JP2010249356A - Refrigerating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerating device that eliminates the need for a heat-radiating heat exchanger of a vapor compression refrigerator as a refrigerating device wherein a vapor compression refrigerator and an absorption refrigerator are combined and the compressed refrigerant of the vapor compression refrigerator is supercooled by a refrigerant evaporator of the absorption refrigerator. <P>SOLUTION: A heat exchanger 10 for collecting refrigerant heat is provided outside a generator 11 of the absorption refrigerator Y, the heat exchanger 10 collecting the heat of the compressed refrigerant in advance during the cooling operation of the vapor pressure refrigerator X, by means of a dilute absorbed solution supplied from an absorber 13 of the absorption refrigerator Y to the generator 11, and causing the dilute absorbed solution to flow into the generator 11 of the absorption refrigerator Y. At the generator 11 of the absorption refrigerator Y, vapor-liquid separation of the solution superheated by the heat of the compressed refrigerant of the vapor compression refrigerator X collected by the heat exchanger 10 is effected, and the solution is heated by an external heat source 34 to generate refrigerant vapor. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The invention of this application includes a vapor compression refrigerator, an absorption refrigerator driven by an exhaust heat of the vapor compression refrigerator and another external heat source, and a refrigeration apparatus operable by combining them as desired. It is about.

  In general, a vapor compression refrigerator has a refrigeration circuit in which a compressor, a condenser, an expansion valve, and an evaporator are connected by refrigerant piping so that a heat pump can be operated, and the direction of the refrigerant flowing in the refrigeration circuit is reversed. By doing so, cooling and heating can be performed (for example, refer to Patent Document 1).

  As one method for improving the refrigeration performance in such a vapor compression refrigeration machine, for example, combining an absorption chiller, which is a heat-driven chiller, has been conventionally known and absorbed by exhaust heat from a gas engine or the like. Conventionally, various methods have been proposed for driving a refrigerator and taking in the cold heat obtained there into a vapor compression refrigerator to increase the refrigeration performance of the vapor compression refrigerator (for example, Patent Document 2). See).

  On the other hand, when the absorption chiller is driven by using the exhaust heat on the vapor compression refrigerator side, the exhaust heat amount of the vapor compression refrigerator itself is small and the exhaust heat temperature is also low. Since it is low, it is generally difficult to drive an absorption refrigerator as it is, and even if it can be driven, the effect of improving the obtained refrigeration performance is small, and there are problems in terms of cost, etc. For reasons that have not been considered so far.

However, because of the measures against the recent increase in energy costs and the need to improve the performance of the vapor compression refrigerator when developing an air conditioner using a natural refrigerant such as a CO ₂ refrigerant, the vapor compression type There is a demand for a method of using the exhaust heat of the refrigerator itself not only for hot water supply or heating, but more effectively by converting it to cold heat itself.

  As proposed based on such circumstances, for example, an absorption refrigeration cycle including a generator, a condenser, an evaporator, an absorber, a compressor, a heat source side heat exchanger, a pressure reducing device, a use side heat exchanger A refrigerant that circulates through each device of the absorption refrigeration cycle, and recovers the exhaust heat of the heat source side heat exchanger of the vapor compression refrigeration cycle, and an evaporator of the absorption refrigeration cycle Cooling the outlet side refrigerant of the heat source side heat exchanger of the vapor compression refrigeration cycle, thereby reducing the amount of heat released as a whole system, reducing power consumption, and improving the coefficient of performance. (For example, refer to Patent Document 3).

  According to such a configuration, the exhaust heat of the vapor compression refrigeration machine itself can be used more effectively by converting it to the necessary cold heat itself rather than mere hot water supply or heating.

JP 2002-228229 A JP 2004-28374 A JP 2006-17350 A

  By the way, in order to improve the refrigeration capacity of a refrigeration system that combines a vapor compression refrigeration machine and an absorption refrigeration machine as described above, how to effectively eliminate the exhaust heat between the vapor compression refrigeration machine and the absorption chiller. The issue is whether to use it.

  At the same time, it is also important to simplify the configuration of the devices and reduce costs, and it is desirable to eliminate the need for a heat-dissipating heat exchanger that dissipates the heat of the vapor compression refrigerator-side compressed refrigerant. .

  In addition, waste heat utilizing absorption refrigerators driven by hot water exhaust heat such as small generators and GHP are often used in single-effect refrigeration cycles from the viewpoint of cost. The problem is how to reduce the cost of the steam generator.

  In particular, the use of waste water is difficult to establish unless it is a cheaper device, and there is a strong demand for greatly reducing the cost of the generator.

  However, in the case of the refrigeration apparatus of Patent Document 3, the compressed refrigerant from the vapor compression refrigerator is added to the first heat source side heat exchanger for generating refrigerant vapor in the absorption refrigeration cycle side generator, and external air is taken in. The generator is supplied to the second heat source side heat exchanger constituting the evaporator via the third heat source side heat exchanger for radiating the compressed refrigerant with the cooling fan, and is supercooled. Since there is a third heat source side heat exchanger for radiating compressed refrigerant, there is a disadvantage that the entire system is complicated and expensive, and it is not possible to meet the above requirements. Not.

