JPH07190545A - Engine exhaust heat recovery absorption type refrigerator - Google Patents

Abstract

PURPOSE:To make a heat exchanger for recovery of engine exhaust heat to cooling water unnecessary, and besides obtain a higher heating capacity than that by engine exhaust heat, and further evade crystallization even in a case wherein a high temperature output is contrived to obtain by making a heat absorbing temperature high through a heat absorbing device. CONSTITUTION:At a heating operation, a liquidized refrigerant generated in a condenser 72 of a cycle 7 for a mono-effective usage is guided to an absorber 74 through a refrigerant flow path 84, and a heat absorption from a heat source water from a coil tube 31 in an evaporator 73 is stopped. By this, a higher heating capacity than that by exhaust heat from an engine 2 can be obtained by executing a further heating and raising temperature by an absorber 74 and a condenser 72 at a side of the cycle 7 for the mono-effective usage which are operated by using an utilization hot water heated at an absorber 45 and a condenser 43 of a cycle 6 for a double-effective usage operated by a heat-pump operation as a mere heater.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention combines a double-effect absorption heat pump cycle and a single-effect absorption heat pump cycle, and makes effective use of exhaust heat and hot water exhaust heat of an engine for heating and cooling. The present invention relates to an engine exhaust heat recovery absorption type refrigerator.

[0002]

2. Description of the Related Art Conventionally, as an absorption type refrigerator utilizing the exhaust heat of an engine, there is a technique disclosed in, for example, Japanese Patent Laid-Open No. 58-99661. This conventional technology is an absorption refrigerating machine that combines a single-effect absorption refrigerating machine and a double-effect absorption refrigerating machine. During heating operation, the exhaust heat of the engine is also collected in hot water and guided to an indoor unit. It was used as the heat source of an absorption water heater that operates as a simple heater.

As for the single-effect and double-effect combined heat pumps, the technique disclosed in Japanese Patent Laid-Open No. 60-33460 is known. In this conventional technique, the hot water heated by the double-effect absorber and the double-effect condenser is further heated and heated by the single-effect condenser.

[0004]

However, in the first prior art, a heating capacity higher than the exhaust heat of the engine cannot be obtained, and the heat exchanger for recovering the exhaust heat of the engine to hot water is used. There was a problem that was required.

However, in the second conventional technique,
In order to obtain the high-temperature output required for air conditioning, the heat source temperature in the regenerator of the single-effect cycle needs to be around 120 ° C, but the temperature of the exhaust heat from the hot water of the engine is too low to be used as a heat source. Furthermore, when air is used as the heat absorption source of the evaporator, the temperature of the heat source water flowing in the evaporator heat transfer tube is low. In this way, when the temperature of the heat source water is low and the endothermic temperature in the absorber is increased to obtain a high temperature output, the evaporation pressure in the evaporator decreases, which also causes the pressure in the absorber to decrease. Go down. Therefore, when the internal pressure of the absorber is lowered, the concentration of the solution is increased, and, for example, lithium bromide is crystallized and the solution circuit is easily clogged.

According to the present invention, a heat exchanger for recovering exhaust heat of exhaust gas of the engine to cooling water is not required, moreover, a heating capacity higher than the exhaust heat of the engine can be obtained, and the heat absorption temperature of the heat absorber is increased. It is an object of the present invention to provide an engine exhaust heat recovery absorption refrigerator that can avoid crystallization even when it is attempted to obtain a high temperature output by raising it.

[0007]

The present invention provides at least a double-effect high temperature regenerator, a double-effect low temperature regenerator, a double-effect condenser, a single-effect regenerator, a single-effect condenser, an evaporator and an absorber. In combination, the exhaust heat of the engine is used as a heat source for the high temperature regenerator, and the engine exhaust heat recovery absorption refrigerator that uses the hot water exhaust heat of the engine as a heat source for the single-effect regenerator is used to cool the cold water. In the double-effect low-temperature regenerator, a cold-water circuit having a cold-water flow path for flowing to the evaporator, and a cooling-water flow path for flowing cooling water to the absorber and the double-effect condenser and then to the single-effect condenser. Alternatively, a solution circuit having a solution flow path for flowing a concentrated solution in the single-effect regenerator to the absorber, and a first refrigerant that causes a liquefied refrigerant condensed by being absorbed by cooling water in the single-effect condenser to flow to the evaporator. Cool in the flow path and the single-effect condenser A single-effect refrigerant circuit having a second refrigerant flow path that causes a liquefied refrigerant that has been absorbed by water and condensed to flow into the absorber; and a switching from the second refrigerant flow path to the first refrigerant flow path during cooling operation, and during heating operation The technical means including the refrigerant flow path switching means for switching from the first refrigerant flow path to the second refrigerant flow path is adopted.

