JP2009052811A - Waste heat driven absorption refrigeration system - Google Patents

Abstract

An exhaust heat drive type absorption refrigeration apparatus adopting an indirect cooling method capable of easily and inexpensively controlling the refrigeration capacity is provided.
The absorber part A is made into a liquid film flow-down type absorber A with a plate that can be easily integrated with the plate type evaporator E, so that the absorber A is housed in an integral casing together with the evaporator E. , By mixing the unevaporated refrigerant in the evaporator E in the dilute solution pool below the absorber A, the solution concentration is prevented from greatly changing due to the increase or decrease in the amount of refrigerant generated in the generator G, and the absorber The refrigeration capacity is controlled by increasing or decreasing the capacity to absorb the refrigerant vapor in the absorber A by changing the supercooling temperature or flow rate of the absorption solution supercooled by the inflowing supercooler H2.
[Selection] Figure 1

Description

  The present invention relates to a configuration of an exhaust heat drive type absorption refrigeration apparatus adopting an indirect air cooling system.

  In the absorber of the conventional air-cooled absorption refrigeration apparatus, the absorber is composed of a plurality of heat transfer tubes provided with a large number of heat transfer fins and an absorption solution distribution tray, and the absorber is provided via a solution pump provided in the solution circulation path. The absorption solution is allowed to flow through the wall surface of the heat transfer tube, and the refrigerant vapor from the evaporator flows through the refrigerant vapor passage in the heat transfer tube and is absorbed by the absorption solution while the absorption solution is cooled by the fan around the heat transfer tube. A direct air cooling method using air cooling fins cooled by wind was adopted. Further, the generator is of a type in which the solution is heated by a burner (see, for example, Patent Document 1).

  In such a direct air cooling generator, the temperature of the cooled fluid on the outlet side of the evaporator (or the temperature difference between the outlet side and the inlet side) is detected as a method for controlling the refrigerating capacity of the refrigerator. Then, determine the load of the refrigerator, and increase or decrease the amount of heat for heating the solution on the generator side (for example, by increasing or decreasing the combustion amount of the burner) so that the refrigeration capacity is commensurate with the load It was common to control by.

  On the other hand, recently, from the viewpoint of effectively utilizing exhaust heat energy, an exhaust heat drive type air-cooled absorption refrigeration apparatus in which a generator is driven by exhaust water or exhaust gas such as a small generator or GHP has come to be provided. ing.

  Therefore, an attempt has been made to save energy by combining the above-described exhaust heat driven generator with the direct air-cooling absorption refrigeration apparatus employing the above-described refrigeration capacity control method.

  FIG. 5 shows an example of a direct air cooling type exhaust heat drive type absorption refrigeration apparatus configured as described above.

That is, in the refrigeration cycle of the absorption refrigeration apparatus of FIG. 5, the refrigerant absorption capacity of an aqueous solution (hereinafter simply referred to as a dilute solution) of an absorbent (for example, LiBr) excellent in the capacity to absorb the refrigerant (for example, water) is enhanced. The generator G for heating and concentrating the solution with a heating medium (waste water or exhaust gas from a small generator or GHP) and the vapor (refrigerant) separated from the solution in the generator G are introduced. A condenser C that is liquefied by cooling it, an evaporator E that introduces a refrigerant liquefied by the condenser C and evaporates under low pressure, and absorbs vapor (refrigerant) generated in the evaporator E An absorber A for introducing a concentrated solution concentrated in the generator G in order to maintain a low pressure state, and a solution (dilute solution) diluted by absorbing vapor (refrigerant) in the absorber A Again from above to concentrate A solution pump P ₁ for pumping the vessel G, the evaporator E coolant pump P ₂ to the refrigerant greeted the bottom of the refrigerant stays 10 to supply circulation to the upper side tray portion of the evaporator E, for heat efficiency A solution heat exchanger (concentrated solution heat exchanger 2a, dilute solution heat) that exchanges heat between a part of the dilute solution exiting from the absorber A (diluted solution supplied to the generator G) and the concentrated solution exiting from the generator G 2b) H, a cooling fan F _{1 for} cooling the condenser C with air, and a cooling fan F _{2 for} cooling the absorber A with air.

The absorber main body 80 of the absorber A includes a plurality of heat transfer tubes 81, 81... Having a plurality of heat transfer fins 83, 83... And an absorbing solution distribution tray (distribution port) 84, 84. .. in the heat transfer tubes 81, 81... Via the solution pump P ₁ provided in the solution circulation path connecting the absorber A, the solution heat exchanger H ₁ , and the generator G. While the absorbing solution flows through the pipe wall surfaces of the refrigerant vapor passages 82, 82,..., The evaporator B side passes through the refrigerant passage 11 to the refrigerant vapor passages 82, 82. The cooling vapor from the cooling fan F _{2 on} the outer periphery of the heat transfer tubes 81, 81 is passed through the air-cooling fins 83, 83. It is designed to cool directly.

