explained at the beginning shows that a desired amount of the absorbing liquid 1b, which is preliminarily cooled in the low temperature heat exchanger 6 in preparation for spraying in the absorber 1, is passed through the low temperature heat exchanger 6 without passing through the absorber. It has been supplied to the liquid reservoir 1r, and is shown in FIG.
Was supplied to the liquid reservoir 5r of the evaporator. Figure 11
Is the sump 1 of the absorber ₁ having a high temperature.
r and the liquid reservoir 5r of the evaporator 5 are distributed and supplied. Branch pipe 32 that realizes this
If the controller 28 controls the opening degree of the three-way valve 33, it is possible to adjust the supply amount of the absorbing liquid in both liquid reservoirs at an appropriate ratio.

In such a structure, the absorbing liquid that is sprayed in the absorber 1 and absorbs the refrigerant vapor 5s and collects in the liquid reservoir 1r does not pass through the low temperature heat exchanger 6 and is stored in the liquid reservoir 1r.
The temperature is raised by the absorption liquid directly supplied to r and the absorption liquid that is supplied to the liquid reservoir 5r of the evaporator and then flows into the liquid reservoir 1r. Needless to say, by lowering the temperature of the absorption liquid 1a from the absorber 1 toward the low temperature heat exchanger 6 in advance, the temperature drop of the absorption liquid 3a supplied to the high temperature regenerator 3 can be avoided, and the high temperature regenerator exhaust gas 29 The temperature drop can be suppressed. Of course, if the setting in the controller 28 is changed, it is needless to say that the branch pipe 32 is not limited to the parallel supply as shown in FIG. 11, but can be made to have the configuration shown in FIG. 1 or the configuration shown in FIG. In the case of FIG. 11 as well, the matters described in FIGS. 3 to 7 and FIGS. 9 and 10 are applicable, and thus the repeated description will be omitted.

FIG. 12 shows an example in which the present invention is applied to a multi-effect absorption refrigerator / cooler / heater 10A having no exhaust heat / hot water heat exchanger. Also in this configuration, any form of the present invention can be applied except for the action of the waste heat hot water heat exchanger and the flow of the cooling water flowing from the condenser to the absorber in the cooling water piping system 9. it can. The heating operation in this case is shown in FIG. 13. When the parallel flow type is used, the piping configuration is as shown in FIG. 14, and when the series flow type is used, the piping configuration is as shown in FIG. In the case of FIG. 12 as well, the matters described in FIGS. 8 to 11 are applicable, and thus the description thereof will be omitted.

Here, the absorbing liquid 1 directed to the low temperature heat exchanger 6
The transition of the temperature of the absorbing liquid will be specifically described by taking as an example the case where a desired amount of b is branched and returned to the liquid reservoir 1r of the absorber. It should be noted that the numerical value indicating the temperature is merely an example for the sake of easy understanding by comparing the two forms.

It is assumed that the cooling operation is in a partial load state in, for example, the apparatus shown in FIG. 17 in which the branch pipe 25 shown in FIG. 12 is not provided. The temperature of the low temperature heat exchanger 6 toward the spray pipe 1c of the absorber 1 is 35 ° C., and the absorbing liquid cooled by the cooling water 9w flowing through the absorber pipe 1p and accumulated in the liquid reservoir 1r becomes 30 ° C. When this is discharged to the low temperature heat exchanger 6, the temperature of the concentrated absorbing liquid 1b introduced at 63 ° C. becomes 35 ° C. described above. After passing through the low temperature heat exchanger 6, the low temperature regenerator 2
The temperature of the absorbing liquid 1a heading to the temperature is only 55 ° C., and the temperature of any of the liquids is about 10 ° C. lower than that under full load. And even if it is heated by the low temperature regenerator 2 and the high temperature heat exchanger 7, it often becomes only 100 ° C. or lower at the time of entering the high temperature regenerator 3. The concentrated absorbing liquid 3b discharged from the high temperature regenerator 3 also interrupts 100 ° C. in some cases at 110 ° C., and at the time of entering the low temperature heat exchanger 6 via the high temperature heat exchanger 7, the above 6
It drops to 3 ° C. At full load, the absorption liquid 3a entering the high temperature regenerator 3 is 140 to 160 ° C., and the temperature of the concentrated absorption liquid 3b discharged from the high temperature regenerator 3 is 150 to 170 ° C.
It can be seen that the temperature is markedly lower than that at ℃. By the way, the reason why the absorption liquid accumulated in the liquid reservoir 1r of the absorber tube is 30 ° C., which is lower than the cooling water temperature of 32 ° C. at full load,
This is because the temperature of the cooling water is suppressed and the cooling in the cooling tower tends to proceed due to the low absorption liquid temperature in the partial load operation.