[0008]

According to the present invention, the solution in the double-effect high temperature regenerator is heated by the exhaust heat of the engine to generate a vapor refrigerant, and the generated vapor refrigerant causes the solution in the double-effect low temperature regenerator to be generated. When heated, steam refrigerant is generated, and the steam refrigerant generated in the double effect low temperature regenerator is cooled by being absorbed by the cooling water flowing in the cooling water flow path in the double effect condenser. In addition, the solution in the single-effect regenerator is heated by the hot water exhaust heat of the engine to generate vapor refrigerant, and the vapor refrigerant generated in this single-effect regenerator is absorbed by the cooling water flowing in the cooling water flow path to produce single-effect. Cooled in condenser.

Here, during the cooling operation, the refrigerant flow path switching means switches the second refrigerant flow path to the first refrigerant flow path, so that the liquefied refrigerant condensed in the double-effect condenser flows into the evaporator, and The liquefied refrigerant condensed in the effect condenser flows into the evaporator through the first refrigerant passage. Therefore, the liquefied refrigerant condensed in the double-effect condenser and the single-effect condenser both evaporates by exchanging heat with cold water in the evaporator. Then, the evaporated refrigerant evaporated in this evaporator is absorbed by the solution in the absorber, and the absorbed heat is removed by the cooling water flowing in the cooling water passage. This cools the cold water flowing in the cold water flow path in the evaporator,
This cooled cold water is used for indoor cooling.

Further, during the heating operation, the first refrigerant passage is switched to the second refrigerant passage by the refrigerant passage switching means, so that the liquefied refrigerant condensed in the double-effect condenser exchanges heat with cold water in the evaporator. However, the liquefied refrigerant condensed in the single-effect condenser flows into the absorber through the second refrigerant passage. When the liquefied refrigerant is absorbed by the solution in the absorber, the absorption temperature is raised without lowering the internal pressure of the absorber.
As a result, the cooling water flowing in the cooling water flow path is heated by the absorber, and the cooling water heated in this heat absorber and the cooling water heated in the double-effect condenser are further heated by the single-effect condenser. It is used to heat the room after raising the temperature.

[0011]

Next, a description will be given based on an embodiment in which the engine exhaust heat recovery absorption refrigerator is applied to an engine exhaust heat recovery absorption heat pump.

[Structure of First Embodiment] FIG. 1 shows a first embodiment of the present invention and is a diagram showing a schematic structure of the entire system. FIG. 2 shows an engine exhaust heat recovery absorption heat pump. It is the figure which showed.

Engine exhaust heat recovery absorption type heat pump 1
Is for cooling and heating the inside of the room by effectively utilizing the exhaust heat of the engine 2 and the exhaust heat of the hot water. The indoor unit 3, the outdoor unit 4, the switching valve device 5, the double-effect absorption heat pump cycle (hereinafter A double-effect cycle 6), a single-effect absorption heat pump cycle (hereinafter abbreviated as single-effect cycle) 7, an electronic control unit (hereinafter referred to as ECU) 8 and the like.

The engine 2 is, for example, an engine that rotationally drives a generator 9, and heat is generated by burning a fuel such as natural gas or diesel oil. This engine 2
Is provided with an exhaust pipe 10 for discharging exhaust gas generated at the time of combustion of fuel to the outside, and a hot water pipe 11 for circulating engine cooling water (hereinafter referred to as hot water) for cooling the engine 2. The exhaust pipe 10 is provided with a coil tube 12 that is guided into the double-effect cycle 6. Further, the hot water pipe 11 is provided with a coil tube 13 that is guided into the single-effect cycle 7.

The indoor unit 3 is for cooling and heating the inside of a building, and is composed of an indoor heat exchanger 14 for exchanging heat between cold water or hot water and air, and an indoor fan 15 for generating cold air or hot air directed to the room. Has been done. In addition,
The indoor heat exchanger 14 is composed of, for example, a coil tube and a plurality of fins, and is connected to the switching valve device 5 via the indoor cold water flow passage 16.

The outdoor unit 4 is installed outdoors of the building, and has an outdoor heat exchanger 17 for cooling the cooling water by exchanging heat with the outdoor air, and an outdoor fan 18 for blowing the outdoor air to the outdoor heat exchanger 17. Etc. The outdoor heat exchanger 17 is composed of, for example, a coil tube and a plurality of fins, and is connected to the switching valve device 5 via the outdoor cold water flow passage 19. A cooling tower may be used as the outdoor unit 4.

