JPH0953864A - Engine type cooling device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize remarkable cost down by a method wherein the circulating route of a cold heat medium for an indoor machine is constituted of one system of the refrigerant of a compression type refrigerating machine only, in an engine type cooling device, in which the compression type refrigerating machine is combined with an absorption type refrigerating machine. SOLUTION: An absorption type refrigerating machine 3 comprises a regenerator 13, a condenser 14, an evaporator 15, an absorber 16 and the like while the heat transfer tube 15a of the evaporator 15 is connected to a high-pressure pipeline 12a, connecting the receiver 8 of a compression type refrigerating machine 2 to an expansion valve 9. Accordingly, refrigerating capacity, obtained by the evaporator 15, is recovered by liquid refrigerant, which flows from the receiver 8 to the expansion valve 9, then, is used for cooling operation by the refrigerant evaporator 11 of the compression type refrigerating machine 2. On the other hand, cooling water, which flows through the absorbing device 16 and the condenser 14 of the absorption type refrigerating machine 3, is cooled by receiving the ventilation of a cooling fan 6 upon passing through an air- cooled heat exchanger 29 provided in a cooling water circuit 18.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an engine type air conditioner in which an absorption type refrigerator utilizing exhaust heat of an engine and a compression type refrigerator driven by the engine are combined.

[0002]

2. Description of the Related Art Absorption refrigerators that utilize exhaust heat of an engine as a heat source of a regenerator have been conventionally known (Japanese Unexamined Patent Publication No. Sho 6 (1994) -6 (1)).
0-93274, JP-A-3-129268). Further, a cooling system has been proposed in which this absorption refrigerator is combined as an auxiliary cooling device for a compression refrigerator driven by an engine. That is, the compression refrigerator is operated by the engine and the exhaust heat of the engine at that time is used to drive the absorption refrigerator.

[0003]

However, when the absorption refrigerator is used as an auxiliary cooling device for a compression refrigerator,
The cold heat medium used in the compression refrigerator is different from that used in the absorption refrigerator. That is, in the compression refrigerator, a chlorofluorocarbon-based refrigerant is used, whereas in the absorption refrigerator, cold water obtained by the evaporator is used for cooling. For this reason, not only is it necessary to install two systems of piping equipment for the compression type refrigerator and the cold water piping for the absorption type refrigerator for the indoor unit, but the indoor heat exchanger is also used for the refrigerant and the cold water. Need to be installed separately. Further, a cold water pump for circulating cold water is also required in the cold water pipe.

Further, in the absorption refrigerator, in order to obtain a predetermined cold water extraction temperature (for example, 5 ° C.) in the evaporator, the water transferred to the atmosphere in the cooling tower is the water cooling in which the heat transferred to the cooling water in the absorber and the condenser is released. Although the formula is generally used, in the case of this water-cooled system, in addition to the cooling water circuit in which the cooling water circulates, water cooling equipment (cooling tower, water cooling pipes, pumps, etc.) is required, so equipment costs and construction are required. Expensive. In addition, maintenance cost increases because it is necessary to control the quality of cooling water. On the other hand, an air-cooled absorption refrigerating machine for air-cooling an absorber and a condenser has been proposed (see Japanese Patent Laid-Open No. 1-310273) as opposed to a water-cooled one, but the absorber used for air cooling is proposed. Since the condenser is complicated and large in size, many problems remain for practical use.

The present invention has been made based on the above-mentioned circumstances, and in an engine type cooling apparatus in which a compression refrigerator and an absorption refrigerator are combined, the circulation route of the cooling / heating medium to the indoor unit is a compression refrigerator. The objective is to realize a significant cost reduction by constructing a single system using only the above refrigerant.

[0006]

According to the first aspect of the present invention, the refrigerating capacity obtained in the absorption refrigerator is recovered in the condensed liquid refrigerant condensed and liquefied in the refrigerant condenser of the compression refrigerator.
That is, the subcooling degree of the condensed liquid refrigerant condensed and liquefied in the refrigerant condenser can be obtained by the refrigerating capacity of the absorption refrigerator. Therefore, the cooling operation can be performed by using the refrigerant evaporator of the compression refrigerator as the indoor heat exchanger. That is, the circulation route of the cooling / heating medium with respect to the indoor unit can be configured by one system of the refrigeration cycle of the compression refrigerator.
As a result, the indoor unit for the absorption chiller, the piping equipment, etc. are not required, so that a significant cost reduction can be realized.

According to the second aspect of the present invention, the refrigerating capacity obtained in the absorption refrigerator is recovered into the condensed liquid refrigerant condensed and liquefied in the refrigerant condenser of the compression refrigerator. The heat transfer pipe of the evaporator can be connected to the high-pressure pipe that connects the refrigerant condenser and the pressure reducing means. Therefore, in the evaporator of the absorption refrigerator, the liquid refrigerant condensed and liquefied in the condenser (absorption refrigerator) transfers latent heat of vaporization from the high-pressure refrigerant (condensed liquid refrigerant condensed and liquefied in the refrigerant condenser) flowing through the heat transfer tube. Take away and evaporate. On the other hand, the high-pressure refrigerant flowing in the heat transfer tube is cooled by the latent heat of vaporization taken away by the liquid refrigerant. That is, the degree of supercooling is obtained.

