JPH0796977B2 - Double-effect air cooling absorption type water heater - Google Patents

Description

TECHNICAL FIELD The present invention relates to a double-effect air-cooled absorption-type chiller-heater, and more particularly,
The present invention relates to a double-effect air-cooled absorption type chiller-heater suitable for operation even when the outside air temperature rises abnormally, using water as a refrigerant and lithium bromide as an absorbent.

[Conventional technology]

Conventionally, the cooling of the double-effect absorption chiller has often been water-cooled by the cooling water of the cooling tower. However, the use of a cooling tower requires cooling water system equipment and piping work, securing a large amount of water, and preventing freezing and contamination of the cooling water system, such as installation work, maintenance and water management. There was a problem that it was costly.

Therefore, the development of the air-cooled absorption type refrigerator has been rapidly advanced, and two systems, a direct air-cooled system and an indirect air-cooled system, are drawing attention.

The indirect air cooling system is a system in which an absorber and a condenser are cooled by latent heat of vaporization of a high pressure refrigerant such as Freon 22, and the vaporized high pressure refrigerant vapor is condensed by outside air.

The direct air cooling method is a method of directly cooling the absorber and the condenser by the outside air. If this can be put to practical use, the problem of the water cooling absorption refrigerator using the conventional cooling tower will be solved with a simple configuration. .

Therefore, as an air-cooled absorption type chiller using water as a refrigerant and lithium bromide as an absorbent, for example, JP-A-61-4997.
The technique described in Japanese Patent No. 0 has been developed. That is, the one described in the publication has a structure in which fins are provided outside the vertical pipe so that the absorber and the condenser are cooled by the air flow by the fan, while the temperature of the high temperature regenerator is increased. By increasing the degree of supercooling of the refrigerant in the condenser, the solution exiting the air-cooled absorber or the solution mixed with the refrigerant vapor is cooled by the supercooled refrigerant liquefied in the condenser, air-cooled absorption type Realizes a chiller.

In this way, when the outside air dry bulb temperature is about 33 ° C,
A double-effect air-cooled absorption-type chiller-heater was provided, which can be operated at an internal pressure below atmospheric pressure and a solution temperature within a practical range.

In general, the outside air dry-bulb temperature is 30.8 ° C in Tokyo, which is the monthly average of the daytime maximum temperature in summer, and it is possible to operate the double-effect air-cooled absorption chiller-heater with the above technology. But,
According to meteorological statistics, the maximum outside air temperature in the summer will rise to 38.4 ° C in Tokyo, and if the outside air temperature becomes abnormally high, the double-effect absorption chiller-heater will no longer have a large internal pressure. If the air pressure exceeds the atmospheric pressure, the cooling operation cannot be performed when the cooling is necessary.

[Problems to be solved by the invention]

As described above, for example, in the technique described in JP-A-61-49970, the absorption cycle, the air-cooled absorber, and the air-cooled condenser are specially devised, but when the outside air temperature becomes abnormally high, Since no consideration was given, there was a problem that even if the air conditioner had it, it could not be operated when needed.

Here, the relationship between the outside air temperature and the absorption cycle will be described.

Generally, when designing air conditioners in a wide area of the world including Japan, the wet-bulb temperature of the outside air in summer is set to 27 ° C. Therefore, conventionally, by utilizing the latent heat of vaporization of cooling water,
In designing a cooling tower that radiates heat to the outside air, it is widely practiced to keep the temperature of cooling water on the inlet side at around 37 ° C and at the outlet at about 32 ° C. If you try to get closer to the wet-bulb temperature, the cooling tower will become extremely large and it will be uneconomical.On the other hand, if you design it further away from the wet-bulb temperature, the cooling tower will become smaller, but the operating conditions on the refrigerator side Not only does this impair energy conservation, but it also makes it impossible for some machines to continue normal operation. Refrigerator operating condition 32 ℃
The temperature of ~ 37 ° C is determined from the above circumstances, and it cannot be easily changed greatly.