The switching valve device 5 is composed of a plurality of flow path switching valves (for example, an on-off valve, a three-way valve, a four-way valve), and the cold water circuit 2
0 based on the control signal of the ECU 8
Alternatively, the outdoor cold water flow path 19 is selectively switched. The cold water circuit 20 is a circuit for circulating cold water or cooling water (may be antifreeze liquid) in the double effect cycle 6 and the single effect cycle 7.
1, a single-effect cold water flow passage 22 and a cooling water flow passage 23.

The double-effect cold water passage 21 is a passage for returning the cold water flowing out of the switching valve device 5 to the switching valve device 5 again through the evaporator 44 of the double-effect cycle 6 described later.
The double-effect cold water flow path 21 is a coil tube 2 for evaporating the liquefied refrigerant (condensed water) that has flowed into the evaporator 44.
4 and a water temperature sensor 25 for detecting the temperature of the cold water flowing out from the coil tube 24. Also, 2
A water pump 26 for generating a water flow in the double effect cold water flow passage 21 is attached to the heavy effect cold water flow passage 21.

The single-effect cold water flow path 22 is an evaporator 73 of a single-effect cycle 7 in which cold water flowing out of the switching valve device 5 is described later.
Is a flow path for returning to the switching valve device 5 again. The single-effect cold water flow path 22 includes a coil tube 27 that evaporates and vaporizes the liquefied refrigerant (condensed water) that has flowed into the evaporator 73. Further, in the single effect cold water flow passage 22, a water pump 28 for generating a water flow in the single effect cold water flow passage 22.
Is attached.

The cooling water flow path 23 is provided with an absorber 45 of a double-effect cycle 6 which cools cold water flowing out from the switching valve device 5, which will be described later.
Condenser 43, absorber 74 of single-effect cycle 7, condenser 7
It is a flow path that passes through 2 and returns to the switching valve device 5 again. The cooling water flow path 23 includes coil tubes 29 to 32. The coil tubes 29 and 31 are the absorbers 45 and 7.
In order to remove the heat of absorption generated when the vapor refrigerant in 4 is absorbed by the concentrated solution, the atmosphere in the absorbers 45, 74 is cooled. The coil tubes 30 and 32 are connected to the condensers 43 and 72.
The vapor refrigerant flowing into the inside is cooled and condensed and liquefied. Further, a water pump 33 for generating a water flow in the cooling water flow path 23 is attached to the cooling water flow path 23.

The double-effect cycle 6 includes a high temperature regenerator 41,
Low temperature regenerator 42, condenser 43, evaporator 44, absorber 4
5, low temperature solution heat exchanger 46 and high temperature solution heat exchanger 47
A double effect refrigerant circuit 48 and a double effect solution circuit 49.
It is configured by operatively connecting with.

The double-effect refrigerant circuit 48 includes the refrigerant passages 51 to 51.
A refrigerant flow is generated by the action of a refrigerant pump 56 that is equipped with a solenoid valve 54 and an electromagnetic on-off valve (hereinafter abbreviated as an electromagnetic valve) 55 and is attached to the refrigerant passage 53. The refrigerant passage 51 is a passage through which the vapor refrigerant generated in the high temperature regenerator 41 flows into the condenser 43, and is provided with a coil tube 57 for heating the aqueous solution in the low temperature regenerator 42 on the way. The refrigerant flow path 52 is a flow path for causing the liquefied refrigerant generated in the condenser 43 to flow to the evaporator 44.

The refrigerant flow path 53 is a flow path for causing the liquefied refrigerant that has not yet evaporated in the evaporator 44 to flow into the evaporator 44 by the action of the refrigerant pump 56, and the liquefied refrigerant is sprayed onto the coil tube 24 at the tip. A nozzle 58 is provided. The refrigerant flow path 54 is a bypass path that branches from the middle of the refrigerant flow path 53 and flows the liquefied refrigerant directly into the absorber 45. The solenoid valve 55 is attached to the refrigerant flow path 54 and opens the refrigerant flow path 54 when opened.

The double-effect solution circuit 49 includes solution flow paths 59 to 59.
A solution flow is generated by the action of the solution pump 62 that is provided with 61 and is attached to the solution flow path 61. Although the lithium bromide aqueous solution is used as the solution in this embodiment, a lithium iodide aqueous solution, a lithium chloride aqueous solution or the like may be used instead.