According to the third aspect of the present invention, the absorption chiller comprises a high temperature side absorption cycle in which the exhaust gas of the engine is used as a heat source and a low temperature side absorption cycle in which the cooling water of the engine is used as a heat source. be able to. This is when comparing engine cooling water and exhaust gas,
Since the exhaust gas temperature is higher than the cooling water temperature, by using this exhaust gas as a heat source of the regenerator, the temperature of the absorbing liquid heated in the regenerator (regeneration temperature) becomes higher. Therefore, at the same absorption temperature and condensation temperature as the low temperature side absorption cycle, it is possible to obtain a lower evaporation temperature than the low temperature side absorption cycle. Therefore, by recovering the refrigerating capacity obtained in the low temperature side absorption cycle to the condensed liquid refrigerant condensed and liquefied in the refrigerant condenser, and further recovering the refrigerating capacity obtained in the high temperature side absorption cycle to the condensed liquid refrigerant, You can get a subcool.

According to the invention of claim 4, in the low temperature side absorption cycle, the upstream region of the heat transfer tube is configured as a first evaporator, and in the high temperature side absorption cycle, the downstream region of the heat transfer tube is configured as a second evaporator. To do. Thereby, the refrigerating capacity of the low temperature side absorption cycle is recovered as a subcool of the condensate refrigerant flowing in the upstream area of the heat transfer tube, and the refrigerating capacity of the high temperature side absorption cycle is the condensate refrigerant flowing in the downstream area of the heat transfer tube, that is, the low temperature. It is recovered as a subcool in the condensed liquid refrigerant cooled by the refrigerating capacity of the side absorption cycle.

According to the invention of claim 5, the absorption refrigerator does not need to directly use the refrigerating capacity obtained by the evaporator as the cooling capacity. That is, it is only necessary to obtain an evaporation temperature at which a subcool can be given to the condensed liquid refrigerant condensed and liquefied by the refrigerant condenser of the compression refrigerator. This allows
Since the temperature of the absorbing liquid in the absorber and the condenser can be set higher than that of the conventional water cooling type, an air cooling type heat exchanger is provided in the cooling liquid circuit to circulate the absorber and the condenser. The cooling liquid can be air-cooled (air-cooled).
As a result, water cooling equipment (cooling tower, water cooling pipes, pumps, etc.) with high equipment costs and construction costs is not required, and the cooling liquid circuit can be closed by air cooling (closed type that is not exposed to the outside air). Also, water quality control is not required, and the cost can be significantly reduced.

According to the sixth aspect of the present invention, in the absorption refrigerator, it is necessary to circulate the cooling liquid in the absorber and the condenser by directly cooling the air by the air blown from the blower means. Since there is no cooling liquid circuit (including a pump), the cost can be further reduced.

According to the seventh aspect of the present invention, the absorption refrigeration exhaust heat is recovered in the condensate refrigerant flowing through the gas injection circuit provided in the compression refrigerating machine, so that it is air-cooled even when the outside air temperature is high. Is possible. That is, when only the absorption refrigerator is used during cooling in the summer, the exhaust heat temperature of the absorber and the condenser becomes 37 to 40 ° C., and a sufficient temperature difference from the outside air temperature cannot be obtained, so air cooling is difficult. is there. On the other hand, by recovering the exhaust heat of the absorption refrigeration system to the condensed liquid refrigerant, the exhaust heat temperature level increases up to about 60 ° C.,
Even an ordinary air-cooled heat exchanger can sufficiently exchange heat with the outside air.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, an embodiment of an engine type air conditioner of the present invention will be described with reference to the drawings. (First Embodiment) FIG. 1 is a schematic view showing the overall construction of an engine type air conditioner. Engine type air conditioner S of the present embodiment
Is composed of a compression refrigerator 2 driven by the engine 1 and an absorption refrigerator 3 using exhaust heat of the engine 1 as a heat source. The engine 1 burns fuel such as gasoline or diesel oil to generate rotational power. This engine 1 is a water-cooled type, and engine cooling water (hereinafter referred to as hot water)
A hot water pipe 4 for circulating is provided. The circulation of hot water is performed by a water pump (not shown).

The compression refrigerator 2 includes a refrigerant compressor 5 driven by the engine 1, and a refrigerant condenser 7 for condensing and liquefying the high temperature and high pressure refrigerant compressed by the refrigerant compressor 5 by the cooling fan 6. , A receiver 8 that stores the refrigerant sent from the refrigerant condenser 7 and sends only the liquid refrigerant, an expansion valve 9 (pressure reducing means) that decompresses and expands the refrigerant sent from the receiver 8, and the expansion valve 9 decompresses the refrigerant. Refrigerant evaporator 11 that evaporates low-temperature low-pressure refrigerant by blowing air from the indoor fan 10
And each of which is connected by a refrigerant pipe 12.

The absorption refrigerator 3 includes a regenerator 13 and a condenser 1.
4, evaporator 15, absorber 16, solution circuit (described below),
It is composed of a refrigerant circuit 17, a cooling water circuit 18 (cooling liquid circuit), and the like. The solution (absorption liquid) used in the absorption refrigerator 3 is, for example, lithium bromide as an absorbent,
It is a lithium bromide aqueous solution using water as a refrigerant.