Therefore, when focusing on air-cooled absorbers and condensers, in the case of the air-cooled type, since the cooling is performed by the sensible heat of the outside air, in general, compared with the cooling water amount by the cooling tower,
It is necessary to flow several times the amount of air flow, and even in that state,
The design must be such that the temperature difference between the air inlet and outlet exceeds 10 ° C. This is, for example, the wet-bulb temperature of the outside air 27 ℃,
In the case of standard atmospheric conditions such as a dry-bulb temperature of 32 ° C, this means that the inlet and outlet on the air side must be set to 32 ° C to 42 ° C.

In addition, the heat transfer coefficient on the air side depends on the flow rate of the heat exchange medium, as compared with a general water-cooled heat exchanger.
It will be reduced by several digits In other words, in order to design the temperature difference between the heat medium and air to be equal to the temperature difference between the heat medium and water, the heat transfer area on the air side should be increased by two orders of magnitude in the case of water, that is, This results in having to take about 100 times more.

When designing a heat exchanger in reality, it is not possible to use a heat exchanger with an infinitely large heat transfer surface, so the temperature difference between the heating medium and air is much larger than that for water cooling. I have no choice. To explain this with an actual cycle value, for example, in the case of water cooling, the absorption temperature and condensation temperature of the water-cooled absorber and moisture condenser are approximately It is designed around 40 ℃.

On the other hand, in the case of air cooling, the above-mentioned air side temperature of 32 ℃ ~
If an air-cooled absorber or condenser with a practical size is used at 42 ° C, the absorption temperature and condensation temperature will rise to about 48 ° C.

Therefore, in the case of a centrifugal compressor, a reciprocating compressor, etc., it is possible to perform air cooling relatively easily by adopting a compressor that realizes such a high compression ratio. In a dual-effect air-cooling absorption cycle device using lithium bromide as a refrigerant, the following two problems are fundamental problems.

This problem will be described with reference to FIG.

FIG. 4 is a solution concentration diagram of a general double-effect air-cooled absorption type chiller-heater, where the solid line indicates the water-cooling cycle and the broken line indicates the air-cooling cycle, both of which show the absorption solution concentration as a parameter.

In Fig. 4, the temperature is plotted on the horizontal axis, and the absorption temperature of the water-cooled absorber and the water-cooled condenser, the design value of the condensation temperature of 40 ° C, the absorption temperature of the air-cooled absorber and the air-cooled condenser, and the design value of the condensation temperature of 48 ° C are shown. Shows. Further, the vertical axis represents pressure, and the isobar levels of the evaporation pressure, the condensation pressure, and the high temperature regenerator pressure in the water cooling cycle are indicated by arrow lines. The first of the basic problems is the problem of solution concentration in the absorber and crystal formation. As shown in Fig. 4, in comparison with the general water-cooled absorption cycle, in the air-cooled absorption cycle shown by the broken line, the solution concentration in the absorber shifts to the darker side due to the increase in the above-mentioned absorption temperature of 48 ° C. , It is very close to the crystal precipitation limit line, and crystals easily form with a slight change in state during operation. That is, when the temperature of the absorber outlet solution is high, it causes crystallization of lithium bromide.

The second problem is that the temperature inside the high temperature regenerator exceeds atmospheric pressure. As shown in Fig. 4, when the concentration in the absorber is high and the concentration temperature is high, the saturation temperature of the low temperature regenerator solution is high, and the vapor condensation from the high temperature regenerator, which is in a heat exchange relationship with it, is condensed. Saturation temperature easily exceeds 100 ° C.

This is not only uneconomical because the entire apparatus has to be a pressure vessel structure, but also the internal solution temperature rises in proportion to the increase in pressure, which causes a problem of corrosion due to lithium bromide.

The present invention has been made to solve the above-mentioned problems of the prior art. Even when the outside air temperature rises abnormally, the temperature of the solution at the outlet of the absorber is lowered, and the internal pressure of the high temperature regenerator exceeds atmospheric pressure. An economical double-effect air-cooled absorption chiller-heater that can be operated continuously without any problems and has no problem even if the heat transfer area of the air-cooled absorber and the air-cooled condenser is designed at an average temperature of 32 ° C. Its purpose is to provide.

