JP2010243083A - Refrigerating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain an effect of improving performance both in cooling operation and heating operation in a refrigerating device formed of a combination of a vapor compression type refrigerating machine and an absorption type refrigerating machine. <P>SOLUTION: In this refrigerating device with the vapor compression type refrigerating machine X and the absorption type refrigerating machine Y, a solenoid valve 41 is arranged in a pipe line 67 reaching a refrigerant heat recovery heat exchanger 6 from the outlet side of the absorber 12 of the absorption type refrigerating machine Y. During cooling operation, the solenoid valve 41 is opened. On the other hand, during heating operation, a four-way selector valve 2 is switched, thereby making the refrigerant of the vapor compression type refrigerating machine flow in a direction opposite to that in cooling operation, and it is closed when the refrigerant temperature of the vapor compression type refrigerating machine X is at a set refrigerant temperature or more, and opened when it is below the set refrigerant temperature, or closed when the temperature of the solution on the outlet side of the supercooling heat exchanger 15 of the absorption type refrigerating machine Y is at the set refrigerant temperature or more, and opened when it is below the set solution temperature. By this constitution, the effect of improving the performance can be obtained both in the cooling operation and heating operation of the vapor compression type refrigerating machine X. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a refrigeration apparatus configured by combining a vapor compression refrigerator and an absorption refrigerator.

  As one of the methods for improving the performance of the vapor compression refrigerator, an absorption refrigerator is combined with the vapor compression refrigerator, the absorption refrigerator is driven using a gas engine or other exhaust heat as a heat source, A method of supercooling the refrigerant of the vapor compression refrigeration machine using the cold heat obtained here, or a method of reducing the condensation temperature of the refrigerant by cooling the refrigerant after compression of the vapor compression refrigeration machine using the obtained cold heat. A refrigeration apparatus that improves performance is known (see, for example, Patent Document 1).

  Further, in a refrigeration apparatus in which an absorption refrigeration machine is combined with a vapor compression refrigeration machine, as a method for further improving the performance as compared with the refrigeration apparatus disclosed in Patent Document 1, In addition to other waste heat, a technology that utilizes waste heat of a vapor compression refrigerator has also been proposed (see Patent Document 2).

JP 2004-28374 A JP 2006-17350 A

  However, in the technique shown in Patent Document 2, since the exhaust heat amount of the vapor compression refrigerator is small and the exhaust heat temperature is also low, even if this exhaust heat is used as a drive heat source for the absorption refrigerator, its effect is limited. However, it can be said that the practicality is limited because it is not large and it takes a lot of cost to combine the absorption refrigerator for using the exhaust heat.

  With regard to the refrigeration apparatus shown in Patent Document 2, the refrigeration apparatus focuses only on the performance improvement during the cooling operation, and is also due to the fact that the performance improvement during the heating operation is not considered. If the performance can be improved both at the time and during the heating operation, it is considered that the practicality will increase as a whole.

  Therefore, regarding the combination of the vapor compression refrigerator and the absorption refrigerator, the basic configuration is similar to the refrigeration apparatus described in Patent Document 2, but the absorption refrigerator described in Patent Document 2 is water-cooled. As an example, an absorption refrigeration machine is assumed to be a conventional system that has a basic structure based on an air cooling system and is provided with a four-way switching valve to enable cooling operation and heating operation. FIG. 8 shows a circuit diagram thereof.

  In FIG. 8, symbol X is a vapor compression refrigerator, and Y is an absorption refrigerator. The vapor compression refrigerator X includes a compressor 1, a four-way switching valve 2, a use side heat exchanger 3, an expansion valve 4, a heat source side heat exchanger 7, and an accumulator 5. The absorption refrigerator Y includes a generator 11, an absorber 12, an evaporator 13, a condenser 14, a supercooling heat exchanger 15, a solution heat exchanger 16, and a solution pump 17.

  In this refrigeration apparatus, in order to supercool the refrigerant of the vapor compression refrigeration machine X in the evaporator 13 of the absorption refrigeration machine Y, between the use side heat exchanger 3 and the heat source side heat exchanger 7, The pipe 54 is connected to the heat exchanger 13a of the evaporator 13 of the absorption refrigeration machine Y, and the exhaust heat of the refrigerant on the vapor compression refrigeration machine X side is connected to the generator 11 of the absorption refrigeration machine Y. In order to use it as a driving heat source, a heat exchanger 11b in which a pipe line 58 between the heat source side heat exchanger 7 and the four-way switching valve 2 of the vapor compression refrigerator X is disposed in the generator 11 is used. Connected to.

  With this configuration, during the cooling operation of the vapor compression refrigeration machine X, the refrigerant compressed by the compressor 1 is introduced into the generator 11, where the refrigerant in the generator 11 The refrigerant heat of the vapor compression refrigerator X is recovered to the solution side by heat exchange between them, and is used as a driving heat source for the generator 11. The refrigerant of the vapor compression refrigeration machine X is cooled and condensed by the atmosphere by the heat source side heat exchanger 7, and the refrigerant exiting the heat source side heat exchanger 7 flows into the evaporator 13 where it is supercooled. As the refrigerant temperature decreases, the specific enthalpy of the refrigerant inlet in the usage-side heat exchanger 3 decreases, and the cooling capacity of the usage-side heat exchanger 3 improves. That is, during the cooling operation, the original purpose can be achieved by the configuration in which the vapor compression refrigerator X and the absorption refrigerator Y are combined. However, the amount of heat that can be recovered in the generator 11 by the refrigerant of the vapor compression refrigerator X is limited by the solution temperature in the generator 11 in which the absorption refrigerator Y can form a cycle. Therefore, the heat exchanger 7 on the heat source side for cooling the refrigerant of the vapor compression refrigerator X in the atmosphere is required.

  On the other hand, during the heating operation, the four-way switching valve 2 is switched and the refrigerant of the vapor compression refrigeration machine X flows in the opposite direction to the cooling operation, but the refrigerant after being compressed by the compressor 1 is used on the usage side. Heat is exchanged in the heat exchanger 3, passes through the pipe 54 from the heat exchanger 13 a in the evaporator 13 of the absorption refrigeration machine Y, absorbs heat from the atmosphere in the heat source side heat exchanger 7, and flows into the generator 11. . For example, the operation of the condenser 14 and the supercooling heat exchanger 15 of the absorption refrigeration machine Y is stopped, and from the solution in the generator 11 driven by the gas engine or other exhaust heat supplied from the pipe 60. The refrigerant of the vapor compression refrigerator X in the generator 11 absorbs heat and returns to the compressor 1 through the four-way switching valve 2, but even if it is circulated by the solution pump 17, Since the heat exchanger 11b is arranged, the heat exchange efficiency between the solution in the generator 11 and the refrigerant vapor on the vapor compression refrigerator X side performed via the heat exchanger 11b is as follows. The effect of heating the refrigerant by the solution temperature to raise the evaporation temperature of the refrigerant is very poor, and as a result, there are few places that contribute to improving the performance of the vapor compression refrigerator X. Moreover, when the heat exchanger 11b in the generator 11 is enlarged in order to obtain the effect sufficiently, it is not practical because of the high cost of the heat exchanger corresponding to the effect.

  Accordingly, during the heating operation, it is necessary to absorb heat from the atmosphere in the heat source side heat exchanger 7, and depending on the temperature of the atmosphere, frosting of the fins of the heat source side heat exchanger 7 is unavoidable, and the heating capacity decreases. It has become a practical issue.

  As described above, even if the refrigeration apparatus is configured as shown in FIG. 8 so that the cooling operation and the heating operation can be performed by combining the vapor compression refrigerator and the absorption refrigerator as shown in Patent Document 2, A great performance improvement effect cannot be expected both during operation and during heating operation, and therefore it is still impractical.

  However, against the background of rising energy costs in recent years and the progress of development of air conditioners using natural refrigerants, there are issues of improving the performance of steam compression refrigerators and promoting the use of waste heat from the steam compression refrigerators However, not only does it take advantage of exhaust heat from gas engines and other wastewater, but it also uses the exhaust heat from the vapor compression refrigeration machine to convert it into cold heat to improve the performance during cooling operation and at the same time during heating operation. In Japan, the development of technology to further improve performance by effectively using the exhaust heat of the vapor compression refrigerator has been requested.

  In this way, when the absorption refrigeration machine is used during heating operation to improve the performance of the vapor compression chiller, the problem is the amount of exhaust heat available in the absorption refrigeration machine, and the amount of exhaust heat is sufficient. Even if the amount of exhaust heat is small, it is required to improve the performance of the vapor compression refrigerator by some method.