The regenerator 13 has a pressure-resistant container 19 common to the condenser 14, and a heat transfer tube 13 a housed in the pressure-resistant container 19.
It is composed of The pressure vessel 19 is divided into a regenerator 13 side and a condenser 14 side by a partition plate 20 inside. However, the partition plate 20 is provided with an opening in the upper portion of the pressure vessel 19 that connects the regenerator 13 side and the condenser 14 side. The heat transfer pipe 13 a is connected to the hot water pipe 4 of the engine 1 while being immersed in the solution in the pressure vessel 19 (on the regenerator 13 side). In this regenerator 13, the hot water (about 8
(5 to 90 ° C.) through the heat transfer tube 13a, the solution contained in the pressure resistant container 19 is heated to evaporate the water, thereby concentrating the solution and obtaining a concentrated solution. The concentrated solution in this example means an aqueous solution in which the solubility of lithium bromide is about 60% by weight.

The condenser 14 comprises the pressure resistant container 19 and the heat transfer tube 14a housed in the pressure resistant container 19. The heat transfer pipe 14a is connected to the cooling water circuit 18, and cooling water (about 40 to 45 ° C.) flows inside. In the condenser 14, the refrigerant vapor (water vapor) evaporated in the regenerator 13 is cooled and liquefied by the cooling water flowing through the heat transfer tube 14a.

The evaporator 15 includes a pressure-resistant container 21 common to the absorber 16 and a heat transfer tube 15 a housed in the pressure-resistant container 21.
It is composed of The pressure-resistant container 21 is partitioned by a partition plate 22 into an evaporator 15 side and an absorber 16 side. However, the partition plate 22 is provided with an opening in the upper part of the pressure-resistant container 21 that connects the evaporator 15 side and the absorber 16 side. The heat transfer tube 15a is connected to a high-pressure pipe 12a that connects the receiver 8 and the expansion valve 9 of the compression refrigerator 2 and is configured so that a high-pressure refrigerant flows inside. In the evaporator 15, the refrigerant liquid (water) liquefied in the condenser 14
Is sprayed into the evaporator 15 and takes heat of vaporization from the refrigerant flowing through the heat transfer tube 15a (that is, the liquid refrigerant sent from the receiver 8) to evaporate, thereby cooling the refrigerant flowing through the heat transfer tube 15a.

The absorber 16 comprises the pressure resistant vessel 21 and a heat transfer tube 16a housed in the pressure resistant vessel 21. The heat transfer tube 16 a is the heat transfer tube 14 a of the condenser 14.
Is connected in series to the cooling water circuit 18, and cooling water (about 40 to 45 ° C.) flows inside. In this absorber 16, the refrigerant vapor evaporated in the evaporator 15 is absorbed by the solution sprayed in the absorber 16, so that the pressure vessel 21 can be kept in vacuum. On the other hand, the solution that has absorbed the refrigerant vapor has a reduced concentration and becomes a dilute solution. The dilute solution means an aqueous solution having a solubility of lithium bromide of about 55% by weight.

The solution circuit comprises a concentrated solution flow path 23, a dilute solution flow path 24, a solution heat exchanger 25, and a solution pump 26. The concentrated solution flow path 23 guides the concentrated solution concentrated in the regenerator 13 to the absorber 16, and has one end with a pressure resistant container 19
It is connected to the bottom of the (regenerator 13 side) and opens into the pressure resistant container 19, and the other end is taken into the pressure resistant container 21 (absorber 16 side). A nozzle 27 for spraying the solution is provided. The dilute solution flow path 24 regenerates the dilute solution whose concentration has been reduced in the absorber 16 by the regenerator 1.
3, which is a pressure-resistant container 21 (on the side of the absorber 16).
Is connected to the bottom of the pressure resistant container 21 and is opened in the pressure resistant container 21, and the other end is connected to the upper part of the pressure resistant container 19 (regenerator 13 side) and is opened in the pressure resistant container 19. The solution heat exchanger 25 exchanges heat between the concentrated solution (high temperature) flowing through the concentrated solution flow path 23 and the diluted solution (low temperature) flowing through the dilute solution flow path 24. Solution pump 26
Is provided in the dilute solution flow path 24 and sends the dilute solution of the absorber 16 to the regenerator 13.

The refrigerant circuit 17 guides the refrigerant liquid liquefied in the condenser 14 to the evaporator 15. One end of the refrigerant circuit 17 is a pressure resistant container 19.
The refrigerant connected to the bottom of (condenser 14 side) and opened in the pressure-resistant container 19 and the other end being taken into the pressure-resistant container 21 (evaporator 15 side) and guided from the condenser 14 to the tip thereof. A nozzle 28 for spraying the liquid is provided.

The cooling water circuit 18 is the heat transfer tube 1 of the absorber 16.
6a and the heat transfer pipe 14a of the condenser 14 are used to flow cooling water, and are provided with an air-cooling heat exchanger 29 and a cooling water pump 30. The air-cooling heat exchanger 29 cools the cooling water circulating in the cooling water circuit 18 by receiving the blowing air of the cooling fan 6, and is installed on the windward side of the refrigerant condenser 7 as shown in FIG. 1. The cooling water pump 30 circulates the cooling water in the cooling water circuit 18, and after the cooling water cooled by the air cooling heat exchanger 29 flows through the absorber 16, flows through the condenser 14 and again the air cooling heat exchange. Return to container 29.