On the other hand, in FIG. 12, a case where most of the absorbing liquid returned to the absorber at the time of partial load is flown to the branch pipe 25 will be described. The temperature of the low temperature heat exchanger 6 toward the spray pipe 1c of the absorber 1 is, for example, 65 ° C. However, since the amount is small, even if it is cooled by the cooling water 9w flowing through the absorber pipe 1p, the liquid Most of the absorption liquid accumulated in the reservoir 1r is the absorption liquid at 65 ° C. bypassing the low temperature heat exchanger 6. This is led to the low temperature heat exchanger 6 and heads for the low temperature regenerator 2 at 65 ° C. Low temperature regenerator 2 and high temperature heat exchanger 7
When it is heated at, it reaches nearly 120 ° C. when it enters the high temperature regenerator 3. The concentrated absorption liquid 3b leaving the high temperature regenerator 3 is 130
The temperature also reaches ℃, and when the temperature enters the low temperature heat exchanger 6 via the high temperature heat exchanger 7, the temperature becomes 65 ° C. mentioned above. If the absorbing liquid circulates at such a temperature, even in the partial load operation, the temperature at which the exhaust gas is condensed does not occur in the high temperature regenerator 3, so that carbonic acid corrosion or the like does not occur.

FIG. 16 shows the branch pipes 25, 31, 3 described above.
Different from 2, a branch pipe 35 is provided in a conduit from the high temperature regenerator 3 to the high temperature heat exchanger 7 and is connected to the liquid reservoir 1r of the absorber. By the way, the pressure of the high temperature regenerator 3 is, for example, 600 mmHg during the cooling operation, and the pressure of the absorber is 7 mm.
It's just Hg. Therefore, such a branch pipe can achieve the object of the present invention only when the pressure seal between the high temperature regenerator 3 and the absorber 1 is broken, that is, when the heating operation is performed. You can do it.

In this figure, during heating operation, as shown in FIG.
In the absorption liquid 3b introduced into the high temperature heat exchanger 7 before being returned to the low temperature heat exchanger 6 as described above, the liquid amount determined based on the exhaust gas temperature t _e of the high temperature regenerator 3 is changed to the high temperature heat exchanger 7 Is intended to be supplied to the liquid reservoir 1r of the absorber without passing through. In the case of the series flow type as shown in FIG. 7 and FIG. 15, the concentrated absorbent 3b exiting the high temperature heat exchanger 7 is returned to the low temperature heat exchanger 6 after passing through the low temperature regenerator 2. However, even in this case, the absorbing liquid 3b introduced into the high temperature heat exchanger 7 before being returned to the low temperature heat exchanger 6 indirectly, is subject to the branched flow.

As a result, the refrigerant liquid flowing from the liquid reservoir 5r of the evaporator 5 and the refrigerant vapor 3s dispersed in the absorber 1 are dispersed.
The absorption liquid that has been mixed with the absorption liquid that has absorbed
It is possible to raise the temperature of the absorbing liquid 1a from the absorber 1 toward the low temperature heat exchanger 6 by raising the temperature with the absorbing liquid 3b that does not pass through the high temperature heat exchanger 7. The temperature drop of the absorbing liquid 3a supplied to the high temperature regenerator 3 is avoided, and the temperature drop of the exhaust gas 29 of the high temperature regenerator 3 is suppressed. It should be noted that although all the matters described in FIGS. 1 to 15 are applicable, the operation is limited to the partial load state during heating as described above.

The examples of application to various absorption refrigerators / chillers / heaters have been described above, but the present invention is not limited to the double-effect type of each, but is also applied to the triple-effect type including an intermediate regenerator. It is clear from the idea that it is possible. Also, when the exhaust heat hot water heat exchanger is adopted, the example was used on the premise of utilizing the exhaust heat of the gas engine, but it is not limited to the exhaust heat hot water of the gas engine, and it is used in the above temperature range. If there is no warm water, it can be used. In that case, needless to say, the exhaust heat hot water heat exchanger may be what is called a hot water heat exchanger.

