JPH1163723A - Complex heat transferring device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To perform an effective utilization of discharged heat of an engine generated in a compression type heat transferring device driven by a water- cooled engine and further perform an effective classification of utilization at an absorbing type freezer or the like and a utilization of improvement of performance with heating of refrigerant at the compression type heat transferring device itself. SOLUTION: A complex heat transferring device provided with a compressing type heat pump system 1 and an absorbing type freezing system 70 or an adsorbing type freezing system is constructed such that a cooling water circuit 40 of the compressing type heat pump system 1 is provided with discharged heat recovering heat exchangers 7, 8, a W-W heat exchanger 43 for transferring heat to a heating section arranged at the adsorbing type freezing system 70 or the like, and a W-R heat exchanger 26 for supplying heat to a low pressure refrigerant in the refrigerant circuit 10 of the compressing type heat pump system 1. Then, there are provided solenoid valves 46, 47 and 49 capable of changing the cooling water flowing rate in respect to the W-W heat exchanger 43 and the W-R heat exchanger 26.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a composite heat transfer device having a compression heat transfer device driven by a water-cooled engine and an absorption or adsorption heat transfer device.

[0002]

2. Description of the Related Art Conventionally, as a heat transfer device constituting a refrigerator or a heat pump, a compression heat transfer device, an absorption heat transfer device and an adsorption heat transfer device are known.

[0003] The compression heat transfer device circulates the refrigerant discharged from the compressor back to the compressor through a condenser, an expansion valve, and an evaporator, and uses heat absorption in the evaporator and heat radiation in the condenser. It is designed to perform cooling and heating.

The absorption type heat transfer device introduces an evaporator for evaporating the refrigerant, an absorber for absorbing the refrigerant vapor guided from the evaporator into an absorption liquid, and an absorption liquid after the absorption of the refrigerant by the absorber. And a regenerator for releasing the refrigerant from the absorbing liquid,
A condenser for condensing the refrigerant vapor sent out from the regenerator, extracting cold heat with the evaporator when used as a refrigerator, and extracting heat with the condenser and absorber when used as a heat pump device It is like that.

Further, the adsorption type heat transfer device comprises an adsorption regenerator for alternately performing an adsorption step for adsorbing a refrigerant using an adsorbent and a regeneration step for desorbing the refrigerant, an evaporator for evaporating the refrigerant, a refrigerant vapor A condenser that condenses water, sends refrigerant vapor from the evaporator to the adsorption regenerator in the adsorption process, while sends refrigerant vapor from the adsorption regenerator in the regeneration process to the condenser, and uses it as a refrigerator. Is a device in which cold heat is taken out by the evaporator, and when the heat pump device is used, heat is taken out by the condenser and the adsorption regenerator in the adsorption process.

Generally, these three types of heat transfer devices are used individually, but it is also considered to use a plurality of types of heat transfer devices together.

Incidentally, in the above-mentioned absorption type heat transfer apparatus, it is necessary to heat the absorption liquid in order to release the refrigerant from the absorption liquid in the regenerator. Although it is necessary to supply heat from a heat source during the process, providing a dedicated heat source for that purpose increases the fuel consumption for securing the required amount of heat.

For example, Japanese Patent Application Laid-Open No. Hei 7-218014 discloses that in an absorption refrigerator, a dilute solution line from an absorber to a regenerator is connected to a two-temperature-level exhaust heat source other than the absorption refrigerator (for example, an absorption refrigerator). The apparatus includes a high-temperature exhaust heat exchanger and a low-temperature exhaust heat exchanger that exchange heat between a high-temperature fluid and a low-temperature fluid supplied from a fuel cell, respectively, and an absorbent dilute solution.

Japanese Patent Application Laid-Open No. Hei 7-111285 discloses a compression type refrigerator using an engine driven compressor, an absorption type refrigerator, and an adsorption type refrigerator. A first exhaust heat recovery system that guides high-temperature engine exhaust heat extracted from a first exhaust gas heat exchanger provided in an upstream portion to an absorption refrigerator is provided, and a second exhaust heat recovery system provided in an exhaust passage downstream portion is provided. A second exhaust heat recovery system is provided to guide the exhaust heat of the engine taken out of the exhaust gas heat exchanger to the adsorption refrigerator, and the heat from the heat exchanger provided between the compressor and the condenser of the compression refrigerator is provided. A device is shown in which a path for extracting the waste heat is connected in parallel to the second exhaust heat recovery system.

[0010]

The above publications disclose a technique in which engine exhaust heat generated in an engine-driven compression refrigerator is sent to an absorption refrigerator or the like and used for heating an absorbent or the like for regeneration. Is shown, but if there is no request to use the engine exhaust heat in the absorption refrigerator, such as when the absorption refrigerator is stopped, or if this request is small, the engine exhaust heat is discarded. In such cases, diversion of engine exhaust heat has not been sufficiently considered, and there is room for improvement.

In view of such circumstances, the present invention makes effective use of engine exhaust heat generated in a compression-type heat transfer device driven by a water-cooled engine, and uses it in an absorption refrigerator or the like and uses a refrigerant in the compression-type heat transfer device itself. It is an object of the present invention to provide a composite heat transfer device that can be effectively used for improving performance by heating.

[0012]

In order to achieve the above object, the present invention comprises a refrigerant circuit for circulating refrigerant discharged from a compressor through a condenser, an expansion valve, and an evaporator so as to return to the compressor. An engine-driven compression heat transfer device in which the compressor is driven by a water-cooled engine; and an absorption heat transfer device or an adsorption heat transfer device. For mobile devices,
In a combined heat transfer apparatus provided with a heating unit for heating an absorbing liquid or an adsorbent for regeneration, heat exchange for exhaust heat recovery for extracting engine exhaust heat to a cooling water circuit of an engine of the compression heat transfer apparatus. A heat transfer unit that sends heat to the heating unit provided in the absorption heat transfer device or the adsorption heat transfer device; and a low-pressure refrigerant downstream of the expansion valve in the refrigerant circuit of the compression heat transfer device. A heat exchanger for supplying heat to the heat exchanger, and a passage for introducing cooling water to the heat supply section downstream of the heat exchanger for recovering exhaust heat, and cooling water to the heat exchanger for heating refrigerant. Are formed to be branched from each other, and valve means for changing the cooling water flow ratio of these passages is provided.

According to this device, when the valve means is operated in a state where the cooling water having recovered the engine exhaust heat is guided to the heat supply section in the cooling water circuit of the compression heat transfer device, the engine exhaust heat is reduced. It is sent to the absorption type heat transfer device or the adsorption type heat transfer device, and is effectively used for heating the absorbing liquid or the adsorbent for regeneration. On the other hand, when the valve means is operated in a state in which the cooling water in which the engine exhaust heat is recovered in the cooling water circuit is guided to the refrigerant heating heat exchanger, the engine exhaust heat is effective for heating the low-pressure refrigerant in the refrigerant circuit. Used. In this way, the utilization of engine exhaust heat is increased.

