JPH0555787B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a multi-effect absorption refrigeration system, and more particularly to a multi-effect absorption refrigeration system that shortens startup time and is suitable for energy saving.

[Background of the invention]

Absorption refrigeration equipment that uses water as a refrigerant and a salt solution such as an aqueous lithium bromide solution as an absorbent has conventionally used the following techniques to prevent crystallization of the absorbent solution (hereinafter referred to as solution) in flow paths such as piping. When the operation is stopped, a dilution operation is performed and the operation is stopped in a state where the temperature is thinner than the crystal precipitation temperature at the ambient temperature.

Therefore, at startup, it is necessary to generate diluted refrigerant. Therefore, the time τ required to start up the absorption refrigeration system is given by the ratio of the amount of heat Q _D required to generate the refrigerant and the amount of heat Q _G provided by the external heat source, τ≒Q _D /Q _G ……(1) .

By the way, the coefficient of performance COP of an absorption refrigeration system is expressed as COP = Refrigeration capacity Q _G ... (2), and the value is COP 2 ≒ 1.2 for a double effect absorption refrigeration system, COP ₂ ≒ 1.2 for a triple effect absorption refrigeration system. COP ₃ is approximately 1.5 to 1.8. That is, the amount of heat Q _G of the external heat source has the following relationship: Q _G triple effect = 0.67 to 0.75 Q _G double effect (3).

Moreover, since the triple-effect absorption refrigerating apparatus is equipped with one more regenerator than the double-effect absorption refrigerating apparatus, the amount of sealed liquid is larger.

Therefore, Q _D is Q _D triple utility > Q _D double utility.

That is, the triple-effect absorption refrigerating apparatus has the disadvantage that it takes 25% or more of the time τ required for startup compared to the double-effect absorption refrigerating apparatus.

Also, for example, when using it as a hot/cold water machine,
Since it is used simply as a boiler, it has the disadvantage that its heating capacity is insufficient compared to its cooling capacity. Therefore, an operation method can be considered in which the heat input of the high-temperature regenerator is increased during heating and decreased during cooling, but a new drawback arises in that the high-temperature regenerator must be increased in size to match the maximum heat input.

This high-temperature regenerator is more expensive than a normal boiler that uses water as a heat medium because it requires consideration of the corrosivity of the solution, and the sealed solution itself is expensive. Therefore, increasing the heat input of the high-temperature regenerator during heating has the drawback of significantly increasing costs.

In addition, the heating capacity itself can be increased by installing an auxiliary hot water boiler separately from the triple-effect absorption chiller/heater, but this has the disadvantage that the installation space for the auxiliary hot water boiler increases.

[Purpose of the invention]

The present invention has been made in order to improve the drawbacks of the above-mentioned prior art, and provides a multi-effect absorption refrigeration system that makes it possible to significantly shorten the start-up time during cooling operation and improve the heating capacity during heating operation. is its purpose.

[Summary of the invention]

The configuration of the multi-effect absorption refrigeration apparatus according to the present invention includes a high-temperature regenerator using an external heat source as a heating source, and cooling steam generated by the high-temperature regenerator as a heating source for a solution in a subsequent low-temperature regenerator. , multiple low-temperature and medium-temperature regenerators that emit refrigerant vapor, equipment such as condensers, evaporators, absorbers, solution heat exchangers, solution circulation pumps, and piping that connects these absorption cycle operating equipment. In a multi-effect absorption refrigeration system comprising: The auxiliary boiler is connected to at least one of the plurality of low-temperature and medium-temperature regenerators by a heat medium piping so that it can serve as an auxiliary heating source for the plurality of regenerators.

Additionally, the idea behind developing the present invention is as follows:
It is as follows.

The present invention indirectly heats at least one of a medium-temperature regenerator and a low-temperature regenerator using an auxiliary external heat source according to the principle of a thermosiphon-only reboiler, thereby providing the required temperature for concentrating the solution in the cycle at the time of startup in cooling operation. This is intended to increase thermal energy to shorten startup time and to increase heating capacity during heating.

That is, since the solution in the cycle is at a low temperature when starting the cooling operation, it is first necessary to heat the solution to at least the boiling point.