  On the other hand, a temperature sensor 6 that detects the temperature of the fluid to be cooled (for example, cold water) is provided at the outlet portion of the fluid to be cooled (for example, cold water) in the cooling heat exchanger 7 of the evaporator E. A flow rate adjusting valve 13 whose valve opening degree is automatically adjusted by a microcomputer-controlled flow rate controller 5 is provided at the inlet portion of the heating fluid (waste hot water or exhaust gas) of the heat exchanger 1 for heating of the generator G. Yes.

  Then, the load of the refrigerator is determined by the temperature of the fluid to be cooled on the outlet side of the evaporator E detected by the temperature sensor 6, and the flow rate controller 5 controls the generator G side so as to have a refrigeration capacity corresponding to the load. The amount of heat for heating the solution in the generator G is increased or decreased by operating the flow rate control valve 13 to increase or decrease the inflow amount (input heat amount) of the generator G side heating fluid.

  However, in such a direct air-cooled absorber A, it is important to expand the gas-liquid interface for simultaneously absorbing the refrigerant vapor and cooling the absorbing solution. In particular, the space between the upper and lower absorber headers including the absorbent solution distribution tray, the use of large-diameter heat transfer tubes to take into account the vapor pressure loss, and the restriction of the flow rate of the refrigerant vapor make the connection tube to the evaporator considerably thicker. Become.

  Moreover, since there are many connection parts by welding also in terms of cost, it is expensive for a small machine.

  In contrast, the absorption solution flowing into the absorber is supercooled with an air-cooled cooler (or water-cooled cooler) and the refrigerant vapor is simply absorbed in the absorber, so that the absorbed heat due to the absorption action is supercooled. There is an indirect air cooling (solution separation cooling) system in which the solution is simply removed by sensible heat (see, for example, Patent Document 2). Therefore, it is advantageous to construct a small air-cooled absorption refrigeration apparatus.

  In addition, even if the amount of solution supplied to the generator is increased, the performance is hardly deteriorated as compared with the conventional air-cooled absorber (in the conventional air-cooled absorber, the increase in the amount of solution supplied to the generator is the solution circulation As the amount increases, the absorber inlet solution concentration decreases and the absorption capacity decreases, so the performance is greatly reduced).

  Therefore, for example, in the absorber A in the configuration of FIG. 5, the solution flowing into the absorber is supercooled by an air-cooled supercooler (or a water-cooled supercooler), and the refrigerant A simply absorbs the refrigerant vapor. In this case, the absorption heat by the absorption action is of the indirect air cooling system in which the sensible heat of the supercooled solution is removed, and the refrigeration capacity of the heat exchanger 1 for heating of the generator G is as shown in the figure. It can be considered that the system is controlled by adjusting the inflow amount of the heating fluid through the flow rate adjusting valve 13 provided at the heating fluid inlet.

JP-A-10-122702 JP-A-7-98163

  By the way, in the case of the absorption refrigeration apparatus of the past indirect air cooling system, the refrigeration cycle is a double effect cycle, and the generator is of a system in which the solution is heated by a burner (for example, the specification of Patent Document 2) (See description of paragraph [0009]).

  However, in the above-described exhaust heat drive type absorption refrigeration system, the amount and temperature of exhaust heat such as exhaust hot water are completely external factors, and the heating amount of the generator is controlled as in the conventional example. Adopting a method for controlling the refrigeration capacity by increasing or decreasing the amount of refrigerant generated in this way is not as simple as in the case of the burner described above, because it directly controls the supply state of exhaust heat that fluctuates due to external factors.

  In particular, controlling the increase / decrease of the exhaust heat exhausted from the external exhaust heat source only for the user side equipment that uses the exhaust heat, or stopping the exhaust also has an effect on the exhaust heat source. It is large and it is often difficult to provide such an adjustment function except in an emergency.

  In addition, when exhaust gas is used as a driving source instead of exhaust hot water, it is conceivable to provide an exhaust gas bypass flow path so that the generator and the exhaust gas bypass flow path are switched by a damper or the like. In this case, there is a new problem such as how to secure the sealing property in consideration of expansion of the damper due to the temperature of the exhaust gas and heat insulation (heat insulation).

  Accordingly, in the exhaust heat drive type absorption refrigeration apparatus, how to control the input of the exhaust heat amount is an important issue.