In the present invention, the cooling water circuit is provided with a passage for guiding the cooling water to the radiator and a passage branching off from the passage and bypassing the radiator, and the cooling water circulation ratio of these passages can be changed. If the valve means is provided, the amount of heat radiation in the radiator is adjusted according to a change in the temperature of the cooling water due to the supply of heat or the like in the heat supply unit,
Good engine cooling performance is also maintained.

Further, in the apparatus of the present invention, the compression heat transfer device constitutes an air conditioner capable of cooling and heating, and comprises an outdoor heat exchanger and an indoor heat exchanger in a refrigerant circuit and a cooling operation. During the heating operation, a four-way valve that switches the refrigerant flow state so that the outdoor heat exchanger becomes a condenser and the indoor heat exchanger becomes an evaporator, and during heating operation, the indoor heat exchanger becomes a condenser and the outdoor heat exchanger becomes an evaporator. If provided, a heat exchanger for heating the refrigerant may be provided between the four-way valve and the outdoor heat exchanger.

Alternatively, an accumulator is further provided between the four-way valve and the suction port of the compressor in the refrigerant circuit of the compression heat transfer device constituting the air conditioner, and the heat exchanger for heating the refrigerant is provided in the accumulator. It may be. Also in this case, the low-pressure refrigerant is heated when the cooling water from which the engine exhaust heat is recovered is guided to the refrigerant heating heat exchanger. In addition, the stagnation of the liquid-phase refrigerant in the accumulator can be reduced.

In the apparatus of the present invention, a fluid circulation path for circulating a heat-carrying fluid through a heating section provided in the absorption-type heat transfer device or the adsorption-type heat transfer device is formed. If a heat exchanger for applying heat from the cooling water in the cooling water circuit to the fluid in the fluid circulation path is provided as a heat supply unit, the valve means operates in a state where the cooling water is guided to the heat exchanger. When the heat transfer is performed, the engine exhaust heat is sent from the heat exchanger to the absorption heat transfer device or the adsorption heat transfer device via the fluid circulation path.

Further, in this structure, a bypass passage which bypasses a heating section provided in the absorption type heat transfer device or the adsorption type heat transfer device is provided in the fluid circulation path, and a bypass passage for the heating section and the bypass passage is provided. If a valve means that can change the flow ratio of the fluid is provided, the amount of heat supplied to the heating unit provided in the absorption heat transfer device or the adsorption heat transfer device is appropriately adjusted.

[0019]

Embodiments of the present invention will be described with reference to the drawings.

FIG. 1 shows an air conditioner as an example of a composite heat transfer device according to the present invention. The air conditioner includes a compression heat pump system 1 as a compression heat transfer device,
An absorption refrigeration system 70 as an absorption heat transfer device is provided.

The compression heat pump system 1 includes a water-cooled gas engine 2 (hereinafter abbreviated as engine 2), a refrigerant circuit 10 having a compressor 11 driven by the engine 2, and cooling the engine 2. And a cooling water circuit 50 are provided. A part of the refrigerant circuit 10 (at least an indoor heat exchanger described later) is provided in the indoor unit A of each room where cooling and heating are to be performed, while the other part of the refrigerant circuit 10, the engine 2, the cooling water circuit 40, and the like are located outside the room. Machine B.

In the main body 3 of the engine 2, a fuel gas supply passage 4 for supplying a fuel gas and an air introduction passage (not shown) are combined by a mixer (not shown) to form a mixture passage (not shown). And the exhaust passage 5 are connected. The fuel gas supply passage 4 is provided with an electromagnetic valve 6 for controlling the flow rate of the fuel gas. The engine body 3 is provided with a water jacket 7. In the exhaust passage 5, a first exhaust gas heat exchanger 8 is provided on the upstream side, and a second exhaust gas heat exchanger 9 is provided on the downstream side.
Is provided.

The refrigerant circuit 10 sends the refrigerant discharged from the compressor 11 through a condenser, an expansion valve, and an evaporator.
This constitutes a closed circuit for circulating back to 1. In the present embodiment, a four-way valve 12 for switching the refrigerant circulation path according to the time of cooling and the time of heating is provided, and the outdoor heat exchanger 13 configuring one of the condenser and the evaporator, and configuring the other Indoor heat exchanger 14 and electronic expansion valves 15, 16, and 17, and a plurality of indoor heat exchangers 14 and electronic expansion valves 15 connected thereto are provided to enable cooling and heating of a plurality of rooms. ing.

More specifically, the refrigerant circuit 10 will be described. Between the compressor 11 and the four-way valve 12, a discharge-side line 21 connecting the discharge port of the compressor 11 and the first port 12a of the four-way valve 12 is provided. , The second port 12b of the four-way valve 12 and the compressor 11
And a suction-side line 22 for connecting the suction port with the suction port. The discharge side line 21 is provided with an oil separator 23 for separating oil from high-pressure refrigerant. An accumulator 24 for separating the liquid-phase refrigerant and returning only the gas-phase refrigerant to the suction port of the compressor 11 is provided in the suction-side line 22.

An outdoor heat exchanger 13 is connected to the third port 12c of the four-way valve 12 via a line 25.
In addition, a refrigerant heat exchanger for supplying the engine exhaust heat to the low-pressure refrigerant downstream of the expansion valve and heating the low-pressure refrigerant is incorporated,
In this embodiment, in order to heat the low-pressure refrigerant at the portion downstream of the expansion valve during heating, a double pipe as a heat exchanger for heating the refrigerant is provided in the middle of the line 25 between the four-way valve 12 and the outdoor heat exchanger 13. Heat exchanger 26 (hereinafter referred to as WR heat exchanger 26)
Is provided.

A receiver 28 is connected to the outdoor heat exchanger 13 via a line 27 and an electronic expansion valve 16. A line 29 extending from the receiver 28 branches on the indoor unit side, and each branch line is connected to the electronic expansion valve 15 of the indoor unit A.

On the other hand, a line 30 is connected to the fourth port 12d of the four-way valve 12, and this line 30 is branched on the indoor unit side, and each branch line is connected to the indoor heat exchanger 14, and An electronic expansion valve 15 is connected to the exchanger 14.

Further, the refrigerant circuit 10 is provided with a bypass passage 31 branched from the discharge side line 21 between the compressor 11 and the four-way valve 12 and having a downstream end reaching the receiver 28. An electronic expansion valve 17 is provided in the bypass passage 31, and a condensed heat recovery heat exchanger 32 (hereinafter, an RW heat exchanger 3) is provided upstream of the electronic expansion valve 17.
2), and the RW heat exchanger 32
An electromagnetic valve 33 for adjusting the flow rate is provided upstream of.