  Therefore, the present invention is mainly intended to obtain a performance improvement effect in both the cooling operation and the heating operation in the refrigeration apparatus configured by combining the vapor compression refrigerator and the absorption refrigerator. .

  In the present invention, the following configuration is adopted as a specific means for solving such a problem.

  In the first invention of the present application, in the refrigeration apparatus configured to include the vapor compression refrigeration machine X and the absorption refrigeration machine Y driven by exhaust heat of the engine or the like, the absorber 12 of the absorption refrigeration machine Y includes While the inflowing solution is supercooled by the air-cooled supercooling heat exchanger 15 and flows into the absorber 12, the refrigerant of the vapor compression refrigerator X and the absorber 12 of the absorption refrigerator Y A heat recovery heat exchanger 6 is provided for exchanging heat with the solution branched from the pipe 67 leading from the outlet to the solution heat exchanger 16 through the solution pump 17, and after heat exchange in the heat recovery heat exchanger 6. The refrigerant of the vapor compression refrigerator X flows into the evaporator 13 of the absorption refrigerator Y, and the solution of the absorption refrigerator Y flows into the generator 11 and from the outlet of the solution pump 17. Solenoid valve on pipe 67 leading to heat recovery heat exchanger 6 1 is opened during the cooling operation of the vapor compression refrigeration machine X, while the four-way switching valve 2 is switched during the heating operation of the vapor compression refrigeration machine X. The refrigerant of the refrigerator X is caused to flow in the opposite direction to the cooling operation, the solution pump 17 and the supercooling heat exchanger fan 20 are operated, and the refrigerant temperature of the vapor compression refrigerator X in the evaporator 13 is set to the set refrigerant temperature. When the temperature is lower than the set refrigerant temperature, the valve is closed, or when the solution temperature on the outlet side of the supercooler 15 of the absorption refrigerator Y is equal to or higher than the set refrigerant temperature, the valve is closed. A feature is that the valve is opened when the temperature is lower than the solution temperature.

  In the second invention of the present application, in the refrigeration apparatus according to the first invention, the inlet-side pipe 66 of the absorber 12 of the absorption refrigerator Y and the refrigerant inlet-side pipe 62 of the evaporator 13 are used. Are connected by a pipe line 73 provided with an electromagnetic valve 43, and the electromagnetic valve 43 is closed during the cooling operation of the vapor compression refrigerator X, and the electromagnetic valve 43 is opened during the heating operation. It is characterized by that.

  According to a third invention of the present application, in the refrigeration apparatus according to the first invention, the pipe 66 on the inlet side of the absorber 12 of the absorption chiller Y is connected to the pipe 74 provided with the electromagnetic valve 43. The electromagnetic valve 43 is connected to the evaporator 13, and the electromagnetic valve 43 is closed during the cooling operation of the vapor compression refrigerator X, and the electromagnetic valve 43 is opened during the heating operation.

  In the fourth invention of the present application, in the refrigeration apparatus according to the first, second, or third invention, the electromagnetic valve 44 is provided in the pipe line 66 on the inlet side of the absorber 12 of the absorption refrigerator Y, The electromagnetic compression valve 44 is closed during the cooling operation of the vapor compression refrigerator X, and the electromagnetic valve 44 is opened during the heating operation.

  According to a fifth invention of the present application, in the refrigeration apparatus according to the first, second, third or fourth invention, an electromagnetic valve 45 is provided in the pipe line 60 on the exhaust heat inlet side of the generator 11 for cooling operation. The solenoid valve 45 is sometimes opened, while the solenoid valve 45 is closed when the solution temperature of the generator 11 is equal to or higher than the set solution temperature during heating operation, and the solenoid valve 45 is opened when the temperature is lower than the set solution temperature. It is characterized by being configured to be valved.

  In the sixth invention of the present application, in the refrigeration apparatus according to the third or fourth invention, the sprayer for spraying the solution and the sprayer for spraying the refrigerant liquid in the evaporator 13 can be configured separately or shared. It is characterized by having an integrated structure.

  According to a seventh invention of the present application, in the refrigeration apparatus according to the first, second, third, fourth, fifth or sixth invention, the evaporator 13 is provided with a transient refrigerant liquid. The refrigerant liquid which flows through the heat transfer surface 13 and has not evaporated yet moves to the absorber 12 side and is absorbed by the solution on the absorber 12 side.

  In the eighth invention of the present application, in the refrigeration apparatus according to the first, second, third, fourth, fifth, sixth or seventh invention, a plurality of the vapor compression refrigerators X are installed. Each of the vapor compression refrigeration machines X is provided with the heat recovery heat exchanger 6 to recover the exhaust heat of the refrigerant of each of the vapor compression refrigeration machines X, and is recovered by each of the heat recovery heat exchangers 6. The exhaust heat is configured to be supplied to the generator 11 of one absorption refrigerator Y.

  In the present invention, the following effects can be obtained.

(A) 1st invention of this application In 1st invention of this application, as illustrated in FIG. 1, it has the vapor | steam compression refrigerator X and the absorption refrigerator Y driven by exhaust heat, such as an engine. In the constructed refrigeration apparatus, the solution flowing into the absorber 12 of the absorption refrigerator Y is supercooled by the air-cooled supercooling heat exchanger 15 to flow into the absorber 12, while the vapor compression refrigeration is performed. Heat recovery heat for heat exchange between the refrigerant of the machine X and the solution branched from the pipe 67 from the outlet of the absorber 12 of the absorption refrigerator Y to the solution heat exchanger 16 via the solution pump 17 An exchanger 6 is provided, and the refrigerant of the vapor compression refrigerator X after heat exchange in the heat recovery heat exchanger 6 is transferred to the evaporator 13 of the absorption refrigerator Y to the solution of the absorption refrigerator Y. Respectively flows into the generator 11 and electromagnetically enters the pipe 67. 41, and the solenoid valve 41 is opened during the cooling operation of the vapor compression refrigerator X, while the four-way switching valve 2 is switched during the heating operation of the vapor compression refrigerator X, and the vapor compression type The refrigerant of the refrigerator X is caused to flow in the opposite direction to the cooling operation, the solution pump 17 and the supercooling heat exchanger fan 20 are operated, and the refrigerant temperature of the vapor compression refrigerator X in the evaporator 13 is set to the set refrigerant temperature. When the temperature is lower than the set refrigerant temperature, the valve is closed, or when the solution temperature on the outlet side of the supercooler 15 of the absorption refrigerator Y is equal to or higher than the set refrigerant temperature, the valve is closed. The valve is configured to open when the temperature is lower than the solution temperature.

Therefore, the following functions and effects can be obtained during the cooling operation and the heating operation of the vapor compression refrigerator X, respectively.
(A-1) During the cooling operation of the vapor compression refrigerator X, the solenoid valve 41 is opened. Therefore, the heat recovery heat exchanger 6 exchanges heat between the refrigerant compressed by the compressor 1 of the vapor compression refrigeration machine X and the solution exiting the absorber 12 of the absorption refrigeration machine Y. The solution after the temperature is increased by heat exchange flows into the generator 11 of the absorption refrigeration machine Y, so that the refrigerant exhaust heat of the vapor compression refrigeration machine X is used as a driving heat source for the generator 11. In addition, effective use of exhaust heat is promoted as compared with the case where the generator 11 is driven only by exhaust heat from an engine or the like.

  Further, the refrigerant of the vapor compression refrigeration machine X after the heat exchange by the heat recovery heat exchanger 6 is changed by the refrigerant from the condenser 14 of the absorption refrigeration machine Y in the evaporator 13 of the absorption refrigeration machine Y. By supercooling the refrigerant of the vapor compression refrigeration machine X, the specific enthalpy of the refrigerant inlet of the vapor compression refrigeration machine X in the use-side heat exchanger 3 is lowered, thereby cooling the vapor compression refrigeration machine X. Performance is improved.

  Furthermore, the refrigerant of the vapor compression refrigeration machine X is supercooled by using the evaporation heat of the refrigerant of the absorption refrigeration machine Y in the evaporator 13 of the absorption refrigeration machine Y, in other words, By evaporating the refrigerant on the absorption refrigerator Y side with the refrigerant on the vapor compression refrigerator X side, for example, the absorption refrigerator Y in the evaporator 13 evaporates the refrigerant with cold water. In comparison with the case, the evaporation temperature of the refrigerant in the evaporator 13 can be increased, and as a result, the absorption refrigeration machine Y is downsized, and effective use of cold heat in the absorption refrigeration machine Y is achieved. Is promoted.