  The present invention has been made in response to such a problem. By mixing the unevaporated refrigerant in the evaporator in the dilute solution reservoir in the lower part of the absorber, the solution concentration can be increased or decreased by the amount of refrigerant generated in the generator. By changing the supercooling temperature or flow rate of the absorbing solution flowing into the absorber, and controlling the increase / decrease of the absorber's ability to absorb refrigerant vapor, the refrigeration capacity can be easily and inexpensively changed. It is an object of the present invention to provide an exhaust heat drive type absorption refrigeration apparatus that employs an indirect cooling system that can control the temperature.

  In order to achieve the same object, the present invention is configured with the following problem solving means.

(1) First Problem Solving Means The first problem solving means of the present invention is that the absorption heat generated in the absorber is supercooled with the absorbing solution flowing into the absorber via the solution pump, thereby revealing the solution. It comprises a supercooling means for removing by heat, and a generator for generating refrigerant vapor and an absorbed concentrated solution by heating the diluted absorption solution supplied from the absorber with a predetermined exhaust heat from an external exhaust heat source. It is an exhaust heat drive type absorption refrigeration system adopting an indirect cooling system, and the absorber part is housed in an integral casing together with the evaporator by using a liquid film flow-down type absorber with a plate, By mixing the non-evaporated refrigerant with the dilute solution in the dilute solution reservoir at the lower part of the absorber, the solution concentration is prevented from changing greatly due to the increase or decrease in the amount of refrigerant generated in the generator, and at the same time the It is characterized in that so as to increase or decrease control the ability to absorb refrigerant vapor by changing the supercooled temperature or flow rate of the solution.

  According to such a configuration, it is necessary to increase / decrease the amount of exhaust heat to increase / decrease the amount of heating to the generator for the equipment side that simply uses the exhaust heat, or to stop the supply of exhaust heat to stop heating. Therefore, instead of these expensive devices, the refrigeration capacity of the exhaust heat drive type absorption refrigeration apparatus can be appropriately controlled with a simple and inexpensive device.

(2) Second Problem Solving Means According to a second problem solving means of the present invention, in the configuration of the first problem solving means, the driving state of the cooling fan for supercooling the absorbing solution flowing into the absorber is set. By changing the temperature, the temperature of the supercooled solution flowing into the absorber is changed to increase / decrease the refrigerant vapor absorption capacity of the absorber.

  Thus, if the driving state of the cooling fan for supercooling the absorbing solution flowing into the absorber, for example, the rotational speed is made variable, the temperature of the supercooling solution flowing into the absorber can be easily changed. Therefore, the refrigerant vapor absorption capacity of the absorber, and consequently the final refrigeration capacity, can be appropriately controlled.

  Accordingly, even with such a configuration, the amount of exhaust heat for increasing / decreasing the amount of heating to the generator simply for the equipment side that uses exhaust heat, and the supply of exhaust heat for stopping heating are stopped. It becomes unnecessary, and it becomes possible to control the refrigeration capacity of the exhaust heat driven refrigerator with a simple and inexpensive device instead of these expensive devices.

(3) Third Problem Solving Means According to a third problem solving means of the present invention, in the configuration of the first problem solving means, there is provided a flow rate varying means for changing the flow rate of the supercooled solution flowing into the absorber. It is provided on the inlet side or the outlet side of the supercooling means, and the refrigerant vapor absorption capacity of the absorber is controlled to increase or decrease by changing the flow rate of the supercooled solution flowing into the absorber.

  Thus, if the amount of the supercooled supercooled solution flowing into the absorber is made variable, the temperature of the supercooled solution flowing into the absorber and the amount of heat of supercooling can be easily changed, and the absorption It is possible to control the refrigerant vapor absorption capacity and thus the final refrigeration capacity.

  Accordingly, even with such a configuration, the amount of exhaust heat for increasing / decreasing the amount of heating to the generator simply for the equipment side that uses exhaust heat, and the supply of exhaust heat for stopping heating are stopped. It becomes unnecessary, and it becomes possible to control the refrigeration capacity of the exhaust heat driven refrigerator with a simple and inexpensive device instead of these expensive devices.

(4) Fourth Problem Solving Means According to a fourth problem solving means of the present invention, in the configuration of the first or second problem solving means, a diluted solution from an absorber that has absorbed refrigerant vapor and a generator are provided. By generating refrigerant vapor and mixing the concentrated solution whose temperature has decreased in the solution heat exchanger on the upstream side of the solution pump, by increasing or decreasing the solution discharge flow rate of the solution pump that sucks and discharges the mixed solution, It is characterized in that the refrigerant vapor absorption capacity of the absorber is controlled to increase or decrease by changing the flow rate of the supercooled solution flowing into the absorber.

  Thus, if the flow rate of the supercooled solution flowing into the absorber is varied by increasing or decreasing the solution discharge flow rate of the solution pump that sucks and discharges the mixed solution of the dilute solution and the concentrated solution, the absorber It is possible to easily change the temperature of the supercooled solution flowing into the heat exchanger and the amount of heat of supercooling, and it is possible to control the refrigerant vapor absorption capacity of the absorber, and thus the final refrigeration capacity.