The cooling water circuit 40 has a water pump 42 for circulating cooling water, and has a water jacket 7 as a heat exchanger for recovering exhaust heat of extracting high-temperature engine exhaust heat.
A heat exchanger 43 (hereinafter, referred to as a WW heat exchanger 43) as a heat supply unit for a heating unit provided in the absorption refrigeration system 70, including the first exhaust gas heat exchanger 8; The WR heat exchanger 26 is incorporated therein, and a passage for introducing cooling water to the WW heat exchanger 43 downstream of the first exhaust gas heat exchanger 8 and cooling to the WR heat exchanger 26 are provided. A passage for guiding water is branched off from each other.
Further, a radiator 44 and a passage that bypasses the radiator 44 are provided.

More specifically, in the main passage 41 of the cooling water circuit 40, the cooling water discharged from the water pump 42 receives the water jacket 7, the first exhaust gas heat exchanger 8, the WW heat exchanger 43, and the radiator. A circulation path is configured so as to return to the water pump 42 via 44. In addition, the WW heat exchanger 4
Radiator bypass passage 4 that branches off from main passage 41 between radiator 44 and radiator 44 and bypasses radiator 44
5 are provided, and electromagnetic valves 46 and 47 are provided in a passage passing through the radiator 44 and a radiator bypass passage 45 to adjust a cooling water flow ratio of these passages. Instead of the two solenoid valves 46 and 47, a three-way solenoid valve may be provided at a branch point of the radiator bypass passage 45 from the main passage 41 (see FIG. 3 described later).

Further, a part of the high-temperature cooling water branched from the main passage 41 downstream of the first exhaust gas heat exchanger 8 is supplied to the WR.
A passage 48 leading to the heat exchanger 26 is provided.
Reaches the main passage 41 downstream from the radiator 44 via the WR heat exchanger 26. An electromagnetic valve 49 for adjusting the flow rate of the cooling water is provided in the middle of the passage 48.

The main passage 41 which guides the cooling water to the WW heat exchanger 43 is formed by the solenoid valve 49 and the solenoid valves 46 and 47.
-R means for changing the flow rate of the cooling water with the passage 48 leading to the heat exchanger 26 is provided.
The valve means 6 and 47 make it possible to change the cooling water flow ratio between the passage for guiding the cooling water to the radiator 44 and the radiator bypass passage 45. That is, the opening degree of these three solenoid valves 46, 47, 48 is controlled by a control unit (not shown), so that the cooling water passing through the WW heat exchanger 43 and the cooling water passing through the WR heat exchanger 26 are cooled. The flow ratio of the water is adjusted, and the flow ratio of the cooling water passing through the radiator 44 and the cooling water passing through the radiator bypass passage 45 among the cooling water passing through the WW heat exchanger 43 is adjusted. ing.

On the other hand, the absorption refrigeration system 70 comprises an evaporator 71, an absorber 72, a regenerator 73, a condenser 74 and the like (see FIG. 2) as described later. A heating unit is provided for heating the absorbent for regeneration using the waste heat given thereto. In this embodiment, two heat receiving heat exchangers 75 and 76 on the high temperature side and the low temperature side are provided as the heating unit. ing. Further, between the compression heat pump system 1 and the absorption refrigeration system 70, a first exhaust heat utilization circuit (fluid circulation circuit) 50 and a second exhaust heat utilization circuit 60 are provided. .

The first exhaust heat utilization circuit 50 is connected to the water jacket 7 and the first exhaust gas heat exchanger 8 by W-
The high-temperature engine exhaust heat taken out through the W heat exchanger 43 is sent to the high-temperature side heat receiving heat exchanger 75 of the absorption refrigeration system 70. It is formed so as to circulate water or antifreeze as a fluid over the heat exchanger 75, and a water pump 51 is provided in the circulation path 50.

The second exhaust heat utilization circulation path 60 is used for exhaust heat from the second exhaust gas heat exchanger 9 and R-
The heat of condensation taken out of the W heat exchanger 32 is sent to the low-temperature side heat receiving heat exchanger 76 of the absorption refrigeration system 70,
The second exhaust gas heat exchanger 9 and the RW heat exchanger 32 arranged in series and the low-temperature-side heat receiving heat exchanger 76 are formed so as to circulate water or antifreeze as a fluid. A water pump 61 is interposed in 60.

The circulation paths 50, 60 are provided with bypass passages 52, 62 for bypassing the heat receiving heat exchangers 75, 76, respectively, and the heat receiving heat exchangers 75, 76 and the bypass passages are provided respectively. Three-way solenoid valves 53 and 63 are provided for regulating the flow of water with respect to 52 and 62. Further, temperature sensors 54, 64 for detecting the temperature of water sent to the heat receiving heat exchangers 75, 76 are provided for the respective circulation paths 50, 60.

The signals from the temperature sensors 54 and 64 are input to a control unit (not shown), and the control unit controls the three-way solenoid valves 53 and 63 according to the detected temperature. In addition,
The four-way valve 12, the electronic expansion valves 15, 16, 17 and the solenoid valve 33 provided in the refrigerant circuit 10, and the solenoid valves 46, 47, 49 provided in the cooling water circuit 40 are also controlled by the control unit. It has become so.

FIG. 2 shows an example of the absorption refrigeration system 70. The absorption refrigeration system shown in FIG. 2 is a single-effect cycle and is used for cooling each room. The absorption refrigeration system 70 includes an evaporator 71, an absorber 7
2. A regenerator 73 and a condenser 74 are provided, between which a passage for the refrigerant and the absorbing liquid is provided, and a cooling water circuit 90 for cooling the refrigerant and the like in the absorber 72 and the condenser 74. And a chilled water circuit 95 for extracting chilled heat from the evaporator 71. And the chilled water circuit 95
(At least the indoor heat exchanger 97) is provided in the indoor unit A ', and the other part is provided in the outdoor unit B'.

In the evaporator 71, a heat transfer tube 95a forming a part of the cold water passage 95 is disposed in a container maintained at a high vacuum.
Refrigerant liquid such as water introduced from above is dropped on the heat transfer tube 95a and evaporated, so that heat corresponding to heat of vaporization is taken from the water in the heat transfer tube 95a.
The evaporator 71 is connected to a refrigerant liquid passage 77 for guiding a refrigerant liquid from a condenser 74 and a refrigerant vapor passage 78 for extracting refrigerant vapor generated in the evaporator 71. Further, in order to return the unevaporated refrigerant accumulated at the bottom of the evaporator 71 to the upper part of the evaporator 71, a passage 79 provided with a refrigerant pump 80 is provided in the evaporator 7
1 connected.

The absorber 72 is configured such that the absorbing liquid is dropped into a container maintained at a high vacuum so that the refrigerant vapor sent from the evaporator 71 is absorbed by the absorbing liquid.
The absorber 72 is connected to the refrigerant vapor passage 78, a concentrated solution passage 81 for leading the absorbing liquid from the regenerator 73, and a dilute solution passage 82 for leading the absorbing liquid (dilute solution) after absorbing the refrigerant. The dilute solution passage 82 is provided with a solution pump 83 for sending the dilute solution to the regenerator 73.