[Means for solving problems]

In order to achieve the above-mentioned object, the structure of the double-effect air-cooled absorption type chiller-heater according to the present invention includes an evaporator, an air-cooled absorber, an air-cooled condenser, a low-temperature regenerator, a high-temperature regenerator, a solution heat exchanger, and a solution. In the double-effect air-cooled absorption chiller-heater, which comprises a pump, a refrigerant pump, and a piping system for operatively connecting these, and a fan that supplies cooling air to the air-cooled absorber and the air-cooled condenser, the low-temperature regeneration is performed. A refrigerant pre-cooler that is air-cooled by the fan is provided in a refrigerant pipe that communicates with the air-cooling condenser from the container, and a flow rate control valve that is controlled by a refrigerant pressure adjusting means is provided in the refrigerant pipe.

The concept of developing the present invention is as follows.

The internal pressure of a double-effect air-cooled absorption refrigerator that uses water as a refrigerant and lithium bromide as an absorbent, especially the high temperature regenerator, determines the solution temperature in the low temperature regenerator, which is the air cooled condenser. It is determined by the refrigerant condensation temperature inside.

Therefore, when the outside temperature is high, a part of the refrigerant vapor that heats the solution in the low-temperature regenerator is directly chilled by the outside air to be cooled and liquefied so that it can flow into the air-cooled condenser. By reducing the amount of heat exchange in the air-cooling condenser, and by reducing the amount of refrigerant vapor flowing into the air-cooling condenser, the refrigerant condensing temperature in the air-cooling condenser becomes close to the atmospheric temperature, and it is possible to prevent the in-machine pressure from rising excessively.

[Action]

The above operation will be described with reference to the solution concentration diagram of FIG.

FIG. 5 is a solution concentration diagram of a double-effect air-cooled absorption type chiller-heater with a refrigerant precooler.

Similarly to FIG. 4, FIG. 5 shows an air-cooling absorption cycle by a broken line with temperature on the horizontal axis and pressure on the vertical axis, and the absorption solution concentration as a parameter.

In a double-effect air-cooled absorption type water heater without a refrigerant precooler that directly cools part of the refrigerant vapor that heats the solution in the low-temperature regenerator with the outside air, the condensing pressure becomes the intersection point a with the water saturation curve of the refrigerant. , The corresponding solution temperature in the low temperature regenerator is b
It becomes a point. Then, the refrigerant vapor that heats the solution in the low temperature regenerator is condensed at a temperature higher than the point b by Δt, and the pressure becomes the point c, so that the internal pressure of the high temperature regenerator exceeds atmospheric pressure.

On the other hand, when a refrigerant precooler is attached, the amount of refrigerant condensed and liquefied in the condenser decreases, and the condensation temperature approaches the outside air temperature,
It becomes point a '. Corresponding to this, the solution temperature in the low temperature regenerator also decreases the concentration width of the solution in proportion to the decrease in the heating amount, b
From point b'to a large drop. Further, since the heat transfer temperature difference decreases from Δt to Δt ′ due to the decrease in the heating amount of the low temperature regenerator, the condensation pressure of the low temperature regenerator heating vapor decreases from c to c ′, and the pressure of the high temperature regenerator decreases. Fall below atmospheric pressure.

The flow rate control valve provided at the outlet of the refrigerant precooler controls the amount of condensed refrigerant flowing into the refrigerant precooler.By providing an appropriate throttle, the condensation pressure in the precooler becomes equal to the pressure in the low temperature regenerator. Held in. Therefore, even if the condensing temperature becomes high and the temperature of the cooling air from the outside is high, it is possible to sufficiently condense and liquefy with a small heat transfer area.

Further, an orifice can be provided at the outlet of the refrigerant precooler so that only the liquid refrigerant flows out and the refrigerant vapor hardly flows out. This is because the volumetric flow rate of gas is extremely larger than that of liquid.

Therefore, if the refrigerant vapor inflow control valve is provided on the inlet side of the precooler for control, control can be easily performed.

〔Example〕

Embodiments of the present invention will be described below with reference to FIGS. 1 to 3.

First, FIG. 1 is a cycle system diagram of a double-effect air-cooled absorption type chiller-heater according to an embodiment of the present invention.

In FIG. 1, 1 is an evaporator, 2 is a refrigerant pump, and 3 is a cold water pipe through which cold water passes.