  Therefore, even with such a configuration, the amount of exhaust heat to increase or decrease the amount of heating to the generator for the device side that simply uses exhaust heat, or the supply of exhaust heat to stop heating is stopped. It becomes unnecessary, and it becomes possible to control the refrigeration capacity of the exhaust heat driven refrigerator with a simple and inexpensive device instead of these expensive devices.

(5) Fifth Problem Solving Means According to a fifth problem solving means of the present invention, in the configuration of the first, second, third or fourth problem solving means, a refrigerant reservoir is provided at the lower part of the evaporator. Instead, all of the unevaporated refrigerant is mixed with the dilute solution by the evaporator in the dilute solution stay at the lower part of the absorber that has absorbed the refrigerant vapor.

  As described above, the absorber part is made into a liquid film flow-down type absorber using a plate so that it is housed in an integral casing together with the evaporator, while the unevaporated refrigerant in the evaporator is stored in a dilute solution reservoir below the absorber. Mixing with dilute solution absorbs all of the unevaporated refrigerant without providing a refrigerant pool on the evaporator side, in order to prevent the solution concentration from changing significantly due to increase or decrease in the amount of refrigerant generated in the generator. When it is introduced to the dilute solution residue at the bottom of the vessel and mixed with the dilute solution, the increase or decrease in the amount of refrigerant generated by the increase or decrease in the amount of exhaust heat, Even if a large amount of non-evaporated refrigerant is generated without being matched, the solution concentration is supplied to the generator side again by the solution pump in the mixed state, so that the solution concentration is constant and a stable absorption cycle can be continued.

  Therefore, in this case, the refrigerant pump and the refrigerant circulation path on the evaporator side can be eliminated, which is more effective for downsizing and cost reduction of the apparatus.

(6) Sixth Problem Solving Means According to a sixth problem solving means of the present invention, in the configuration of the first, second, third, or fourth problem solving means, a fixed volume of refrigerant remains in the lower part of the evaporator. It is characterized in that only a certain amount of non-evaporated refrigerant is accumulated in the refrigerant residue, and the remaining refrigerant is mixed with the dilute solution in the dilute solution residue below the absorber.

  As described above, the absorber part is made into a liquid film flow-down type absorber using a plate so that it is housed in an integral casing together with the evaporator, while the unevaporated refrigerant in the evaporator is stored in a dilute solution reservoir below the absorber. When mixing with a dilute solution, to prevent the solution concentration from changing significantly due to the increase or decrease in the amount of refrigerant generated in the generator, a fixed volume of refrigerant is also provided on the evaporator side. When a certain amount of non-evaporated refrigerant is supplied, it is mixed with the dilute solution on the dilute solution side, while a certain amount of non-evaporated refrigerant is circulated on the evaporator side by a refrigerant pump. The structure of the evaporator can be simplified as compared with the case of the refrigerant supply method.

(Best Embodiment 1)
FIG. 1 shows the configuration of an exhaust heat drive type absorption refrigeration apparatus employing an indirect air cooling system (solution separation cooling system) according to the best embodiment 1 of the present invention.

The refrigeration cycle of this absorption refrigeration apparatus is designed to increase the refrigerant absorption capacity of an aqueous solution (hereinafter simply referred to as a dilute solution) of an absorbent (for example, LiBr) having an excellent ability to absorb a refrigerant (for example, water). Liquefaction is achieved by introducing a generator G for heating and concentrating with a heating medium (for example, exhaust water from a small generator or GHP), and steam (refrigerant) separated from the solution in the generator G and cooling it. A condenser C to be generated, an evaporator E which introduces a refrigerant liquefied by the condenser C and evaporates (vaporizes) under a low pressure, and the above-mentioned generation to absorb the vapor (refrigerant) generated in the evaporator E An absorber A for introducing the concentrated solution concentrated in the vessel G, a dilute solution diluted by absorbing the vapor (refrigerant) in the absorber A, and a solution heat exchanger H ₁ described later are supplied. Concentrated solution from generator G and Mixture below the subcooler H ₂ side and the solution pump P for pumping into the generator G side, we are introduced a part (most) of the mixed solution discharged from the solution pump P Subcooler (air-cooled heat exchanger) H ₂ to be supplied to the absorber A after being supercooled, a part of the mixed solution from the solution pump P (mixed solution supplied to the generator G) and the generation A solution heat exchanger H ₁ for exchanging heat with the concentrated solution refluxed from the condenser G to the upstream side of the solution pump P, a cooling fan F ₁ for air-cooling the condenser C, and the subcooler H _2. And a cooling fan F ₂ for cooling the air.