The regenerator 73 is configured to evaporate and separate the refrigerant by heating the dilute solution sent from the absorber 72. The dilute solution passage 82 is provided above the regenerator 73 to introduce the dilute solution. Are connected to each other, and a refrigerant vapor passage 84 and a concentrated solution passage 81 are formed at an upper end and a lower end of the regenerator 73 to derive the separated refrigerant vapor and the absorbent (concentrated solution) after the refrigerant separation. It is connected.

A high-temperature-side heat-receiving heat exchanger 75 is provided in the dilute solution passage 82 near the regenerator 73. The low-temperature-side heat-receiving heat exchanger 76 is provided at an upstream portion (portion near the absorber) of the dilute solution passage 82, and further, the dilute solution in the dilute solution passage 82 is concentrated in the dilute solution passage 82. A solution heat exchanger 85 for performing heat exchange with the concentrated solution in the solution passage 81 is provided. The regenerator 73 is provided with a burner 86, and the burner 86 is provided with a gas control valve 88.
Is connected to the fuel gas passage 87.

The condenser 74 cools the refrigerant vapor sent from the regenerator 73 by cooling water to condense and liquefy the refrigerant vapor. The refrigerant vapor passage 84 is provided at the upper end of the condenser 74.
Is connected to the refrigerant liquid passage 7 at the lower end of the condenser 74.
7 is connected.

The cooling water circuit 90 is formed over a cooling tower 91, a pump 92, a passage arranged inside the absorber 72, and a passage arranged inside the condenser 74. The cooling water cooled in 91 is absorbed by the absorber 7
2 and a condenser 74 to cool them.

The chilled water circuit 95 is configured to circulate water through a heat transfer tube 95a disposed inside the evaporator 71, a pump 96, and a passage on the indoor unit side, and is cooled by the evaporator 71. The cooled water is sent to an indoor heat exchanger 97 provided in the indoor unit to be used for cooling or the like.
As a passage on the indoor unit side, a passage 95b connected to each of the plurality of indoor exchangers 97 is provided in parallel, and further, a passage 95c that bypasses the indoor exchanger 97 in parallel with these.
Are provided, and a control valve 98 for controlling the flow rate is interposed in these passages 95b and 95c.

The operation of the composite heat transfer device according to this embodiment as described above will be described below.

During the cooling operation, in the refrigerant circuit 10 of the compression heat pump system 1, the first port 12a and the third port 12c of the four-way valve 12 are controlled by a controller (not shown).
Are communicated, and the fourth port 12d and the second port 12b are communicated. Further, the solenoid valve 33 and the electronic expansion valve 17 in the bypass passage 31 are opened, and the line 27 is opened.
The electronic expansion valve 16 is closed except that it is temporarily opened periodically as described later. The electronic expansion valve 15 of the indoor unit A is set to an appropriate throttle state.

In such a state, the refrigerant discharged from the compressor 11 to the discharge side line 21 passes through the bypass passage 31 and is radiated by the RW heat exchanger 32 as indicated by a solid line arrow in FIG. , After being condensed and liquefied, the electronic expansion valve 17,
After reaching the electronic expansion valve 15 via the receiver 28 and the line 29, the expansion is performed here, and then the air is guided to the indoor heat exchanger 14 serving as an evaporator, where the heat is absorbed to cool the room. Then, it flows into the suction side line 22 through the line 30 and the four-way valve 12, and is returned to the compressor 11 through the accumulator 24. In this case, in the present embodiment, the refrigerant flows through the bypass passage 31 so that the RW heat exchanger 32 becomes a condenser instead of the outdoor heat exchanger 13, but the so-called refrigerant stays in the outdoor heat exchanger 13. To prevent falling asleep,
The cooling fan (not shown) for the outdoor heat exchanger 13 is configured to reduce or stop the rotation speed, and the electronic expansion valve 16 is closed, but may be temporarily opened at regular intervals.

In the cooling water circuit 40, the electromagnetic valve 4 provided in the passage 48 for guiding the cooling water to the WR heat exchanger 26
9 is closed, and according to the temperature of the cooling water at the engine outlet, the cooling water flows to the radiator 44 when the cooling water temperature is higher than a set temperature, and when the cooling water temperature is low, the cooling water flows when the cooling water temperature is low. The electromagnetic valves 46 and 47 are controlled so as to flow into the radiator bypass passage 45.

On the other hand, in the absorption refrigeration system 70, the refrigerant liquid is evaporated in the evaporator 71, and the refrigerant vapor is guided to the absorber 72 and absorbed by the absorption liquid. And the refrigerant is evaporated and separated by heating, and the absorbing liquid after the refrigerant separation is sent to the absorber 72, while the separated refrigerant vapor is condensed and liquefied in the condenser 74 and then sent to the evaporator 71. Is repeated. Then, the water in the heat transfer tube 95 a of the chilled water circuit 95 is cooled by the evaporation of the refrigerant in the evaporator 71, and the chilled water is sent to the indoor heat exchanger 97 to perform cooling.

Thus, the compression heat pump system 1
When the and the absorption refrigeration system 70 are performing the cooling operation, the solenoid valve 49 is closed in the cooling water circuit 40 as described above, so that the water jacket 7 and the first exhaust gas heat exchanger 8 are connected. The passed cooling water passes through the WW heat exchanger 43, and the high-temperature engine exhaust heat extracted from the water jacket 7 and the first exhaust gas heat exchanger 8 is first exhausted by the WW heat exchanger 43. It is transmitted to the water in the heat utilization circuit 50. Then, the engine exhaust heat is sent to the high-temperature side heat receiving heat exchanger 75 of the absorption refrigeration system 70 by the first exhaust heat utilization circulation path 50, and is used for heating the absorbing liquid near the regenerator 73. Can be

Further, the RW heat exchanger 32 and the second exhaust gas heat exchanger 9 in the compression heat pump system 1 convert the heat of condensation of the high-pressure refrigerant in the refrigerant circuit and the engine exhaust heat into the second heat.
Is transferred to the water in the exhaust heat utilization circulation path 60, and is sent to the low-temperature-side heat-receiving heat exchanger 76 of the absorption refrigeration system 70, and in the dilute solution passage 82 upstream of the high-temperature-side heat-receiving heat exchanger 75. Provided for heating the absorbing liquid.

As described above, the absorbing liquid is heated by the engine exhaust heat or the like given from the compression heat pump system 1 to the absorption refrigeration system 70. In this embodiment, particularly,
The heating of the absorbing liquid is efficiently performed in a stepwise manner by the low-temperature-side heat receiving heat exchanger 76 and the high-temperature-side heat receiving heat exchanger 75.
Therefore, the amount of heat required when the refrigerant is evaporated and separated by heating with the burner in the regenerator 73 can be reduced, and the fuel consumption can be greatly reduced.