Next, the operation of this embodiment will be described. The hot water heated with the start of operation of the engine 1 circulates in the hot water pipe 4 by the operation of the water pump. In the regenerator 13 connected to the hot water pipe 4, the dilute solution in the pressure vessel 19 is heated by the hot water flowing through the heat transfer pipe 13a and concentrated by evaporation of water. The refrigerant vapor evaporated and separated from the solution in the regenerator 13 is cooled by the cooling water flowing through the heat transfer tube 14a of the condenser 14, and then inside the pressure vessel 19 (condenser 14 side).
Liquefy with. The liquefied refrigerant liquid is guided through the refrigerant circuit 17 into the pressure-resistant container 21 (on the side of the evaporator 15) and the nozzle 28.
From the refrigerant flowing through the heat transfer tube 15a of the evaporator 15 to remove the latent heat of vaporization and evaporate. Therefore, the heat transfer tube 15a
The refrigerant flowing through is deprived of the latent heat of vaporization when the refrigerant liquid sprayed on the surface of the heat transfer tube 15a evaporates, and is cooled.

The solution (concentrated solution) concentrated in the regenerator 13 is introduced into the pressure resistant container 21 through the concentrated solution flow path 23 and sprayed from the nozzle 27. In the absorber 16 including the same pressure resistant container 21 as the evaporator 15, the refrigerant vapor generated in the evaporator 15 is absorbed by the concentrated solution sprayed from the nozzle 27. The diluted solution whose concentration has been reduced by absorbing the refrigerant vapor is sent from the absorber 16 through the diluted solution flow path 24 to the regenerator 13 by the solution pump 26. The concentrated solution passing through the concentrated solution flow path 23 and the diluted solution passing through the diluted solution flow path 24 are heat-exchanged by the solution heat exchanger 25, whereby the concentrated solution is cooled and the diluted solution is heated.

On the other hand, in the compression refrigerator 2, the refrigerant compressor 5 is driven as the engine 1 starts operating,
The gas refrigerant sucked from the low pressure side is compressed into high temperature and high pressure and discharged. The discharged refrigerant is blown by the cooling fan 6 in the refrigerant condenser 7 to be condensed and liquefied, and then sent to the receiver 8 to be separated into gas and liquid, and only the liquid refrigerant is sent out. The refrigerant sent from the receiver 8 is subcooled by the refrigerating capacity obtained by the evaporator 15 of the absorption refrigerator 3 (see FIG. 3). The refrigerant that has obtained this subcool is decompressed and expanded by the expansion valve 9 and sent to the refrigerant evaporator 11. The refrigerant evaporator 11 evaporates by heat exchange with the indoor air blown by the indoor fan 10, and again the refrigerant compressor. 5 is sucked.

(Characteristics and Effects of the First Embodiment) The engine type air conditioner S of the present embodiment is the evaporator 1 of the absorption refrigerator 3.
The refrigerating capacity obtained in 5 is used as the refrigerant condenser 7 of the compression refrigerator 2.
The air-cooling operation can be performed by recovering the liquid refrigerant condensed in the above step. Therefore, as shown in the Mollier diagram of FIG. 3, since a subcool of the liquid refrigerant is obtained, it is possible to realize a capacity improvement of about 60% as compared with the case where the compression refrigerator 2 is operated alone. .

Further, according to the system of the present embodiment, the circulation path of the cooling / heating medium with respect to the indoor unit 31 can be constituted by one system of the refrigerant used in the compression refrigerator 2. As a result, the indoor unit for the absorption chiller 3 and the piping equipment for the indoor unit are not required, so that the cost can be significantly reduced. The refrigerating capacity of the absorption refrigerator 3 is used for supercooling the liquid refrigerant flowing out from the receiver 8 of the compression refrigerator 2, but the refrigerating capacity of the refrigerant evaporator 11 of the compression refrigerator 2 is again used. Therefore, the refrigerating capacity of the absorption refrigerator 3 does not decrease.

Further, in this embodiment, the cooling water flowing through the absorber 16 and the condenser 14 of the absorption refrigerator 3 can be air-cooled. The reason for this will be described with reference to the Duhring diagram of FIG. 2 while comparing it with the conventional absorption refrigerator 3. Note that, in FIG. 2, the Duhring diagram of the present embodiment is shown by a solid line graph, and the conventional Duhring diagram is shown by a broken line graph. In the conventional absorption refrigerator, the regeneration temperature (point G ′ in FIG. 2) becomes 80 to 90 ° C. when the hot water exhaust heat of the engine 1 is used as the heat source of the regenerator, and low temperature cold water is taken out by the evaporator. The evaporation temperature (point E ′ in FIG. 2) to 4 to 6
Set to ° C. Therefore, the condensation temperature (C ′ in FIG. 2)
Point) and the absorption temperature (point A ′ in FIG. 2) are 35 to 42 ° C., and there is no temperature difference with the outside air (for example, around 40 ° C. in summer), so it is difficult to perform air cooling.

On the other hand, the absorption refrigerator 3 of this embodiment
Is only required to obtain the condensation temperature and the absorption temperature at which the liquid refrigerant flowing out from the receiver 8 of the compression refrigerator 2 can be supercooled by the refrigerating capacity obtained by the evaporator 15. That is,
If the refrigerant temperature at the receiver outlet is about 60 ° C., the evaporation temperature (point E in FIG. 2) is set to 25 to 30 ° C., and the condensation temperature (point C in FIG. 2) and absorption temperature (point A in FIG. 2) are set to 50. ~ 55
° C. Therefore, it is possible to sufficiently cool the cooling water circulating in the cooling water circuit 18 even in the summer when the outside air temperature is high.