Then, the liquid mixture discharged from the solution pump P is diverted at a predetermined diversion ratio set in advance to the supercooler H ₂ side and the generator G side.

The diversion ratio between them is, for example, set to 1 on the generator G side and 8 on the subcooler H ₂ side, and the mixed liquid is diverted at a ratio of about 1: 8.

In the case of this embodiment, the LiBr absorption solution entering the absorber A as described above is supercooled by the air-cooled supercooler H ₂ provided with the cooling fan F ₂ , and the absorber arranged in parallel with the evaporator E. In A, an indirect air cooling (solution separation cooling) system is adopted in which only the refrigerant vapor evaporated by the evaporator E is absorbed, and the absorption heat generated during absorption is removed by the sensible heat of the supercooled absorption solution. Yes.

  The evaporator E and the absorber A are housed in the same casing 3, and a refrigerant distribution tray and an absorption solution distribution tray for evenly distributing, for example, a refrigerant and an absorption solution are provided in the upper part of each of them. (Not shown). The cooling heat exchanger 7 of the evaporator E is, for example, a plate-type heat exchanger in which a cooled body passage for flowing cold water or the like is formed inside, and the refrigerant is allowed to flow down on the surface in a liquid film to evaporate. The heat exchange section 8 of the absorber A is, for example, a plate type in which a heat transfer plate is bent into a corrugated structure and arranged on both sides of each heat transfer plate. By allowing the solution to flow vertically in a liquid film state, absorption of refrigerant vapor is more effectively promoted.

  As described above, when the heat exchanger 7 of the evaporator E is of a plate type, while it is of a liquid film flow type with a plate that can be easily integrated with the absorber A and the evaporator E, the evaporator E as shown in the figure. And the absorber A can be combined and integrated into the same casing 3, and a simple, compact and inexpensive evaporator-integrated air-cooled absorber can be provided.

And in the case of this embodiment, without providing a refrigerant retainer in the lower part of the evaporator E in particular, the non-evaporated refrigerant in the evaporator E is allowed to flow as it is toward the dilute solution reservoir 12 side in the lower part of the absorber A, By mixing with the absorbing dilute solution at the portion 12 of the dilute solution and supplying it to the solution pump P, it is possible to prevent the concentration of the solution from greatly changing due to increase or decrease in the amount of refrigerant generated on the generator G side. In addition, as control of the refrigeration capacity, the absorption solution to the absorber A is further supercooled according to the temperature detected by the temperature sensor 6 that detects the temperature of the cold water outlet side of the evaporation heat exchanger 7 of the evaporator E. cooling fan F ₂ of the driving state of the subcooler H ₂ cooled with air, for example by varying the number of revolutions, the absorber a by varying the supercooling temperature of the absorbent solution flowing in the absorber a Refrigerant vapor in The refrigerating capacity is appropriately controlled by appropriately increasing or decreasing the capacity to absorb.

  According to such a configuration, the exhaust heat source side exhaust heat amount increase / decrease control for increasing / decreasing the heating amount of the generator G, the exhaust heat supply stop, etc. for the equipment side (refrigeration apparatus side) that simply uses exhaust heat, etc. It is possible to effectively control the refrigerating capacity with simple and inexpensive equipment only on the use side instead of these expensive equipment.

Further, in the same configuration, as described above, the absorption solution is supercooled by the supercooler H ₂ and the indirect air cooling method (solution separation cooling method) is used to remove the heat of absorption by the sensible heat of the solution. Even when the amount of the solution supplied is increased, the performance hardly deteriorates as compared with the conventional air-cooled absorber.

  Further, in the above configuration, the refrigerant E is not provided in the lower part of the evaporator E, and all the refrigerant that has not evaporated in the evaporator E is removed by the dilute solution holder 12 in the lower part of the absorber A that has absorbed the refrigerant vapor. Mix with dilute solution.

  In such a case, since the diluted solution in the same refrigerant mixed state is supplied again to the absorber A side by the solution pump P, an absorption action on the absorber A side is realized.

  Therefore, in this case, the conventional refrigerant pump and refrigerant circuit on the evaporator E side can be dispensed with, which is more effective for downsizing and cost reduction of the apparatus.

  In the above configuration, the concentrated solution after the heat exchange from the generator G is mixed with the diluted solution (refrigerant mixture) from the absorber A on the upstream side of the solution pump P. The dedicated pump is not required and the discharge head of the solution pump P is reduced, so that the power consumption can be reduced (in the conventional indirect air cooling method, the concentrated solution and the absorber from the generator). The dilute solution is mixed on the downstream side of the solution pump and requires a jet pump or the like).

(Best Mode 2)
Next, FIG. 2 shows a configuration of an exhaust heat drive type absorption refrigeration apparatus adopting an indirect cooling method according to the best embodiment 2 of the present invention.