That is, the temperature of the absorbing liquid is raised by recovering the exhaust heat and the condensing heat of the engine, and when the outlet temperature of the evaporator 71 becomes lower than the set temperature (about 7 ° C.), the gas control valve 88 is throttled. The fuel is reduced.

The amount of water supplied to the heat receiving heat exchangers 75 and 76 in each of the exhaust heat utilization circulation paths 50 and 60 is controlled according to the temperature detected by the temperature sensors 54 and 64. That is, if the temperature of the water in the first exhaust heat utilization circulation path 50 detected by the temperature sensor 54 is equal to or higher than the first set temperature (about 70 ° C.), the hot water flows to the high-temperature side heat receiving heat exchanger 75. However, when the temperature is lower than the first set temperature, the three-way solenoid valve 53 is controlled to a bypass state (a state in which the bypass passage 52 is opened).
Further, the temperature of the water in the second exhaust heat utilization circuit 60 detected by the temperature sensor 64 is equal to the second set temperature (about 50 ° C.).
If so, the hot water flows to the low-temperature-side heat-receiving heat exchanger 76, but when the temperature is lower than the second set temperature, the three-way solenoid valve 63 is controlled to a bypass state (a state in which the bypass passage 62 is opened).

The absorption refrigeration system 70 can perform cooling operation alone even when the operation of the compression heat pump system 1 is stopped. In this case, exhaust heat is not supplied from the compression heat pump system 1. The amount of fuel supplied to the burner 86 of the regenerator 73 may be increased by that amount.

The above-mentioned compression heat pump system 1
During heating by the first port 12a of the four-way valve 12,
And the fourth port 12d, and the third port 12c and the second port 12b. further,
The electromagnetic valve 33 and the electronic expansion valve 17 in the bypass passage 31 are closed, the electronic expansion valve 16 in the line 27 is set to an appropriate throttle state, and the electronic expansion valve 15 is controlled to adjust the flow rate.

In such a state, the refrigerant discharged from the compressor 11 to the discharge side line 21 passes through the four-way valve 12 through the line 30 as shown by the broken line arrow in FIG. It is led to the heat exchanger 14, where it is condensed and liquefied, and the condensed heat is used for heating. Then, the electronic expansion valve 15, line 29, receiver 28, electronic expansion valve 16,
After passing through the line 27 and being led to the outdoor heat exchanger 13 serving as an evaporator, where the heat is absorbed and vaporized, the WR heat exchanger 2
The air flows into the suction side line 22 through the 6 and the four-way valve 12, and returns to the compressor 11 through the accumulator 24.

At this time, in the cooling water circuit 40, the solenoid valve 49 is opened, so that the warm water recovered from the engine exhaust heat by the water jacket 7 and the first exhaust gas heat exchanger 8 is supplied to the WR heat exchanger. Guided to 26, the low pressure refrigerant is heated. Thereby, the evaporation of the refrigerant is promoted, and the temperature of the refrigerant sucked into the compressor 11 rises, and accordingly, the temperature of the refrigerant discharged from the compressor rises, so that the heating performance is improved.

As described above, the solenoid valve 49 is switched between the closed state and the open state according to the time of cooling and the time of heating of the compression heat pump system 1, so that the engine exhaust heat is absorbed during the cooling and the absorption refrigeration system is used. And is used for heating the absorbing liquid for regeneration, while it is used for heating the low-pressure refrigerant to improve the heating performance of the compression heat pump system 1 during heating. Therefore, the exhaust heat of the engine is used most effectively.

The specific structure of the device of the present invention is not limited to the above embodiment, but can be variously modified.

For example, one end of the bypass passage 31 in the refrigerant circuit 10 of the compression heat pump system 1 is connected between the four-way valve 12 and the outdoor heat exchanger 13 as shown by a two-dot chain line in FIG. You may keep it. In this way, during cooling, the high-pressure refrigerant is guided to the bypass passage 31 and the RW heat exchanger 32 supplies condensing heat as in the above embodiment. On the other hand, at the time of heating and the absorption refrigeration system 7
0 is stopped, the second refrigerant utilization circuit 60
When the three-way electromagnetic valve 63 is in the bypass state and the electromagnetic valve 33 in the bypass passage 31 is opened, the low-pressure refrigerant that has passed through the indoor heat exchanger 14 and the electronic expansion valve 15 flows into the bypass passage 31, and R -W heat exchanger 32
However, the low-pressure refrigerant is heated by the exhaust heat of the engine. Thereby, the heating performance is further improved.

As shown in FIG. 3, in the compression heat pump system 1, the heat exchanger 101 for guiding the cooling water (hot water) after the recovery of the engine exhaust heat from the cooling water circuit 40 to heat the low-pressure refrigerant is connected to the refrigerant. Suction side line 22 of circuit 10
May be arranged in the accumulator 24 provided in the storage device.

That is, in the embodiment shown in this figure, heat exchangers 101 and 102 for heating the stored liquid-phase low-pressure refrigerant are arranged in the accumulator 24, and the heat exchanger 101 is provided with a cooling water circuit. 40 to three-way solenoid valve 103
The three-way solenoid valve 1 is provided in a passage 104 branched through
03, when the passage 104 is opened to the cooling water circuit 40, the cooling water recovered from the engine exhaust heat is supplied to the heat exchanger 1
01. In addition, the heat exchanger 10
2 cools the liquefied refrigerant that has passed through the RW heat exchanger 32 or the outdoor heat exchanger 13 during cooling, and further cools the refrigerant during the cooling to a supercooled state.

Also in this embodiment, the cooling water recovered from the engine exhaust heat is guided to the heat exchanger 101 during heating, thereby heating the low-pressure refrigerant and reducing the accumulation of the liquid-phase refrigerant in the accumulator 24. Can be. In addition, during cooling, the cooling water that has recovered the engine exhaust heat is
The three-way solenoid valve 103 is switched to a state where the three-way solenoid valve 103 is guided to the heat exchanger 43, and the first exhaust heat utilization circuit 5 is connected to the WW heat exchanger 43.
The engine exhaust heat is supplied to the absorption refrigeration system via the refrigeration system.

For adjusting the flow rate of the radiator 44 and the radiator bypass passage 45 in the cooling water circuit, a three-way solenoid valve 105 is provided at a separation point of the radiator bypass passage 45 in the example shown in FIG. The electromagnetic valves 46 and 47 shown in FIG.

FIG. 4 shows a modified example (only the main part) of the absorption refrigeration system 70. This example is also a single-effect cycle, but the difference from the one shown in FIG. In the example shown in FIG. 1, exhaust heat sent from the compression heat pump system is recovered only by sensible heat, whereas in this example, latent heat and sensible heat are recovered.