  The present invention was made to solve such a problem, and during cooling operation, heat of the refrigerant after compression of the compression refrigerator is preliminarily recovered and heat is recovered with an absorption dilute solution of the absorption refrigerator, Then, only the absorption dilute solution whose temperature has been raised is allowed to flow into the absorption chiller generator to separate the refrigerant vapor, thereby simplifying the configuration of the absorption chiller generator and simultaneously absorbing it. Providing a refrigeration system that improves the supercooling performance by cooling the refrigerant of the vapor compression refrigerator supplied to the evaporator of the refrigerator, and eliminates the heat exchanger for heat dissipation of the vapor compression refrigerator It is intended.

  In order to achieve the above object, the present invention comprises the following effective problem solving means.

(1) The problem-solving means of the invention of claim 1 The problem-solving means of the present invention is a combination of a vapor compression refrigerator and an absorption refrigerator having an external heat source, and refrigerant cooling of the absorption refrigerator during cooling operation. In the refrigeration apparatus configured to supercool the compressed refrigerant of the vapor compression refrigeration machine, the heat of the compressed refrigerant during the cooling operation of the vapor compression refrigeration machine is provided outside the generator of the absorption refrigeration machine. The heat for recovering refrigerant heat that is collected in advance by the absorption dilute solution supplied from the absorber of the absorption chiller to the generator and then flows into the generator of the absorption chiller In the generator of the absorption refrigeration machine, a gas-liquid separation of a solution superheated by the heat of the compressed refrigerant of the vapor compression refrigeration machine recovered by the refrigerant heat recovery heat exchanger is performed in the generator of the absorption refrigeration machine. The solution is heated and cooled by the external heat source. It is characterized in that so as to generate steam.

  As already mentioned, in order to improve the refrigeration capacity of a refrigeration system that combines a vapor compression refrigerator and an absorption chiller, how effectively the heat exhausted between the vapor compression chiller and the absorption chiller is effectively utilized. The issue is whether to use it.

  At the same time, it is also important to simplify the configuration of the devices and reduce costs, and it is desirable to eliminate the need for a heat-dissipating heat exchanger that dissipates the heat of the vapor compression refrigerator-side compressed refrigerant. .

  In addition, waste heat utilizing absorption refrigerators driven by hot water exhaust heat such as small generators and GHP are often used in single-effect refrigeration cycles from the viewpoint of cost. The problem is how to reduce the cost of the steam generator.

  In particular, the use of waste water is difficult to establish unless it is a cheaper device, and there is a strong demand for greatly reducing the cost of the generator.

  Further, the amount of heat of such an external exhaust heat source fluctuates, and a certain amount or more of the exhaust heat amount is not always supplied stably. Therefore, it is required to ensure a necessary refrigerant vapor generation action even when a necessary and sufficient amount of external heat source cannot be obtained.

  On the other hand, in the case of the above configuration, a low-temperature absorbing dilute solution supplied from the absorber to the generator in the refrigerant heat recovery heat exchanger portion provided outside the generator of the absorption chiller However, the heat of the high-temperature compressed refrigerant on the vapor compressor side is recovered and heated to a sufficiently high temperature state, and then supplied into the generator. In the generator, refrigerant vapor is generated by the flash action of the absorbed diluted solution. Gas-liquid separation into vapor and absorption concentrated solution.

  On the other hand, after the high-temperature compressed refrigerant discharged from the compressor is efficiently cooled, it is further supplied to the evaporator of the absorption refrigeration machine to be supercooled.

  Therefore, according to this configuration, the heat of the vapor compression refrigeration machine side compressed refrigerant can be effectively utilized for driving the absorption refrigeration machine, and the refrigeration capacity of the absorption refrigeration machine can be increased accordingly. it can.

  In addition, even when the amount of exhaust heat from the external heat source becomes a certain value or less, a stable absorption refrigeration operation can be ensured.

  On the other hand, the compressed refrigerant on the one side of the vapor compression refrigeration machine is cooled as a result of the heat being taken away by the dilute solution side on the absorption refrigeration machine side as described above, and then the absorption refrigeration machine side is further reduced. Is supplied to the evaporator and supercooled. Therefore, compared with the case where there is no heat exchanger for recovering refrigerant heat, the compressed refrigerant is more effectively subcooled, and the inlet specific enthalpy of the refrigerant liquid supplied to the use side heat exchanger can be effectively reduced. . As a result, the cooling performance of the use side heat exchanger is improved.

  As a result of the above, according to the means for solving the same problem, a heat exchanger for radiating compressed refrigerant on the vapor compression refrigerator side is not required, and the absorption refrigerator generator also heats the solution with an external heat source. Thus, a simple and low-cost configuration in which a gas-liquid separation function is simply added to a heat exchanger that generates refrigerant vapor is sufficient.

  Furthermore, when supercooling of the refrigerant compressed in the vapor compression refrigerator is performed in the evaporator of the absorption refrigerator, the absorption refrigerator is compared with a structure in which cold water is separately circulated in the evaporator. In addition, since the structure becomes simple and the evaporation temperature of the refrigerant of the absorption refrigerator in the evaporator can be increased, for example, when the required evaporation capacity of the refrigerant is constant, the evaporation temperature with respect to the refrigerant increases. Therefore, it is possible to reduce the cost of the evaporator or reduce the size by reducing the capacity of the evaporator.

(2) The problem solving means of the invention of claim 2 The problem solving means of the invention is an absorption liquid air-cooled cooler that supercools the absorption liquid flowing into the absorber in the configuration of the problem solving means of the invention of claim 1 above. And a solution heat exchanger for exchanging heat between the absorption diluted solution supplied from the absorber to the generator and the absorption concentrated solution from the generator, and the absorption diluted solution at the outlet side of the absorber is cooled by air cooling of the absorption solution. In the above absorber, the refrigerant vapor is sensible by the sensible heat of the absorbed liquid after being supercooled via the absorption liquid air-cooled cooler. It is characterized in that it is made to absorb.