[0070]

According to the present invention, when a partial load operation is performed, the amount of liquid determined based on the exhaust gas temperature of the high temperature regenerator is stored in the liquid reservoir of the absorber without passing through the low temperature heat exchanger. Since it is supplied, it is possible to raise the temperature of the absorbing liquid in the absorber and then raise the temperature of the absorbing liquid to the low temperature heat exchanger in advance. This prevents the temperature drop of the absorbing liquid supplied to the high temperature regenerator, and suppresses the temperature drop of the high temperature regenerator exhaust gas, and prevents the occurrence of carbonic acid corrosion or sulfuric acid corrosion due to the generation of exhaust gas drain in the flue. Can be set.

When the cooling water is made to flow from the condenser pipe to the absorber pipe in the cooling water piping system, the saturation pressure in the condenser is increased by the cooling water having a low temperature before flowing through the absorber pipe. The saturation pressure generated in the condenser can be kept lower by the cooling water flowing into the condenser tube after flowing through the absorber tube. As a result, in the hot water heat exchanger, it is possible to cause the absorption liquid to recover the latent heat of the hot water under the low saturation pressure that reaches the condenser in the vapor reservoir, and the refrigerant vapor generates the refrigerant in the low temperature regenerator. The burden of steam generation can be reduced. The amount of refrigerant vapor from the high temperature regenerator that is introduced into the regenerator pipe can be reduced, the fuel consumed in the high temperature regenerator can be significantly reduced, and it can be compared with the case where cooling water flows from the absorber pipe to the condenser pipe. Then, the gas reduction rate may be increased to 2.5 times.

In a multi-effect absorption refrigerator / chiller / heater without a hot water heat exchanger, the effect of the hot water heat exchanger may not be exhibited, but the absorption liquid having a high temperature is supplied to the absorber. The flue corrosion prevention effect during partial load operation is not impaired. It should be noted that the same effect is exhibited even when the absorbing liquid is supplied to the evaporator or is sent to both the absorber and the evaporator at the same time. If the means for realizing the supply to the evaporator is adopted, the conditions for strengthening the heating action under the full load / high load during heating will be additionally provided.

Based on the exhaust gas temperature of the high temperature regenerator, a part of the absorption liquid introduced into the high temperature heat exchanger before being returned to the low temperature heat exchanger during the heating operation is stored in at least one of the absorber and the evaporator. If it is directly supplied, the temperature of the absorbing liquid accumulated in the absorber can be raised, and eventually the temperature of the exhaust gas of the high temperature regenerator can be suppressed from being lowered to prevent the flue from corroding.

[Brief description of drawings]

FIG. 1 shows a reverse-flow type absorption refrigerating machine / cooling / heating machine in a cooling operation to which a flue wall corrosion prevention operating method at partial load is applied in a multiple-effect absorption refrigerating machine / cooling / heating machine according to the present invention. Overall system diagram.

FIG. 2 is a system diagram of the absorption refrigerator / cooler / heater of FIG. 1 during heating operation.

FIG. 3 is a system diagram showing a cogeneration system and a cooling operation of the absorption refrigerator / cooler / heater when cooling water is flowed from the absorber pipe to the condenser pipe.

FIG. 4 is a system diagram in which the present invention is applied to a parallel flow type absorption refrigerator / cooler / cooler / heater.

5 is a system diagram applied to a parallel flow type absorption refrigerator / cooler / heater in which the flow passing through the exhaust heat / hot water heat exchanger is different from that in FIG. 4.

FIG. 6 is a system diagram applied to a parallel flow type absorption refrigerator / cooler / heater in which the flow passing through the exhaust heat / hot water heat exchanger is different from those in FIGS. 4 and 5.

FIG. 7 is a system diagram when the present invention is applied to a series flow type absorption refrigerator / cooler / heater.

FIG. 8 is a system diagram of a reverse-flow type multiple-effect absorption refrigerator / cooler / heater configured to supply an absorbing liquid to an evaporator under partial load operation during cooling.

FIG. 9 is a system diagram when the multi-effect absorption refrigerator / cooler / heater of FIG. 8 is in heating operation.

FIG. 10 is a system diagram in the case where the refrigerant pump is driven to spray the refrigerant liquid mixed with the absorbing liquid when the multi-effect absorption refrigerator / cooler / heater of FIG. 8 is operated for heating.