Also in this embodiment, the LiBr absorption solution entering the absorber A is supercooled by an air-cooled supercooler H ₂ equipped with a cooling fan F ₂ and evaporated as in the best embodiment 1 described above. Indirect air cooling in which the absorption heat generated during absorption is removed by the sensible heat of the supercooled absorption solution only by absorbing the refrigerant vapor evaporated in the evaporator E in the absorber A arranged in parallel with the vessel E ( Solution separation cooling method is adopted.

  Similarly, the heat exchanger 7 of the evaporator E is of a plate type, whereas the absorber A and the evaporator E are absorbed by the liquid film flow-down type using a plate that can be easily integrated with the evaporator A. The device A can be combined and integrated in the same casing 3, and a compact and inexpensive air-cooled absorber can be provided.

  Then, without providing a refrigerant stay in the lower part of the evaporator E, all of the unevaporated refrigerant on the evaporator E side is caused to flow to the dilute solution reservoir 12 side in the lower part of the absorber A, so that By mixing with the absorbing solution, the concentration of the refrigerant generated in the generator G is prevented from greatly changing due to the increase or decrease in the amount of refrigerant, and the operation is exactly the same as in the first embodiment. Is obtained.

However, in the case of this embodiment, with respect to the control of the refrigerating capacity described above, instead of changing the supercooling temperature of the absorbing solution flowing into the absorber A as in the first embodiment, the absorbing solution is changed. A first flow rate adjusting valve 4 for adjusting the flow rate of the absorbing solution itself is provided on the inlet side of the subcooler H _{2 to be} supercooled, and the temperature of the cold water outlet side of the evaporation heat exchanger 7 of the evaporator E is detected. The flow rate of the absorbing solution flowing into the absorber A (the flow rate of the supercooled absorbing solution flowing into the absorber A) by varying the opening degree of the first flow rate adjusting valve 4 according to the temperature detected by the temperature sensor 6. The refrigeration capacity is controlled by increasing or decreasing the capacity to absorb the refrigerant vapor in the absorber A by changing.

  Even with such a configuration, the exhaust heat amount increase / decrease control for increasing / decreasing the heating amount of the generator G, the exhaust heat supply stop, etc. are also performed for the equipment side (refrigeration apparatus side) that simply uses the exhaust heat. In addition to being unnecessary, it is possible to effectively control the refrigerating capacity with a simple and inexpensive device on the use side instead of these expensive devices.

In the same configuration, the solution is supplied to the generator G because of the indirect air cooling method (solution separation cooling method) in which the solution is supercooled by the supercooler H ₂ and the absorbed heat is removed by sensible heat of the solution as described above. Even if the amount is increased, the performance hardly deteriorates as compared with the conventional air-cooled absorber.

  Further, in the same configuration, the concentrated solution from the generator G is mixed with the diluted solution from the absorber A on the upstream side of the solution pump P, so that a dedicated pump such as a liquid jet pump need not be used.

(Best Mode 3)
Next, FIG. 3 shows a configuration of an exhaust heat drive type absorption refrigeration apparatus adopting an indirect cooling method according to the third preferred embodiment of the present invention.

Also in this embodiment, the LiBr absorption solution entering the absorber A is supercooled by an air-cooled supercooler H ₂ equipped with a cooling fan F ₂ and evaporated as in the best embodiment 1 described above. By absorbing the refrigerant vapor evaporated by the evaporator E in the absorber A arranged in parallel with the container E, the absorption heat generated at the time of absorption is indirectly cooled by the sensible heat of the supercooled absorption solution. Indirect air cooling (solution separation cooling) system is used.

  Similarly, the heat exchanger 7 of the evaporator E is of a plate type, whereas the absorber A and the evaporator E are absorbed by the liquid film flow-down type using a plate that can be easily integrated with the evaporator A. The device A can be combined and integrated in the same casing 3, and a compact and inexpensive air-cooled absorber can be provided.

In this embodiment, a refrigerant pool 10 is provided at the lower part of the evaporator E, and the unevaporated refrigerant on the evaporator E side overflowing from the refrigerant pool 10 is flowed to the dilute solution pool 12 side at the lower part of the absorber A. Then, by mixing with the absorbing solution in the dilute solution residue 12 portion, it is possible to prevent the solution concentration from greatly changing due to the increase or decrease in the amount of refrigerant generated in the generator G, and to control the refrigeration capacity described above. relates, instead of changing the supercooling temperature of the absorbent solution flowing into the absorber a as in the above-described first embodiment, the flow rate of the absorbing solution absorption solution on the outlet side of the subcooler H ₂ supercooling A second flow rate adjusting valve 9 for adjusting is provided, and the second flow rate adjusting valve 9 is opened according to the detected temperature of the temperature sensor 6 for detecting the temperature of the cold water outlet side of the evaporating heat exchanger 7 of the evaporator E. The flow rate of the absorbing solution flowing into the absorber A (the absorber A By increasing or decreasing the ability to absorb the refrigerant vapor in the absorber by changing the flow rate) of the sub-cooled absorbent solution flows, is characterized in that so as to control the refrigerating capacity.