That is, the point that the low-temperature-side heat receiving heat exchanger 76 for receiving heat from the second exhaust heat utilization circulation path 60 and the solution heat exchanger 85 are provided in the dilute solution passage 82 is shown in FIG. However, the heat exchanger 110 for high-temperature side heat receiving, which receives heat from the first exhaust heat utilization circuit 50, is a regenerator 73.
It is provided in. And, the heat exchanger 76 for low-temperature side heat receiving
And the heat given to the dilute solution by the solution heat exchanger 85 becomes sensible heat that raises the temperature of the dilute solution, but the heat given by the high-temperature side heat receiving heat exchanger 110 becomes latent heat for evaporating the refrigerant. Have been.

Also in this example, the exhaust heat of the engine and the heat of condensation of the refrigerant of the compression heat pump system 1 are effectively used in the absorption refrigeration system 70, and the absorption liquid after absorbing the refrigerant is heated stepwise and efficiently.

FIG. 5 shows, as a modified example of the absorption refrigeration system 70, a double effect cycle in which the waste heat sent from the compression heat pump system 1 is recovered only by sensible heat. .

In this figure, evaporator 71, absorber 7
2. The configurations of the condenser 74, the cooling water circuit 90, the cooling water circuit 95, and the like are the same as those shown in FIG. 2, but two high temperature regenerators 73A and 73B are provided as regenerators. A low temperature side heat receiving heat exchanger 76, a solution heat exchanger 85, and a high temperature side heat receiving heat exchanger 75 are provided in a dilute solution passage 82 for drawing out a dilute solution from the absorber 72 via a pump 83. Downstream, the dilute solution passage 82 has two passages 8.
2a and 82b, one of the passages 82a reaches the high-temperature regenerator 73A via the high-temperature solution heat exchanger 111, and the other passage 82b reaches the low-temperature regenerator 73B.

The high temperature regenerator 73A is provided with a burner 86. The high-temperature regenerator 73A is connected to a refrigerant passage 112 for leading out the refrigerant separated and evaporated, and a passage 114 for leading out the absorbent after the refrigerant separation. After passing through the low-temperature regenerator 73B, the refrigerant passage 112 passes through the condenser 74.
Has been reached. Further, a refrigerant vapor passage 113 for leading the refrigerant evaporated and separated by the regenerator 73B and a passage 11 for leading the absorbent after the refrigerant separation are provided to the low-temperature regenerator 73B.
5 is connected, and the refrigerant vapor passage 113 is connected to the condenser 74.
Has been reached.

The passage 114 passes through the high-temperature solution heat exchanger 111 and then passes through the passage 114 and the passage 11.
5 have passed through the low-temperature solution heat exchanger 85 and reached the absorber 72. Other structures are the same as those shown in FIG.

According to this example, the dilute solution is heated by the high-temperature regenerator 73A, the refrigerant is evaporated and separated, and the refrigerant vapor is led out to the passage 112. In the low-temperature regenerator 73B,
The dilute solution is heated by the heat of condensation of the refrigerant in the passage 112 passing therethrough, and the refrigerant is evaporated and separated.
The refrigerant vapor led from B to the passage 113 and the refrigerant in the passage 112 are sent to the condenser 74. On the other hand, the high temperature regenerator 73A
And passages 114 and 115 from the low-temperature regenerator 73B, respectively.
Is discharged to the absorber 72 after the separation of the refrigerant.

As described above, the two-stage heat treatment is performed by the high-temperature regenerator 73A and the low-temperature regenerator 73B. Further, the heat exchangers 76, 85, 75, 111 are used while the absorbent after absorbing the refrigerant passes through the dilute solution passage 82 toward the regenerator.
And the temperature is raised sufficiently. For this reason, the efficiency is further improved.

FIG. 6 shows, as a modified example of the absorption refrigeration system 70, a double effect cycle in which waste heat sent from the compression heat pump system 1 is recovered by sensible heat and latent heat. ing.

In this figure, a low-temperature-side heat receiving heat exchanger 76 and a solution heat exchanger 85 are provided in a dilute solution passage 82, and a dilute solution passage 82
5a and 5b, one of the passages 82a reaches the high-temperature regenerator 73A via the high-temperature solution heat exchanger 111, and the other passage 82b reaches the low-temperature regenerator 73B.
Is the same as that shown in FIG.
The high-temperature side heat-receiving heat exchanger 120 for receiving heat from the low-temperature regenerator 73B. Then, the heat given to the dilute solution in the low-temperature side heat receiving heat exchanger 76 and the solution heat exchangers 85 and 111 becomes sensible heat that raises the temperature of the dilute solution.
The low-temperature regenerator 73B is configured so that the heat given by the heat exchanger 120 becomes latent heat for evaporating the refrigerant.

FIG. 7 shows a further modification of the absorption refrigeration system 70 in which the system 70 is configured to perform heating in addition to cooling.

More specifically, the system 70 shown in this figure has a structure similar to that shown in FIG. 5, and a passage 121 branched from a passage 112 for leading the refrigerant vapor from the high-temperature regenerator 73A. It is formed so as to bypass the container 73B and the condenser 74 and reach the container 71 which becomes an evaporator during cooling, and an electromagnetic valve 122 is interposed in this passage 121. Further, a passage 123 is formed to connect the lower part of the container (evaporator) 71 and the middle of the dilute solution passage 82, and an electromagnetic valve 124 is provided in the passage 123. Further, the low-temperature regenerator 73 branches off from the dilute solution passage 82.
An electromagnetic valve 125 is provided in the passage 82a reaching B. In the case of this figure, instead of the refrigerant vapor passage 78 that connects the ceiling of the evaporator 71 and the ceiling of the absorber 72 and allows the refrigerant vapor to pass through, the intermediate part of the evaporator 71 and the intermediate part of the absorber are used. In addition, a passage 78A for passing mainly a refrigerant vapor or a dilute solution absorbing and diluting the refrigerant liquid, and in some cases, passing both the dilute solution and the refrigerant vapor is disposed.

According to this structure, during cooling, the solenoid valve 1
By opening the solenoid valve 25 and closing the solenoid valves 122 and 124, the same operation as that shown in FIG. 5 is performed.
Further, at the time of heating, when the electromagnetic valve 125 is closed and the electromagnetic valves 122 and 124 are opened, the refrigerant vapor derived from the high-temperature regenerator 73A is guided to the container 71, where it is liquefied. The heat of condensation heats the water circulating in circuit 95. The dilute solution flowing to the evaporator 71 through the passage 123 branched from the dilute solution passage 82 is
The refrigerant vapor (refrigerant liquid) sprayed by the refrigerant pump 80 and introduced from the high-temperature regenerator is absorbed and diluted, and the passage 78
And overflows to the absorber 72 side. The dilute solution in the absorber passes through the dilute solution passage 82 as in FIG.
It is led to A.