  Thus, in the heat exchanger for recovering refrigerant heat and the solution heat exchanger for recovering the heat of the absorbed concentrated solution supplied from the generator to the absorber to the absorption dilute solution side supplied from the absorber to the generator In addition, an absorption liquid air cooling cooler that supercools the absorption liquid flowing into the absorber is provided, and the absorption liquid is supercooled by the absorption liquid air cooling cooler and then supplied to the absorber. The absorption refrigeration system adopting the solution separation cooling system that absorbs the refrigerant vapor from the evaporator with the sensible heat of the absorbed liquid removes the absorbed heat with the sensible heat of the solution itself, so supply the dilute solution to the generator Even if the amount is increased, the performance hardly deteriorates as compared with the conventional direct cooling type air-cooled or water-cooled absorber.

  Therefore, it is possible to increase the supply amount of the dilute solution to the generator, increase the generation amount of refrigerant vapor, or reduce the size of the heat exchanger for recovering refrigerant heat.

  On the other hand, the absorber is configured to absorb the refrigerant vapor from the evaporator with the sensible heat of the absorbed liquid that has flowed in, while the absorption diluted solution on the outlet side of the absorber is used as a solution heat exchanger, heat for refrigerant heat recovery If each of the exchangers is divided and introduced, heat recovery to the absorption refrigerator side dilute solution is performed effectively and appropriately in each of them (absorption of concentrated concentrated solution and vapor compression refrigerator side compressed refrigerant heat). ), And efficient heat recovery is realized as a whole.

(3) The problem-solving means of the invention of claim 3 The problem-solving means of the invention is the structure of the problem-solving means of the invention of claim 2 described above, wherein the absorption concentrated solution and heat from the generator are passed through the solution heat exchanger. The exchanged diluted diluted solution is allowed to flow into the refrigerant heat recovery heat exchanger.

  According to such a configuration, the absorption dilute solution whose temperature has been increased through heat exchange with the absorption concentrated solution from the generator in the solution heat exchanger is further heated by the heat of the compressed refrigerant in the refrigerant heat recovery heat exchanger. Thus, the refrigerant is supplied to the generator, and the generation effect of the refrigerant vapor in the generator is further improved.

(4) The problem-solving means of the invention of claim 4 The problem-solving means of the invention is the structure of the problem-solving means of the invention of claim 2 described above, wherein the absorption concentrated solution and heat from the generator are passed through the solution heat exchanger. The exchanged diluted diluted solution is caused to flow into the generator and the refrigerant heat recovery heat exchanger.

  According to such a configuration, a part of the absorption dilute solution whose temperature has been increased by heat exchange with the absorption concentrated solution from the generator in the solution heat exchanger is the generator, and the other is the heat exchanger for refrigerant heat recovery Thus, the temperature of the compressed refrigerant is increased by heating, and the refrigerant is supplied to the generator, so that the generator can generate refrigerant vapor more effectively.

(5) The problem solving means of the invention of claim 5 The problem solving means of the present invention is the structure of the problem solving means of the invention of claim 2, wherein the refrigerant heat recovery heat exchanger is arranged from the upstream side to the downstream side of the compressed refrigerant. Of the dilute solution from the absorber to the generator through the solution heat exchanger, and the absorbed dilute solution before entering the solution heat exchanger is divided into the refrigerant heat in the downstream side of the compressed refrigerant. The absorption dilute solution exiting the solution heat exchanger is allowed to flow into the recovery heat exchanger and into the refrigerant heat recovery heat exchanger on the upstream side of the compressed refrigerant.

  According to such a configuration, the absorbing dilute solution having the lowest temperature that does not pass through the solution heat exchanger is on the downstream side of the compressed refrigerant, and the absorbing dilute solution having a relatively high temperature through the solution heat exchanger is disposed on the compressed refrigerant upstream. On the side, the heat of the compressed refrigerant is recovered, and an effective temperature difference can be ensured and heat can be recovered efficiently.

(6) Problem solving means of the invention of claim 6 The problem solving means of the present invention is the structure of the problem solving means of the invention of claim 2, wherein the refrigerant heat recovery heat exchanger is arranged from the upstream side to the downstream side of the compressed refrigerant. Of the dilute solution from the absorber to the generator through the solution heat exchanger, and the absorbed dilute solution before entering the solution heat exchanger is divided into the refrigerant heat in the downstream side of the compressed refrigerant. The absorption dilute solution exiting from the solution heat exchanger is allowed to flow into the recovery heat exchanger and into the generator and the refrigerant heat recovery heat exchanger on the upstream side of the compressed refrigerant.

  According to such a configuration, the absorption dilute solution having the lowest temperature that does not pass through the solution heat exchanger is the downstream side of the compressed refrigerant, and the absorption dilute solution having a relatively high temperature through the solution heat exchanger is The refrigerant is supplied to the refrigerant heat recovery heat exchanger on the upstream side of the compressed refrigerant, and an effective temperature difference can be ensured for efficient heat recovery.