Generally, the medium temperature regenerator and the low temperature regenerator are not heated at all during the time period during which the high temperature regenerator is heated by the primary external heat source and high temperature, high pressure refrigerant vapor is generated from the high temperature regenerator. Similarly, if the low temperature solution in the medium temperature regenerator is heated by the refrigerant vapor in the high temperature regenerator and boils, generating high temperature, high pressure refrigerant vapor that does not heat the low temperature regenerator, the low temperature regenerator will not heat up at all. Not done.

Therefore, in order to shorten the time it takes to heat the medium-temperature regenerator and low-temperature regenerator to a predetermined temperature level, it is necessary to heat the medium-temperature regenerator after the high-temperature regenerator is heated, as described above, and then We have reformed the serial heat transfer characteristic of multi-effect refrigeration equipment, in which the low-temperature regenerator is heated after the heat has been removed, and we have introduced an auxiliary boiler so that multiple regenerators such as high, medium, and low temperatures can be heated in parallel. It was designed to be installed.

In addition to the above, the idea is to use the thermal energy of the auxiliary boiler as an auxiliary heating source for hot water during slow room operation.

Furthermore, in order to reduce the cost of the heating medium of the auxiliary boiler, we considered using a refrigerant (water) circulating within the cycle as the heating medium of the auxiliary boiler.

Furthermore, in order to reduce the installation space, the thermosiphon-only reboiler principle is utilized for heat exchange between the auxiliary boiler and the low-temperature regenerator or medium-temperature regenerator or both, and the low-temperature regenerator or medium-temperature regenerator is installed on the top of the auxiliary boiler. It is designed so that .

[Embodiments of the invention]

Embodiments of the present invention will be described below with reference to FIGS. 1 to 7.

First, FIG. 1 is a cycle configuration diagram during cooling operation of a triple-effect absorption type water chiller/heater according to an embodiment of the present invention. In the figure, arrows indicate the flow of refrigerant, heat medium, or solution. There is.

We will begin with an explanation of the main components of a typical triple-effect absorption type water chiller/heater.

In FIG. 1, 1 is a high-temperature regenerator that is heated by a main heating source 14 related to an external heat source and generates refrigerant vapor;
2 is a medium temperature regenerator heated by the refrigerant vapor generated from the high temperature regenerator 1, 3 is a low temperature regenerator heated by the refrigerant vapor generated from the medium temperature regenerator 2, and 29 and 31 are the medium temperature regenerator 2 and the low temperature regenerator 2, respectively. The heated steam conduits 30 and 32 of the regenerator 3 are respectively connected to the medium temperature regenerator 2,
This is the condensed water conduit of the low temperature regenerator 3. 19 and 20 are orifices for reducing pressure.

A condenser 4 guides refrigerant vapor generated in the low-temperature regenerator to the condenser 4 through a conduit 33, and cools the refrigerant vapor with cooling water 16 to condense and liquefy it.

5 is an evaporator, which leads the liquid refrigerant in the condenser 4 to the evaporator 5 through a conduit 34, and sprays the liquid refrigerant with a refrigerant spray pump 10 onto a group of heat transfer tubes through which cold water 15 flows, evaporating the refrigerant and discharging the cold water. 15 to provide refrigeration capacity.

An absorber 6 absorbs the refrigerant vapor evaporated in the evaporator 5 into the solution concentrated in each of the three regenerators. Cooling water 16 flows through the heat transfer tube of the absorber 6 to cool the concentrated solution and remove the absorbed heat during absorption of refrigerant vapor.

The solution cooled and diluted in the absorber 6 is sent to the high temperature regenerator 1, medium temperature regenerator 2, and low temperature regenerator 3 through solution supply pipes 2 by a solution circulation pump 11, respectively.
3, 24, and 25, and are concentrated and returned to the absorber 6, which is discharged through solution discharge pipes 26, 27, and 28, respectively.

Note that solution exchangers 7, 8, and 9 are provided in order to save the amount of heating heat of each regenerator.