  (A-2) On the other hand, at the time of heating operation of the vapor compression refrigeration machine X, the four-way switching valve 2 is switched, and the refrigerant of the vapor compression refrigeration machine X is caused to flow in the opposite direction to the cooling operation. The solution pump 17 of the refrigerator Y and the fan 20 for the supercooling heat exchanger are operated, and heat exchange with the solution circulating between the supercooling heat exchanger 15 and the absorber 12 causes the above-mentioned vapor compression refrigerator X side. The refrigerant absorbs heat from the outside air. In this case, the solenoid valve 41 is based on the refrigerant temperature of the vapor compression refrigerator X in the evaporator 13 or the supercooler 15 of the absorption refrigerator Y. The valve is opened and closed based on the solution temperature on the outlet side.

  (A-2-1) When the solenoid valve 41 is opened and closed based on the refrigerant temperature of the vapor compression refrigerator X in the evaporator 13 of the absorption refrigerator Y, the solenoid valve 41 is The valve is closed when the refrigerant temperature on the vapor compression refrigerator X side is equal to or higher than the set refrigerant temperature, and is opened when the refrigerant temperature is lower than the set refrigerant temperature.

  When the refrigerant temperature on the vapor compression refrigerator X side is equal to or higher than the set refrigerant temperature, the absorption refrigerator Y side used for heat exchange with the refrigerant on the vapor compression refrigerator X side in the evaporator 13 The temperature of the solution circulating between the supercooling heat exchanger 15 and the absorber 12 is also high, and the solution on the vapor compression refrigeration machine X side that circulates the solution flowing through the absorber 12 and the evaporator 13 is used. Therefore, it is not necessary to increase the temperature by circulating the solution on the generator 11 side to the supercooling heat exchanger 15 side. Therefore, the solenoid valve 41 is closed. To be spoken.

  However, when the refrigerant temperature on the vapor compression refrigerator X side is lower than the set refrigerant temperature, the absorption refrigeration used for heat exchange with the refrigerant on the vapor compression refrigerator X side in the evaporator 13. The temperature of the solution circulating between the supercooling heat exchanger 15 and the absorber 12 on the machine Y side decreases, and the vapor compression refrigerator that circulates the solution flowing through the absorber 12 and the evaporator 13 While heat exchange performance with the refrigerant on the X side is deteriorated, frost formation may occur in the supercooling heat exchanger 15. In this case, when the electromagnetic valve 41 is opened, a solution having a high temperature on the generator 11 side circulates to the supercooling heat exchanger 15 side, thereby increasing the solution temperature, and the evaporator 13 is recovered, and frost formation in the supercooling heat exchanger 15 is prevented. Therefore, in addition to no reduction in heating capacity during frost formation, uncomfortable operation for removing frost does not occur.

  That is, the performance improvement effect is obtained in both the cooling operation and the heating operation of the vapor compression refrigerator X, and a practical refrigeration apparatus is obtained.

  (A-2-2) When the vapor compression refrigerator X is operated for heating, the solenoid valve 41 is opened and closed based on the solution temperature on the outlet side of the supercooler 15 of the absorption refrigerator Y. In this case, the solenoid valve 41 is closed when the solution temperature of the absorption refrigeration machine Y is equal to or higher than the set refrigerant temperature, and is opened when the temperature is lower than the set solution temperature.

  When the solution temperature of the absorption refrigeration machine Y is equal to or higher than the set refrigerant temperature, the heat exchange performance between the solution in the evaporator 13 and the refrigerant on the vapor compression refrigeration machine X side is favorably maintained. It is not necessary to circulate the solution on the generator 11 side to the supercooling heat exchanger 15 side to increase its temperature, and therefore the solenoid valve 41 is closed.

  However, when the solution temperature of the absorption refrigerator Y is lower than the set solution temperature, the heat exchange performance between the solution in the evaporator 13 and the refrigerant on the vapor compression refrigerator X side decreases, and the above There is also a possibility that frost formation may occur in the subcooling heat exchanger 15. In this case, when the electromagnetic valve 41 is opened, a solution having a high temperature on the generator 11 side circulates to the supercooling heat exchanger 15 side, thereby increasing the solution temperature, and the evaporator 13 is recovered, and frost formation in the supercooling heat exchanger 15 is prevented. Accordingly, there is no unpleasant operation for removing frost as well as no reduction in heating capacity during frost formation.

  That is, the performance improvement effect is obtained in both the cooling operation and the heating operation of the vapor compression refrigerator X, and a practical refrigeration apparatus is obtained.

  (A-3) Furthermore, during the cooling operation of the vapor compression refrigeration machine X, the refrigerant of the vapor compression refrigeration machine X is condensed by heat recovery in the refrigerant heat recovery heat exchanger 6, and during the heating operation. Since the evaporation of the refrigerant of the vapor compression refrigerator X is performed by heat recovery in the refrigerant heat recovery heat exchanger 6, the heat radiation side provided as an essential component in the conventional vapor compression refrigerator A heat exchanger becomes unnecessary, and the structure of the vapor compression refrigerator X can be simplified.

(B) Second Invention of the Present Application In the refrigeration apparatus according to the second invention of the present application, as illustrated in FIG. 2, the pipe line 66 on the inlet side of the absorber 12 of the absorption refrigerator Y and the evaporation described above. The refrigerant inlet side pipe line 62 of the condenser 13 is connected by a pipe line 73 provided with an electromagnetic valve 43, and the electromagnetic valve 43 is closed during the cooling operation of the vapor compression refrigeration machine X, and the above four valves are used during the heating operation. The path switching valve 2 is switched, the refrigerant of the vapor compression refrigerator X is caused to flow in the direction opposite to the cooling operation, and the electromagnetic valve 43 is opened.

  Therefore, according to the refrigeration apparatus Z according to the present invention, the following specific effects can be obtained in addition to the effects described in (a) above.

  (B-1) During the cooling operation of the vapor compression refrigeration machine X, the solenoid valve 43 is closed so that the circuit configuration is the circuit configuration during the cooling operation of the refrigeration apparatus according to the first invention. The same effects can be obtained.

  (B-2) During the heating operation of the vapor compression refrigerator X, the solution pump 17 and the supercooling heat exchanger fan 20 of the absorption refrigerator Y are operated. In this state, when the electromagnetic valve 43 is opened, a part of the solution circulating between the supercooling heat exchanger 15 and the absorber 12 of the absorption refrigeration machine Y is part of the evaporator 13 side. In the evaporator 13, heat exchange is performed between the solution and the refrigerant on the vapor compression refrigerator X side, and heat exchange is indirectly performed in the evaporator 13 via the absorber 12. The heat exchange performance is further improved as compared with the case where it is performed.

  (B-3) As a synergistic effect of the above (b-1) and (b-2), the performance improvement effect can be obtained in both the cooling operation and the heating operation of the vapor compression refrigeration machine X. A refrigeration apparatus rich in nature will be obtained.

  (B-4) On the other hand, the pipe line 66 on the inlet side of the absorber 12 of the absorption refrigerator Y and the pipe line 62 on the refrigerant inlet side of the evaporator 13 are connected by a pipe line 69 including an electromagnetic valve 43. Since the pipe 62 is also used as a pipe for the solution flowing from the supercooling heat exchanger 15 to the absorber 12 during heating operation, the evaporation is performed as compared with a case where a pipe is separately provided. The pipe line configuration on the inlet side of the vessel 13 is simplified.

(C) Third invention of the present application In the refrigeration apparatus according to the third invention of the present application, as illustrated in FIG. 3, the conduit 66 on the inlet side of the absorber 12 of the absorption refrigerator Y is electromagnetically coupled. Connected to the evaporator 13 via a pipe line 74 provided with a valve 43, the electromagnetic valve 43 is closed during the cooling operation of the vapor compression refrigerator X, and the four-way switching valve 2 is switched during the heating operation. The refrigerant of the vapor compression refrigerator X is made to flow in the opposite direction to the cooling operation, and the electromagnetic valve 43 is opened.

  Therefore, according to the refrigeration apparatus Z according to the present invention, the following specific effects can be obtained in addition to the effects described in (a) above.

  (C-1) During the cooling operation of the vapor compression refrigeration machine X, the solenoid valve 43 is closed so that the circuit configuration is the circuit configuration during the cooling operation of the refrigeration apparatus according to the first invention. The same effects can be obtained.

  (C-2) During the heating operation of the vapor compression refrigerator X, the solution pump 17 and the supercooling heat exchanger fan 20 of the absorption refrigerator Y are operated. In this state, when the electromagnetic valve 43 is opened, a part of the solution circulating between the supercooling heat exchanger 15 and the absorber 12 of the absorption refrigeration machine Y is part of the evaporator 13 side. In the evaporator 13, heat exchange is performed between the solution and the refrigerant on the vapor compression refrigerator X side, and heat exchange is indirectly performed in the evaporator 13 via the absorber 12. The heat exchange performance is further improved as compared with the case where it is performed.

