JP2010249357A - Refrigerating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To simplify the configuration of a generator of an absorption refrigerator and to improve the refrigeration performance of a vapor compression refrigerator in a refrigerating device wherein the vapor compression refrigerator and the absorption refrigerator are combined and the absorption refrigerator is driven by the exhaust heat of the vapor compression refrigerator. <P>SOLUTION: The refrigerating device includes a vapor compression refrigerator and an absorption refrigerator driven by the exhaust heat of the vapor compression refrigerator. A heat exchanger for collecting refrigerant heat is provided which collects the heat of refrigerant after compression of the vapor compression refrigerator by means of a dilute absorbed solution of the absorption refrigerator. The heat exchanger causes the dilute absorbed solution to flow into a generator of the absorption refrigerator after the solution has collected the heat of the compressed refrigerant, and refrigerant vapor is separated whereby the generator of the absorption refrigerator is used as a gas-liquid separator serving only to separate the refrigerant vapor from the dilute absorbed solution flowing in, and the compressed refrigerant of the vapor compression refrigerator is cooled or supercooled to improve the refrigeration performance of the vapor compression refrigerator. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The invention of this application relates to a refrigeration apparatus that includes a vapor compression refrigerator and an absorption refrigerator that is driven by exhaust heat of the vapor compression refrigerator, and that can be operated by combining them as desired.

  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 And a refrigerant that circulates through each device including the generator of the absorption refrigeration cycle, and recovers the exhaust heat of the heat source side heat exchanger of the vapor compression refrigeration cycle and absorbs the refrigeration By cooling the refrigerant on the outlet side of the heat source side heat exchanger of the vapor compression refrigeration cycle by the cycle evaporator, the amount of heat released as a whole system can be reduced, the power consumption can be reduced, and the coefficient of performance can be improved. There is a refrigeration apparatus (see, for example, Patent Document 3).

  According to such a configuration, the exhaust heat of the vapor compression refrigeration machine itself can be effectively used as a drive source of the absorption refrigeration machine by converting it into necessary cold heat instead of 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 refrigerating capacity of the refrigerating apparatus combining the vapor compression refrigerator and the absorption refrigerator as described above, the heat exhausted between the vapor compression refrigerator and the absorption refrigerator as described above. The issue is how to effectively use the system.

  At the same time, it is important to simplify the configuration of each other and reduce the cost. In particular, it is desirable to eliminate the need for a heat-dissipating heat exchanger that dissipates the heat of the refrigerant compressed in the vapor compression refrigerator. It is.

  In addition, waste heat utilization type absorption refrigerators are often used in single-effect refrigeration cycles from the viewpoint of cost, but how to reduce the cost of a generator that generates refrigerant vapor by exhaust heat. It becomes a problem.

  That is, it is difficult to establish an exhaust-type absorption refrigerator that uses exhaust heat unless it is a cheaper device, and there is a strong demand for a significant reduction in 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. It is supplied to the second heat source side heat exchanger constituting the evaporator via the third heat source side heat exchanger for heat dissipation of the compressed refrigerant with the cooling fan, and is supercooled. The system cannot be simplified, and the third heat source side heat exchanger for heat dissipation of the compressed refrigerant is necessary. Therefore, there is a disadvantage that the entire system is complicated and expensive. Not cut upon request.

  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, In addition, only the diluted absorption solution that has been heated is allowed to flow into the generator of the absorption chiller to separate the refrigerant vapor, thereby simplifying the configuration of the absorption chiller generator without using an external heat source. At the same time, by cooling the refrigerant of the vapor compression refrigeration machine, the cooling or supercooling performance of the compressed refrigerant before expansion supplied to the use side heat exchanger is improved, and the heat radiation of the vapor compression refrigeration machine is improved. An object of the present invention is to provide a refrigeration apparatus that does not require a heat exchanger.

  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 refrigeration apparatus comprising a vapor compression refrigerator and an absorption refrigerator driven by exhaust heat of the vapor compression refrigerator. A refrigerant heat recovery heat exchanger for recovering the heat of the refrigerant after compression of the vapor compression refrigerator by the absorption diluted solution of the absorption refrigerator, and the heat exchanger for refrigerant heat recovery The absorption dilute solution that has recovered the heat of the compressed refrigerant flows into the generator of the absorption refrigeration machine in a flow-through state, and separates the refrigerant vapor, thereby causing the absorption dilute solution to flow into the generator. On the other hand, the refrigerant of the vapor compression chiller is separated from the vapor compression chiller by cooling or supercooling the compressed refrigerant of the vapor compression refrigeration by the evaporator of the absorption chiller. It is characterized by improved performance.