The hot water heated in the container 71 is supplied to the circuit 95
Is guided to the indoor heat exchanger 97 provided in the
Heating is performed.

FIG. 8 shows another embodiment of the combined heat transfer apparatus of the present invention, in which the compression heat pump system 1 and the adsorption refrigeration system 130 as the adsorption heat transfer apparatus are combined. Note that the compression heat pump system 1 may be configured similarly to FIG. 1 or FIG.
Detailed illustration is omitted.

In this figure, the adsorption refrigeration system 13
0 indicates two adsorption regenerators 131,
132, an evaporator 133, and a condenser 134, and a chilled water passage 170 for extracting cold generated in the evaporator 133.

Each of the two adsorption regenerators 131 and 132 has an adsorbent such as silica gel in its container, adsorbs a refrigerant such as water to the adsorbent while cooling the inside of the container, and heats the inside of the container. The regenerating process of desorbing the refrigerant from the adsorbent while repeating the process is repeated.
The strokes are shifted from each other so that when one of the 32 is the suction stroke, the other is the regeneration stroke.

In the evaporator 133, a heat transfer tube 170a forming a part of the cold water passage 170 is disposed in the container, and a refrigerant liquid guided from the condenser 134 through the passage 135 is dropped on the heat transfer tube 170a. By evaporating, heat corresponding to the heat of vaporization is taken from the water in the heat transfer tube 170a. Unevaporated refrigerant remaining at the bottom of the evaporator 133 passes through a passage provided with a refrigerant pump 136, and the evaporator 13
3 to be returned to the top. Further, the evaporator 133 is connected to each of the adsorption regenerators 1 through a passage 137 and a pair of solenoid valves 138 and 139 which are opened and closed alternately.
The refrigerant vapors which are connected to the evaporator 133 are sent to an adsorption regenerator in an adsorption process.

The condenser 134 is connected to the adsorption regenerators 131 and 132 via a passage 140 and a pair of solenoid valves 141 and 142 which are opened and closed alternately.
Refrigerant vapor derived from the adsorption regenerator in the regeneration step is guided to the condenser 134, condensed and liquefied by the condenser 134, and then sent to the evaporator 133.

Further, in order to cool the adsorption regenerator and the condenser 134 in the adsorption process, the cooling water passage 14 through which the cooling water cooled in the cooling tower 143 is supplied by the pump 144.
The cooling water passage 145 is branched into two passages 146 and 147 downstream of the pump 144.
The passage 146 passes through the inside of the condenser 134 to cool the condenser 134, and passes through the cooling water passage 14 leading to the cooling tower 143.
9 has been reached. An electromagnetic valve 148 is provided in the passage 146.

Each of the adsorption regenerators 131 and 132 has a first heat exchanger 15 serving both for high-temperature side heat receiving and cooling.
1, 153 and second heat exchangers 152, 154, which are heat exchangers for low-temperature side heat reception. Then, the compression heat pump system 1 is connected to the first exhaust heat utilization circuit 50.
And the engine exhaust heat and the refrigerant condensation heat sent by the second exhaust heat utilization circuit 60 are supplied to the adsorption regenerator in the regeneration step.
The passage between these and the heat exchangers 151 to 154 is configured so that the adsorption regenerator in the adsorption process is cooled by the cooling water guided from the cooling water passage 145.

That is, the passage 1 leading to the introduction side of each of the first heat exchangers 151 and 153 of both the adsorption regenerators 131 and 132
59, 160, the passage 14 branched from the inflow side passage 50a of the first exhaust heat utilization circulation passage 50 and the cooling water passage 145.
7 are connected via electromagnetic valves 155 to 158 such that they selectively communicate with each other to switch the communication state, and communicate with the outlet sides of the first heat exchangers 151 and 153. The solenoid valve 163 is connected to the passages 161 and 162 so that the outflow side passage 50b of the first exhaust heat utilization circulation passage 50 and the cooling water passage 149 selectively communicate with each other and switch the communication state. Through 166.

Further, the inlet side passages 60a of the second exhaust heat utilization circulation path 60 alternately communicate with the introduction side portions of the second heat exchangers 152 and 154 of both the adsorption regenerators 131 and 132. The second heat exchangers 152 and 154 are connected to the outlet side portions of the second heat exchangers 152 and 154, respectively.

The chilled water passage 170 circulates water through a heat transfer tube 170 a disposed inside the evaporator 133, a pump 171, a passage connected to a plurality of indoor heat exchangers 172, and a passage bypassing these. The passages connected to the indoor heat exchangers 172 and the passages bypassing them are provided with a solenoid valve 173 for adjusting the flow rate.

According to this embodiment, in the adsorption refrigeration system 130, the solenoid valves 138, 139, 141,
142,155-158,163-166,167,1
68 are switched at predetermined intervals, and among them, the solenoid valves 138, 142, 155, 158,
163, 166, 167 are open, and the solenoid valve 1 shown in black
39,141,156,157,164,165,16
When 8 is in the closed state, the adsorption regenerator 131 enters the adsorption step, and the adsorption regenerator 132 enters the regeneration step.

That is, in this state, refrigerant vapor is introduced from the evaporator 133 to the adsorption regenerator 131 through the electromagnetic valve 138, and the refrigerant vapor is introduced from the cooling water passage 145 to the electromagnetic valve 15
The cooling water is led to the first heat exchanger 151 of the adsorption regenerator 131 through 8 to cool the interior of the adsorption regenerator 131 and adsorb refrigerant vapor. On the other hand, the hot water in the first exhaust heat utilization circulation path 50 is guided to the first heat exchanger 153 of the adsorption regenerator 132 through the electromagnetic valve 155, and
The hot water in the exhaust heat utilization circulation path 60 is guided to the second heat exchanger 154 of the adsorption regenerator 132 through the electromagnetic valve 167, so that the inside of the adsorption regenerator 132 is heated to desorb the refrigerant from the adsorbent. Is performed, and the desorbed refrigerant vapor is sent to the condenser 134 via the solenoid valve 142.

Also, contrary to the above state, the solenoid valves 138, 1
42,155,158,163,166,167 are closed,
Solenoid valves 139, 141, 156, 157, 164, 16
When 5,168 is opened, the adsorption regenerator 1
31 is a regeneration step, the adsorption regenerator 132 is an adsorption step,
The refrigerant vapor is introduced from the evaporator 133 to the adsorption regenerator 132 through the electromagnetic valve 139 and is adsorbed, while the refrigerant is desorbed by the adsorption regenerator 131 and the refrigerant vapor is supplied to the electromagnetic valve 141.
Through to the condenser 134.

As described above, the adsorption process and the regeneration process are alternately performed in each of the adsorption regenerators 131 and 132, while the evaporator 1 is being operated.
At 33, the refrigerant is continuously evaporated, whereby the chilled water circuit 1
70 is cooled, and the cold water is guided to the indoor heat exchanger 172 to perform cooling.