  Even with such a configuration, the exhaust heat amount increase / decrease control for increasing / decreasing the heating amount of the generator G, the exhaust heat supply stop, etc. are also performed for the equipment side (refrigeration apparatus side) that simply uses the exhaust heat. In addition to being unnecessary, it is possible to effectively control the refrigerating capacity with a simple and inexpensive device on the use side instead of these expensive devices.

In the same configuration, the solution is supplied to the generator G because of the indirect air cooling method (solution separation cooling method) in which the solution is supercooled by the supercooler H ₂ and the absorbed heat is removed by sensible heat of the solution as described above. Even if the amount is increased, the performance hardly deteriorates as compared with the conventional air-cooled absorber.

  Further, in the same configuration, the concentrated solution from the generator G is mixed with the diluted solution from the absorber A on the upstream side of the solution pump P, so that a dedicated pump such as a liquid jet pump need not be used.

In the case of the third embodiment, the refrigerant from the condenser C is not directly supplied to the upper portion of the evaporator E as in the first and second embodiments, but for example, as shown in FIG. A refrigerant retainer 10 is provided at the bottom of the evaporator E side to supply the refrigerant, and the refrigerant remaining in the refrigerant retainer 10 is supplied to the upper part of the evaporation heat exchanger 7 of the evaporator E via the refrigerant pump P _2. The continuous supply is performed in a circulating state, and the structure of the evaporator is simplified as compared with the temporary ones as in the first and second embodiments.

  Only the unevaporated refrigerant overflowing from the refrigerant residue 10 is supplied to the solution residue 12 on the absorber A side and mixed with the absorbing solution.

(Fourth Embodiment)
Next, FIG. 4 shows a configuration of an exhaust heat drive type absorption refrigeration apparatus employing an indirect cooling method according to the best embodiment 4 of the present invention.

Also in this embodiment, the LiBr absorption solution entering the absorber A is supercooled by an air-cooled supercooler H ₂ equipped with a cooling fan F ₂ and evaporated as in the best embodiment 1 described above. By absorbing the refrigerant vapor evaporated by the evaporator E in the absorber A arranged in parallel with the container E, the absorption heat generated at the time of absorption is indirectly cooled by the sensible heat of the supercooled absorption solution. Indirect air cooling (solution separation cooling) system is used.

  Similarly, the heat exchanger 7 of the evaporator E is of a plate type, whereas the absorber A and the evaporator E are absorbed by the liquid film flow-down type using a plate that can be easily integrated with the evaporator A. The device A can be combined and integrated in the same casing 3, and a compact and inexpensive air-cooled absorber can be provided.

As in the case of the first and second embodiments, all of the unevaporated refrigerant on the evaporator E side is supplied to the dilute solution reservoir 12 side on the lower side of the absorber A without providing the refrigerant retainer 10 on the lower part of the evaporator E. In order to prevent the solution concentration from greatly changing due to the increase or decrease in the amount of refrigerant generated in the generator G, the mixture is mixed with the absorbing solution in the dilute solution residue 12 portion. In the case of the embodiment, regarding the control of the refrigerating capacity described above, the supercooling temperature for supercooling the absorbing solution is not changed, instead of changing the supercooling temperature of the absorbing solution flowing into the absorber A as in the first embodiment. The solution discharge amount of the solution pump P ₁ on the upstream side of the cooler H ₂ is varied in accordance with the detected temperature of the temperature sensor 6 for detecting the temperature of the cold water outlet side of the evaporation heat exchanger 7 of the evaporator E, thereby Absorbent solution flow rate into absorber A (absorber A The capacity of absorbing the refrigerant vapor in the absorber is increased or decreased by changing the flow rate of the supercooled absorbing solution flowing into the absorber.

  Even with such a configuration, the exhaust heat amount increase / decrease control for increasing / decreasing the heating amount of the generator G, the exhaust heat supply stop, etc. are also performed for the equipment side (refrigeration apparatus side) that simply uses the exhaust heat. In addition to being unnecessary, it is possible to effectively control the refrigerating capacity with a simple and inexpensive device on the use side instead of these expensive devices.

In the same configuration, the solution is supplied to the generator G because of the indirect air cooling method (solution separation cooling method) in which the solution is supercooled by the supercooler H ₂ and the absorbed heat is removed by sensible heat of the solution as described above. Even if the amount is increased, the performance hardly deteriorates as compared with the conventional air-cooled absorber.