FIG. 11 is a system diagram of a reverse-flow type multiple-effect absorption refrigerator / cooler / heater configured to supply the absorbing liquid to both the absorber and the evaporator under partial load operation during cooling.

FIG. 12 is a system diagram of a reverse-flow type multi-effect absorption refrigerator / cooler / heater that does not include a waste heat / hot water heat exchanger, when absorbing liquid is supplied to the absorber.

FIG. 13 is a system diagram when the multi-effect absorption refrigerator / cooler / heater of FIG. 12 is in heating operation.

FIG. 14 is a system diagram in which the idea of FIG. 12 is applied to a parallel flow type absorption refrigerator / cooler / heater.

FIG. 15 is a system diagram when the concept of FIG. 12 is applied to a series flow type absorption refrigerator / cooler / hot water heater.

FIG. 16 shows a reverse-flow type multi-effect absorption refrigerator / cooler without a waste heat / hot water heat exchanger, in which the absorbing liquid is taken out and supplied to the absorber before the high temperature heat exchanger. System diagram.

FIG. 17 is a system diagram of an entire system of an existing reverse-flow type absorption refrigerator / cooler / heater as a conventional technique, in a cooling operation.

FIG. 18 is a system diagram of the multi-effect absorption refrigerator / cooler / heater of FIG. 17 during heating operation.

[Explanation of symbols]

1 ... absorber, 1a ... absorbing solution, 1b, 1b ₁ ... absorbent liquid,
1c ... Spraying tube, 1p ... Absorber tube, 1r ... Absorbing liquid reservoir, 2
… Low temperature regenerator, 3… High temperature regenerator, 3B… Flue, 3a, 3
a ₁ , 3a ₂ ... Absorbing liquid, 3b, 3b ₇ ... Absorbing liquid (concentrated absorbing liquid), 4 ... Condenser, 4p ... Condenser tube, 5 ... Evaporator, 5r
… Refrigerant liquid reservoir, 5s… Refrigerant vapor, 6… Low temperature heat exchanger, 7
... high temperature heat exchanger, 8 ... hot water heat exchanger (exhaust heat hot water heat exchanger), 9 ... cooling water piping system, 9w ... cooling water 10,10A
... Double-effect absorption refrigerator / cooler / heater, 12a ... Exhaust heat hot water (externally generated hot water), 25 ... Branch pipe, 26 ... Flow control valve (two-way valve), 27 ... Exhaust gas temperature sensor, 28 ... Controller, 29 ... exhaust gas 31 ... branch pipe, 33 ... flow control valve (three-way valve), 35 ... branch pipe, t _e ... exhaust gas temperature.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Masumi Ota             1000 Aochi-cho, Kusatsu City, Shiga Prefecture             Business (72) Inventor Toshio Kawada             1000 Aochi-cho, Kusatsu City, Shiga Prefecture             Business F term (reference) 3L093 AA05 BB11 BB22 BB37 CC00                       DD00 EE00 EE12 GG02 HH04                       HH15 JJ04 KK01

Claims (6)