  (C-3) As a synergistic effect of the above (c-1) and (c-2), the performance improvement effect is obtained in both the cooling operation and the heating operation of the vapor compression refrigeration machine X. A refrigeration apparatus rich in nature will be obtained.

  (C-4) On the other hand, the pipe line 66 on the inlet side of the absorber 12 of the absorption refrigeration machine Y is connected to the evaporator 13 via the pipe line 70 provided with the electromagnetic valve 43, and during the heating operation. Since the solution from the supercooling heat exchanger 15 is caused to flow directly to the evaporator 13 side through the pipe line 70, the connection structure of the pipe line 70 to the evaporator 13 side is used as the evaporation structure. The heat exchange in the evaporator 13 can be set uniquely so that the heat exchange can be performed efficiently, whereby the heat exchange performance in the evaporator 13 can be improved.

(D) Fourth Invention of the Present Application In the refrigeration apparatus according to the fourth invention of the present application, as illustrated in FIG. 4 or FIG. 5, a pipe line 66 on the inlet side of the absorber 12 of the absorption refrigeration machine Y. Is provided with a solenoid valve 44, the solenoid valve 44 is closed during the cooling operation of the vapor compression refrigerator X, the four-way switching valve 2 is switched during the heating operation, and the refrigerant of the vapor compression refrigerator X is cooled. The solenoid valve 44 is configured to open in the reverse direction.

  Therefore, according to the refrigeration apparatus Z according to the present invention, in addition to the effects described in the above (b) or (c), the following specific effects can be obtained.

  (D-1) When the vapor compression refrigerator X is in the cooling operation, the solenoid valve 44 is opened so that the circuit configuration is during the cooling operation of the refrigeration apparatus according to the second or third invention. The circuit configuration is similar to that in FIG.

  (D-2) During the heating operation of the vapor compression refrigerator X, the solution pump of the absorption refrigerator Y and the supercooling heat exchanger fan 20 are operated. In this state, when the electromagnetic valve 44 is closed, the entire amount of the solution from the supercooling heat exchanger 15 of the absorption refrigeration machine Y circulates to the evaporator 13 side. Since heat exchange is performed between the solution and the refrigerant on the vapor compression refrigerator X side, for example, a part of the solution from the supercooling heat exchanger 15 is circulated to the evaporator 13 side. Compared with the case where heat exchange is performed, the heat exchange performance in the evaporator 13 is further improved.

  (D-3) As a synergistic effect of the above (d-1) and (d-2), the performance improvement effect can be obtained in both the cooling operation and the heating operation of the vapor compression refrigeration machine X. A refrigeration apparatus rich in nature will be obtained.

(E) Fifth Invention of the Present Application According to the refrigeration apparatus of the fifth invention of the present application, as illustrated in FIG. 6, the solenoid valve 45 is provided in the pipe line 60 on the exhaust heat inlet side of the generator 11. During the cooling operation, the electromagnetic valve 45 is opened, and during the heating operation, the electromagnetic valve 45 is closed when the solution temperature of the generator 11 is equal to or higher than the set solution temperature, and when the temperature is lower than the set solution temperature, the electromagnetic valve is opened. 45 is configured to open.

  Therefore, according to the refrigeration apparatus Z according to the present invention, in addition to the effects described in (a), (b), (c) or (d), the following specific effects can be obtained.

  (E-1) Since the electromagnetic valve 45 is opened during the cooling operation of the vapor compression refrigerator X, the circuit configuration thereof is the refrigeration according to the first, second, third or fourth invention. The circuit configuration is the same as that during the cooling operation of the apparatus, and the same operation and effect can be obtained.

  (E-2) During the heating operation of the vapor compression refrigeration machine X, the four-way switching valve 2 is switched so that the refrigerant of the vapor compression refrigeration machine X flows in the opposite direction to the cooling operation, and the absorption refrigeration machine The Y solution pump 17 and the supercooling heat exchanger fan 20 are operated, and the refrigerant on the vapor compression refrigerator X side is exchanged by heat exchange with the solution circulating between the supercooling heat exchanger 15 and the absorber 12. On the other hand, the electromagnetic valve 45 is closed when the solution temperature of the generator 11 is equal to or higher than the set solution temperature, and is opened when the temperature is lower than the set solution temperature.

  Accordingly, when the solution temperature of the generator 11 is equal to or higher than the set solution temperature, the electromagnetic valve 45 is closed, and supply of exhaust heat from the engine or the like to the generator 11 is stopped, so that the generator 11 is stopped. The solution temperature inside is prevented from becoming too high. As a result, it is suppressed that the refrigerant temperature on the vapor compression refrigeration machine X side becomes too high due to the heat exchange in the refrigerant heat recovery heat exchanger 6, and proper heating is realized.

  On the other hand, when the solution temperature of the generator 11 is lower than the set solution temperature, the electromagnetic valve 45 is opened, and exhaust heat from the engine or the like is supplied to the generator 11, so that the solution in the generator 11 is supplied. An excessive decrease in temperature is prevented. As a result, the heat exchange in the refrigerant heat recovery heat exchanger 6 prevents the refrigerant temperature on the vapor compression refrigeration machine X side from becoming too low, thereby realizing proper heating.

  Thus, by opening and closing the solenoid valve 45 based on the solution temperature of the generator 11, the heating operation in the vapor compression refrigeration machine X is always properly performed, and the heating performance is improved. It is.

  As described above, the refrigeration apparatus Z is excellent in practicality since the performance improvement effect can be obtained in both the cooling operation and the heating operation of the vapor compression refrigerator X.

(F) Sixth invention of the present application In the refrigeration apparatus according to the sixth invention of the present application, in addition to the effects described in (d) or (e) above, the following specific effects are obtained. That is, in the refrigeration apparatus according to the present invention, as illustrated in FIG. 5 or FIG. 6, the sprayer 18 for spraying the solution and the sprayer 19 for spraying the refrigerant liquid in the evaporator 13 can be configured separately or shared. It has a one-piece construction.

  Therefore, in the case where the solution spraying device 18 and the coolant spraying device 19 are configured separately, the evaporator 13 of the coolant spraying device 19 that is originally provided for the coolant spraying is used. The structure or installation position of the solution spraying device 18 is set so that the solution is properly sprayed to the heat exchanger of the evaporator 13 while maintaining the proper spraying state of the refrigerant on the coil. Can do.

  Further, in the case where the solution spraying device 18 and the refrigerant solution spraying device 19 are integrated, the evaporator 13 can be made compact and low in cost by narrowing the space for the spraying device. I can plan.

(G) 7th invention of this application According to the refrigeration apparatus which concerns on 7th invention of this application, as described in said (a), (b), (c), (d), (e) or (f). In addition to the effects, the following unique effects can be obtained. That is, according to the refrigeration apparatus according to the present invention, the refrigerant liquid is transient in the evaporator 13 and flows through the heat transfer surface of the evaporator 13, and the unevaporated refrigerant liquid moves to the absorber 12 side. For example, as compared with the case where the evaporator 13 is a circulation type, the evaporator 13 and the absorption installed adjacent to the evaporator 13 are absorbed. Thus, the refrigerator 12 can be made compact, and thus the refrigeration apparatus configured by combining the vapor compression refrigerator X and the absorption refrigerator Y can be made compact.

(H) Eighth Invention of the Present Invention According to the refrigeration apparatus according to the eighth invention of the present application, the above (a), (b), (c), (d), (e), (f) or (g) In addition to the effects described in (1), the following specific effects can be obtained. That is, according to the refrigeration apparatus according to the present invention, as illustrated in FIG. 7, a plurality of the vapor compression chillers X are installed, and the heat recovery heat exchanger is installed in each of the vapor compression chillers X. 6 to recover the exhaust heat of the refrigerant of each of the vapor compression refrigerators X, and the exhaust heat recovered by each of the heat recovery heat exchangers 6 to the generator 11 of one absorption refrigerator Y Since the amount of recovered heat from the refrigerant side of the vapor compression refrigeration machine X to the generator 11 side of the absorption refrigeration machine Y increases, the exhaust heat from the engine or the like is small. Even in this case, the absorption refrigeration machine Y can be properly operated. As a result, the refrigerant of the vapor compression refrigeration machine X can be sufficiently subcooled by heat exchange in the evaporator 13 of the absorption refrigeration machine Y. As a result, the performance improvement effect of the entire refrigeration system can be improved. It is possible to obtain.