  According to such a configuration, it is possible to secure a heat source for driving the absorption refrigerator even when there is no external heat source, and to condense or dissipate the refrigerant in the vapor compression refrigerator during the cooling operation. The amount of heat can be used as a heating source for the absorption refrigerator.

  And in the conventional generator, it is necessary to heat the supplied absorbing solution to separate the solution and the refrigerant vapor, and the generator solution temperature is determined by the operation cycle of the absorption refrigerator, so the generator The amount of heat exchanged with the refrigerant in the vapor compression refrigerator is limited, but if the solution flows into the generator after recovering heat in the refrigerant heat recovery heat exchanger separated from the generator, the absorbing solution The refrigerant vapor generator can be configured with a once-through gas-liquid separator that only needs to separate the refrigerant vapor, and heat source side heat exchange that flows an external heat source as in the past A vessel is not required. Therefore, the configuration becomes extremely simple and the cost is reduced.

  At the same time, the heat of the compressed refrigerant of the vapor compression refrigerator is recovered by the absorbed dilute solution on the absorption refrigerator side and efficiently cooled, so that the degree of subsequent supercooling is improved and the vapor compression refrigerator The refrigeration performance of the machine itself is improved and a conventional heat exchanger for heat dissipation of compressed refrigerant is not required, so that the apparatus configuration is simple and low-cost.

  Further, in this case, if the refrigerant is precooled before expansion by the evaporator of the absorption refrigeration machine, the cooling water is added to the evaporator of the absorption refrigeration machine. As compared with the case where the refrigerant is circulated and supercooled, the evaporation temperature of the refrigerant in the evaporator can be increased.

  As a result, the absorption refrigerator can be miniaturized as much as possible, and cold energy can be used effectively.

(2) The problem-solving means of the invention of claim 2 The problem-solving means of the invention is the absorption-solution supercooler for supercooling the absorption liquid flowing into the absorber in the configuration of the problem-solving means of the invention of claim 1 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 on the outlet side of the absorber is supercooled with the absorption solution. The absorber, the solution heat exchanger, and the refrigerant heat recovery heat exchanger. In the absorber, the absorption liquid is absorbed by the sensible heat of the absorption liquid after being supercooled via the absorption liquid supercooler. It is characterized in that the refrigerant vapor is absorbed.

  Thus, the heat exchanger for refrigerant heat recovery described above, and the solution heat exchanger that recovers the heat of the concentrated concentrated solution supplied from the generator to the absorber to the absorption dilute solution side supplied from the absorber to the generator In addition to the above, an absorption liquid supercooler for supercooling the absorption liquid flowing into the absorber is provided, and the absorption liquid is supercooled by the absorption liquid subcooler 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 amount of exchange heat, increase the amount of refrigerant vapor generated, or reduce the size of the refrigerant heat recovery heat exchanger.

  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 diverted to flow, each of them effectively and appropriately recovers heat to the absorption refrigerator side dilute solution over a wide temperature range (recovery of heat from the absorption concentrated solution and (Recovery of heat from the vapor compression refrigerator side compressed refrigerant) is performed, and a heat recovery action with high efficiency is realized as a whole.

(3) Problem solving means of the invention of claim 3 The problem solving means of the present invention is the structure of the problem solving means of the invention of claim 2 described above, wherein heat is exchanged with the absorbed concentrated solution from the generator through the solution heat exchanger. It is characterized in that the absorbed dilute solution is caused to flow into the refrigerant heat recovery heat exchanger.

  According to such a configuration, the heat can be effectively recovered with the low-temperature absorption dilute solution that is supplied to the refrigerant heat recovery heat exchanger without passing through the solution heat exchanger, and flows through the heat exchanger. The absorption dilute solution whose temperature has been increased by heat exchange with the absorption concentrated solution from the generator in the generator is further flowed upstream from the middle of the refrigerant heat recovery heat exchanger in the upstream direction of the compressed refrigerant, and is effectively absorbed by the heat of the compressed refrigerant. The temperature is raised and the temperature is supplied to the generator, the heat recovery effect is further improved, and the gas-liquid separation effect in the generator is 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. It is characterized in that the exchanged diluted absorption solution is allowed to flow into the generator and the refrigerant heat recovery heat exchanger.