(7) Problem solving means of the invention of claim 7 The problem solving means of the invention is the structure of the problem solving means of the invention of claim 1, 2, 3, 4, 5 or 6, wherein the evaporator is a refrigerant liquid. Flows temporarily on the heat transfer surface of the evaporator, and the unevaporated refrigerant liquid flowing down the heat transfer surface moves to the absorber side and is absorbed by the absorption solution flowing down the absorber. It is characterized by becoming.

  According to such a configuration, the non-evaporated refrigerant liquid that has not evaporated on the heat transfer surface of the evaporator and has flowed down to the bottom moves to the bottom of the absorber, and is again absorbed by the absorbing solution at the bottom of the absorber. Therefore, the absorption efficiency is improved.

(8) Problem solving means of the invention of claim 8 The problem solving means of the present invention is the structure of the problem solving means of the invention of claim 1, 2, 3, 4, 5, 6 or 7, wherein a plurality of steams are provided. It is equipped with a compression refrigeration machine and a heat exchanger for refrigerant heat recovery corresponding to each of these vapor compression refrigeration machines, for recovering the heat of the compressed refrigerant of each vapor compression refrigeration machine and for corresponding absorption chiller drive It is characterized by being used as a heat source.

  According to such a configuration, the effects of the configurations of the above-described inventions can be obtained, and the exhaust heat amount of the compressed refrigerant on the vapor compression refrigerator side is increased (by the number of installed units), so that the absorption refrigerator side The driving ability (the amount of generated refrigerant vapor) can also be increased.

  As a result of the above, according to the present invention, it is possible to effectively utilize the exhaust heat between the vapor compression refrigerator and the absorption refrigerator, as well as the heat dissipation of the refrigerant in the conventional compressed refrigerant on the vapor compression refrigerator. The heat exchanger for the absorption refrigeration machine has a simple and low-cost configuration that simply adds a gas-liquid separation function to the heat exchanger that generates refrigerant vapor by heating the solution with an external heat source. Things will suffice.

  Furthermore, in the evaporator of the absorption chiller, the configuration is simplified and the evaporation temperature of the refrigerant of the absorption chiller in the evaporator is higher than that in the case where the chilled water is separately circulated through the evaporator. Therefore, if the required evaporation capacity of the refrigerant is constant, the evaporator capacity can be kept low by the increase in the evaporation temperature relative to the refrigerant, and the cost can be reduced or the size can be reduced. It becomes possible.

  In addition, even when the amount of exhaust heat from the external heat source becomes a certain value or less, a stable absorption refrigeration operation can be ensured.

It is a freezing circuit diagram which shows the structure of the freezing apparatus which concerns on Embodiment 1 of this invention. It is a freezing circuit diagram which shows the structure of the freezing apparatus which concerns on Embodiment 2 of this invention. It is a freezing circuit diagram which shows the structure of the freezing apparatus which concerns on Embodiment 3 of this invention. It is a freezing circuit diagram which shows the structure of the freezing apparatus which concerns on Embodiment 4 of this invention.

  Hereinafter, several embodiments of the present invention will be described in detail.

(Embodiment 1)
First, FIG. 1 shows a combination of a vapor compression refrigerator and an absorption refrigerator equipped with an external heat source, and the refrigerant of the vapor compression refrigerator is supercooled by the evaporator of the absorption refrigerator. In the cooling operation of the vapor compression refrigeration machine, the heat of the refrigerant is recovered in advance by the absorption dilute solution supplied from the absorber of the absorption refrigeration machine to the generator, and then the absorption dilute solution is absorbed by the absorption type. A heat exchanger for recovering refrigerant heat that flows into the generator of the refrigerator is provided separately from the generator, and in the generator of the absorption chiller, the solution is heated by heat from an external heat source to generate refrigerant vapor. In addition, the configuration of the refrigeration apparatus according to Embodiment 1 of the present invention in which gas-liquid separation is efficiently performed by the heat of the refrigerant of the vapor compression refrigeration machine recovered by the refrigerant heat recovery heat exchanger is shown. ing.

As an example in this embodiment, the vapor compression refrigeration machine X employs carbon dioxide (CO ₂ ), which is a natural refrigerant, as a refrigerant. Side heat exchangers (indoor units) 3, 3, accumulator 4 and the like are connected by refrigerant pipes 5a and 5b (compressor discharge side 5a / suction side 5b) so that a heat pump can be operated as shown in the figure to constitute a refrigeration circuit For example, a four-way switching valve or the like (not shown) is provided, and cooling and heating can be performed by reversing the direction of the refrigerant flowing in the refrigeration circuit as necessary. That is, the use-side heat exchangers 3 and 3 function to cool the room by absorbing the indoor heat to the carbon dioxide refrigerant during the cooling operation, while dissipating the heat of the carbon dioxide refrigerant during the heating operation. It serves to heat the room.

  However, in this embodiment, since the case of the heating operation is not a problem, the drawing shows the case of the cooling operation (therefore, the illustration of the four-way switching valve is also omitted).