In the triple-effect absorption type water chiller/heater as described above, in the device of this embodiment, the vacuum steam boiler 12 related to the auxiliary boiler is disposed below the medium-temperature regenerator 2 and the low-temperature regenerator 3, and the intermediate-temperature regenerator 2 and the low-temperature regenerator 3 are respectively provided with heat exchangers 35 and 36, and the inlet sides of the heat exchangers 35 and 36 are connected to the vacuum steam boiler (hereinafter referred to as auxiliary boiler).
12 vapor phase sections and heat medium vapor conduits 37, 3, respectively.
The outlet sides of the heat exchangers 35 and 36 are communicated with the liquid phase portion of the auxiliary boiler 12 through condensed water conduits 39 and 40, respectively.

The auxiliary boiler 12 is provided with a safety valve, a temperature relay, a pressure switch, a liquid level switch, etc., although they are not particularly shown or explained.

The auxiliary heating source 13 uses combustion heat of kerosene, fuel gas, or the like. As the heat medium for the auxiliary boiler 12, water is desirable.

The operation of the triple-effect absorption type water chiller/heater having such a configuration will first be described with respect to cooling operation.

During start-up, the cold water 15 flows into the evaporator 5.
The cooling water 16 is passed through the heat transfer tubes of the condenser 4,
Water is passed through each heat transfer tube of the absorber 6.

The combustors of the main heating source 14 and the auxiliary heating heat source 13 are ignited, and the solution in the high-temperature regenerator 1 and the heat medium (water) in the auxiliary boiler 12 are heated. The heat medium in the auxiliary boiler 12 is boiled and evaporated, and the heat medium vapor conduits are respectively transferred to a heat exchanger 35 immersed in the solution of the medium-temperature regenerator 2 and a heat exchanger 36 immersed in the solution of the low-temperature regenerator 3. 37 and 38, and undergoes heat exchange to condense and liquefy. The latent heat of condensation at this time heats the solutions in the medium temperature regenerator 2 and the low temperature regenerator 3. Note that since the solution in the medium temperature regenerator 2 is heated in parallel with the latent heat of condensation of the refrigerant generated in the high temperature regenerator 1, the time for the solution to reach the boiling point is shortened.

The heat medium condensed in the heat exchangers 35 and 36 is returned to the auxiliary boiler 12 located below via condensed water conduits 39 and 40. That is, the auxiliary boiler 12 and the heat exchangers 35 and 36 are arranged in a thermosiphon relationship. Therefore, first, when the solution temperature in the intermediate temperature regenerator 2 exceeds the condensation temperature of the heat medium vapor generated in the auxiliary boiler 12, the heat exchanger 35
heat exchange will stop automatically. In addition, low temperature regenerator 3
The heat exchanger 36 continues to exchange heat during cooling operation when the auxiliary boiler 12 is heated, and the thermal energy of the auxiliary heating source 13 is used as a single effect in the absorption refrigeration cycle and contributes to increasing the refrigeration capacity.

When it is confirmed that steady operation has been reached by detecting either the temperature or pressure within the cycle, the combustion of the auxiliary heat source 13 of the auxiliary boiler 12 is stopped, and the device of this embodiment It operates as a triple-effect absorption refrigeration cycle that achieves high COP.

As described above, according to this embodiment, the low-temperature regenerator 3 and the medium-temperature regenerator 2 can be heated in parallel by the auxiliary boiler 12 at the time of startup in cooling operation, so the startup time is shortened.

Next, the heating operation of the above device will be explained with reference to FIG. 2.

FIG. 2 is a cycle configuration diagram of the same triple-effect absorption type water chiller/heater during heating operation as in FIG. 2, and the same reference numerals as in FIG. 1 indicate the same parts.

In the case of heating operation, hot water is obtained from the flow path of the cooling water 16, and in order to lower the solution concentration in the cycle, the refrigerant generated in the high temperature regenerator 1 and the medium temperature regenerator 2 is passed through the three-way valve 18, the refrigerant It is led to the low temperature regenerator 3 via the bypass pipe 22. Also, the evaporator 5
The liquid refrigerant is discharged to the absorber 6 through the evaporator refrigerant discharge pipe 21 and the gate valve 17.