  According to such a configuration, a part of the diluted diluted solution whose temperature has been increased by heat exchange with the absorbed concentrated solution from the generator in the solution heat exchanger remains as it is in the generator, and the other diluted diluted solution is used for refrigerant heat recovery. Heat is heated by the compressed refrigerant both in the whole heat exchanger and in the middle, and is supplied to the generator. Heat recovery is effectively performed at each stage, and the heat recovery rate as a total. Will improve.

(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 absorption dilute solution from the absorber through the solution heat exchanger to the generator, and the absorption dilute solution before entering the solution heat exchanger is divided into the refrigerant on the downstream side of the compressed refrigerant. A feature of the present invention is that the absorption diluted solution that has exited the solution heat exchanger is allowed to flow into the heat recovery heat exchanger and the refrigerant heat recovery heat exchanger upstream 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 other hand, the heat of the compressed refrigerant is recovered, and a temperature difference effective for heat exchange can be ensured for efficient heat recovery.

(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 improve the performance of the vapor compression refrigerator by effectively utilizing the exhaust heat between the vapor compression refrigerator and the absorption refrigerator. A heat exchanger for radiating the refrigerant heat of the compressed refrigerant on the compression refrigerator side becomes unnecessary, and the absorption refrigerator generator on the absorption refrigerator side only needs to have a simple and low-cost configuration with a gas-liquid separator.

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 is a combination of a vapor compression refrigerator and an absorption refrigerator equipped with an external heat source so that the refrigerant of the vapor compression refrigerator is cooled or supercooled by the evaporator of the absorption refrigerator. In the refrigeration system, the heat of the compressed refrigerant during the cooling operation of the vapor compression chiller is supplied to the generator (gas-liquid separator) from the absorber of the absorption chiller in advance. A heat exchanger for recovering refrigerant heat is provided to collect the absorption diluted solution, and only the diluted absorption solution is allowed to flow into the generator of the absorption refrigeration machine by liquid alone or in a two-layer flow-through system. The generator efficiently performs gas-liquid separation by the heat of the refrigerant of the vapor compression refrigeration machine recovered by the refrigerant heat recovery heat exchanger without using an external heat source. Implementation of the present invention for effective heat dissipation It shows a configuration of a refrigerating apparatus according to a 1.

As an example in this embodiment, the vapor compression refrigerator X employs carbon dioxide (CO ₂ ), which is a natural refrigerant, as a refrigerant. The compressor 1, the expansion valves 2 and 2, and the use side compress the refrigerant. The refrigeration circuit is configured by connecting the heat exchangers (indoor units) 3 and 3 and the accumulator 4 with refrigerant pipes 5a and 5b (compressor discharge side 5a / suction side 5b) so that the heat pump can operate as shown in the figure. 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 absorb the heat of the carbon dioxide refrigerant and cool the room during the cooling operation, while radiating the heat of the carbon dioxide refrigerant and heating the room during the heating operation. It is designed to fulfill the actions to be performed.

  However, in this embodiment, since the case of heating operation is not particularly problematic, the figure shows the case of 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). The necessary refrigeration capacity is demonstrated. And in the case of this embodiment, without providing a heat exchanger for heating (hot water coil or the like) by an external heat source, the refrigerant vapor is absorbed from the absorbing dilute solution in which the refrigerant is absorbed by the absorber 13 and the concentration of the absorbing liquid is reduced. And a cooling fan 12a that introduces a refrigerant vapor separated from the absorbing dilute solution and cools it with external air. An air-cooled condenser 12 to be condensed and liquefied, and an evaporation which is disposed adjacent to each other in one sealed container 19 and introduces the refrigerant liquid liquefied by the air-cooled condenser 12 and evaporates (vaporizes) under a low pressure. 14 and the absorber 13 for absorbing the refrigerant vapor generated in the evaporator 14 and a part of the absorbed dilute solution discharged from the solution pump 17 (most of the mixture of the concentrated solution and dilute solution) are introduced. Then, the air-cooled cooler 15 having the cooling fan 15a for supercooling this, the high-temperature absorption concentrated solution from the generator 11 and the low-temperature absorption dilute solution from the absorber 13 are mutually heat-exchanged. A solution heat exchanger 16 that raises the temperature of the absorbing dilute solution, and again supplies the generator 11 with the absorber 13 in order to concentrate the absorbing dilute solution that has absorbed the refrigerant vapor and reduced the concentration of the absorbent, and Each of these is 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 employs a solution separation cooling method for absorbing refrigerant vapor from the evaporator 14 by sensible heat of the flowing absorbing solution. In the case of the absorption refrigerator employed, the solution is supercooled by air cooling or other solution cooler (air cooling in the figure), and the absorption heat is removed by sensible heat of the solution. Even if it is increased, there is almost no decrease in performance.