On the other hand, the absorption refrigerator Y uses, for example, lithium bromide (LiBr) as an absorption liquid and water (H ₂ O) as a refrigerant, and utilizes the absorption (H ₂ O) and release action of the refrigerant into the absorption liquid (LiBr). In this way, the necessary refrigeration capacity is exhibited. In the case of this embodiment, a hot water heat exchanger 34 by an external heat source is provided, and hot water from an external exhaust heat source such as a small generator or GHP is circulated in the hot water heat exchanger 34, The generator 11 is provided with a generator 11 that separates the refrigerant vapor from the absorption dilute solution whose concentration has been reduced by absorbing the refrigerant in the absorber 13 to obtain a high concentration concentrated absorption solution, and a cooling fan 12a. The air-cooled condenser 12 that condenses and liquefies by introducing the refrigerant vapor separated from the air and cooled by external air and the air-cooled condenser 12 are disposed adjacent to each other in one sealed container 19. An evaporator 14 for evaporating (vaporizing) the refrigerant liquid under low pressure, an absorber 13 for absorbing the refrigerant vapor generated in the evaporator 14, and a cooling fan 15a. An air-cooled cooler 15 that introduces a part of the absorbing dilute solution discharged from the pump 17 (most of the mixture of the concentrated solution and dilute solution) and supercools this, and the high-temperature absorbing concentration from the generator 11 A solution heat exchanger 16 that raises the temperature of the absorption dilute solution by mutually exchanging heat between the solution and the low-temperature absorption dilute solution from the absorber 13, and the concentration of the absorbent by absorbing the refrigerant vapor in the absorber 13 A solution pump 17 that is supplied again to the generator 11 to concentrate the absorbed dilute solution having decreased, and is supercooled via the air-cooled cooler 15 and then supplied to the absorber 13. Are connected by a refrigerant pipe 21 and solution pipes 23 to 27 so that a heat pump can be operated.

  That is, in the case of this embodiment, the absorption solution entering the absorber 13 is sufficiently subcooled (circulated through the solution pipe 25) by the air cooling cooler 15 provided with the cooling fan 15a as described above. In the absorber 13 arranged in parallel with the evaporator 14, the absorbed vapor is absorbed by the refrigerant vapor evaporated by the evaporator 14. Absorption heat generated during absorption is absorbed by the air-cooled cooler 15. A solution separation cooling (indirect air cooling) system in which the supercooled absorbing solution is removed by sensible heat and the absorbing solution is indirectly cooled by an air cooling cooler 15 is employed.

  As described above, the air cooling cooler 15 for supercooling the absorbing solution flowing into the absorber 13 is provided, and the absorber 13 absorbs the refrigerant vapor from the evaporator 14 by the sensible heat of the flowing absorbing solution. In the case of an absorption chiller that employs the above, the amount of dilute solution supplied to the generator 11 because the solution is supercooled by air cooling or other solution cooler (air cooling in the figure) and the absorbed heat is removed by sensible heat of the solution. Even if this is increased, the performance is hardly degraded.

  Therefore, since the supply amount of the dilute solution to the generator 11 can be increased, the amount of refrigerant vapor generated can be increased, or the refrigerant heat recovery heat exchanger can be downsized.

  Further, the absorber 13 can be made more compact than a direct cooling method in which the solution that directly absorbs the refrigerant vapor in the absorber 13 portion is cooled to absorb the refrigerant vapor.

Although a detailed structure is not shown in FIG. 1, for example, a refrigerant distribution tray and an absorption solution distribution tray for evenly distributing the refrigerant and the absorption solution are provided above the evaporator 14 and the absorber 13, respectively. Each is provided. Further, the heat exchanger 7 of the evaporator 14 is configured to form a part of the compressor discharge side refrigerant pipe 5a of the vapor compression refrigerator X side refrigeration circuit, for example, and the inside thereof is discharged from the compressor 1. It becomes a to-be-cooled body passage through which the compressed refrigerant (CO ₂ refrigerant) flows.

  Then, the internal compressed refrigerant is efficiently cooled by allowing the refrigerant to flow down, for example, in a liquid film state on the surface of the heat exchanger 7 and evaporating it. Further, the heat exchanger 18 of the absorber 13 can more effectively promote the absorption of the refrigerant vapor by allowing the solution to flow vertically in a liquid film state on both sides of a plate that is bent and arranged in a corrugated structure, for example. It has a simple structure.

  Further, the evaporator 14 is configured such that, for example, the refrigerant liquid is transient and flows down the heat transfer surface of the heat exchanger 7, and the unevaporated refrigerant liquid that has flowed down to the bottom of the evaporator 14 is liquid at the bottom of the absorber 13. It moves to the nozzle part 19a and is absorbed by the absorbing solution again at the liquid retaining part 19a. Therefore, the absorption efficiency is improved.

  Reference numeral 10 indicates that the inner heat exchanging portion 6 forms a part of the compressor discharge side refrigerant pipe 5a of the vapor compression refrigerator X in the same manner as the heat exchanger 7 of the evaporator 14. And a heat exchanger having a double-pipe structure in which a dilute solution passage 8 is formed on the outer periphery of the heat exchanging section 6. The compressor 1 of the vapor compression refrigerator X This is a heat exchanger for heat recovery of the refrigerant for recovering heat of the compressed refrigerant compressed in step 1 by the absorbed diluted solution supplied from the absorber 13 of the absorption refrigeration machine Y to the generator 11. The refrigerant vapor is absorbed in the dilute solution passage 8 of the industrial heat exchanger 10 by the absorber 13, and a part of the dilute diluted solution whose concentration and temperature are reduced, for example, the dilute solution before passing through the solution heat exchanger 16 Is introduced via a solution pipe (branch pipe) 26B, from the downstream side of the compressed refrigerant to the upstream side. The heat of the compressed refrigerant discharged from the compressor 1 is effectively recovered, and then the liquid is introduced and mixed into the generator 11 of the absorption refrigeration machine Y through the solution pipe 27. By increasing the temperature of the absorption diluted solution itself separately from the external heat source and greatly improving the generation efficiency of the refrigerant vapor, while efficiently cooling the compressed refrigerant on the vapor compression refrigerator X side, While improving the supercooling performance in the heat exchanger 7, the heat dissipation heat exchanger (the third heat source heat exchanger 35 of Patent Document 3) on the conventional vapor compression refrigerator side is not required. The refrigerant heat recovery heat exchanger 10 is external to the generator 11 (between the absorption refrigeration machine Y and the vapor compression refrigeration machine X) and is completely separate.