The solution flow path 59 is a flow path for flowing the dilute solution in the absorber 45 into the high temperature regenerator 41 via the low temperature solution heat exchanger 46 and the high temperature solution heat exchanger 47. The solution flow channel 60 is
This is a flow path through which the concentrated solution in the high temperature regenerator 41 flows into the low temperature regenerator 42 via the high temperature solution heat exchanger 47. Solution flow path 61
Is a low temperature solution heat exchanger 46 for the concentrated solution in the low temperature regenerator 42.
A nozzle 63 for spraying the concentrated solution onto the coil tube 29 is provided at the tip end portion in a flow path that flows into the absorber 45 via.

The high temperature regenerator 41 is a double-effect high temperature regenerator of the present invention, and is constituted by the coil tube 12 of the exhaust pipe 10 of the engine 2, the shell (container) 64 for accommodating the coil tube 12, and the like. ing. The high temperature regenerator 41 includes the dilute solution (a small aqueous solution having a solubility of lithium bromide of about 55% by weight) flowing into the shell 64 from the solution flow path 59 of the double effect solution circuit 49 and the coil tube 1.
Exhaust gas exhaust heat (for example, 400 ° C. to 500 ° C.) flowing in 2 is heat-exchanged to generate a vapor refrigerant from the aqueous solution to concentrate the aqueous solution.

The low temperature regenerator 42 is the dual effect low temperature regenerator of the present invention, and is a refrigerant flow passage 51 of the dual effect refrigerant circuit 48.
Coil tube 57, and this coil tube 57
And a shell (container) 65 for accommodating the. The low-temperature regenerator 42 has a concentrated solution (a small aqueous solution having a solubility of lithium bromide of about 60% by weight) flowing into the shell 65 from the solution channel 60 of the double-effect solution circuit 49 and steam flowing in the coil tube 57. Heat exchange with the refrigerant to generate a vapor refrigerant from the concentrated solution to further concentrate the concentrated solution.

The condenser 43 is a double-effect condenser of the present invention, and contains the coil tube 30 of the cooling water flow path 23 of the cold water circuit 20, and the coil tube 30, and is the same as the low temperature regenerator 42. It is composed of a shell (container) 65 and the like. This condenser 43 is mainly a low temperature regenerator 42.
The steam refrigerant generated in step 1 and the cooling water flowing in the coil tube 30 are heat-exchanged to condense and liquefy the steam refrigerant.

The evaporator 44 is constituted by a coil tube 24 of the double-effect cold water flow path 21 of the cold water circuit 20, a shell 66 that accommodates the coil tube 24, and has an internal pressure of 6.5 mmHg, for example. There is. The evaporator 44 causes heat exchange between the liquefied refrigerant sprayed on the coil tube 24 and the cold water flowing in the coil tube 24 from the nozzle 58 provided at the tip of the refrigerant flow path 53 of the dual effect refrigerant circuit 48. To evaporate the refrigerant and cool the cold water.

The absorber 45 is constituted by the coil tube 29 of the cooling water flow path 23 of the cold water circuit 20, and the shell 66 which houses the coil tube 29 and is the same as the evaporator 44. A partition plate 67 having a plurality of communication ports (not shown) is provided between the absorber 45 and the evaporator 44. The absorber 45 absorbs the vapor refrigerant generated in the evaporator 44 into the concentrated solution sprayed on the coil tube 29 from the nozzle 63 provided at the tip of the solution flow path 61 of the double effect solution circuit 49. Is.

The low temperature solution heat exchanger 46 exchanges heat between the low temperature dilute solution flowing in the solution flow path 59 of the double effect solution circuit 49 and the high temperature concentrated solution flowing in the solution flow path 61. The high temperature solution heat exchanger 47 has a double effect solution circuit 49.
Low temperature dilute solution flowing in the solution flow path 59 and the solution flow path 60
The dilute solution is heated by exchanging heat with the hot concentrated solution flowing therein, and the concentrated solution is cooled.

The single-effect cycle 7 includes a regenerator 71, a condenser 72, an evaporator 73, an absorber 74, and a solution heat exchanger 75.
Are operatively connected by a single-effect refrigerant circuit 76 and a single-effect solution circuit 77.

The single-effect refrigerant circuit 76 includes the refrigerant passages 81 to 8
4 and an electromagnetic on-off valve (hereinafter, abbreviated as an electromagnetic valve) 85, a refrigerant flow is generated by the action of a refrigerant pump 86 attached to the refrigerant passage 83. The refrigerant passage 81 is a passage through which the vapor refrigerant generated in the regenerator 71 flows into the condenser 72. The refrigerant passage 82 is a passage through which the liquefied refrigerant generated in the condenser 72 flows to the evaporator 73.