Reference numeral 4 denotes an air-cooled absorber. In this air-cooled absorber 4, a fin 4b for cooling is formed outside the vertical pipe 4a, an upper header is formed by a vapor passage 5 above the vertical pipe 4a, and a lower portion is formed below the vertical pipe 4a. This is a configuration including a Hezda 4c.

6 is a solution pump, 7 is a solution heat exchanger, 10 is a high temperature regenerator, and 11 is a low temperature regenerator.

Reference numeral 15 is an air-cooled condenser, and in this air-cooled condenser 15, a fin 15b for cooling is formed outside the vertical pipe 15a, the upper part of the vertical pipe 15a is an upper head by the steam passage 14, and the lower part is below the vertical pipe 15a. This is a configuration including a Hezda 15c.

The air-cooled absorber 4 and the air-cooled condenser 15 are air-cooled by the flow of outdoor air by the fan 20, and the thick arrow in the figure indicates the flow direction of the cooling air.

The above-mentioned devices are operatively connected by a refrigerant pipe and a solution pipe to form a cycle.

21 is the low temperature regenerator 11 to the lower head 15c of the air-cooled condenser 15.
A refrigerant precooler provided in a refrigerant pipe 13 leading to the refrigerant precooler 21. Cooling fins are formed on the outer circumference of the refrigerant precooler 21.
In the example of FIG. 1, the refrigerant precooler 21 is arranged in the vicinity of the air-cooled condenser 15, and the cooling air by the fan 20 cools the air-cooled absorber 4 and the air-cooled condenser 15 as shown by the arrow, and then the refrigerant. The arrangement is such that the precooler 21 is cooled.

22 is a flow rate control valve provided in the refrigerant pipe line 13 on the outlet side of the refrigerant precooler 21, 23 is a pressure sensor for detecting the refrigerant vapor pressure in the high temperature regenerator 10, 24 is the pressure related to the refrigerant pressure adjusting means. The pressure regulator 24 is a regulator that controls the flow control valve 22 according to the detection result of the pressure sensor 23.

The operation of the basic cycle of the double-effect air-cooled absorption type chiller-heater having such a configuration will be described.

The refrigerant (water) in the evaporator 1 is sprinkled by the refrigerant pump 2 onto the cold water pipe 3 through which cold water passes, and the heat of evaporation is taken from the cold water to become low-pressure refrigerant vapor, which passes through the vapor passage 5 and the air-cooled absorber 4
Flow into. The air-cooled absorber 4 is directly cooled by the outside air by the fan 20, and the refrigerant vapor is sprayed from the upper header and is absorbed by the concentrated lithium bromide solution flowing down the vertical pipe 4a to become a dilute solution.

The diluted solution is sent out by the solution pump 6, passed through the solution heat exchanger 7 and sent to the high temperature regenerator 10 and the low temperature regenerator 11 via the diluted solutions 8 and 9.

An external heat source 12 is supplied to the high temperature regenerator 10, and the dilute solution is concentrated by the heat generated when burning in the furnace 10a, and steam is generated at this time. This generated refrigerant vapor heats and concentrates the dilute solution in the low-temperature regenerator 11 via the heat transfer pipe portion 13a of the refrigerant pipe 13, condenses and liquefies from the refrigerant itself into a liquid refrigerant, and the lower header 15c of the air-cooled condenser 15 is condensed. Sent to.

The steam generated from the dilute solution concentrated in the low temperature regenerator 11 is
It flows through the vapor passage 14 into the vertical pipe 15a of the air-cooled condenser 15, where it is also cooled by the outside air by the fan 20 to become a liquid refrigerant, and returns from the lower header 15c to the evaporator 1 via the refrigerant pipe 16.

The solutions condensed respectively in the high-temperature regenerator 10 and the low-temperature regenerator 11 are sent to the upper head of the air-cooled absorber 4 via the concentrated solution pipes 17 and 18 and the solution heat exchanger 7 and then the concentrated solution pipe 19. The absorption process is repeated again.

Next, the operation of the embodiment of FIG. 1 provided with the refrigerant precooler will be described.