On the other hand, the absorption dilute solution heated up through the solution heat exchanger 16 is directly flowed into the generator 11 through the downstream solution pipe 26A.

  As described above, in order to improve the refrigerating capacity of the refrigerating apparatus that combines the vapor compression refrigerator X and the absorption refrigerator Y, the exhaust heat between the vapor compression refrigerator Y and the absorption refrigerator X is reduced. The issue is how to use it effectively.

  At the same time, it is important to simplify the configuration of each other and reduce costs, and eliminate the need for a conventional heat-dissipating heat exchanger that dissipates the heat of the vapor compression refrigerator X side compressed refrigerant. Is desired.

  In addition, the waste heat utilization type absorption refrigerator X driven by hot water exhaust heat such as a small generator or GHP is used in a single-effect refrigeration cycle from the viewpoint of cost. The problem is how to reduce the cost of the generator to be generated.

  In particular, the use of waste heat water is difficult to establish unless it is a cheaper device, and a drastic reduction in the cost of the generator is required for the waste heat drive type absorption refrigeration apparatus.

  On the other hand, in the case of the configuration as described above, the absorber 13 is the heat exchanger 10 for recovering the refrigerant heat that is located outside the refrigerant vapor generator 11 and is completely separate from the generator 11. The high-temperature compressed refrigerant discharged from the compressor 1 is efficiently cooled by the low-temperature absorbing dilute solution supplied from the generator 11 to the generator 11 and then is supplied to the evaporator of the absorption refrigeration machine Y and is supercooled. After the absorbing dilute solution is heated to a high temperature, it is supplied into the generator 11 through the outlet side solution pipe 27, and is effectively flushed to be separated into a refrigerant vapor and an absorbing concentrated solution.

  Therefore, according to this configuration, the heat of the vapor compression refrigeration machine side compressed refrigerant can be effectively utilized for driving the absorption refrigeration machine, and the refrigeration capacity of the absorption refrigeration machine can be increased accordingly. it can.

  In addition, even when the amount of exhaust heat from the external heat source supplied via the hot water heat exchanger 34 becomes a certain value or less, a stable absorption refrigeration operation can be ensured.

  In particular, the compressed refrigerant on the vapor compression refrigeration machine side is cooled by the heat deprived on the absorption dilute solution side as described above and the temperature is lowered, and is further supplied to the evaporator on the absorption refrigeration machine side. Undercooled. Therefore, compared with the case where there is no heat exchanger for recovering refrigerant heat, the compressed refrigerant is more effectively subcooled, and the inlet specific enthalpy of the refrigerant supplied to the use side heat exchanger can be effectively reduced. As a result, the cooling performance of the use side heat exchanger is improved.

  As a result, the conventional heat exchanger for heat dissipation of the compressed refrigerant on the vapor compression refrigeration machine side becomes unnecessary, and the absorption chiller side generator also heats the solution with an external heat source to generate refrigerant vapor. A simple and low-cost configuration in which a gas-liquid separation function is simply added to the generated heat exchanger is sufficient.

  Furthermore, when supercooling of the refrigerant compressed in the vapor compression refrigerator is performed in the evaporator of the absorption refrigerator, the absorption refrigerator is compared with a structure in which cold water is separately circulated in the evaporator. In addition, since the structure can be simplified and the evaporation temperature of the refrigerant liquid of the absorption chiller in the evaporator can be increased, for example, when the required evaporation capacity of the refrigerant liquid is constant, the heating temperature for the refrigerant Therefore, it is possible to reduce the cost of the evaporator or reduce the size of the evaporator by reducing the capacity of the evaporator by the amount of the increase.

(Embodiment 2)
Next, FIG. 2 shows a configuration of a refrigeration apparatus according to Embodiment 2 of the present invention.

  Also in the case of this second embodiment, similarly to the first embodiment, a vapor compression refrigerator and an absorption refrigerator having an external heat source are combined and steam is absorbed by the refrigerant evaporator of the absorption refrigerator. In a refrigeration system configured to supercool the compressed refrigerant of the compression refrigerator, absorption of heat supplied from the absorber of the absorption refrigerator to the generator during cooling operation of the vapor compression refrigerator After collecting with a dilute solution, a heat exchanger for recovering refrigerant heat that flows into the generator of the absorption refrigeration machine is provided. In the generator of the absorption refrigeration machine, recovery is performed with an external heat source and the same heat exchanger for heat recovery of the refrigerant. The refrigerant vapor is efficiently generated by the heat of the compressed refrigerant of the vapor compression refrigerator.