The heat amount of the main heating source 14 is 56% to 67% of the refrigeration capacity.
Since the auxiliary heat source is about 30-50% of the refrigerating capacity
If you keep it to a certain level, you can make the heating capacity and refrigeration capacity the same. That is, the thermal energy of the main heating source 14 given to the high-temperature regenerator 1 is transferred to the hot water 16 flowing through the heat transfer tube of the condenser 4 by boiling and condensing the refrigerant in the solution. In addition, the thermal energy of the auxiliary heating source 13 given to the auxiliary boiler 12 is transferred to the solution of the low temperature regenerator 3 via the heat exchanger 36 of the low temperature regenerator 3 by boiling and condensation of the heat medium, and is further transferred to the solution of the low temperature regenerator 3. The boiling of the solution in the regenerator 3 gives the refrigerant vapor, and the condensation of the refrigerant vapor in the condenser 4 gives the hot water 16 flowing through the heat transfer tubes.

In this way, heating capacity can be increased.

In the embodiment shown in FIGS. 1 and 2, the medium temperature regenerator 2
and a heat exchanger 3 that condenses the heat medium into the low temperature regenerator 3.
5 and 36 are installed, and the auxiliary boiler 12 is installed below it.
Since the solutions in the medium temperature regenerator 2 and the low temperature regenerator 3 are heated using the thermosiphon principle, the following effects can be obtained.

(1) Since the minimum condensation temperature is the boiling point of the solution in the low temperature regenerator 3, which is 100°C or lower, the auxiliary boiler 12 operates under vacuum even if inexpensive water is used as a heat medium, so it is safe and In terms of anti-corrosion technology, the temperature of the auxiliary boiler 12 is around 80°C, so acid dew point corrosion can be avoided, and the auxiliary boiler 1 is thin and lightweight.
2, and an inexpensive device can be provided.

(2) Since the auxiliary boiler 12 must be installed below the low temperature regenerator and medium temperature regenerator 2,
There is no need to increase the installation area of the water cooler/heater.

(3) Since the heat medium circulation path is a closed circuit, it is easy to take measures in the event of a failure.

Note that when the heat exchanger 35 disposed in the medium-temperature regenerator 2 is removed, the effect of shortening the cooling operation start-up time is only slightly reduced, and there is an effect that a simplified device can be provided.

Furthermore, when the heat exchanger 36 installed in the low-temperature regenerator 3 is removed, if water or an aqueous solution is used as the heat medium in the auxiliary boiler 12, the heat medium condensation pressure will exceed atmospheric pressure, and the auxiliary boiler 12 will become a vacuum steam boiler. There is a problem where it disappears. Therefore, the same effect can be obtained by using an organic solvent with a boiling point of 100°C or higher and a pressure of lower than atmospheric pressure as the heating medium. When operated during cooling operation, the thermal energy given to the auxiliary boiler 12 by the auxiliary heating medium 13 forms a double-effect cycle and contributes to an increase in refrigeration capacity with a coefficient of performance of approximately 1.2. In this case, the auxiliary heat source 13 is not only the combustion gas generated in the combustor, but also 140~
Exhaust steam, exhaust gas, etc. over 150℃ can also be used. In this case as well, the auxiliary boiler 12 is installed below the medium-temperature regenerator 2 and the heat medium is circulated using the thermosiphon principle, so a special heat medium circulation pump or the like is not required, and a simplified device can be used. You can get the effects that you can.

Next, another embodiment of the present invention will be described with reference to FIG.

FIG. 3 is a cycle configuration diagram during cooling operation of a triple-effect absorption type water chiller/heater according to another embodiment of the present invention, in which the same symbols as in FIG. 1 indicate equivalent parts. .

Note that the heat exchangers 7, 8, and 9 are omitted from illustration in this figure.

The triple effect absorption type water chiller/heater of the embodiment shown in Figure 3 is as follows:
The dilute solution in the absorber 6 is supplied in parallel to the high temperature regenerator 1 and the low temperature regenerator 3 by the circulation pump 11, and is supplied in series from the low temperature regenerator 3 to the medium temperature regenerator 2 by the auxiliary circulation pump 45. This embodiment differs from the previous embodiments shown in FIGS. 1 and 2 in that it is curved.