Since the cooling water can be air-cooled as described above, a water-cooling facility (cooling tower, water-cooling pipe, pump, etc.) having high equipment costs and construction costs is not required, and the cooling water is cooled by the air-cooling. Since the circuit 18 can be of a closed type, water quality control is not required and the cost can be significantly reduced.

(Second Embodiment) FIG. 4 is a schematic view showing the overall construction of the engine type air conditioner S. The absorption refrigerating machine 3 of the present embodiment includes a low temperature side absorption cycle in which hot water of the engine 1 is used as a heat source and an exhaust gas of the engine 1 (about 400 to 5).
(00 ° C.) as a heat source. Since the structure of the compression refrigerator 2 is the same as that of the first embodiment, its explanation is omitted. In the low temperature side absorption cycle and the high temperature side absorption cycle, only the condenser 32 is shared, and a regenerator, an evaporator and an absorber are provided separately.

That is, the low temperature side absorption cycle is the engine 1
Low temperature regenerator 33 that heats the solution by using the cooling water (warm water) as a heat source, a condenser 32 that condenses and liquefies the refrigerant vapor evaporated in the low temperature regenerator 33 by heat exchange with the cooling water, and liquefies in the condenser 32. A first evaporator 34 that evaporates the refrigerant liquid by removing latent heat of vaporization from the refrigerant flowing through the heat transfer tube 34a, and a first vaporizer that absorbs the refrigerant vapor evaporated in the first evaporator 34 into the concentrated solution sent from the low temperature regenerator 33. An absorber 35, a first pump 36 that absorbs the refrigerant vapor in the first absorber 35 and sends a dilute solution having a reduced concentration to the low temperature regenerator 33, and a concentrated solution that flows from the low temperature regenerator 33 to the first absorber 35. First absorber 3
A first solution heat exchanger 37 for exchanging heat with the dilute solution sent from 5 to the low temperature regenerator 33 is provided.

In the high temperature side absorption cycle, the high temperature regenerator 38 that heats the solution by using the exhaust gas of the engine 1 as a heat source, and the condenser 32 that condenses and liquefies the refrigerant vapor evaporated in the high temperature regenerator 38 by heat exchange with cooling water. , A second evaporator 39 which evaporates the refrigerant liquid liquefied in the condenser 32 by evaporating latent heat of evaporation from the refrigerant flowing through the heat transfer tube 39a, and the second evaporator 3
A second absorber 40 for absorbing the refrigerant vapor evaporated in 9 into the concentrated solution sent from the high temperature regenerator 38, and the second absorber 40.
From the high temperature regenerator 38 to the high temperature regenerator 38, the second solution pumping the diluted solution whose concentration has been reduced by absorbing the refrigerant vapor in
The second solution heat exchanger 42 and the like for exchanging heat between the concentrated solution flowing to the absorber 40 and the dilute solution sent from the second absorber 40 to the high temperature regenerator 38 are provided.

The first evaporator 34, the first absorber 35,
The second evaporator 39 and the second absorber 40 can share the pressure resistant container 43, but since the pressure and the temperature are different between the low temperature side and the high temperature side, the inside of the pressure resistant container 43 has a high temperature side and a high temperature side. A partition plate 44 divides the side from the side in an airtight manner. The cooling water circulating in the cooling water circuit 18 flows in the order of the air cooling heat exchanger 29 → the first absorber 35 → the second absorber 40 → the condenser 32, and returns to the air cooling heat exchanger 29 again.

Since the absorption refrigerator 3 of this embodiment does not need to take out cold water from the first evaporator 34 and the second evaporator 39, the condensation temperature (point C in FIG. 5) and the absorption temperature (FIG. 5). Since A1 point and A2 point) can be set to, for example, 50 ° C., the cooling water can be air-cooled as in the first embodiment. Further, in the low temperature side absorption cycle and the high temperature side absorption cycle, since the high temperature side absorption cycle has a higher regeneration temperature (point G2 in Fig. 5), the evaporation temperature (point E2 in Fig. 5) is higher than that in the low temperature side absorption cycle. Can be lowered (eg about 4 ° C).

Therefore, as shown in the Mollier diagram of FIG. 6, after supercooling the liquid refrigerant liquefied in the refrigerant condenser 7 of the compression refrigerator 2 by the refrigerating capacity obtained in the low temperature side absorption cycle, the high temperature side absorption is performed. By further subcooling by the refrigerating capacity obtained in the cycle, it is possible to obtain a larger subcool than in the first embodiment, and the cooling capacity can be improved accordingly. Specifically, as shown in FIG. 7, about 39% of the cooling capacity in the low temperature side absorption cycle and about the cooling capacity in the high temperature side absorption cycle with respect to the cooling capacity when the compression type refrigerator 2 is operated independently. Two
It is possible to improve the capacity by 5%, or about 64% in total. Note that the effect of cooling the cooling water by air and the fact that the circulation path of the cooling / heating medium with respect to the indoor unit can be configured by one system of the refrigerant used in the compression refrigerator 2 (a drastic reduction in cost) is Is the same as.