In this case, in this second embodiment, as shown in detail in FIG. 2, for example, the outer peripheral absorption diluted solution passage 8 portion of the refrigerant heat recovery heat exchanger 10 in the first embodiment is compressed. The upstream heat exchange is performed by dividing the two absorption dilute solution passages 8A and 8B through the communication passage 29 by dividing them into two parts, the upstream 8A part and the downstream 8B part, along the refrigerant flow. Absorption heat supplied from the absorber 13 side to the generator 11 side without passing through the solution heat exchanger 16 via the solution pipes 26 and 26B. The solution is supplied to the downstream end of the absorption diluted solution passage 8B of the downstream heat exchanger 10B, and a high-temperature vapor compression refrigerator side compressed refrigerant (from the downstream absorption diluted solution tube 8B side to the upstream absorption diluted solution passage 8A) the flow of CO ₂ refrigerant) It is configured to flow to direction. Also, the lower end of the absorption dilute solution passage 8A of the refrigerant heat recovery heat exchanger 10A having a long upstream length is used for the slightly diluted high temperature absorption dilute solution heat-exchanged with the absorption concentrated solution from the generator 11 through the solution heat exchanger 16. After being supplied to the portion and exchanging heat with each of the high-temperature compressed refrigerant (CO ₂ refrigerant), the heat of the compressed refrigerant is effectively recovered and sufficiently heated, and then the generator is generated via the outlet-side solution pipe 27. 11 is supplied.

  As described above, the refrigerant heat recovery heat exchanger 10 (specifically, the dilute solution passage 8 portion through which the absorbed dilute solution flows) is divided into the upstream portion 10A and the downstream portion 10B, and a communication passage is formed between them. If the absorbing dilute solution is caused to flow stepwise by communicating at 29, the residence time of the absorbing dilute solution in the passage portion of each of the downstream heat exchanger 10B and the upstream heat exchanger 10A becomes longer, and the corresponding heat exchange The heat exchange time with the parts 6B and 6A also becomes longer.

Then, the low-temperature absorption dilute solution before passing through the solution heat exchanger 16 is efficiently heat-exchanged with the high-temperature compressed refrigerant (CO ₂ refrigerant), and the heat of the compressed refrigerant is recovered more effectively to sufficiently raise the temperature. Then, the dilute solution alone is supplied into the generator 11 through the outlet side solution pipe 27, and the refrigerant vapor is efficiently generated in cooperation with an external heat source in the generator 11, while the vapor compression refrigerator X The temperature of the side compressed refrigerant is effectively lowered and then supplied to the evaporator 14 to be more effectively supercooled.

  According to such a configuration, the degree of heat recovery of the compressed refrigerant is improved and the temperature of the absorbing diluted solution is sufficiently increased, and more effective refrigerant vapor separation effect and absorption liquid concentration effect can be obtained. Therefore, the generator 11 can be simplified.

  Further, it is possible to reduce the heat exchanger for heat dissipation of the vapor compression refrigerator, and the heat conversion by the absorption refrigerator can be effectively used, so the performance of the vapor compression refrigerator is greatly improved.

  The structure of other parts is the same as that of the first embodiment described above, and has the same effects.

(Embodiment 3)
Next, FIG. 3 shows a configuration of a refrigeration apparatus according to Embodiment 3 of the present invention.

  In the third embodiment, as in the second embodiment, the absorption diluted solution passage 8 of the refrigerant heat recovery heat exchanger 10 is replaced with a vapor compression refrigerator as shown in FIG. 3, for example. Two heat exchangers 10A and 10B are formed by dividing into two parts, an upstream side 8A part and a downstream side 8B part, along the X compressor 1 discharge side refrigerant pipe 5a. The length of the exchanger 10A is made longer than that of the downstream heat exchanger 10B, and a branch pipe 26c downstream of the solution heat exchanger 16 of the dilute solution pipe 26 is provided at the downstream end of the upstream heat exchanger 10A. A branch pipe 26B from the upstream side (front side) of the solution heat exchanger 16 of the dilute solution pipe 26 is connected to the downstream end of the downstream heat exchanger 10B, and a branch pipe 26A is connected to the generator. Absorbing dilute solution from each absorber 13 outlet is supplied It is configured to so that.

As a result, the absorption dilute solution having a large temperature difference from the compressed refrigerant at a low temperature that does not pass through the solution heat exchanger 16 is first removed from the downstream end of the refrigerant heat recovery heat exchanger 10B having a short downstream length to the upstream length. The refrigerant having a long upstream side is passed through the heat exchanger 10A for long refrigerant heat recovery, and the slightly diluted high-temperature absorption diluted solution exchanged with the absorption concentrated solution from the generator 11 through the solution heat exchanger 16. After supplying the downstream end portion of the heat recovery heat exchanger 10A and exchanging heat with each of the high-temperature compressed refrigerant (CO ₂ refrigerant), and effectively recovering the heat of each compressed refrigerant and sufficiently raising the temperature, This is characterized in that it is supplied into the generator 11 through the outlet side solution pipe 27 so that the absorption diluted solution can be effectively gas-liquid separated.

  With such a configuration, on the refrigerant heat recovery heat exchanger 10A side having a long upstream length, the temperature of the diluted diluted solution supplied by the amount recovered through the solution heat exchanger 16 is increased, Since the heat has not yet been exchanged, the temperature of the compressed refrigerant is also high. On the other hand, the downstream side refrigerant heat recovery heat exchanger 10B side having the shorter length is not passed through the solution heat exchanger 16, so the temperature of the supplied diluted diluted solution is low. Therefore, each effective temperature difference can be taken, and more efficient heat exchange can be achieved by exchanging heat with the compressed refrigerant over time corresponding to the length thereof. The separation effect of the refrigerant vapor and the concentration effect of the absorption liquid are higher than those of the second embodiment.

  The configuration of the other parts is the same as that of the second embodiment described above, and provides the same effects.