The refrigerant vapor generated in the high-temperature regenerator 10 flows into the heat transfer tube portion 13a of the low-temperature regenerator of the refrigerant pipe line 13, heats and concentrates the dilute solution outside the tube, condenses and liquefies itself, and becomes a refrigerant liquid. The refrigerant enters the refrigerant precooler 21, is air-cooled by the outside air by the fan 20, becomes a supercooled liquid, and flows into the lower header 15c of the air-cooled condenser 15 via the flow control valve 22. The flow control valve 22 is used for the refrigerant precooler 2
The amount of refrigerant flowing from 1 to the air-cooled condenser 15 is determined by the high temperature regenerator 10
It is controlled by a signal from a pressure regulator 23 connected to a pressure sensor 23 for detecting the refrigerant vapor pressure therein.

When the outside air temperature is below an average value, the pressure inside the high temperature regenerator 10 is below atmospheric pressure, the flow rate control valve 22 is narrowed down, and the refrigerant liquid becomes difficult to flow, so the inside of the refrigerant precooler 21 is the refrigerant liquid. The inside of the heat transfer tube 13a of the low temperature regenerator 11 which is filled up is also partially filled with the refrigerant liquid, and the condensation heat transfer area of the heat transfer tube 13a is reduced.
Therefore, in order for the amount of refrigerant condensed in the heat transfer tube 13a to be the same, the heat transfer area must be saved and the condensation temperature must rise. That is, the internal pressure of the high temperature regenerator 10 communicating with the heat transfer tube 13a increases. When the internal pressure of the high temperature regenerator 10 rises, the pressure sensor 2
3. The pressure regulator 24 controls the flow control valve 22 in the opening direction. When the flow control valve 22 opens, the flow rate of the refrigerant liquid increases, and conversely to the above, the refrigerant liquid in the heat transfer tube 13a of the low temperature regenerator decreases and the heat transfer area increases, so that the pressure in the high temperature regenerator 10 decreases.

As described above, by controlling the refrigerant flow rate by controlling the pressure regulator 24, a state in which all the refrigerant vapor is condensed in the heat transfer tube 13a of the low temperature regenerator 11 can be created, and,
The pressure inside the high temperature regenerator 10 is maintained below atmospheric pressure,
A double-effect absorption cycle is formed.

When the outside air temperature is particularly high, the absorber solution temperature rises, the solution concentration rises, the condenser temperature rises, and the solution temperature in the low temperature regenerator 11 rises, so that the internal pressure of the high temperature regenerator 10 rises. When the internal pressure of the high temperature regenerator 10 rises, the flow sensor 22 and the pressure regulator 24 open the flow control valve 22,
Since the flow rate of the refrigerant increases, the amount of the refrigerant liquid in the refrigerant precooler 21 decreases, and finally, the refrigerant vapor is not completely condensed in the heat transfer tube 13a of the low temperature regenerator 11, and the air cooling precooler in a partial vapor state. It flows into 21, is cooled to the outside air in the refrigerant precooler 21, and is condensed and liquefied. In such a state, all the latent heat of condensation of the refrigerant vapor generated in the high temperature regenerator 10 will not be used to concentrate the solution in the low temperature regenerator, and the amount of refrigerant vapor generated from the low temperature regenerator 11 will also decrease, Since the heat load on the air-cooled condenser 15 is reduced, the condensing pressure drops, and the high temperature regenerator pressure also drops.

The refrigerant flowing into the refrigerant precooler 21 as the refrigerant vapor radiates heat to the outside air and is condensed and liquefied. In other words, the latent heat of the refrigerant vapor is not used for the concentration action of the solution, but is radiated to the atmosphere to act in a single-effect cycle.

The position of the refrigerant precooler 21 shown in FIG. 1 is the outdoor cooling air from the fan 20, which cools the air-cooled absorber 4 first, then the air-cooled condenser 15, and finally the refrigerant precooler 21. It is an array configured to do.

With such an arrangement, the air-cooled absorber 4 is well cooled, the solution concentration of the absorber is lowered, and the refrigerant saturation temperature of condensation in the refrigerant precooler 21 is as high as 80 to 95 ° C.
There is no problem even if the cooling air temperature rises to 50 to 55 ° C.