1 is an overall circuit diagram of a refrigeration apparatus according to a first embodiment of the present invention. It is a whole circuit diagram of the freezing apparatus which concerns on 2nd Embodiment of this invention. It is a whole circuit diagram of the freezing apparatus which concerns on 3rd Embodiment of this invention. It is a whole circuit diagram of the freezing apparatus which concerns on 4th Embodiment of this invention. It is a whole circuit diagram of the freezing apparatus which concerns on 5th Embodiment of this invention. It is a whole circuit diagram of the freezing apparatus which concerns on the 6th Embodiment of this invention. It is a whole circuit diagram of the freezing apparatus which concerns on the 7th Embodiment of this invention. It is a whole circuit diagram of the conventional freezing apparatus.

  Hereinafter, the present invention will be specifically described based on preferred embodiments.

I: First Embodiment FIG. 1 shows a circuit configuration of a refrigeration apparatus Z according to a first embodiment of the present invention. This refrigeration apparatus Z is configured by combining a vapor compression refrigeration machine X and an absorption refrigeration machine Y described below, and is used for indoor air conditioning.

I-1: Configuration of Vapor Compression Refrigerator X The vapor compression chiller X includes a compressor 1, a four-way switching valve 2, a use-side heat exchanger 3 (that is, an indoor unit), an expansion valve 4, and an accumulator. 5 are connected by a pipe 51 to a pipe 57, and a cooling operation and a heating operation are selectively realized by a switching operation of the four-way switching valve 2. That is, the four-way switching valve 2 is provided in the discharge-side pipe 51 of the compressor 1, and the pipe 51 reaches the use-side heat exchanger 3 by switching the four-way switching valve 2. The pipeline 52 (during heating operation) and the pipeline 56 (during cooling operation) leading to the accumulator 5 are selectively switched, and the use side heat exchanger 3 performs refrigerant evaporation during cooling operation, thereby heating operation. Sometimes the refrigerant condenses.

I-2: Configuration of Absorption Refrigerator Y The absorption chiller Y has, for example, a function of absorbing and releasing (regenerating) refrigerant into the absorbing liquid using lithum bromide (LiBr) as an absorbing liquid and water as a refrigerant. Refrigeration is performed by using a generator 11, an air-cooled condenser 14, an adjacently disposed absorber 12, an evaporator 13, an air-cooled supercooling heat exchanger 15 and a cooling fan. 20, a solution heat exchanger 16 and a solution pump 17, and these elements are connected by a pipeline 61 to a pipeline 67.

  The generator 11 is basically driven by using exhaust heat from an engine or the like as a drive heat source, and a heat exchanger 11a for exhaust heat is provided to exchange heat between the exhaust heat and the solution. Built-in. The generator 11 is connected to a discharge side pipe 58 of a heat recovery heat exchanger 6 to be described later in order to take in the exhaust heat of the vapor compression refrigerator X as a driving heat source.

  Further, the upper part of the generator 11 and the condenser 14 are connected by a pipe 61 so that the refrigerant vapor (water vapor) generated by the generator 11 flows into the condenser 14.

  Further, the generator 11 is provided with a pipe line 67 from the solution pump 17 and a pipe line 63 connected to the outlet side of the absorber 12 to be described later. The generator 11 is connected to the generator 11 by the solution pump 17. A dilute solution is introduced from the absorber 12 and a concentrated solution concentrated in the generator 11 is sent from the pipe 63 to the outlet side of the absorber 12.

  The solution heat exchanger 16 is provided between the pipe line 67 and the pipe line 63, and in the solution heat exchanger 16, between the concentrated solution flowing through the pipe line 63 and the dilute solution flowing through the pipe line 67. Then, heat exchange is performed, and heat is recovered from the concentrated solution side to the diluted solution side.

  The absorber 12 absorbs refrigerant vapor generated in the evaporator 13 described below to form a dilute solution. The absorber 12 is supercooled by a supercooling heat exchanger 15 from a pipe 66. After that, the solution is introduced.

  The evaporator 13 has a temporary evaporation function, and the liquid refrigerant condensed by the condenser 14 flows in from the pipe 62 and flows down while contacting the refrigerant with the built-in heat exchanger 13a. By doing so, this is heated and evaporated by the fluid flowing in the heat exchanger 13a (in this embodiment, the refrigerant on the vapor compression refrigerator X side as will be described later) to generate refrigerant vapor. The refrigerant vapor generated here moves toward the absorber 12 and is absorbed by the solution in the absorber 12. On the other hand, the non-evaporated refrigerant in the evaporator 13 flows from the bottom of the evaporator 13 into the liquid pool at the bottom of the absorber 12 and is absorbed by the solution on the absorber 12 side.

I-3: Specific Configuration Here, in the refrigeration apparatus Z, heat exchange between the refrigerant of the vapor compression refrigeration machine X and the solution refluxed to the generator 11 of the absorption refrigeration machine Y, In order to realize heat exchange between the refrigerant of the vapor compression refrigerator X and the solution on the evaporator 13 side of the absorption refrigerator Y, a specific configuration is provided.

  That is, the pipeline 54 of the vapor compression refrigerator X is connected to the heat exchanger 13a of the evaporator 13 of the absorption refrigerator Y, and the refrigerant on the vapor compression refrigerator X side and the absorption refrigerator are connected. Heat exchange is performed between the solutions on the Y side, and in particular during cooling operation of the vapor compression refrigerator X, the refrigerant on the vapor compression refrigerator X side is supercooled by heat exchange in the evaporator 13. I have to.

  Further, a heat recovery heat exchanger 6 is provided between the vapor compression refrigerator X and the absorption refrigerator Y, and the solution is recovered through a pipe 71 branched from the pipe 67 of the absorption refrigerator Y. After flowing into the heat exchanger 6, the refrigerant is refluxed to the generator 11 through the pipe 58, and one end of the heat exchanger 6 a built in the refrigerant heat recovery heat exchanger 6 is connected to the steam. The other end is connected to the pipe 56 of the compression refrigeration machine X, and the solution on the absorption refrigeration machine Y side and the vapor compression refrigeration machine X side in the refrigerant heat recovery heat exchanger 6 are connected. Heat is exchanged between the refrigerants.

  Further, an electromagnetic valve 41 is provided on a pipe 67 that reaches the generator 11 through the outlet side of the solution pump 17 and the solution heat exchanger 16. The opening / closing characteristics of the electromagnetic valve 41 are set as follows.

  That is, during the cooling operation of the vapor compression refrigerator X, the electromagnetic valve 41 is held open.

  On the other hand, during the heating operation of the vapor compression refrigeration machine X, the four-way switching valve 2 is switched to allow the refrigerant of the vapor compression refrigeration machine X to flow in the opposite direction to the cooling operation, and exchange heat with the solution pump 17. The fan 20 is operated, and the solenoid valve 41 is operated based on the refrigerant temperature of the vapor compression refrigerator X in the evaporator 13 or the solution temperature on the outlet side of the supercooler 15 of the absorption refrigerator Y. Open and close. That is, when the refrigerant temperature is used as a control reference, the solenoid valve 41 is closed when the refrigerant temperature is equal to or higher than the set refrigerant temperature, and is opened when the refrigerant temperature is lower than the set refrigerant temperature. When the solution temperature is used as a control reference, the solenoid valve 41 is closed when the solution temperature is equal to or higher than the set solution temperature, and is opened when the temperature is lower than the set solution temperature.

  The “set refrigerant temperature” or “set solution temperature” that serves as a control reference for the electromagnetic valve 41 is the value when heat exchange is appropriately performed in the absorber 12 and the evaporator 13 of the absorption refrigerator Y. It is set according to the minimum temperature. Further, as will be described later, even if any of these control standards is adopted, the same effect can be obtained as a result, and can be arbitrarily selected and set as necessary.

I-4: Explanation of Operation of Refrigeration Apparatus Z I-4-a: During Cooling Operation During the cooling operation of the vapor compression refrigeration machine X, the solenoid valve 41 is held open. Therefore, the high-temperature refrigerant (gas refrigerant) after being compressed in the compressor 1 of the vapor compression refrigeration machine X with the operation of the vapor compression refrigeration machine X and the absorption refrigeration machine Y is the refrigerant heat recovery. While flowing into the heat exchanger 6, a part of the solution (dilute solution) on the outlet side of the absorber 12 of the absorption refrigeration machine Y passes from the electromagnetic valve 41 through the pipe 67 and the pipe 71 to the above. The refrigerant flows into the refrigerant heat recovery heat exchanger 6, passes through the outside of the heat exchanger 6 a in the heat recovery heat exchanger 6, and then returns to the generator 11 side.