(Embodiment 4)
Next, FIG. 4 shows a configuration of a refrigeration apparatus according to Embodiment 4 of the present invention.

In the case of the fourth embodiment, the configuration is basically the same as that of the first embodiment, but in the fourth embodiment, the vapor compression refrigeration provided with the refrigerant heat recovery heat exchanger 10 is used. the machine X provided multiple X _1, X ₂ minutes, and is characterized in that they were adapted to heat recovery in the same way by combining the common on a single absorption refrigerating machine Y.

  According to such a configuration, not only the effects of the configuration of the first embodiment described above can be obtained, but also the amount of exhaust heat of the vapor compression refrigeration machine X side compressed refrigerant becomes large (only for the number of installed units). Thus, the driving capability (refrigerant vapor generation amount) on the absorption refrigerator Y side can also be increased.

  1 is a compressor, 2 is an expansion valve, 3 is a use side heat exchanger, 5a is a compressor discharge side refrigerant pipe, 5b is a compressor suction side refrigerant pipe, and 6 (6A, 6B) is a compressor refrigerant pipe side heat exchange. , 7 is a heat exchanger of the evaporator, 8 (8A, 8B) is a diluted solution passage of the heat exchanger for refrigerant heat recovery, 10 (10A, 10B) is a heat exchanger for refrigerant heat recovery, 11 is a generator, 12 is an air-cooled condenser, 13 is an absorber, 14 is an evaporator, 15 is an air-cooled cooler, 17 is a solution pump, 18 is a plate of the absorber, X is a vapor compression refrigerator, and Y is an absorption refrigerator. .

Claims (8)

  A refrigeration system that combines a vapor compression refrigerator and an absorption refrigerator equipped with an external heat source to supercool the compressed refrigerant of the vapor compression refrigerator with the refrigerant evaporator of the absorption refrigerator during cooling operation In the above, the heat of the compressed refrigerant during the cooling operation of the vapor compression refrigeration machine is transferred to the outside of the generator of the absorption refrigeration machine by an absorption dilute solution supplied from the absorber of the absorption refrigeration machine to the generator. A refrigerant heat recovery heat exchanger is provided for allowing the absorption diluted solution to flow into the absorption chiller generator after being collected in advance. In the absorption chiller generator, the refrigerant heat recovery The solution superheated by the heat of the compressed refrigerant of the vapor compression refrigerator recovered by the heat exchanger is gas-liquid separated, while the solution is heated by the external heat source to generate refrigerant vapor. Refrigeration equipment characterized.   An absorption liquid air-cooled cooler that supercools the absorbent flowing into the absorber, and a solution heat exchanger that exchanges heat between the absorbed diluted solution supplied from the absorber to the generator and the absorbed concentrated solution from the generator are provided. The absorption dilute solution at the outlet side of the absorber is divided into each of the absorption liquid air-cooled cooler, the solution heat exchanger, and the refrigerant heat recovery heat exchanger, while the absorber passes through the absorption liquid air-cooled cooler. 2. The refrigeration apparatus according to claim 1, wherein the refrigerant vapor is absorbed by the sensible heat of the absorption liquid introduced after being supercooled.   3. The refrigeration apparatus according to claim 2, wherein the absorption diluted solution from the generator and the absorption diluted solution exchanged through the solution heat exchanger are caused to flow into the refrigerant heat recovery heat exchanger.   3. The absorption dilute solution heat-exchanged with the absorption concentrated solution from the generator through the solution heat exchanger is caused to flow into each of the generator and the refrigerant heat recovery heat exchanger. Refrigeration equipment.   The refrigerant heat recovery heat exchanger is divided into a plurality of stages from the upstream side to the downstream side of the compressed refrigerant, and enters the solution heat exchanger from the dilute solution that reaches the generator through the solution heat exchanger from the absorber. The previous diluted diluted solution flows into the refrigerant heat recovery heat exchanger on the downstream side of the compressed refrigerant, and the absorbed diluted solution exiting the solution heat exchanger flows into the refrigerant heat recovered heat exchanger on the upstream side of the compressed refrigerant. The refrigeration apparatus according to claim 2, wherein:   The refrigerant heat recovery heat exchanger is divided into a plurality of stages from the upstream side to the downstream side of the compressed refrigerant, and enters the solution heat exchanger from the dilute solution that reaches the generator through the solution heat exchanger from the absorber. The previous absorption diluted solution is transferred to the refrigerant heat recovery heat exchanger on the downstream side of the compressed refrigerant, and the absorption diluted solution discharged from the solution heat exchanger is transferred to the generator and the refrigerant refrigerant on the upstream side of the compressed refrigerant. The refrigeration apparatus according to claim 2, wherein each of the refrigeration apparatuses is allowed to flow into a container.   In the evaporator, the refrigerant liquid flows temporarily on the heat transfer surface of the evaporator, and the unevaporated refrigerant liquid flowing down the heat transfer surface moves to the absorber side and flows down the absorber. The refrigeration apparatus according to claim 1, wherein the refrigeration apparatus is adapted to be absorbed by the absorbed solution.   A plurality of vapor compression refrigeration units and a heat exchanger for recovering refrigerant heat corresponding to each of these vapor compression refrigeration units, recovering the heat of the compressed refrigerant of each vapor compression refrigeration unit and corresponding absorption type 8. The refrigeration apparatus according to claim 1, wherein the refrigeration apparatus is used as a heat source for driving a refrigerator.

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