  Therefore, it is possible to increase the supply amount of the absorbing diluted solution to the generator 11.

  Further, the absorber 13 can be made more compact than the direct cooling method in which the inflow solution is directly cooled in the absorber 13 portion 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.

  Moreover, the code | symbol 10 is an example of the inside heat exchanging part 6 of the compressor discharge side refrigerant | coolant piping 5a of the said vapor | steam compression refrigeration machine X similarly to the heat exchanger 7 for the supercooling of the said evaporator 14. A heat exchanger having a double pipe structure in which a part of the heat exchanger 6 is formed and a dilute solution passage 8 is provided on the outer periphery of the heat exchanger 6 is compressed by the compressor 1 of the vapor compression refrigerator X. A heat exchanger for heat recovery of the refrigerant for recovering heat from the absorbed dilute solution supplied from the absorber 13 of the absorption refrigeration machine Y to the generator 11. In the dilute solution passage 8 of the exchanger 10, a part of the absorbed dilute solution whose concentration and temperature are reduced by absorbing the refrigerant vapor by the absorber 13, for example, the absorber 13 outlet pipe before passing through the solution heat exchanger 16 Absorption dilute solution from 24 side is introduced through solution pipes 26 and 26B (branch pipes) Then, after flowing the compressed refrigerant from the downstream side to the entire upstream direction and effectively recovering the heat of the compressed refrigerant discharged from the compressor 1, While flowing into the generator 11 as a single liquid or in a two-layer flow, and causing flashing of the solution in the generator 11, refrigerant vapor is efficiently generated to perform gas-liquid separation, while further vapor compression refrigeration By efficiently cooling the compressed refrigerant on the machine X side, the cooling or supercooling performance in the subsequent supercooling heat exchanger 7 portion of the evaporator 14 is improved, and for the heat radiation on the conventional vapor compression refrigerator side A heat exchanger (corresponding to the third heat source heat exchanger 35 of Patent Document 3) is unnecessary. The refrigerant heat recovery heat exchanger 10 is configured separately from the generator 11.

  On the other hand, in the case of this embodiment, the absorption diluted solution that has been heat-exchanged through the solution heat exchanger 16 and whose temperature has been raised flows directly into the generator 11 through the downstream-side solution pipe 26A.

  As a result, the dilute solution supplied from the outlet of the absorber 13 to the generator 11 side is effectively heat-recovered from a low temperature to a high temperature.

  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.

  Further, in the exhaust heat utilization type absorption refrigerator X that is generally driven by exhaust heat, it is used in a single-effect refrigeration cycle from the viewpoint of cost. The problem is whether to cost.

  In other words, it is difficult to establish an exhaust heat utilization type absorption chiller in terms of the amount of recovered heat unless it is a cheaper device, and a significant reduction in the cost of the generator is an exhaust heat driven absorption refrigeration system. It has been demanded.

  On the other hand, in the case of the configuration as described above, the refrigerant heat recovery heat exchanger 10 portion which is located outside the generator 11 which is the refrigerant vapor generating means and is completely separate from the generator 11. Thus, after the high-temperature compressed refrigerant discharged from the compressor 1 on the vapor compression refrigerator X side is efficiently cooled by the low-temperature absorbing dilute solution supplied from the outlet of the absorber 13 to the generator 11 side, After being supplied to the evaporator of the absorption refrigeration machine Y and cooled or supercooled and thereby the absorption diluted solution is heated to a high temperature state, the outlet side solution pipe 27 of the heat exchanger 10 for recovering refrigerant heat is used. The gas is supplied into the generator 11 through an effective flushing and gas-liquid separation into a refrigerant vapor and an absorption concentrated solution.