  In this case, in the refrigerant heat recovery heat exchanger 6, heat exchange is performed between the gas refrigerant on the vapor compression refrigeration machine X side flowing in the heat exchanger 6a and the solution flowing outside the heat exchanger 6a. The refrigerant heat on the vapor compression refrigerator X side is recovered to the solution side of the absorption refrigerator Y. Accordingly, the amount of heat recovered from the solution flowing into the generator 11 is added to the amount of heat generated by exhaust heat from the engine or the like supplied through the pipe 60, and the generator 11 is driven as a driving heat source.

  As a result, compared with the case where the generator 11 is driven only by exhaust heat from the engine or the like, the effective use of exhaust heat is promoted by the amount of use of refrigerant exhaust heat on the vapor compression refrigerator X side, for example, Even when the amount of exhaust heat from the engine or the like is reduced, the absorption refrigerator Y can be operated without any trouble.

  On the other hand, the gas refrigerant on the vapor compression refrigerator X side flowing into the refrigerant heat recovery heat exchanger 6 is cooled by heat exchange with the solution on the absorption refrigerator Y side in the heat recovery heat exchanger 6. Is condensed into a liquid refrigerant. Therefore, as a result of the refrigerant condensing action being performed in the refrigerant heat recovery heat exchanger 6, it is necessary to provide the heat source side heat exchanger, which is an essential component in the conventional configuration, on the vapor compression refrigerator X side. Accordingly, the structure of the vapor compression refrigerator X can be simplified and the cost can be reduced accordingly.

  The liquid refrigerant of the vapor compression refrigeration machine X condensed by the heat exchange in the refrigerant heat recovery heat exchanger 6 flows into the evaporator 13 side of the absorption refrigeration machine Y, and the evaporator 13 When flowing through the heat exchanger 13a, the refrigerant of the vapor compression refrigeration machine X is supercooled by heat exchange with the refrigerant (water) in the solution flowing outside the heat exchanger 13a. It flows into the use side heat exchanger 3. In this case, since the temperature of the refrigerant is lowered due to the supercooling in the evaporator 13, the specific enthalpy of the refrigerant at the inlet in the use side heat exchanger 3 is lowered, thereby the vapor compression refrigerator. The cooling performance of X is improved.

I-4-b: During heating operation During heating operation of the vapor compression refrigeration machine X, the four-way switching valve 2 is switched, and the refrigerant of the vapor compression refrigeration machine X flows in the opposite direction to the cooling operation, In the absorption refrigerator Y, the operation of the condenser 14 is stopped, but the supercooling heat exchanger fan 20 and the solution pump 17 are operated. Further, the exhaust heat supply to the generator 11 is continued.

  On the other hand, the solenoid valve 41 provided in the pipe line 67 is based on the refrigerant temperature of the vapor compression refrigerator X in the evaporator or the solution temperature on the outlet side of the supercooler of the absorption refrigerator Y. Open and close. That is, when the refrigerant temperature is used as a control reference, the solenoid valve 41 is closed when the refrigerant temperature is equal to or higher than the set refrigerant temperature, and is opened when the refrigerant temperature is lower than the set refrigerant temperature. When the solution temperature is used as a control reference, the valve is closed when the solution temperature is equal to or higher than the set solution temperature, and is opened when the temperature is lower than the set solution temperature.

  Here, the operation state of the electromagnetic valve 41 will be described by taking as an example the case of opening / closing control of the solenoid valve 41 based on the refrigerant temperature.

  As described above, the solenoid valve 41 is closed when the refrigerant temperature on the vapor compression refrigerator X side in the evaporator 13 is equal to or higher than the set refrigerant temperature, and is opened when the refrigerant temperature is lower than the set refrigerant temperature.

  When the refrigerant temperature on the vapor compression refrigerator X side is equal to or higher than the set refrigerant temperature, the absorption refrigerator Y side used for heat exchange with the refrigerant on the vapor compression refrigerator X side in the evaporator 13 The temperature of the solution circulating between the supercooling heat exchanger 15 and the absorber 12 is also high, and the solution on the vapor compression refrigeration machine X side that circulates the solution flowing through the absorber 12 and the evaporator 13 is used. The heat exchange performance with the above is maintained well, and the vapor compression refrigerator X is heated in an appropriate state.

  However, when the refrigerant temperature on the vapor compression refrigerator X side in the evaporator 13 decreases and becomes lower than the set refrigerant temperature, the evaporator 13 is used for heat exchange with the refrigerant on the vapor compression refrigerator X side. The temperature of the solution circulating between the supercooling heat exchanger 15 and the absorber 12 on the absorption refrigeration machine Y side is also lowered, and the solution flowing through the absorber 12 and the evaporator 13 are circulated. While heat exchange performance with the refrigerant on the vapor compression refrigerator X side is deteriorated, frost formation may occur in the supercooling heat exchanger 15.

  In this case, when the solenoid valve 41 is opened, a solution having a high temperature on the generator 11 side circulates to the supercooling heat exchanger 15 side. As a result, the absorption from the supercooling heat exchanger 15 is performed. The temperature of the solution flowing to the evaporator 12 side rises, and the heat exchange performance with the refrigerant on the vapor compression refrigerator X side in the evaporator 13 is restored. At the same time, frost formation in the supercooling heat exchanger 15 occurs. Occurrence of this will also be prevented. Accordingly, there is no unpleasant operation for removing frost as well as no reduction in heating capacity during frost formation.

  As described above, in this refrigeration apparatus Z, by combining the absorption refrigeration machine Y with the vapor compression refrigeration machine X, both during the cooling operation and the heating operation of the vapor compression refrigeration machine X, The performance improvement effect is obtained, and a refrigeration apparatus rich in practicality is obtained.

  Further, in this refrigeration apparatus Z, during the cooling operation of the vapor compression refrigeration machine X, the refrigerant of the vapor compression refrigeration machine X is condensed by heat recovery in the refrigerant heat recovery heat exchanger 6, and the heating is performed. During operation, the refrigerant of the vapor compression refrigeration machine X is evaporated by heat recovery in the refrigerant heat recovery heat exchanger 6, so that it is provided as an essential component in the conventional vapor compression refrigeration machine. The heat radiation side heat exchanger is not required, and the structure of the vapor compression refrigerator X can be simplified.

II: Second Embodiment FIG. 2 shows a circuit configuration of a refrigeration apparatus Z according to a second embodiment of the present invention. This refrigeration apparatus Z is based on the circuit configuration of the refrigeration apparatus Z according to the first embodiment. In this basic circuit, the pipe line 66 on the inlet side of the absorber 12 of the absorption refrigeration machine Y and the evaporation. A pipe 62 on the refrigerant inlet side of the vessel 13 is connected by a pipe 73 provided with an electromagnetic valve 43. The electromagnetic valve 43 is controlled to be closed during the cooling operation of the vapor compression refrigerator X and opened during the heating operation. Since the configuration other than this is the same as that of the refrigeration apparatus Z of the first embodiment, the description is given by attaching the reference numerals to the respective constituent members in FIG. 2 corresponding to the respective constituent members in FIG. Omitted.

Explanation of the operation of the refrigeration apparatus Z During the cooling operation of the vapor compression refrigeration machine X During the cooling operation of the vapor compression refrigeration machine X, the solenoid valve 43 is closed so that the circuit configuration is the same as that of the first embodiment. It becomes the same as that of the circuit structure at the time of air_conditionaing | cooling operation of the refrigerating apparatus which concerns on a form, and the same effect is obtained. Therefore, the corresponding description of the first embodiment is used, and the description here is omitted.

During the heating operation of the vapor compression refrigerator X During the heating operation of the vapor compression refrigerator X, the operation of the condenser 14 is stopped in the absorption refrigerator Y, but the fan for the supercooling heat exchanger 20 and the solution pump 17 are operated. Further, the exhaust heat supply to the generator 11 is continued.

  The solenoid valve 41 provided in the pipeline 67 is similar to the solenoid valve 41 in the refrigeration apparatus Z of the first embodiment, and the refrigerant temperature of the vapor compression refrigerator X in the evaporator 13 or the absorption. It is opened and closed based on the solution temperature on the outlet side of the supercooler 15 of the type refrigerator Y. That is, when the refrigerant temperature is used as a control reference, the solenoid valve 41 is closed when the refrigerant temperature is equal to or higher than the set refrigerant temperature, and is opened when the refrigerant temperature is lower than the set refrigerant temperature. Further, when the solution temperature is used as a control reference, the valve is closed when the solution temperature is equal to or higher than the set solution temperature, and is opened when the solution temperature is lower than the set solution temperature. A case where opening / closing control is performed based on the above will be described as an example. Further, the electromagnetic valve 43 provided in the pipe 69 which is a characteristic configuration in this embodiment is opened.