The refrigerant passage 83 is the first refrigerant passage of the present invention, and is a passage through which the liquefied refrigerant that has not yet evaporated in the evaporator 73 flows into the evaporator 73 by the action of the refrigerant pump 86. A nozzle 87 for spraying the liquefied refrigerant onto the coil tube 27 is provided at the tip. The refrigerant flow path 84 is the second refrigerant flow path of the present invention, and is a bypass path that branches from the middle of the refrigerant flow path 83 and flows the liquefied refrigerant directly into the absorber 74. The solenoid valve 85 is the refrigerant channel switching means of the present invention, is attached to the refrigerant channel 84, and opens the refrigerant channel 84 when opened.

The single-effect solution circuit 77 includes solution flow paths 88, 8
9 and a solution pump 9 attached to the solution flow path 88.
A solution flow occurs due to the action of zero. Solution flow path 88
Is a flow path through which the dilute solution in the absorber 74 flows into the regenerator 71 via the solution heat exchanger 75. The solution flow path 89 uses the solution heat exchanger 75 to pass the concentrated solution in the regenerator 71 to the absorber 7.
A nozzle 91 for spraying a concentrated solution is provided on the coil tube 31 at the tip of the flow path of the fluid flowing in the coil 4.

The regenerator 71 is the single-effect regenerator of the present invention, and is the coil tube 1 of the hot water pipe 11 of the engine 2.
3 and a shell (container) 92 for accommodating the coil tube 13 and the like. This regenerator 71
Is from the solution flow path 88 of the single effect solution circuit 77 to the shell 92.
The dilute solution (a small aqueous solution having a solubility of lithium bromide of about 55% by weight) flowing into the inside of the coil tube 13 is exchanged with the hot water exhaust heat (for example, 80 ° C. to 105 ° C.) to exchange heat from the dilute solution as a vapor refrigerant. Is generated and the dilute solution is concentrated.

The condenser 72 is the single-effect condenser of the present invention, and is constituted by the coil tube 32 of the cooling water flow path 23 of the cold water circuit 20, the shell (container) 93 for accommodating the coil tube 32, and the like. There is. This condenser 72
Is the vapor refrigerant generated in the regenerator 71 and the coil tube 3
Heat is exchanged with the cooling water flowing in 2 to condense and liquefy the vapor refrigerant.

The evaporator 73 is composed of the coil tube 27 of the single-effect cold water flow path 22 of the cold water circuit 20, the shell 94 for housing the coil tube 27, and the like. The evaporator 73 exchanges heat between the liquefied refrigerant sprayed on the coil tube 27 from the nozzle 87 provided at the tip of the refrigerant flow path 83 of the single-effect refrigerant circuit 76 and the cold water flowing in the coil tube 27. Evaporate the refrigerant and cool the cold water.

The absorber 74 is constituted by the coil tube 31 of the cooling water flow path 23 of the cold water circuit 20 and the shell 94 which houses the coil tube 31 and is the same as the evaporator 73. A partition plate 95 having the same shape as the partition plate 67 is provided between the absorber 74 and the evaporator 73. The absorber 74 absorbs the vapor refrigerant generated in the evaporator 73 into the concentrated solution sprayed on the coil tube 31 from the nozzle 91 provided at the tip of the solution flow path 89 of the single-effect solution circuit 77. is there.

The solution heat exchanger 75 has a single-effect solution circuit 77.
Low temperature dilute solution flowing in the solution flow passage 88 and the solution flow passage 89
The dilute solution is heated by exchanging heat with the hot concentrated solution flowing therein, and the concentrated solution is cooled.

As shown in FIG. 1, the ECU 8 has a CPU, a ROM, and a RAM built therein, and includes an operation switch 36, a cooling / heating switching switch 37, and a water temperature sensor 25.
Based on the input signal input from the engine 2, the indoor fan 15 of the indoor unit 3, the outdoor fan 18 of the outdoor unit 4, the plurality of flow path switching valves of the switching valve device 5, the solenoid valve 55 of the double-effect cycle 6, Refrigerant pump 56, solution pump 6
2, single-effect cycle 7 solenoid valve 85, refrigerant pump 86,
A solution pump 90, a water pump 26 for the cold water circuit 20,
Control devices such as 28 and 33.

The operation switch 36 is a switch for starting or stopping the entire system including the indoor fan 15 of the indoor unit 3. The cooling / heating switching switch 37 is a switch for switching the air conditioning mode of the room such as cooling operation and heating operation. The ECU 8 stops the operation of the water pump 28 during the heating operation and opens the electromagnetic valve 85. Then, when the water temperature of the cold water detected by the water temperature sensor 25 falls below a predetermined water temperature (for example, 1.5 ° C.), the operation of the water pump 26 is stopped and the solenoid valve 5 is operated.
5 is opened.