  Therefore, according to the same configuration, the heat of the vapor compression refrigeration machine X side compressed refrigerant during cooling operation (all the amount of heat when radiating or condensing) can be effectively used as a drive heat source on the absorption refrigeration machine Y side. As a result, the refrigerating capacity of the absorption refrigerator can be increased accordingly.

  Further, even when there is no external exhaust heat source, a stable absorption refrigeration action can be ensured.

  In particular, the compressed refrigerant on the vapor compression refrigeration machine X side is cooled by the heat deprived to the absorption dilute solution side as described above and the temperature is lowered, and then the refrigerant is further transferred to the evaporator 14 on the absorption refrigeration machine Y side. Supplied and supercooled. Therefore, compared with the case where there is no heat exchanger 10 for recovering refrigerant heat, the compressed refrigerant is more effectively subcooled, and the temperature of the liquid refrigerant supplied to the use side heat exchanger 3 can be effectively reduced. . As a result, the cooling performance of the use side heat exchanger is sufficiently improved.

  As a result, the conventional heat exchanger for heat dissipation of the compressed refrigerant on the vapor compression refrigeration machine X side becomes unnecessary, the absorption refrigeration machine Y side generator is unnecessary, and the generator 11 is also rare. It is only necessary to separate the liquid, and a simple and low-cost configuration is sufficient.

  Further, when the refrigerant before expansion of the vapor compression refrigerator X is supercooled by the evaporator 14 of the absorption refrigerator Y as described above, the evaporator of the absorption refrigerator Y as in the prior art. Compared with the case where the cooling water is circulated through the condenser 14 and supercooled, the evaporation temperature of the refrigerant in the evaporator 14 can be increased.

  As a result, the absorption refrigerator Y can be reduced in size as much as possible, and cold energy can be used effectively.

(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 embodiment, as in the first embodiment, a vapor compression refrigerator and an absorption refrigerator driven by the exhaust heat of the vapor compression refrigerator are externally installed type refrigerants. Combined via a heat recovery heat exchanger, during cooling operation, heat is exchanged between the compressed refrigerant on the compression refrigeration machine side and the diluted diluted solution from the absorption chiller side absorber, and is absorbed by the heat of the compressed refrigerant By increasing the temperature of the absorption diluting solution of the refrigerator and then flowing it into the generator of the absorption refrigerator to drive the absorption refrigerator, the generator part of the absorption refrigerator is simply absorbed and diluted. While it consists of a gas-liquid separator that only needs to separate the refrigerant vapor from the solution, it also improves the cooling performance of the vapor compression refrigerator side compressed refrigerant by cooling the compressed refrigerant of the vapor compression refrigerator , Heat exchange for heat dissipation of compressed refrigerant on the vapor compression refrigerator side And eliminates the need for vessel.

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 8A portion and the downstream 8B portion are divided into two portions along the refrigerant flow direction, and the two absorbing dilute solution passages 8A and 8B are separated by a communication passage 29 having a relatively small diameter. By communicating with each other, two heat exchangers, an upstream heat exchanger 10A and a downstream heat exchanger 10B, are formed, and from the outlet pipe 24 side of the absorber 13 through solution pipes 26 and 26B (branch pipes). A part of the absorption diluted solution before passing through the solution heat exchanger 16 supplied to the generator 11 side is supplied to the downstream end of the absorption diluted solution passage 8B of the downstream heat exchanger 10B, and the downstream absorption diluted solution is supplied. Absorbing diluted solution from the downstream end side of the passage 8B to the upstream side Flowed into the upstream end direction of the road 8A so as to face the flow of the hot vapor compression type refrigerator side compressed refrigerant (CO ₂ refrigerant), and all of the absorbent dilute solution exchanging heat absorption dilute solution through the solution heat exchanger 16 (Remaining absorption dilute solution) is supplied to the downstream end side of the absorption dilute solution passage 8A of the upstream heat exchanger 10A (in the middle of the whole refrigerant heat recovery heat exchanger 10) via the solution pipe 26A. The upstream absorbing dilute solution passage 8A is flowed from the downstream end side to the upstream end direction so as to face the flow of the high-temperature vapor compression refrigerator side compressed refrigerant (CO ₂ refrigerant).