  During heating operation of the vapor compression refrigerator X, the electromagnetic valve 43 is held open, so that the solution from the supercooling heat exchanger 15 flows into the absorber 12 and the evaporator 13 separately. To do.

  When the refrigerant temperature on the vapor compression refrigerator X side is equal to or higher than the set refrigerant temperature, the absorption refrigerator Y side used for heat exchange with the refrigerant on the vapor compression refrigerator X side in the evaporator 13 The temperature of the solution circulating between the supercooling heat exchanger 15 and the absorber 12 and the evaporator 13 is also high, and the solution flowing through the absorber 12 and the evaporator 13 and the evaporator 13 are circulated. The heat exchange performance with the refrigerant on the vapor compression refrigerator X side is maintained satisfactorily, and the vapor compression refrigerator X is heated in an appropriate state.

  However, when the refrigerant temperature on the vapor compression refrigerator X side decreases and becomes lower than the set refrigerant temperature, the absorption used for heat exchange with the refrigerant on the vapor compression refrigerator X side in the evaporator 13 is performed. The temperature of the solution circulating between the supercooling heat exchanger 15 and the absorber 12 and the evaporator 13 on the side of the refrigerating machine Y side also decreases, and the vapor compression refrigerator X side that circulates the evaporator 13 The heat exchange performance with other refrigerants may be reduced, and frost may be generated in the supercooling heat exchanger 15.

  In this case, when the solenoid valve 41 is opened, a solution having a high temperature on the generator 11 side circulates to the supercooling heat exchanger 15 side. As a result, the absorption from the supercooling heat exchanger 15 is performed. The temperature of the solution flowing to the evaporator 12 and the evaporator 13 side rises, and the heat exchange performance with the refrigerant on the vapor compression refrigerator X side in the evaporator 13 is restored, and at the same time, the supercooling heat exchanger The occurrence of frost formation at 15 is also prevented in advance. Accordingly, there is no unpleasant operation for removing frost as well as no reduction in heating capacity during frost formation.

  In this case, since a part of the solution from the supercooling heat exchanger 15 flows into the evaporator 13, for example, compared with the case where the solution flows into only the absorber 12 side, the evaporation is performed. The heat exchange performance in the vessel 13 is further improved.

III: Third Embodiment FIG. 3 shows a circuit configuration of a refrigeration apparatus Z according to a third embodiment of the present invention. The refrigeration apparatus Z is positioned as a modified example of the refrigeration apparatus Z according to the second embodiment. In the second embodiment, the absorption chiller Y on the inlet side of the absorber 12 of the absorption chiller Y is used. A pipe 66 and a pipe 62 on the refrigerant inlet side of the evaporator 13 are connected by a pipe 73 provided with an electromagnetic valve 43, which is closed during the cooling operation of the vapor compression refrigerator X and opened during the heating operation. In contrast to this, in this embodiment, the evaporator 66 is connected to the inlet 66 of the absorber 12 of the absorption refrigerator Y via the pipe 71 provided with the electromagnetic valve 43. 13, the electromagnetic valve 43 is configured to close the electromagnetic valve 43 during the cooling operation of the vapor compression refrigerator X and open the electromagnetic valve 43 during the heating operation.

  Therefore, in the refrigeration apparatus Z of this embodiment, the same action and effect can be obtained both during the cooling operation and during the heating operation of the vapor compression refrigeration machine X. Here, the corresponding case of the second embodiment is applicable. The explanation is used and the explanation is omitted.

  Moreover, the effects peculiar to the refrigeration apparatus Z of this embodiment are as follows. That is, in the heating operation of the vapor compression refrigeration machine X in which the electromagnetic valve 43 is opened, the pipe 66 on the inlet side of the absorber 12 of the absorption refrigeration machine Y is provided with the electromagnetic valve 43. Since the solution from the supercooling heat exchanger 15 is directly flowed into the evaporator 13 side, the evaporator 13 in the pipe 74 is connected to the evaporator 13 through the pipe 74. The connection structure to the side can be uniquely set so that heat exchange in the evaporator 13 can be performed efficiently, and thus the heat exchange performance in the evaporator 13 can be further improved. .

  Note that, in the refrigeration apparatus Z of this embodiment, the solution spraying device 18 and the refrigerant liquid spraying device 19 are configured separately, so that the refrigerant spraying device originally provided for the coolant spraying is provided. While maintaining the proper spraying state of the refrigerant to the heat exchanger of the evaporator 13 in the sprayer 19, the solution spraying is performed so that the solution is sprayed properly to the heat exchanger of the evaporator 13. The structure or installation position of the spreader 18 can be set.

IV: Fourth Embodiment FIG. 4 shows a circuit configuration of a refrigeration apparatus Z according to a fourth embodiment of the present invention. This refrigeration apparatus Z has the refrigeration apparatus Z according to the second embodiment as a basic configuration, and in addition to this basic configuration, an electromagnetic valve is connected to a pipe line 66 on the inlet side of the absorber 12 of the absorption refrigeration machine Y. 44, and the solenoid valve 44 is closed during the cooling operation of the vapor compression refrigerator X, and the solenoid valve 44 is opened during the heating operation.

  Accordingly, since the operational effect during the cooling operation of the vapor compression refrigerator X in which the electromagnetic valve 44 is opened is the same as in the case of the second embodiment, the corresponding description is used here. Description is omitted.

  On the other hand, during the heating operation of the vapor compression refrigeration machine X in which the electromagnetic valve 44 is closed, the operation is basically the same as in the case of the second embodiment. By providing and closing the valve during heating operation, the entire amount of the solution from the supercooling heat exchanger 15 of the absorption refrigeration machine Y circulates to the evaporator 13 side. Heat exchange is performed between the solution and the refrigerant on the vapor compression refrigerator X side. As a result, for example, compared with a case where a part of the solution from the supercooling heat exchanger 15 is circulated to the evaporator 13 side to perform heat exchange (in the case of the second embodiment), the evaporation is performed. The heat exchange performance in the vessel 13 is further improved.

  For the operational effects other than the above, the corresponding description of the second embodiment is used.

V: Fifth Embodiment FIG. 5 shows a circuit configuration of a refrigeration apparatus Z according to a fifth embodiment of the present invention. This refrigeration apparatus Z has the refrigeration apparatus Z according to the third embodiment as a basic configuration, and in addition to this basic configuration, an electromagnetic valve is connected to a pipe line 66 on the inlet side of the absorber 12 of the absorption refrigeration machine Y. 44, and the solenoid valve 44 is closed during the cooling operation of the vapor compression refrigerator X, and the solenoid valve 44 is opened during the heating operation.

  Therefore, since the operational effect during the cooling operation of the vapor compression refrigerator X in which the electromagnetic valve 44 is opened is the same as that in the case of the third embodiment, the corresponding explanation is used here. Description is omitted.

  On the other hand, during the heating operation of the vapor compression refrigeration machine X in which the electromagnetic valve 44 is closed, the operation is basically the same as in the case of the third embodiment. By providing and closing the valve during heating operation, the total amount of the solution from the supercooling heat exchanger 15 of the absorption refrigeration machine Y flows directly into the evaporator 13, and the evaporator 13 Then, heat exchange is performed between the solution and the refrigerant on the vapor compression refrigerator X side.

  As a result, for example, as compared with a case where a part of the solution from the supercooling heat exchanger 15 is circulated to the evaporator 13 side to perform heat exchange (in the case of the third embodiment), the evaporation is performed. The heat exchange performance in the vessel 13 is further improved.

  For the effects other than the above in the heating operation, the corresponding description of the third embodiment is used.

VI: Sixth Embodiment FIG. 6 shows a circuit configuration of a refrigeration apparatus Z according to a sixth embodiment of the present invention. This refrigeration apparatus Z has the refrigeration apparatus Z according to the fifth embodiment as a basic configuration, and in addition to this basic configuration, an electromagnetic valve 45 is provided in the pipe line 60 on the exhaust heat inlet side of the generator 11 for cooling. While the solenoid valve 45 is opened during operation, the solenoid valve 45 is closed when the solution temperature of the generator 11 is equal to or higher than the set solution temperature during heating operation, and when the temperature is less than the set solution temperature, the solenoid valve 45 is opened. The valve is configured to be opened.

  Therefore, since the operational effect during the cooling operation of the vapor compression refrigeration machine X with the electromagnetic valve 45 opened is the same as in the case of the fifth embodiment, the corresponding explanation is used here. Description is omitted.