Also in this embodiment, the exhaust heat of the engine and the exhaust heat (condensation heat) of the refrigerant circuit generated in the compression heat pump system 1 driven by the engine are equal to the first and second heat.
Is supplied to the adsorption-type refrigeration system 130 through the waste heat utilization circulation paths 50, 60, and is effectively used for regeneration in the adsorption regenerators 131, 132.

In each of the above embodiments, the compression heat pump system 1 is used for cooling and heating each room.
Although the absorption refrigeration system or the adsorption refrigeration system is used for cooling or heating and cooling each room, the absorption refrigeration system or the adsorption refrigeration system may be used as a refrigerator for making ice or supplying cold water. Good. In this case, antifreeze is circulated in the circuit 95 and the passage 170 instead of water.

In the illustrated embodiment, the cooling water circuit 40 and the first exhaust heat utilization circuit 50 are separately formed in the compression heat pump system 1, and the WW heat exchanger 43 is provided therebetween. But the water jacket 7 and the first
The heat supply unit may be configured by providing a passage in the cooling water circuit 40 for guiding the cooling water that has passed through the exhaust gas heat exchanger 8 to an absorption or adsorption refrigeration system.

[0099]

As described above, the present invention relates to a composite heat transfer apparatus comprising a compression heat transfer apparatus driven by a water-cooled engine and an absorption heat transfer apparatus or an adsorption heat transfer apparatus. In the cooling water circuit of the device, a heat exchanger for exhaust heat recovery, a heat supply unit that sends heat to a heating unit provided in an absorption type heat transfer device and the like, and a refrigerant circuit of the compression type heat transfer device A refrigerant heating heat exchanger for supplying heat to the low-pressure refrigerant is provided, and a valve means for changing a cooling water flow ratio between the passage on the heat supply unit side and the passage on the refrigerant heating heat exchanger side is provided. Therefore, when heat for heating the absorbing liquid or the like is required in the absorption heat transfer device or the like, the engine exhaust heat can be supplied from the compression heat transfer device to the absorption heat transfer device or the like, Heating low-pressure refrigerant in the refrigerant circuit of a compression heat transfer device It can be supplied to the engine exhaust heat to the refrigerant heating heat exchanger when required. Therefore,
The utilization of the engine exhaust heat can be greatly increased.

[Brief description of the drawings]

FIG. 1 is an overall circuit diagram showing an embodiment of a composite heat transfer device according to the present invention.

FIG. 2 is a circuit diagram of an absorption refrigeration system in the composite heat transfer device.

FIG. 3 is a circuit diagram showing another example of the compression heat pump system.

FIG. 4 is a main part circuit diagram showing a modification of the absorption refrigeration system.

FIG. 5 is a circuit diagram showing another example of the absorption refrigeration system.

FIG. 6 is a main part circuit diagram showing a further modification of the absorption refrigeration system.

FIG. 7 is a circuit diagram showing still another example of the absorption refrigeration system.

FIG. 8 is a circuit diagram showing another embodiment of the composite heat transfer device of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Compression heat pump system 2 Engine 7 Water jacket 8 First exhaust gas heat exchanger 10 Refrigerant circuit 11 Compressor 12 Four-way valve 13 Outdoor heat exchanger 14 Indoor heat exchanger 15, 16, 17 Electronic expansion valve 26 WR heat exchange Device 40 Cooling water circuit 43 WW heat exchanger 44 Radiator 46, 47, 49 Solenoid valve 50 Waste heat utilization circuit 70 Absorption refrigeration system 75, 76 Heat receiving heat exchanger 130 Adsorption type heat exchanger 151-154 Heat Exchanger

Claims (6)

[Claims] 1. A refrigerant circuit for circulating refrigerant discharged from a compressor through a condenser, an expansion valve, and an evaporator to return to the compressor, and the compressor is driven by a water-cooled engine. An engine-driven compression heat transfer device, comprising an absorption heat transfer device or an adsorption heat transfer device, wherein the absorption heat transfer device or the adsorption heat transfer device includes:
In a combined heat transfer apparatus provided with a heating unit for heating an absorbing liquid or an adsorbent for regeneration, heat exchange for exhaust heat recovery for extracting engine exhaust heat to a cooling water circuit of an engine of the compression heat transfer apparatus. A heat transfer unit that sends heat to the heating unit provided in the absorption heat transfer device or the adsorption heat transfer device; and a low-pressure refrigerant downstream of the expansion valve in the refrigerant circuit of the compression heat transfer device. A heat exchanger for supplying heat to the heat exchanger, and a passage for introducing cooling water to the heat supply section downstream of the heat exchanger for recovering exhaust heat, and cooling water to the heat exchanger for heating refrigerant. And a passage for guiding the cooling water, and a valve means for changing a cooling water flow rate of these passages is provided. 2. A valve for providing cooling water to the radiator and a passage branching off from the passage and bypassing the radiator in the cooling water circuit, the valve being capable of changing a cooling water flow ratio of these passages. The composite heat transfer device according to claim 1, further comprising means. 3. The compression type heat transfer device constitutes an air conditioner capable of cooling and heating, comprising an outdoor heat exchanger and an indoor heat exchanger in a refrigerant circuit, and an outdoor heat exchanger during a cooling operation. Is the condenser, the indoor heat exchanger is the evaporator,
During the heating operation, a four-way valve that switches the refrigerant flow state so that the indoor heat exchanger becomes a condenser and the outdoor heat exchanger becomes an evaporator is provided, and heat exchange for refrigerant heating is performed between the four-way valve and the outdoor heat exchanger. The composite heat transfer device according to claim 1, further comprising a vessel. 4. The compression type heat transfer device constitutes an air conditioner capable of cooling and heating, comprising an outdoor heat exchanger and an indoor heat exchanger in a refrigerant circuit, and an outdoor heat exchanger during a cooling operation. Is the condenser, the indoor heat exchanger is the evaporator,
At the time of heating operation, it has a four-way valve that switches the refrigerant flow state so that the indoor heat exchanger becomes a condenser and the outdoor heat exchanger becomes an evaporator, and furthermore, an accumulator is provided between this four-way valve and the suction port of the compressor 3. The composite heat transfer device according to claim 1, wherein the accumulator is provided with a heat exchanger for heating the refrigerant. 5. A fluid circulation path for circulating a fluid carrying heat so as to pass through a heating unit provided in the absorption type heat transfer device or the adsorption type heat transfer device, and as the heat supply unit, The combined heat transfer device according to any one of claims 1 to 4, further comprising a heat exchanger for applying heat from the cooling water in the cooling water circuit to the fluid in the fluid circulation path. 6. A bypass passage for bypassing a heating unit provided in the absorption heat transfer device or the adsorption heat transfer device is provided in the fluid circulation path, and a fluid flows through the heating unit and the bypass passage. 6. The combined heat transfer device according to claim 5, further comprising a valve means capable of changing the ratio.