[Operation of First Embodiment] Next, the operation of the engine exhaust heat recovery and absorption heat pump 1 of this embodiment will be briefly described with reference to FIGS. 1 and 2.

(Cooling operation) When the operation switch 36 is closed and the cooling / heating switching switch 37 selects the cooling operation, the control device is controlled so that the ECU 8 performs the cooling operation. Then, when the diluted solution in the high temperature regenerator 41 of the dual effect cycle 6 is heated by the high temperature exhaust gas exhaust heat generated in the engine 2 that rotationally drives the generator 9, a high temperature vapor refrigerant is generated. This high-temperature vapor refrigerant is used in the dual-effect refrigerant circuit 48.
Is guided to the coil tube 57 through the refrigerant flow path 51.

On the other hand, the concentrated solution concentrated in the high temperature regenerator 41 is introduced into the condenser 43 through the solution flow passage 60 of the double effect solution circuit 49. Then, the concentrated solution in the low temperature regenerator 42 is heated by the condensation heat of the vapor refrigerant, and the low temperature regenerator 42 is heated.
A vapor refrigerant is generated from the concentrated solution inside and the concentrated solution is further concentrated.

The vapor refrigerant generated in the low temperature regenerator 42 reaches the condenser 43 and is cooled on the surface of the coil tube 30 of the cooling water flow path 23 through which the cooling water flows to be condensed and liquefied. The liquefied refrigerant from the high temperature regenerator 41 condensed and liquefied in the low temperature regenerator 42 also flows into the condenser 43 through the refrigerant flow path 51.

The liquefied refrigerant generated in the condenser 43 flows into the low pressure evaporator 44 through the refrigerant passage 52. And
The liquefied refrigerant that cannot be completely evaporated is sprayed from the nozzle 58 of the refrigerant channel 53 by the action of the refrigerant pump 56, and is evaporated on the surface of the coil tube 24 of the double effect cold water channel 21 in which the utilization cold water flowing on the load side flows. The cold water in the coil tube 24 is cooled to obtain a cooling effect.

Further, the vapor refrigerant evaporated in the evaporator 44 is absorbed in the concentrated solution concentrated in the high temperature regenerator 41 and the low temperature regenerator 42 in the absorber 45, and the aqueous solution becomes diluted. At this time, absorbed heat is generated, but this absorbed heat is cooled and removed by the cooling water flowing through the coil tube 29 of the cooling water flow path 23.

The dilute solution accumulated below the absorber 45 is again sent to the high temperature regenerator 41 through the solution flow path 59 by the action of the solution pump 62, and in the process, the low temperature solution heat exchanger 46 and the high temperature solution are exchanged. The solution heat exchanger 47 recovers heat from the concentrated solution at the outlet of the low temperature regenerator 42 and the concentrated solution at the outlet of the high temperature regenerator 41.

On the other hand, in the single-effect cycle 7, the engine 2
The diluted solution in the regenerator 71 is heated by the exhaust heat of the warm water generated by the combustion of the gas to generate the vapor refrigerant, which flows into the condenser 72 through the refrigerant flow path 81 and is condensed in the condenser 72 to be liquefied. Get the refrigerant. Then, the liquefied refrigerant generated in the condenser 72 flows into the evaporator 73 through the refrigerant passage 82. Then, the liquefied refrigerant that has not been evaporated is sprayed from the nozzle 87 of the refrigerant channel 83 by the action of the refrigerant pump 86, and cools the cold water in the coil tube 27 to obtain a cooling effect.

Further, the vapor refrigerant evaporated in the evaporator 73 is absorbed in the concentrated solution concentrated in the regenerator 71 in the absorber 74, and the concentrated solution becomes thin. At this time, absorbed heat is generated, but the absorbed heat is cooled by cooling water flowing in the coil tube 31 and removed. The dilute solution accumulated below the absorber 74 is sent again to the regenerator 71 through the solution flow passage 88 by the action of the solution pump 90, and in the process, the outlet of the regenerator 71 at the solution heat exchanger 75. Heat is recovered from the concentrated solution of.