[Claims] 1. An absorber, a low-temperature regenerator, a high-temperature regenerator, a condenser, an evaporator, and a low-temperature heat exchanger for introducing the absorption liquid returned to the absorber as a heat source and preheating the absorption liquid discharged from the absorber. , A high-temperature heat exchanger for preheating the absorbing liquid that is introduced from the high-temperature regenerator and is introduced as a heat source toward the high-temperature regenerator, and cooling water in which the absorber pipe of the absorber and the condenser pipe of the condenser are connected. Absorption refrigerator equipped with a hot water heat exchanger that exchanges heat between the piping system, hot water introduced from outside the system, and all or part of the absorption liquid that is derived from the absorber and heated by the low-temperature heat exchanger In the operation method of the water machine, when the partial load operation is performed regardless of the cooling operation or the heating operation, the high temperature regenerator among the absorbents that are previously cooled in the low temperature heat exchanger in preparation for spraying in the absorber. Determined based on the exhaust gas temperature of The amount of liquid that has been supplied to the liquid reservoir of the absorber without passing through the low temperature heat exchanger, absorbs the refrigerant vapor dispersed in the absorber and accumulates in the liquid reservoir, and absorbs the absorbed liquid to the low temperature heat exchanger. Of the absorption liquid supplied to the high temperature regenerator by raising the temperature of the absorption liquid from the absorber to the low temperature heat exchanger in advance by raising the temperature by the absorption liquid supplied to the liquid reservoir without passing through A method for preventing flue wall corrosion during partial load in a multi-effect absorption refrigerator / cooler / heater, which is characterized in that it is possible to prevent the temperature from falling and to suppress the temperature drop of the exhaust gas from the high temperature regenerator. 2. The cooling water piping system causes cooling water to flow from the condenser pipe toward the absorber pipe during cooling operation, and the cooling water having a low temperature before flowing through the absorber pipe causes The multi-effect absorption refrigerator according to claim 1, wherein the saturation pressure is set to be lower than the saturation pressure generated in the condenser by the cooling water flowing into the condenser tube after flowing through the absorber tube. Operation method of flue wall corrosion prevention in chiller-heater under partial load. 3. The operation method for preventing corrosion of a flue wall during partial loading in a multiple-effect absorption refrigerator / cooler / hot water generator according to claim 1, wherein the hot water heat exchanger is not provided. 4. A desired amount of the absorbing liquid which is previously cooled in the low temperature heat exchanger in preparation for spraying in the absorber, is supplied to a liquid reservoir of the absorber without passing through the low temperature heat exchanger. Instead, the amount of liquid determined based on the exhaust gas temperature of the high-temperature regenerator is supplied to the liquid reservoir of the evaporator without passing through the low-temperature heat exchanger, and the refrigerant vapor dispersed in the absorber is absorbed. Then, the absorption liquid accumulated in the liquid reservoir is heated by the absorption liquid flowing into the liquid reservoir of the absorber after being supplied to the liquid reservoir of the evaporator without passing through the low temperature heat exchanger. By preliminarily raising the temperature of the absorbing liquid toward the heat exchanger, the temperature of the absorbing liquid supplied to the high temperature regenerator can be prevented from decreasing, and the temperature drop of the high temperature regenerator exhaust gas can be suppressed. In any one of Claim 1 thru | or 3. Flue wall corrosion prevention operation method at the time of partial load of the mounting has been multiple-effect absorption chiller-chiller. 5. Supplying a desired amount of absorbing liquid, which has been lowered in temperature in said low temperature heat exchanger, to a liquid reservoir of said absorber without passing through said low temperature heat exchanger in preparation for spraying in said absorber. Instead, the amount of liquid determined based on the exhaust gas temperature of the high temperature regenerator is distributed to the liquid reservoir of the absorber and the liquid reservoir of the evaporator without passing through the low temperature heat exchanger, and in the absorber, The absorption liquid that is sprayed and absorbs the refrigerant vapor and collects in the liquid reservoir is supplied to the absorption liquid supplied to the liquid reservoir and the liquid reservoir of the evaporator without passing through the low temperature heat exchanger, and then to the liquid reservoir. Raise the temperature with the flowing absorption liquid,
By increasing the temperature of the absorption liquid from the absorber toward the low temperature heat exchanger in advance, it is possible to avoid the temperature drop of the absorption liquid supplied to the high temperature regenerator, and to suppress the temperature drop of the high temperature regenerator exhaust gas. 4. The method according to claim 1, wherein
A method for preventing flue wall corrosion during partial load in a multiple-effect absorption refrigerator / cooler / heater described in any one of 1. 6. A desired amount of the absorbing liquid which has been lowered in temperature in the low temperature heat exchanger in preparation for spraying in the absorber, is supplied to a liquid reservoir of the absorber without passing through the low temperature heat exchanger. Instead, during heating operation, the amount of liquid that is determined based on the exhaust gas temperature of the high temperature regenerator out of the absorption liquid that is introduced into the high temperature heat exchanger before being returned directly or indirectly to the low temperature heat exchanger. , Supplying it to at least one of the liquid reservoirs of the absorber and evaporator without passing through the high temperature heat exchanger, absorbing the refrigerant vapor scattered in the absorber and accumulating in the liquid reservoir, The temperature of the absorption liquid supplied to the high temperature regenerator is reduced by raising the temperature of the absorption liquid that does not pass through the exchanger and raising the temperature of the absorption liquid from the absorber to the low temperature heat exchanger in advance. Avoid and lower the temperature of high temperature regenerator exhaust gas Flue wall corrosion prevention operation method at the time of partial load in a multiple effect absorption refrigerating machine, chiller as claimed in any one of claims 1 to 3, characterized in that to be able to suppress.