(Third Embodiment) FIG. 8 is a schematic view showing the overall construction of the engine type air conditioner S. The absorption refrigerating machine 3 of the present embodiment has a configuration in which the condenser 14 and the absorber 16 are directly air-cooled with respect to the configuration described in the first embodiment.
A blower 45 (blowing means) for that purpose is provided.

As shown in FIG. 8, the condenser 14 and the absorber 16 constitute a heat exchanger in which heat transfer fins 14b and 16b are attached to the outer circumferences of the heat transfer tubes 14a and 16a, respectively. Therefore, the regenerator 13 is separated from the condenser 14 and has a dedicated pressure-resistant container 19, and is connected to the condenser 14 (heat transfer tube 14 a) by the refrigerant passage 46. Similarly, the evaporator 15 is separated from the absorber 16 in a dedicated pressure vessel 21.
And the absorber 16 (heat transfer tube 16
a).

The operation of this embodiment will be described. Regenerator 13
Then, the dilute solution in the pressure vessel 19 is heated by the hot water flowing through the heat transfer tube 13a and concentrated by evaporation of water. The refrigerant vapor evaporated and separated from the solution in the regenerator 13 is guided to the condenser 14 through the refrigerant passage 46 and is cooled by the air blow from the blower 45 when flowing through the heat transfer tube 14a of the condenser 14 to be condensed and liquefied. . The liquefied refrigerant liquid is introduced into the pressure-resistant container 21 of the evaporator 15, is sprayed from the nozzle 28, and removes latent heat of vaporization from the refrigerant (the refrigerant circulating in the compression refrigerator 2) flowing through the heat transfer pipe 15 a of the evaporator 15. Evaporate. Therefore, the refrigerant flowing through the heat transfer tube 15a is
When the refrigerant liquid sprayed on the surface of a is evaporated, the latent heat of vaporization is taken away and cooled.

Solution concentrated in the regenerator 13 (concentrated solution)
Is guided to the absorber 16 through the concentrated solution flow path 23 and is fed into the heat transfer tube 16 a of the absorber 16. Communication pipe 4
Inside the heat transfer tube 16a communicating with the pressure resistant container 21 of the evaporator 15 by 7, the refrigerant vapor introduced from the evaporator 15 is absorbed by the concentrated solution sent into the heat transfer tube 16a. The diluted solution whose concentration has been reduced by absorbing the refrigerant vapor inside the heat transfer tube 16a is sent from the absorber 16 through the diluted solution flow path 24 to the regenerator 13 by the solution pump 26. In addition,
The concentrated solution passing through the concentrated solution flow path 23 and the diluted solution passing through the diluted solution flow path 24 are heat-exchanged by the solution heat exchanger 25,
The concentrated solution is cooled and the dilute solution is heated.

On the other hand, as described in the first embodiment, the compression refrigerator 2 is supercooled by the refrigerating capacity of the refrigerant sent from the receiver 8 obtained by the evaporator 15 of the absorption refrigerator 3 ( (See FIG. 3). The refrigerant that has obtained this subcool is decompressed and expanded by the expansion valve 9 and sent to the refrigerant evaporator 11. The refrigerant evaporator 11 evaporates by heat exchange with the indoor air blown by the indoor fan 10, and again the refrigerant compressor. 5
Is sucked.

In the engine type air conditioner of this embodiment, as in the first embodiment, the evaporation temperature of the absorption refrigerator 3 (point E in FIG. 2).
Can be set to 25 to 30 ° C., and the condensation temperature (point C in FIG. 2) and the absorption temperature (point A in FIG. 2) can be set to 50 to 55 ° C. As a result, the condenser 14 and the absorber 16 can be sufficiently air-cooled even in the summer when the outside air temperature is high. For this reason, in the first embodiment, the cost is reduced by realizing the cooling of the cooling water circulating through the condenser 14 and the absorber 16, but in the present embodiment, the blower 45 is used to cool the condenser 14 and the absorber. The cooling water circuit 18 (including the air-cooling heat exchanger 29 and the cooling water pump 30) described in the first embodiment becomes unnecessary by adopting the system configuration of directly cooling the air in the cooling device 16. Thereby, the first
Even when compared with the embodiment, the cost can be further reduced.

Further, in this embodiment, since the condenser 14 and the absorber 16 are directly air-cooled by the blower 45,
The cooling efficiency is superior to the method of circulating cooling water in the condenser 14 and the absorber 16 and cooling the cooling water by air (that is, the system described in the first embodiment). Therefore, the effect that the power consumption of the blower 45 can be reduced can be obtained.

(Fourth Embodiment) FIG. 9 is a schematic view showing the overall construction of the engine type air conditioner S. The present embodiment shows an example of a configuration in which the exhaust heat of the absorption refrigerator 3 is recovered in the condensed liquid refrigerant of the compression refrigerator 2. The first
The same components as those in the embodiment are designated by the same reference numerals. The compression type refrigerator 2 includes a refrigerant compressor 5, a refrigerant condenser 7, a receiver 8, an expansion valve 9 and a refrigerant evaporator 11 in addition to a refrigeration cycle in which functional parts of the refrigerant evaporator 11 are annularly connected. A gas injection circuit 47 for branching a part of the condensed liquid refrigerant to return it to the refrigerant compressor 5 is provided, and the gas injection circuit 47 is provided with a second expansion valve 48. The absorption refrigerator 3 includes a regenerator 13, a condenser 14, an evaporator 15, and an absorber 16, and uses exhaust heat of the engine 1 (heat of engine cooling water) as a heat source of the regenerator 13. However, the heat transfer tubes 14a, 16a of the condenser 14 and the absorber 16
Respectively constitute a part of the gas injection circuit 47.