  Further, in the same configuration, the concentrated solution from the generator G is mixed with the diluted solution from the absorber A on the upstream side of the solution pump P, so that a dedicated pump such as a liquid jet pump need not be used.

1 is a refrigeration circuit diagram showing a configuration of an exhaust heat drive type absorption refrigeration apparatus that employs an indirect air cooling system in an absorber according to a first embodiment of the present invention. It is a freezing circuit diagram which shows the structure of the exhaust-heat drive type absorption refrigerating apparatus which employ | adopted the indirect air cooling system for the absorber which concerns on best Embodiment 2 of this invention. It is a freezing circuit diagram which shows the structure of the principal part of the exhaust-heat drive type absorption refrigerating apparatus which employ | adopted the indirect air cooling system for the absorber which concerns on best Embodiment 3 of this invention. It is a freezing circuit diagram which shows the structure of the exhaust-heat drive type absorption refrigerating apparatus which employ | adopted the indirect air cooling system for the absorber which concerns on best Embodiment 4 of this invention. It is a freezing circuit diagram which shows the structure of the exhaust-heat drive type absorption refrigerating device which has not employ | adopted the conventional indirect air cooling system.

Explanation of symbols

1 waste hot water heat exchanger, 2a, 2b rare solution and concentrated solution of each of the heat exchanger portion of the solution heat exchanger H _1, the first flow regulating valve 4, 5A is a rotational speed of the cooling fan F ₂ flow controllers to adjust the refrigerating capacity by varying, 5B are flow controllers to adjust the refrigerating capacity by varying the mixture flow to the subcooler H _2, the temperature sensor 6, the second flow rate 9 A regulating valve, A is an absorber, P is a solution pump, E is an evaporator, H ₂ is a subcooler, and H ₁ is a solution heat exchanger.

Claims (6)

  A superabsorbing means for removing the absorption heat generated in the absorber with the sensible heat of the solution by supercooling the absorption solution flowing into the absorber via the solution pump, and an absorption dilute solution supplied from the absorber An exhaust heat drive type absorption refrigeration apparatus adopting an indirect cooling system including a generator that generates refrigerant vapor and an absorption concentrated solution by heating with predetermined exhaust heat from an external exhaust heat source, the absorber By making the part into a liquid film flow-down type absorber with a plate, it is housed in an integral casing together with the evaporator, while mixing the unevaporated refrigerant in the evaporator with the diluted solution in the diluted solution reservoir at the bottom of the absorber The refrigerant vapor is prevented by changing the supercooling temperature or flow rate of the absorbing solution flowing into the absorber while preventing the solution concentration from greatly changing due to the increase or decrease in the amount of refrigerant generated in the generator. Heat-driven absorption refrigerating apparatus is characterized in that so as to increase or decrease control the ability to absorb.   By changing the driving state of the cooling fan for supercooling the absorption solution flowing into the absorber, the temperature of the supercooling solution flowing into the absorber is changed to increase / decrease the refrigerant vapor absorption capacity of the absorber The exhaust heat drive type absorption refrigeration apparatus according to claim 1, wherein   The flow rate variable means for changing the flow rate of the supercooling solution flowing into the absorber is provided on the inlet side or the outlet side of the supercooling device, and the refrigerant vapor of the absorber is changed by changing the flow rate of the supercooling solution flowing into the absorber. 2. The exhaust heat drive type absorption refrigeration apparatus according to claim 1, wherein the absorption capacity is controlled to increase or decrease.   The dilute solution from the absorber that has absorbed the refrigerant vapor is mixed with the concentrated solution that has generated the refrigerant vapor at the generator and the temperature has decreased in the solution heat exchanger at the upstream side of the solution pump. The refrigerant vapor absorption capacity of the absorber is controlled to increase / decrease by changing the flow rate of the supercooled solution flowing into the absorber by increasing / decreasing the solution discharge flow rate of the suction / discharge solution pump. Item 2. An exhaust heat drive type absorption refrigeration apparatus according to Item 1.   It is characterized in that all the non-evaporated refrigerant is mixed with the dilute solution in the evaporator with the dilute solution stay in the lower part of the absorber that has absorbed the refrigerant vapor, without providing the refrigerant stay at the lower part of the evaporator. The exhaust heat drive type absorption refrigeration apparatus according to claim 1, 2, 3, or 4.   Provide a fixed volume of refrigerant in the lower part of the evaporator so that only a certain amount of unevaporated refrigerant is stored in the refrigerant, and mix the remaining refrigerant with the dilute solution in the dilute solution in the lower part of the absorber. The exhaust heat drive type absorption refrigeration apparatus according to claim 1, 2, 3 or 4, wherein the exhaust heat drive type absorption refrigeration apparatus is provided.

Images