  Thus, the refrigerant heat recovery heat exchanger 10 (specifically, the diluted solution passage 8 portion through which the absorbed diluted solution flows) is divided into the upstream portion 10A (8A) and the downstream portion 10B (8B), While communicating with each other through a communication passage 29 having a reduced passage diameter, the respective absorption dilute solutions before and after the solution heat exchanger 16 are caused to flow into the downstream end portions of the respective passages while taking effective temperature differences step by step. When the absorbing dilute solution is allowed to flow over time, a temperature gradient effective for heat recovery can be secured in each of the passage portions of the downstream heat exchanger 10B (8B) and the upstream heat exchanger 10A (8A). At the same time, the residence time of the absorbed dilute solution in each passage becomes longer, and the heat exchange time with the corresponding downstream heat exchange section 6B and upstream heat exchange section 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. After the absorption dilute solution is supplied into the generator 11 via the solution pipe 27, the generator 11 is flushed efficiently for gas-liquid separation, while the temperature of the vapor compression refrigeration machine X side compressed refrigerant is increased. It is characterized by being effectively lowered and then supplied to the evaporator 14 for more effective supercooling.

  As described above, the refrigerant heat recovery heat exchanger 10 is divided into a plurality of stages from the upstream side to the downstream side where the compressed refrigerant flows, and from the outlet side of the absorber 13 via the solution pipes 24 and 26 and the solution heat exchanger 16. Among the total absorbed diluted solution supplied to the generator 11 side, the absorbed diluted solution before entering the solution heat exchanger 16 is transferred to the refrigerant heat recovery heat exchanger 10B on the downstream side of the compressed refrigerant, and the solution heat When all of the remaining absorbed diluted solution from which the heat of the absorbed concentrated solution from the generator 11 has been recovered through the exchanger 16 is caused to flow into the refrigerant heat recovery heat exchanger 10A on the upstream side of the compressed refrigerant, the solution heat The absorption dilute solution having the lowest temperature that does not pass through the exchanger 16 is heat-recovered throughout the refrigerant heat recovery heat exchangers 10B and 10A from the downstream side to the upstream side of the compressed refrigerant and through the solution heat exchanger 16, and Temperature increased All of the diluted solution can effectively recover the heat of the compressed refrigerant while maintaining the temperature difference effective for heat recovery in the refrigerant heat recovery heat exchanger 10A on the upstream side of the higher-temperature compressed refrigerant. As a result, the degree of heat recovery from the absorbing concentrated solution and the compressed refrigerant is improved, and the temperature of the absorbing dilute solution is further increased, and more effective refrigerant vapor separation effect, absorbing solution concentration effect, and compressed refrigerant cooling effect are achieved. Can be obtained.

  Further, as in the case of the first embodiment, it is possible to reduce the heat exchanger for heat dissipation of the conventional vapor compression refrigerator, and the heat conversion by the absorption refrigerator can be effectively used. The performance of the vapor compression refrigerator is also greatly improved.

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

(Modification)
In addition, with respect to the above configuration, the refrigerant heat recovery heat exchanger 10 has a single unit structure similar to that of the first embodiment, and is provided at the downstream end portion and the intermediate portion (midway) of the dilute solution passage 8. By connecting the downstream sides of the solution pipes 26B and 26A, respectively, the same operation as described above may be obtained.

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

  Also in the case of this embodiment, as in the first embodiment, a vapor compression refrigerator and an absorption refrigerator driven by the exhaust heat of the vapor compression refrigerator are externally installed type refrigerants. Combined via a heat recovery heat exchanger, during cooling operation, heat is exchanged between the compressed refrigerant on the compression refrigeration machine side and the diluted diluted solution from the absorption chiller side absorber, and is absorbed by the heat of the compressed refrigerant The absorption chiller generator is simply absorbed into the absorption chiller generator by driving the absorption chiller by increasing the temperature of the absorption chiller solution of the refrigerator and then flowing it into the generator of the absorption chiller. While it is configured with a gas-liquid separator that only needs to separate the refrigerant vapor from the refrigerant, it also improves the cooling performance of the vapor compression refrigerator side compressed refrigerant by cooling the compressed refrigerant of the vapor compression refrigerator, Do not install a heat exchanger for heat dissipation of the compressed refrigerant on the compression refrigerator side. It has to.