However, in applying the present invention, changing the cycle configuration of such a triple effect absorption type water chiller/heater does not pose an obstacle.

The embodiment shown in FIG. 3 differs greatly from the previous example in that the refrigerant (water) circulated within the cycle is used as the heat medium for the auxiliary boiler 12. To achieve this, the following steps are taken. It is configured.

(1) The heat medium vapor generated by the auxiliary boiler 12 is guided to the heating steam pipe 31 side of the refrigerant piping of the low temperature regenerator 3 via the heat medium vapor pipe 38'.

(2) Connect the condensed water discharge pipe 32' from the low-temperature regenerator 3,
It was connected to the condensate water conduit 40' of the auxiliary boiler 12.

(3) Connect the condensed water discharge pipe 46 from the auxiliary boiler 12,
Condenser 4 via three-way valve 18 and orifice 19
The three-way valve 18 and the low temperature regenerator 3 were connected to each other through a refrigerant bypass pipe 22'.

According to the triple effect absorption type water heater having such a configuration, the following effects can be obtained.

(1) The boiling point of the solution in the low temperature regenerator 3 is approximately 80℃,
Since the auxiliary boiler 12 is a vacuum-operated boiler, it can be made lightweight and compact.

(2) Since the heat exchanger tube section installed in the low-temperature regenerator 3 can function as a condensing heat exchanger for the refrigerant vapor generated in the auxiliary boiler 12, there is no need to separately provide the heat exchanger 36 in the previous example. , it can be made into a compact device. In the embodiment shown in FIGS. 1 and 2 above, the heat exchangers 35 and 3 are closed during rated operation.
6 is idle and serves as a dead space, but in this embodiment, the heat exchangers 35 and 36 are shared with the heating heat exchanger tubes of the medium-temperature regenerator 2 and the low-temperature regenerator 3, respectively. Therefore, it is always effectively utilized.

(3) As shown in Fig. 3, the low temperature regenerator 3, medium temperature regenerator 2, and auxiliary boiler 12 are arranged in a stacked manner, so that the arrangement space can be saved.

Next, still another embodiment of the present invention will be described with reference to FIG.

FIG. 4 is a cycle configuration diagram of a triple effect absorption type water chiller/heater according to still another embodiment of the present invention.
In the figure, parts with the same reference numerals as those in FIGS. 1 and 3 have the same functions as in the previous example, so their explanation will be omitted.

The triple effect absorption chiller/heater shown in Figure 4 has an absorber 6.
The dilute solution is supplied in parallel to the high temperature regenerator 1 and the medium temperature regenerator 2 by the circulation pump 11, and is supplied in series from the medium temperature regenerator 2 to the low temperature regenerator 3.

The embodiment shown in FIG. 4 differs from the embodiments described in FIGS. 1 and 3 in the following points.

That is, the difference is that the heated steam conduit 29 side of the refrigerant piping of the medium temperature regenerator 2 and the heat medium steam conduit 38' of the auxiliary boiler 12 are connected by a heat medium steam conduit 50 equipped with a gate valve 51.

The gate valve 51 can detect the pressure of the auxiliary boiler 12 and automatically open and close.

With this configuration, when starting the cooling operation, the gate valve 51 can be opened and the refrigerant vapor generated in the auxiliary boiler 12 can be used to heat the solution in the medium temperature regenerator 2, thereby shortening the startup time. Effects can be obtained. When it is detected that the solution in the low temperature regenerator 3 approaches the rated operating temperature, the gate valve 51 is closed, and the refrigerant vapor generated from the high temperature regenerator 1 is transferred to the auxiliary boiler 12 and the heated steam conduit of the low temperature regenerator 3. 31 so that it does not flow backwards.

Here, the timing to close the gate valve 51 is as follows: (1) Timer (2) Detection of temperature rise in each part of the cycle (3) The direction of steam flow in the heat medium steam conduit 50 is adjusted by paddle,
Opening and closing can be controlled by detection using a differential pressure gauge, etc.