Next, the operation of this embodiment will be described. In the compression refrigerator 2, when the refrigerant compressor 5 is driven by receiving the driving force of the engine 1, the high-temperature and high-pressure refrigerant compressed by the refrigerant compressor 5 is sent to the outdoor refrigerant condenser 7, and the refrigerant. The condenser 7 receives air from a cooling fan (not shown) to radiate heat. The refrigerant condensed and liquefied in the refrigerant condenser 7 is subcooled in the evaporator 15 of the absorption refrigerator 3 except for a part branched downstream of the receiver 8. The supercooled refrigerant flows through the expansion valve 9
After being decompressed by, the refrigerant evaporator 11 in the room evaporates by heat exchange with room air and returns to the refrigerant compressor 5 again. A part of the condensed liquid refrigerant branched to the gas injection circuit 47 downstream of the receiver 8 is decompressed by the second expansion valve 48, then cools the absorber 16 of the absorption refrigerator 3, and further cools the condenser 14. Then, the exhaust heat of the absorption refrigerator 3 is recovered and returned to the refrigerant compressor 5 at an intermediate pressure.

On the other hand, in the absorption refrigerator 3, the solution heated by the exhaust heat of the engine 1 in the regenerator 13 generates vapor and is concentrated. The vapor evaporated in the regenerator 13 is the condenser 1
After being cooled and liquefied by the condensed liquid refrigerant flowing through the heat transfer tube 14a of No. 4, the condensed liquid refrigerant flowing through the heat transfer tube 15a of the evaporator 15 is sprayed from the nozzle 28 of the evaporator 15 to remove latent heat of vaporization and evaporate. . Therefore, the condensed liquid refrigerant flowing through the heat transfer tube 15a is cooled (supercooled) by removing latent heat of vaporization when the spray liquid sprayed on the surface of the heat transfer tube 15a is evaporated. The solution concentrated in the regenerator 13 is the absorber 1
6 is sprayed from the nozzle 27 in 6 and absorbed by the vapor evaporated in the evaporator 15 while being cooled by the condensate refrigerant flowing through the heat transfer tube 16a and diluted, and is fed again to the regenerator 13 by the solution pump 26.

As described above, by recovering the exhaust heat of the absorption refrigerating machine 3 into the condensate refrigerant of the compression refrigerating machine 2, the exhaust heat temperature level rises to about 60 ° C., so that the normal air-cooled heat Even the exchanger (refrigerant condenser 7 in this embodiment) can sufficiently exchange heat with the outside air, and an air-cooled type, which is lower in cost than the water-cooled type, can be adopted. Since the circulation route of the cooling / heating medium with respect to the indoor unit can be configured by one system of the refrigerant used in the compression refrigerator 2, the indoor unit for the absorption refrigerator 3 and the piping facility for the indoor unit are provided. It is the same as the first embodiment in that it is not necessary and a large cost reduction can be achieved.

Further, the apparatus of this embodiment is the compression refrigerator 2
Since the gas injection circuit 47 is provided in FIG. 10, a cycle B in which a subcool is obtained in the evaporator 15 and a cycle C in which the gas injection circuit 47 flows are established as shown in FIG. Therefore, compared with the circuit configuration shown in the first embodiment, the capacity is reduced by the amount of a part of the condensed liquid refrigerant used in the cycle C, but the capacity is improved as compared with the normal refrigeration cycle A. For example, comparing the normal refrigeration cycle with a single effect that uses only the exhaust heat of the engine hot water and a double effect that also uses exhaust heat It is possible to improve the capacity by about 12% and about 25% in the case of double effect (see FIG. 11).

(Modification) In the first to fourth embodiments,
Although the compression refrigerator 2 of the receiver cycle has been described, the same effect can be obtained in the accumulator cycle. Further, in the first and second embodiments, the refrigerant condenser 7 of the compression type refrigerator 2 is arranged leeward of the air-cooling heat exchanger 29 of the cooling water circuit 18, but the reverse is also possible. That is, the refrigerant condenser 7 may be arranged on the windward side of the air-cooling heat exchanger 29.
Alternatively, the air-cooling heat exchanger 29 and the refrigerant condenser 7 may be arranged in parallel.

In the third embodiment, the system configuration of the first embodiment is applied to directly cool the condenser 14 and the absorber 16, but the system configuration of the second embodiment is also applied. good. That is, the condenser 32, the first absorber 35, and the second absorber 40 of the second embodiment may be directly air-cooled by the blower 45.

[Brief description of drawings]

FIG. 1 is a schematic diagram showing an overall configuration of an engine type air conditioner (first embodiment).

FIG. 2 is a Dühring diagram of the absorption refrigerator according to the first embodiment.

FIG. 3 is a Mollier diagram of the compression refrigerator shown in the first embodiment.

FIG. 4 is a schematic diagram showing an overall configuration of an engine type air conditioner (second embodiment).

FIG. 5 is a Dühring diagram of the absorption refrigerator according to the second embodiment.

FIG. 6 is a Mollier diagram of the compression refrigerator shown in the second embodiment.