  In that case, as in the case of the second embodiment, the refrigerant heat recovery heat exchanger 10 portion is replaced with the refrigerant on the discharge side of the compressor 1 of the vapor compression refrigerator X as shown in FIG. The heat exchanging part 6 in the middle of the pipe 5a is divided into two parts, an upstream side 6A and a downstream side 6B, and each of the outer peripheral absorption dilute solution passage 8 parts is also divided into two parts 8A and 8B on the upstream side and downstream side. And before the solution heat exchanger 16 is passed from the downstream end of the downstream passage 8B toward the upstream passage 8A from the downstream end of the downstream passage 8B. The solution pipe in the absorbed dilute solution passes through the solution heat exchanger 16 through the solution pipe (branch pipe) 26B and from the downstream end of the upstream passage 8A toward the upstream end of the upstream passage 8A. Directly supplied to the generator 11 via 26A. Via absorption dilute solution solution pipe (branch pipe) 26C excluding supplies respectively, and configured to flow is opposed to the flow of each compressed refrigerant.

  In this way, the refrigerant heat recovery heat exchanger 10 is divided into a plurality of stages from the upstream side to the downstream side where the compressed refrigerant flows, and from the outlet pipe 24 side of the absorber 13 via the solution pipe 26 and the solution heat exchanger 16. Of the absorbed dilute solution supplied to the generator 11 side, the absorbed dilute solution before entering the solution heat exchanger 16 is used for refrigerant heat recovery at the downstream side of the compressed refrigerant through the solution pipe (branch pipe) 26B. A part of the absorbed dilute solution obtained by recovering the heat of the absorbed concentrated solution from the generator 11 through the solution heat exchanger 16 through the heat exchanger 10B is passed through a solution pipe (branch pipe) 26C to the refrigerant on the upstream side of the compressed refrigerant. When each of the heat recovery heat exchangers 10A is allowed to flow, the absorption dilute solution having the lowest temperature that does not pass through the solution heat exchanger 16 is upstream from the downstream side of the compressed refrigerant, as in the second embodiment. Heat exchanger for recovering refrigerant heat up to 1 B, 10A as a whole, and heat recovery through the solution heat exchanger 16, and a part of the remaining absorbed dilute solution having a relatively high temperature is used for heat exchange for refrigerant heat recovery upstream of the higher-temperature compressed refrigerant. Since the heat of the compressed refrigerant can be effectively recovered while maintaining the temperature difference effective for heat recovery in each of the vessels 10A, the degree of heat recovery from the concentrated concentrated solution and the compressed refrigerant is improved, and the absorption rare The temperature of the solution is increased, and more effective refrigerant vapor separation effect, absorption solution concentration effect, and compressed refrigerant cooling effect can be obtained.

  Further, as in the case of the first embodiment, it is possible to reduce the heat exchanger for heat dissipation of the conventional vapor compression refrigerator, and it is possible to effectively use the cold heat conversion by the absorption refrigerator.

  Of course, in this configuration, not all of the absorbed dilute solution supplied from the outlet pipe 24 side of the absorber 13 to the generator 11 side via the solution pipe 26 is heated by the heat of the compressed refrigerant. Since the absorption dilute solution supplied to the generator 11 as it is through the heat exchanger 16 is heat-exchanged once with the absorption concentrated solution and sufficiently heated, when entering the generator 11, it is almost the embodiment. The effect which contributes to concentration of an absorption liquid can be acquired like 2 things.

  The configuration of the other parts is exactly the same as that of the first and second embodiments, and provides the same operational effects.