Note that during heating operation, the heat medium vapor conduit 50
can be used as a bypass pipe for refrigerant vapor, and the refrigerant vapor generated by the high-temperature regenerator 1 can be directly supplied to the heated steam conduit 31 of the low-temperature regenerator 3, so the high-temperature regenerator 1 can be operated at a significantly lower temperature and pressure than during cooling operation. I can drive.

Therefore, the high temperature regenerator 1 has the following characteristics: (1) The lower the temperature, the smaller the corrosion deterioration of the constituent materials, so the lifespan is extended.

(2) Since the heat of the heating heat source 14 can be recovered to a lower temperature, boiler efficiency is improved.

There is an effect.

Next, still another embodiment of the present invention will be described with reference to FIG.

FIG. 5 is a cycle configuration diagram of a triple effect absorption type water chiller/heater according to still another embodiment of the present invention,
In the figure, the same reference numerals as those in FIGS. 1, 3, and 4 are parts having the same functions as those in the previous embodiment, so the explanation thereof will be omitted.

The embodiment shown in FIG. 5 differs from the embodiments described in FIGS. 3 and 4 in that a heat exchanger tube, that is, a hot water heat exchanger 47, is provided to flow hot water into the steam phase of the auxiliary boiler 12. This is where I am.

As a result, hot water 48 at about 80° C. can be taken out without reducing the refrigerating capacity even during cooling operation.

Note that when the hot water heat exchanger 47 is installed in the shell of the auxiliary boiler 12 as shown in FIG. 5, the condensed water immediately flows down to the liquid level of the boiler 12.

However, although not specifically shown or explained, it is also conceivable to install a hot water heat exchanger in the middle of the heat medium steam conduit 38'; It is desirable to return it to the liquid phase.

Next, still another embodiment of the present invention will be described with reference to FIGS. 6 and 7.

FIG. 6 is a cycle configuration diagram during cooling operation of a triple effect absorption type water chiller/heater according to still another embodiment of the present invention, and FIG. 7 is a cycle configuration diagram during heating operation of the apparatus shown in FIG. 6. The arrows in the figure indicate the flow of refrigerant, heat medium, or solution. In the figure, 1st and 2nd
Components with the same reference numerals as those in the drawings have the same function, so their explanation will be omitted.

In FIGS. 6 and 7, 1A is a high-temperature regenerator, which includes a once-through heat exchanger 54 that heats the solution flowing inside the tube with a combustor 53 (main heat source 14) related to an external heat source;
This type is constructed with a gas-liquid separator 55 that separates refrigerant vapor from the heated solution.

2A is medium temperature regenerator, 3A is low temperature regenerator, 4A
5A is a condenser, 5A is an evaporator, 6A is an absorber, 9A is a solution heat exchanger on the low temperature side, and 12A is an auxiliary boiler.

The dilute solution generated in the absorber 6A is transferred by the solution circulation pump 11 to the once-through heat exchanger 54 in the high-temperature regenerator 1A, the medium-temperature regenerator 2A, and the low-temperature regenerator 3.
A is supplied through solution supply pipes 23, 24, 25, respectively, and is concentrated and sent to solution discharge pipes 26, 2, respectively.
7 and 28, it is returned to the absorber 6A.

52 is an auxiliary circulation pump provided in the solution supply pipe 23, and 60 is an auxiliary circulation pump provided in the solution discharge pipe 26, 2.
This is an auxiliary circulation pump for dispersing concentrated solutions of Nos. 7 and 28 onto the heat transfer tube group of the absorber 6A.

In this embodiment, an exhaust gas heat exchanger 55 is installed in the combustion exhaust gas passage of the once-through heat exchanger 54, and its refrigerant inlet end 56 is connected to the bottom of the solution tank 57 of the gas-liquid separator 55 and to the intermediate temperature regenerator 2A. Condensed water conduit 30
and the exhaust gas heat exchanger 55.
The refrigerant vapor outlet end 58 of the solution tank 57 is communicated with the vapor section of the gas-liquid separator 55 and the heated vapor conduit 29 of the medium temperature regenerator 2A, and the liquid phase section of the solution tank 57 and the low temperature regenerator 3A are communicated with each other. Heating steam conduit 3
1 through an orifice 20.