  On the other hand, during the cooling operation of the vapor compression refrigerator X, the electromagnetic valve 45 is opened and closed according to the solution temperature of the generator 11. That is, when the solution temperature of the generator 11 is equal to or higher than the set solution temperature, the solenoid valve 45 is closed, and when the temperature is lower than the set solution temperature, the solenoid valve 45 is opened.

  Accordingly, when the solution temperature of the generator 11 is equal to or higher than the set solution temperature, the electromagnetic valve 45 is closed, and supply of exhaust heat from the engine or the like to the generator 11 is stopped, so that the generator 11 is stopped. The solution temperature inside is prevented from becoming too high. As a result, it is suppressed that the refrigerant temperature on the vapor compression refrigeration machine X side becomes too high due to the heat exchange in the refrigerant heat recovery heat exchanger 6, and proper heating is realized.

  On the other hand, when the solution temperature of the generator 11 is lower than the set solution temperature, the electromagnetic valve 45 is opened, and exhaust heat from the engine or the like is supplied to the generator 11, thereby the generator 11. The temperature of the solution is prevented from excessively decreasing. As a result, the heat exchange in the refrigerant heat recovery heat exchanger 6 prevents the refrigerant temperature on the vapor compression refrigeration machine X side from becoming too low, and an appropriate heating operation is realized.

  Thus, by opening and closing the solenoid valve 45 based on the solution temperature of the generator 11, the heating operation in the vapor compression refrigeration machine X is always properly performed, and the heating performance is improved. It is.

  For the effects other than the above in the heating operation, the corresponding description of the third embodiment is used.

  In the refrigeration apparatus Z of this embodiment, the solution spraying device 18 provided in the evaporator 13 of the absorption refrigeration machine Y is integrally configured so that it can be shared as a sprayer for spraying refrigerant liquid. ing. With this configuration, the evaporator 13 can be reduced in size and cost by reducing the arrangement space of the spreader.

VII: Seventh Embodiment FIG. 7 shows a circuit configuration of a refrigeration apparatus Z according to a seventh embodiment of the present invention. This refrigeration apparatus Z is positioned as a modification of the refrigeration apparatus Z according to the fifth embodiment. That is, in the refrigeration apparatus Z according to the fifth embodiment, the refrigeration apparatus Z is constituted by one vapor compression refrigeration machine X and one absorption refrigeration machine Y. In the refrigeration apparatus Z according to the embodiment, this is constituted by two vapor compression refrigeration machines X and one absorption refrigeration machine Y, and the increase in the number of installed vapor compression refrigeration machines X is supported. Each of the vapor compression refrigeration machines X is provided with the refrigerant heat recovery heat exchanger 6, and the exhaust heat of the refrigerant of each of the vapor compression refrigeration machines X is absorbed in the corresponding heat recovery heat exchanger 6. It collect | recovers to the solution side of the refrigerator Y, and is comprised so that this recovered waste heat may be supplied to the said generator 11 of the said absorption-type refrigerator Y.

  According to such a configuration, since the amount of recovered heat from the refrigerant side of the vapor compression refrigeration machine X to the generator 11 side of the absorption refrigeration machine Y increases, for example, even when there is little exhaust heat from the engine or the like, The absorption refrigeration machine Y can be appropriately operated by effectively using the recovered refrigerant exhaust heat, and as a result, each of the vapor compression refrigeration machines by heat exchange in the evaporator 13 of the absorption refrigeration machine Y. The refrigerant of X can be sufficiently subcooled, and as a result, the performance improvement effect of the entire refrigeration apparatus Z can be obtained.

  In addition, there is no restriction | limiting in the juxtaposition number of the said vapor compression type refrigerators X, What is necessary is just to set the juxtaposition number as needed.

DESCRIPTION OF SYMBOLS 1 ... Compressor 2 ... Four-way switching valve 3 ... Use side heat exchanger 4 ... Expansion valve 5 ... Accumulator 6 ... Heat recovery heat exchanger 7 ... Heat source side Heat exchanger 11 ... Generator 12 ... Absorber 13 ... Evaporator 14 ... Condenser 15 ... Supercooling heat exchanger 16 ... Solution heat exchanger 17 ... Solution pump 18, 19 ... Sprinkler 20 ... Fan 41 ... Solenoid valve 43-45 ... Solenoid valve 51-57 ... Pipe 61-67 ... Pipe 71-74 ... Pipe X ... Steam Compression refrigerator Y ・ ・ Absorption refrigerator Z ・ ・ Refrigerator

Claims (8)

A refrigerating apparatus comprising a vapor compression refrigerator (X) and an absorption refrigerator (Y) driven by exhaust heat from an engine or the like,
While the solution flowing into the absorber (12) of the absorption refrigerator (Y) is supercooled by the air-cooled supercooling heat exchanger (15) and flows into the absorber (12),
The refrigerant of the vapor compression refrigeration machine (X) and a pipe line (from the outlet of the absorber (12) of the absorption refrigeration machine (Y) to the solution heat exchanger (16) through the solution pump (17) ( 67) is provided with a heat recovery heat exchanger (6) for exchanging heat with the solution branched from the solution, and the vapor compression refrigerator (X) after heat exchange in the heat recovery heat exchanger (6) is provided. The refrigerant flows into the evaporator (13) of the absorption refrigerator (Y), and the solution of the absorption refrigerator (Y) flows into the generator (11), and the outlet of the solution pump (17). A solenoid valve (41) is provided in the pipe line (67) from the side to the heat recovery heat exchanger (6), and the solenoid valve (41) is opened during cooling operation of the vapor compression refrigerator (X). On the other hand, during the heating operation of the vapor compression refrigerator (X), the four-way switching valve (2) is switched to The refrigerant of the compression refrigerator is caused to flow in the opposite direction to the cooling operation, the solution pump (17) and the supercooling heat exchanger fan (20) are operated, and the vapor compression refrigerator (13) in the evaporator (13) is operated. X) is closed when the refrigerant temperature is equal to or higher than the set refrigerant temperature, and is opened when the refrigerant temperature is lower than the set refrigerant temperature, or on the outlet side of the supercooling heat exchanger (15) of the absorption refrigeration machine (Y). A refrigeration apparatus configured to close when a solution temperature is equal to or higher than a set refrigerant temperature and to open when the temperature is lower than the set solution temperature. In claim 1,
The absorption refrigeration machine (Y) has an electromagnetic valve (43) including a pipe (66) on the inlet side of the absorber (12) and a pipe (62) on the refrigerant inlet side of the evaporator (13). Connected by a line (73)
A refrigeration apparatus configured to close the solenoid valve (43) during cooling operation of the vapor compression refrigerator (X) and open the solenoid valve (43) during heating operation. In claim 1,
The pipe (66) on the inlet side of the absorber (12) of the absorption refrigerator (Y) is connected to the evaporator (13) through a pipe (74) provided with a solenoid valve (43). The solenoid valve (43) is closed during the cooling operation of the vapor compression refrigerator (X), and the solenoid valve (43) is opened during the heating operation. . In claim 2 or 3,
An electromagnetic valve (44) is provided in a pipe line (66) on the inlet side of the absorber (12) of the absorption refrigeration machine (Y), and the electromagnetic valve (44) is used during the cooling operation of the vapor compression refrigeration machine (X). 44), and the solenoid valve (44) is opened during heating operation. In claim 1, 2, 3 or 4,
A solenoid valve (45) is provided in the pipe (60) on the exhaust heat inlet side of the generator (11), and the solenoid valve (45) is opened during cooling operation, while the generator (11) is used during heating operation. A refrigeration apparatus configured to close the electromagnetic valve (45) when the solution temperature of the liquid is higher than a set solution temperature and to open the solenoid valve (45) when the temperature is lower than the set solution temperature. In claim 3 or 4,
The refrigeration apparatus characterized in that the sprayer for spraying the solution and the sprayer for spraying the refrigerant liquid in the evaporator (13) have a separate structure or an integrated structure that can be shared. In claim 1, 2, 3, 4, 5 or 6,
In the evaporator (13), the refrigerant liquid is transient and flows on the heat transfer surface of the evaporator (13), and the non-evaporated refrigerant liquid moves to the absorber (12) side and moves to the absorber (12). The refrigeration apparatus is configured to be absorbed by the solution on the side. In claim 1, 2, 3, 4, 5, 6 or 7,
A plurality of the vapor compression refrigeration units (X) are installed, and the heat recovery heat exchanger (6) is provided in each of the vapor compression refrigeration units (X), and the respective vapor compression refrigeration units (X) The exhaust heat of each refrigerant is recovered, and the exhaust heat recovered by each heat recovery heat exchanger (6) is supplied to the generator (11) of one absorption refrigerator (Y). A refrigeration apparatus characterized by that.

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