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

  Also in the case of this embodiment, as in the first, second, and third embodiments, the vapor compression refrigerator and the absorption refrigerator driven by the exhaust heat of the vapor compression refrigerator are used as refrigerant. Combined via a heat recovery heat exchanger, during cooling operation, heat is exchanged between the compressed refrigerant on the compression refrigeration machine side and the diluted diluted solution from the absorption chiller side absorber, and is absorbed by the heat of the compressed refrigerant The refrigerant vapor generator of the absorption refrigeration machine is driven by driving the absorption chiller by increasing the temperature of the absorption diluted solution of the refrigeration refrigerator and then flowing it into the refrigerant vapor generation part of the absorption chiller. While a gas-liquid separator capable of separating the refrigerant vapor from the absorbed dilute solution is sufficient, the refrigeration performance on the side of the vapor compression refrigerator is thereby reduced by cooling the compressed refrigerant of the vapor compression refrigerator. Improved heat exchange for heat dissipation of the compressed refrigerant on the vapor compression refrigerator side And eliminates the need for vessel.

In this case, in the fourth embodiment, a plurality of the vapor compression refrigeration machines X are provided for X ₁ and X ₂ , and the same refrigerant heat recovery heat exchangers 10, 10. In addition, it is characterized in that it is configured in combination with one absorption refrigerator Y similar to each embodiment (however, in the configuration of FIG. Example when applied to Form 1).

  According to such a configuration, the effects of the configurations of the above-described first to third embodiments can be obtained, and the amount of exhaust heat of the vapor compression refrigeration machine X-side compressed refrigerant greatly increases. The driving capacity on the absorption refrigerator Y side can be greatly increased, and the performance is further improved.

1 is a compressor, 2 is an expansion valve, 3 is a use side heat exchanger, 4 is an accumulator, 5a and 5b are refrigerant pipes of a vapor compression refrigerator side refrigeration circuit, 6 (6A, 6B) is a heat exchange section, 7 Is the heat exchanger of the evaporator, 8 (8A, 8B) is the dilute solution passage of the heat exchanger for refrigerant heat recovery, 10 (10A, 10B) is the heat exchanger for refrigerant heat recovery, 11 is the generator, 12 is air-cooled Condenser, 13 absorber, 14 evaporator, 15 air-cooled cooler, 17 solution pump, 18 absorber plate, X (X ₁ , X ₂ ) is a vapor compression refrigerator, Y is an absorption type It is a refrigerator.

Claims (8)

  A refrigeration apparatus comprising a vapor compression refrigerator and an absorption refrigerator driven by exhaust heat of the vapor compression refrigerator, wherein the absorption of heat of the refrigerant after compression of the vapor compression refrigerator A refrigerant heat recovery heat exchanger that recovers with an absorption dilute solution of the refrigerator type refrigerator is provided, and the absorption dilute solution that has recovered the heat of the compressed refrigerant by the refrigerant heat recovery heat exchanger is contained in the generator of the absorption refrigerator. The absorption refrigeration generator generator is a gas-liquid separator that only separates the refrigerant vapor from the absorbed diluted solution, while separating the refrigerant vapor. A refrigeration apparatus characterized by improving the refrigeration performance of the vapor compression refrigerator by cooling or supercooling the compressed refrigerant.   An absorption liquid supercooler that supercools the absorption liquid flowing into the absorber and a solution heat exchanger that exchanges heat between the absorption diluted solution supplied from the absorber to the generator and the absorption 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 supercooler, the solution heat exchanger, and the refrigerant heat recovery heat exchanger. 2. The refrigeration apparatus according to claim 1, wherein the refrigerant vapor is absorbed by the absorption liquid by the sensible heat of the absorption liquid that has flowed in 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 the solution is exchanged from the absorber to the generator through the solution heat exchanger to the solution heat exchanger. The absorbed dilute solution before entering the refrigerant heat recovery heat exchanger at the downstream side of the compressed refrigerant, and the absorbed dilute solution exiting the solution heat exchanger into the refrigerant heat recovery heat exchanger at the upstream side of the compressed refrigerant. The refrigeration apparatus according to claim 2, wherein each of the refrigeration apparatuses is allowed to flow.   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 the solution is exchanged from the absorber to the generator through the solution heat exchanger to the solution heat exchanger. The absorbed diluted solution before entering the refrigerant heat recovery heat exchanger in the downstream stage of the compressed refrigerant, and the absorbed diluted solution exiting the solution heat exchanger is used as the heat for recovering the refrigerant heat upstream of the generator and the compressed refrigerant upstream. 3. The refrigeration apparatus according to claim 2, wherein each of the refrigeration apparatuses flows into the exchanger.   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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