Therefore, heat can be recovered from the main heating source 14 of the high-temperature regenerator 1A with the low-temperature liquid refrigerant, resulting in the effect of improving boiler efficiency.

In addition, in the embodiment shown in FIGS. 6 and 7, the auxiliary boiler 12A is installed below the medium temperature regenerator 2A, and the upper shell of the auxiliary boiler 12A and the lower shell of the medium temperature regenerator 2A are made into a common member and are integrally constructed. This embodiment differs from the previous embodiments in that the heat exchanger 35A is configured.

Furthermore, the liquid refrigerant in the condensed water discharge pipe 46 and the dilute solution discharged from the absorber 6A by the solution circulation pump 11 are passed through the condensed water discharge pipe 46 of the auxiliary boiler 12A to the solution heat exchanger 9A. This embodiment also differs from the previous embodiments in that the liquid refrigerant recovery heat exchanger 61 for heat exchange is configured.

In this way, the medium temperature regenerator 2A and the auxiliary boiler 1
Since the heat exchanger 35A is configured by stacking the 2A and 2A, the auxiliary boiler 12A is
When heated with the auxiliary heating source 13 to generate heat medium vapor, it is condensed in the heat exchanger 35A, and the latent heat of condensation can heat the solution in the intermediate temperature regenerator 2A. The condensed water condensed in the heat exchanger 35A flows down to the auxiliary boiler 12A. Further, when the medium temperature regenerator 2A reaches a high temperature, condensation is no longer performed and heat exchange is automatically stopped. Incidentally, since the bottom shell of the medium temperature regenerator 2A is kept warm by vacuum steam, there is an additional effect that the heat insulating material can be saved.

It goes without saying that the purpose of the present invention, which is to shorten the start-up time, can be achieved.

Further, the temperature of the liquid refrigerant related to the condensate discharged from the auxiliary boiler 12A is approximately 80°C, and the sensible heat thereof is used for preheating the solution in the liquid refrigerant circuit heat exchanger 61. The amount of heat radiated can be reduced, saving energy, and the solution can be heated more effectively when the cooling operation is started, thereby achieving the desired goal of shortening the startup time.

According to each embodiment described above, the auxiliary boiler 1
2, 12A is arranged below the low temperature regenerators 3, 3A and the medium temperature regenerators 2, 2A, and the low temperature regenerators 3, 3A, the medium temperature regenerators 2, 2A, or both are activated by the thermosiphon principle. Since it is heated indirectly, the following effects can be obtained.

(1) Start-up time during cooling operation can be significantly reduced.

In other words, if the shortened time is Δτ, Δτ≒τ ₀ −τ ₀
Auxiliary boiler heat input/auxiliary boiler heat input + high temperature regenerator heat input can be obtained. Here, τ ₀ is the high temperature regenerator 1, 1A
This is the start-up time required to start up with only one unit.

(2) The capacity during heating operation is auxiliary boiler 12, 1.
It increases to an extent almost equal to the amount of heat input of 2A.

(3) Since the high-pressure regenerators 1 and 1A can be downsized according to the refrigeration capacity, and the auxiliary boilers 12 and 12A are installed below the medium-temperature regenerators 2 and 2A or the low-temperature regenerator 3, installation space can be saved. , can provide a compact device.

Although each of the above embodiments describes an example of a triple effect absorption type water chiller/heater, the present invention is not limited thereto, and the scope of the present invention is a multiple effect absorption type refrigerating device related to a product that can be expected to have the same effect. It is a general-purpose item.

〔Effect of the invention〕

As described above, according to the present invention, it is possible to provide a multi-effect absorption refrigeration system that can significantly shorten the startup time during cooling operation and improve the heating capacity during heating operation.