According to this embodiment, even when the outside air temperature rises abnormally,
The temperature of the solution at the outlet of the absorber can be lowered and operation can be continued without the internal pressure of the high-temperature regenerator exceeding atmospheric pressure. Even if the heat transfer area of the air-cooled absorber and air-cooled condenser is designed at an average temperature of 32 ° C. It is possible to provide an economical double-effect air-cooled absorption type water heater without any problems.

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

FIG. 2 is a cycle system diagram of a double-effect air-cooled absorption type chiller-heater according to another embodiment of the present invention. In the figure, the same reference numerals as those in FIG. Since it is an equivalent part, its explanation is omitted.

The embodiment of FIG. 2 is different from the embodiment of FIG. 1 in that the flow rate control valve 22A is connected to the artificial refrigerant line 1 of the refrigerant precooler 21.
3, the orifice 25 is provided in the refrigerant pipe line 13 on the outlet side of the refrigerant precooler 21.

By providing the orifice 25 on the outlet side of the refrigerant precooler 21, only the liquid refrigerant can flow out and the refrigerant vapor can hardly flow out. Therefore, by providing the flow rate control valve 22A on the inlet side of the refrigerant precooler 21, the refrigerant vapor inflow amount can be easily controlled.

Therefore, according to the embodiment of FIG. 2, the same effect as that described in the embodiment of FIG. 1 can be expected.

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

FIG. 3 is a cycle system diagram of a double-effect air-cooled absorption type chiller-heater according to still another embodiment of the present invention.
The parts having the same reference numerals as those in the figure are the same parts as those in the previous embodiment, and therefore their explanations are omitted.

The difference between the embodiment of FIG. 3 and the embodiment of FIG.
Since the refrigerant precooler 21A is arranged close to the air cooling absorber 4, the cooling air by the fan 20 cools the refrigerant precooler 21A, the air cooling absorber 4, and the air cooling condenser 15 in this order as shown by the arrow. They are arranged like this.

The flow rate control valve 22B is a refrigerant line 1 on the outlet side of the refrigerant precooler 21A.
It is provided on 3 ', especially at the lower header 15c inlet of the air-cooled condenser 15.

Even in the arrangement position of such a refrigerant precooler, the same function as that of the refrigerant precooler shown in FIG. 1 can be achieved.

Further, in the embodiment shown in FIG. 3, the concentrated solution pipe 18 from the low temperature regenerator 11 is provided with a temperature sensor 26 for detecting the solution outlet temperature of the low temperature regenerator and is connected to the pressure regulator 24.

Even in this case, the change in the refrigerant vapor pressure in the high temperature regenerator 10 corresponds to the change in the refrigerant temperature or the solution temperature in the low temperature regenerator 11 one to one.
The control function of the refrigerant flow rate control valve 22B and the function and effect of the refrigerant precooler 21A are the same as those of the embodiment shown in FIGS.

For the same reason, although not particularly shown, the pressure regulator 24
Needless to say, a temperature sensor connected to the low temperature regenerator 11 may be provided in the refrigerant pipe line 13 'from the low temperature regenerator 11 to detect the refrigerant temperature at the outlet of the low temperature regenerator.

Further, the attachment of these temperature sensors may be applied to the arrangement of the refrigerant precooler 21 shown in FIGS.

Further, in the arrangement of the refrigerant precooler 21A shown in FIG. 3, as in the embodiment of FIG. 2, a flow rate control valve is provided on the artificial side of the refrigerant precooler and an orifice is provided on the outlet side of the refrigerant precooler. Even with the above configuration, the same effect as that of each of the above-described embodiments is expected.

〔The invention's effect〕

As described above, according to the present invention, even when the outside air temperature rises abnormally, the absorber outlet solution temperature is lowered, and the operation can be continued without the internal pressure of the high temperature regenerator exceeding the atmospheric pressure.
Set the heat transfer area of the air-cooled absorber and air-cooled condenser to the average temperature of 32
It is possible to provide an economical double-effect air-cooled absorption type chiller-heater with no trouble even if designed at ℃.