(During heating operation) When the cooling / heating switching switch 37 switches from cooling operation to heating operation, the ECU
The control device is controlled so that 8 performs heating operation. The double effect cycle 6 side is the same as the operation during the cooling operation, but the heat source water flows in the coil tube 24 of the double effect cold water flow passage 21 in the evaporator 44, and the absorber 45, the condenser. Utilized hot water flows in the coil tubes 29, 30 of the cooling water flow path 23 in 43. The evaporator 44 absorbs heat from the heat source water, and the absorber 45 and the condenser 43 absorb heat,
The hot water used is heated by the heat of condensation and operates as a heat pump.

On the other hand, on the single-effect cycle 7 side, the condensing heat of the vapor refrigerant generated from the regenerator 71 heats the hot water used in the coil tube 32 of the cooling water passage 23, and the liquefied refrigerant flows into the evaporator 73. Then, it accumulates as a liquid refrigerant at the bottom of the evaporator 73 and is pressure-fed by the action of the refrigerant pump 86. At this time, the electromagnetic valve 85 is opened during the heating operation, and therefore passes through the refrigerant flow path 84 to the absorber 74. Direct inflow, regenerator 7
It is absorbed and diluted in a concentrated solution from 1. At this time as well, absorption heat is generated, and thus the absorption heat also heats the hot water used in the coil tube 31 of the cooling water flow path 23.

At this time, on the single-effect cycle 7 side, the solenoid valve 85 is opened and the water pump 28 is stopped, so that the circulation of the heat source water into the evaporator 73 and the spraying of the liquefied refrigerant are not performed. There is no heat absorption, and it operates as a mere heater. The double-effect cycle 6 side has an evaporator 44 and an absorber 45 in order to allow heat absorption from low-temperature heat source water.
The internal pressure is operated at a low level of, for example, about 5 mmHg to 6 mmHg, but it is difficult to obtain a high temperature output from the double effect cycle 6 in order to avoid the problem of crystallization of the dilute solution in the absorber 45.

On the other hand, since the single-effect cycle 7 side operates as a mere heater, the pressure in the absorber 74 can be increased to, for example, about 60 mmHg, and the absorption temperature can be set high. It is possible to operate under a dilute concentration condition that does not exist, and it is possible to prevent the solution flow passage 88 of the single-effect solution circuit 77 from being clogged. In addition, since the operation is performed with the dilute solution, the condenser 72 is operated at the temperature level of the exhaust heat of the hot water of the engine 2.
Since the condensation temperature can be as high as about 50 ° C., a high temperature output can be obtained.

When the temperature of the heat source water circulating in the double effect cold water flow passage 21 on the side of the double effect cycle 6 falls below a predetermined water temperature (for example, 1.5 ° C.), the evaporator 4
Since a problem occurs due to freezing of the refrigerant (water) in the No. 4, the double-effect cycle 6 side is switched from the heat pump operation to the heater operation by opening the solenoid valve 55 and stopping the water pump 26.

[Effects of the First Embodiment] As described above, in this embodiment, the exhaust heat of the engine 2 is the double effect cycle 6, the hot water exhaust heat of the engine 2 is the single effect cycle 7, and the respective temperature levels. The cooling capacity of the engine exhaust heat recovery and absorption heat pump 1 can be increased by properly using the heat pump 1.

Further, in this embodiment, the absorber 4 of the double effect cycle 6 which is operated by the heat pump during the heating operation.
5. By further increasing the heating temperature of the utilization hot water heated by the condenser 43 by the absorber 74 and the condenser 72 on the side of the single-effect cycle 7 that operates as a mere heater, the heating capacity higher than the exhaust heat of the engine 2 is obtained. Obtainable.

Therefore, while avoiding the crystallization of lithium bromide in the absorber 74, the heating capacity is increased by the heat pump operation of the double-effect cycle 6 and the single-effect cycle 7 is increased.
It is possible to simultaneously achieve both the increase in the output temperature due to the heater operation described above. Further, since a heat exchanger for recovering exhaust heat from the engine 2 into hot water is not required, the number of parts can be reduced.

[Second Embodiment] FIG. 3 shows a second embodiment of the present invention and is a view showing an engine exhaust heat recovery and absorption heat pump. In this embodiment, the evaporator 44, the absorber 45 and the solution pump 62 of the double-effect cycle 6 and the single-effect cycle 7 are integrated. And
The liquefied refrigerant generated in the condenser 72 is introduced into the evaporator 44 through the refrigerant flow paths (first refrigerant flow paths) 83 and 52 during the cooling operation, and the refrigerant flow path (second refrigerant flow path) during the heating operation. It is designed to be guided directly into the absorber 45 via 84.