[Brief explanation of the drawing]

FIG. 1 is a cycle configuration diagram during cooling operation of the triple effect absorption type water chiller/heater according to an embodiment of the present invention, FIG. 2 is a cycle configuration diagram during heating operation of the device shown in FIG. 1, and FIG. is a cycle configuration diagram during cooling operation of a triple effect absorption type water chiller/heater according to another embodiment of the present invention,
FIG. 4 is a cycle configuration diagram of a triple effect absorption type water chiller/heater according to yet another embodiment of the present invention, and FIG. 5 is a cycle configuration diagram of a triple effect absorption type water chiller/heater according to yet another embodiment of the present invention. Figure 6 is a cycle configuration diagram during cooling operation of a triple-effect absorption type water chiller/heater according to still another embodiment of the present invention, and Figure 7 is a cycle configuration diagram during heating operation of the device shown in Figure 6. be. 1,1A...High temperature regenerator, 2,2A...Medium temperature regenerator, 3,3A...Low temperature regenerator, 4,4A...Condenser, 5,5A...Evaporator, 6,6A...Absorber , 7, 8, 9, 9A...solution heat exchanger, 10...
... Refrigerant spray pump, 11 ... Solution circulation pump,
12... Auxiliary boiler, 13... Auxiliary heating source, 1
4... Main heating source, 23, 24, 25... Solution supply pipe, 26, 27, 28... Solution discharge pipe, 29, 3
1... Heating steam conduit, 30, 32... Condensed water conduit, 33... Refrigerant vapor conduit, 35, 35A, 36
... Heat exchanger, 37, 38, 38' ... Heat medium vapor conduit, 39, 40, 40' ... Condensed water pipe, 46
... Condensed water discharge pipe, 47 ... Hot water heat exchanger, 50
... Heat medium vapor conduit, 51 ... Gate valve, 45,5
2, 60...Auxiliary circulation pump, 61...Liquid refrigerant recovery heat exchanger.

Claims (1)

[Scope of Claims] 1. A high-temperature regenerator using an external heat source as a heating source, and refrigerant vapor generated in the high-temperature regenerator as a heating source for a solution in a subsequent low-temperature regenerator, respectively, to generate refrigerant vapor. multiple low and medium temperature regenerators, condensers, evaporators, absorbers, solution heat exchangers,
In a multi-effect absorption refrigeration system consisting of equipment such as a solution circulation pump and piping that connects these absorption cycle operating equipment, an auxiliary boiler that heats the heat medium is placed below the plurality of low-temperature and medium-temperature regenerators. the auxiliary boiler and at least one of the plurality of low-temperature and medium-temperature regenerators, so that the heat medium vapor generated in the auxiliary boiler can serve as an auxiliary heating source for the plurality of low-temperature and medium-temperature regenerators; A multi-effect absorption refrigeration system characterized by connecting the two with piping. 2. In what is stated in claim 1,
In order to use the liquid refrigerant in the refrigeration cycle as a heating medium for the auxiliary boiler, the condensed water conduit side of the refrigerant piping in the low-temperature regenerator is connected to the auxiliary boiler, and the steam conduit for the heat medium vapor generated in the auxiliary boiler is connected to the auxiliary boiler. . A multi-effect absorption refrigeration system, which is connected to the heated steam conduit side of the refrigerant piping in the low-temperature regenerator, and the condensed water discharge pipe of the auxiliary boiler is connected to the condenser. 3 In what is stated in claim 2,
A multi-effect absorption refrigeration system in which the auxiliary boiler and the heated steam conduit side of the refrigerant piping in the medium-temperature regenerator are connected by a heat medium steam conduit equipped with a gate valve. 4 In what is stated in claim 2,
A multi-effect absorption refrigeration system equipped with a liquid refrigerant recovery heat exchanger that exchanges heat between the liquid refrigerant in the condensed water discharge pipe of the auxiliary boiler and the dilute solution discharged from the absorber by the solution circulation pump. 5. In either of claims 1 or 2, the intermediate temperature regenerator and the auxiliary boiler are formed into an integral shell structure, and the intermediate temperature regenerator and the auxiliary boiler are disposed in the upper part and the auxiliary boiler in the lower part, A multi-effect absorption refrigeration system that is configured to directly heat part or all of the shell of a medium-temperature regenerator using heat medium steam generated in an auxiliary boiler. 6. A multi-effect absorption refrigeration system as set forth in either Claim 1 or 2, in which a heat transfer tube for circulating hot water is disposed in a gas phase part that generates a heat medium in an auxiliary boiler. .