FIG. 7 is a graph showing an effect (improvement of cooling capacity) of the second embodiment.

FIG. 8 is a schematic diagram showing an overall configuration of an engine type air conditioner (third embodiment).

FIG. 9 is a schematic diagram showing an overall configuration of an engine type air conditioner (fourth embodiment).

FIG. 10 is a Mollier diagram of the compressor refrigerator shown in the fourth embodiment.

FIG. 11 is a graph showing performance improvement (fourth example).

[Explanation of symbols]

 S Engine type air conditioner 1 Engine 2 Compression type refrigerator 3 Absorption type refrigerator 5 Refrigerant compressor 7 Refrigerant condenser 9 Expansion valve (Decompression means) 11 Refrigerant evaporator 12a High pressure piping 13 Regenerator 14 Condenser (first embodiment) , 3rd Example) 15 evaporator 15a heat transfer tube 16 absorber 18 cooling water circuit (cooling liquid circuit) 29 air cooling heat exchanger 32 condenser (second example) 33 low temperature regenerator 34 first evaporator 34a heat transfer tube 35 1st absorber 36 1st pump 38 High temperature regenerator 39 2nd evaporator 40 2nd absorber 41 2nd pump 45 Blower (blower means / 3rd Example) 47 Gas injection circuit

Claims (7)

[Claims] 1. An absorption refrigerating machine comprising an engine that burns fuel to generate rotational power, a regenerator, a condenser, an evaporator, and an absorber, and uses exhaust heat of the engine as a heat source of the regenerator. A refrigerant compressor, a refrigerant condenser, a pressure reducing means, a refrigerant evaporator, the refrigerant compressor is composed of a compression refrigerator driven by the engine, the refrigerating capacity obtained by the absorption refrigerator, An engine type air conditioner having a configuration in which the condensed liquid refrigerant condensed and liquefied by the refrigerant condenser is recovered. 2. The engine type air conditioner according to claim 1, wherein the evaporator of the absorption chiller is connected to a high pressure pipe that connects the refrigerant condenser of the compression chiller and the pressure reducing means. An engine type air conditioner having a heat transfer tube configured to perform heat exchange between the liquid refrigerant sent from the condenser of the absorption refrigerator and the high-pressure refrigerant flowing in the heat transfer tube. 3. The engine type air conditioner according to claim 1, wherein the absorption refrigerator has a high temperature side absorption cycle in which exhaust gas of the engine is used as a heat source, and cooling water of the engine is used as a heat source. A refrigerating capacity obtained in the high temperature side absorption cycle, which is composed of a low temperature side absorption cycle to be used, and after recovering the refrigerating capacity obtained in the low temperature side absorption cycle to the condensed liquid refrigerant condensed and liquefied in the refrigerant condenser. Is recovered in the condensate refrigerant as an engine type air conditioner. 4. The engine type air conditioner according to claim 3, wherein, in the low temperature side absorption cycle, a low temperature regenerator that heats an absorbing liquid by using cooling water of the engine as a heat source, and a refrigerant generated in the low temperature regenerator. The condenser for condensing and liquefying steam by heat exchange with a cooling liquid, and the first evaporator for depriving the high-pressure refrigerant flowing in the upstream region of the heat transfer tube to evaporate the refrigerant liquid liquefied in the condenser by evaporation. A first absorber that absorbs the refrigerant vapor evaporated in the first evaporator into a high-concentration absorption liquid sent from the low-temperature regenerator, and an absorption in which the refrigerant vapor is absorbed in the first absorber to reduce the concentration. A first pump for sending the liquid to the low temperature regenerator, and the high temperature side absorption cycle comprises a high temperature regenerator for heating the absorbing liquid using the exhaust gas of the engine as a heat source, and a refrigerant vapor evaporated in the high temperature regenerator. With cooling liquid , A second evaporator for condensing and liquefying the condensed refrigerant liquid by the heat exchange, a second evaporator for evaporating the refrigerant liquid liquefied by the condenser from the high pressure refrigerant flowing in the downstream region of the heat transfer tube to evaporate latent heat of vaporization, and the second evaporator. A second absorber that absorbs the refrigerant vapor evaporated in step S2 into a high-concentration absorption liquid sent from the high-temperature regenerator; and a second absorber that absorbs the refrigerant vapor and reduces the concentration of the absorption liquid. An engine-type air conditioner, comprising: a second pump for sending to an air conditioner. 5. The engine cooling apparatus according to any one of claims 1 to 4, wherein the absorption refrigerator has a cooling liquid circuit in which a cooling liquid circulates through the absorber and the condenser, An engine type air conditioner characterized in that an air-cooled heat exchanger is provided in the cooling liquid circuit. 6. The engine cooling apparatus according to any one of claims 1 to 3, wherein the absorption refrigerating machine includes a blowing unit that blows air to the absorber and the condenser. An engine-type air conditioner, wherein the air conditioner is cooled by receiving air blown from the air blower. 7. The engine type air conditioner according to claim 1, wherein the compression refrigerator cools a part of the condensed liquid refrigerant condensed and liquefied by the refrigerant condenser upstream of the pressure reducing means. The engine cooling system has a gas injection circuit that branches back to the refrigerant compressor and recovers the absorption refrigeration exhaust heat to the condensed liquid refrigerant flowing through the gas injection circuit. apparatus.