[Brief description of drawings]

FIG. 1 is a cycle system diagram of a double-effect air-cooled absorption type water heater / cooler according to an embodiment of the present invention, and FIG. 2 is a double-effect air-cooled absorption type water heater / chiller according to another embodiment of the present invention. FIG. 3 is a cycle system diagram of a double-effect air-cooled absorption type cold / hot water machine according to still another embodiment of the present invention, and FIG. 4 is a general double-effect air-cooled absorption type cold / hot water. 5 is a solution concentration diagram of the double effect air cooling absorption type water heater with a refrigerant precooler. 1 ... Evaporator, 2 ... Refrigerant pump, 4 ... Air-cooled absorber,
6 ... Solution pump, 7 ... Solution heat exchanger, 10 ... High temperature regenerator, 11 ... Low temperature regenerator, 13 ... Refrigerant pipeline, 15 ... Air cooling condenser, 20 ... Huan, 21,21A ...... Refrigerant precooler, 22,22
A, 22B …… Flow control valve, 23 …… Pressure sensor, 24 …… Pressure regulator, 25 …… Olyphus, 26 …… Temperature sensor.

 ─────────────────────────────────────────────────── ─── Continued Front Page (72) Inventor Yoshikazu Nagaoka 5-22-4 Kamisoshiya, Setagaya-ku, Tokyo Kamisoshiya Heights No. 302 (72) Inventor Shinichi Kanno 4-9-4 Takawashi, Habikino-shi, Osaka Prefecture −303 (72) Inventor Sadaju Takemoto 11-8, Toyonen-cho, Chikusa-ku, Nagoya-shi, Aichi (72) Inventor Shigeo Sugimoto 603, Jinritsu-cho, Tsuchiura-shi, Ibaraki Hitate Works Co., Ltd. Tsuchiura Plant (72) Inventor Large Uchi Tomihisa 502, Jinrachicho, Tsuchiura-shi, Ibaraki Machinery Research Laboratory, Hiritsu Manufacturing Co., Ltd. (56) References JP 62-218771 (JP, A) JP 51-100376 (JP, A)

Claims (7)

[Claims] 1. An evaporator, an air-cooled absorber, an air-cooled condenser, a low-temperature regenerator, a high-temperature regenerator, a solution heat exchanger, a solution pump, a refrigerant pump, and a piping system for operatively connecting them, and the air-cooled In a double-effect air-cooled absorption-type chiller-heater equipped with a fan that supplies cooling air to an absorber and an air-cooled condenser,
A refrigerant pre-cooler that is air-cooled by the fan is provided in a refrigerant pipeline that leads from the low-temperature regenerator to the air-cooled condenser, and a flow rate control valve that is controlled by a refrigerant pressure adjusting means is provided in the refrigerant pipeline. A double-effect air-cooled absorption type hot and cold water machine characterized by. 2. A double-effect air-cooled absorption chiller-heater according to claim 1, wherein the flow control valve is provided in the refrigerant pipe line on the outlet side of the refrigerant precooler. 3. The flow control valve according to claim 1, wherein the flow rate control valve is provided in a refrigerant pipeline on the population side of the refrigerant precooler, and an orifice is provided in the refrigerant pipeline on the outlet side of the refrigerant precooler. It is a double-effect air-cooled absorption type hot and cold water machine. 4. The refrigerant precooler according to any one of claims 1 to 3, wherein the cooling air by the fan cools the air cooling absorber and the air cooling condenser, and then the refrigerant precooler is turned on. A double-effect air-cooled absorption type hot water machine that is arranged to cool. 5. The refrigerant pressure adjusting means according to any one of claims 1 to 4, wherein the refrigerant pressure adjusting means is responsive to a detection result of a pressure sensor for detecting a refrigerant vapor pressure of the high temperature regenerator. A double-effect air-cooled absorption type chiller-heater that controls 6. The flow control valve according to any one of claims 1 to 4, wherein the refrigerant pressure adjusting means is responsive to a detection result of a temperature sensor for detecting a solution outlet temperature of the low temperature regenerator. A double-effect air-cooled absorption type chiller-heater that controls 7. The flow rate control valve according to any one of claims 1 to 4, wherein the refrigerant pressure adjusting means is responsive to a detection result of a temperature sensor for detecting a refrigerant temperature at an outlet of the low temperature regenerator. A double-effect air-cooled absorption type chiller-heater that controls