During the heating operation, by opening the solenoid valve 85, the refrigerant passage 84 is opened and the liquefied refrigerant generated in the condenser 72 is directly introduced into the absorber 45, and further inside the cooling water passage 23. The used hot water flowing through the heater is sequentially heated by the absorber 45, the condenser 43, and the condenser 72 to obtain a high-temperature output for heating.

[Modification] In this embodiment, the hot water exhaust heat of the engine 2 is used as the heating source of the regenerator 71 of the single-effect cycle 7, but the steam of the boiling cooling engine is used as the regenerator 71 of the single-effect cycle 7. It may be used as a heating source.

In the first embodiment, the cooling water was made to flow through the absorber 45 of the double-effect cycle 6 and the condenser 43, the absorber 74 of the single-effect cycle 7 and the condenser 72 in this order. After the absorber 45 and the condenser 43 of the cycle 6 flow in parallel, the absorber 74 and the condenser 72 of the single-effect cycle 7 may flow in parallel. If the cooling water is made to flow from the double effect cycle 6 side to the single effect cycle 7 side, it may be made to flow in the order of condenser 43 → absorber 45, condenser 72 → absorber 74.

In this embodiment, the solenoid valve 85 is used as the refrigerant passage switching means, but a switching valve such as a three-way valve may be used instead of the solenoid valve 85. Although the solenoid valve 55 is used in this embodiment, a switching valve such as a three-way valve may be used instead of the solenoid valve 55.

[0065]

According to the present invention, exhaust heat of an engine is used as a heating source for a double-effect high-temperature regenerator, and hot water exhaust heat of an engine is used as a heating source for a single-effect regenerator to absorb heat during heating operation. It is possible to obtain a heating capacity higher than the exhaust heat of the engine by further heating and heating the utilization hot water heated by the condenser and the double-effect condenser by the double-effect condenser. Further, a heat exchanger for recovering exhaust heat from the exhaust gas of the engine to the cooling water is unnecessary, so that the number of parts can be reduced. Furthermore, even if an attempt is made to obtain a high temperature output by raising the heat absorption temperature of the heat absorber, crystallization does not occur, and thus the solution circuit can be prevented from being blocked.

[Brief description of drawings]

FIG. 1 is a configuration diagram showing a schematic structure of an entire system of a first embodiment of the present invention.

FIG. 2 is a configuration diagram showing a first embodiment of the present invention.

FIG. 3 is a configuration diagram showing a second embodiment of the present invention.

[Explanation of symbols]

 1 Engine exhaust heat recovery absorption heat pump 2 Engine 6 2 Double effect cycle 7 Single effect cycle 20 Cold water circuit 21 Double effect cold water flow path 22 Single effect cold water flow path 23 Cooling water flow path 41 High temperature regenerator (Double effect high temperature regenerator) ) 42 low-temperature regenerator (double-effect low-temperature regenerator) 43 condenser (double-effect condenser) 44 evaporator 45 absorber 48 double-effect refrigerant circuit 49 double-effect solution circuit 61 solution flow path 71 regenerator 72 condensation Device 73 Evaporator 74 Absorber 76 Single-effect refrigerant circuit 77 Single-effect solution circuit 83 Refrigerant flow path (first refrigerant flow path) 84 Refrigerant flow path (second refrigerant flow path) 85 Solenoid valve (refrigerant flow path switching means) 89 Solution flow path

Claims (1)

[Claims] 1. A high-temperature regenerator comprising a combination of at least a double-effect high-temperature regenerator, a double-effect low-temperature regenerator, a double-effect condenser, a single-effect regenerator, a single-effect condenser, an evaporator and an absorber. In an engine exhaust heat recovery absorption refrigerator that uses exhaust heat from an engine as a heat source for exhaust gas and uses exhaust heat from an engine as hot water as a heat source for the single-effect regenerator, (a) flowing cold water to the evaporator A cold water circuit having a cold water flow path and a cooling water flow path for flowing cooling water to the single effect condenser after the absorber and the double effect condenser; and (b) in the double effect low temperature regenerator or A solution circuit having a solution flow path for flowing the concentrated solution in the single-effect regenerator to the absorber, and (c) a liquefied refrigerant that is condensed by being absorbed by cooling water in the single-effect condenser to flow to the evaporator. The coolant flow path and the single-effect condenser absorb the cooling water. A single-effect refrigerant circuit having a second refrigerant flow path for flowing the condensed and condensed liquefied refrigerant to the absorber; (d) switching from the second refrigerant flow path to the first refrigerant flow path during cooling operation, and during heating operation An engine exhaust heat recovery absorption refrigerator having a refrigerant flow path switching means for switching from the first refrigerant flow path to the second refrigerant flow path.