JP2019070506A - Absorption type heat exchange system - Google Patents

Abstract

To provide an absorption type heat exchange system which can reduce energy required for fluid conveyance even when a place heat is supplied for is away from a place using it.SOLUTION: An absorption type heat exchange system 1 includes: a temperature rise absorption heat pump X1 higher in evaporation pressure of a cooling medium than in condensation pressure; a carburetion absorption heat pump Y1 lower in evaporation pressure of the cooling medium than in condensation pressure; a temperature rise object fluid passage 81 leading heated temperature rise object fluid RP to the carburetion absorption heat pump Y1; and a low-temperature heat source fluid passage 82 leading a low-temperature heat source fluid GP flown out of the carburetion absorption heat pump Y1 to the temperature rise absorption heat pump X1. The carburetion absorption heat pump Y1 has: a carburetion object fluid introduction part Y56 introducing a carburetion object fluid TS; and a carburetion object fluid outflow part Y58 flown out to a heat consuming part HCF. The temperature rise absorption heat pump X1 has: a temperature rise drive heat source fluid inflow part X56 introducing a temperature rise drive heat source fluid RS from a heat supply part HSF; and a temperature rise drive heat source fluid outflow part X58 flowing the temperature rise drive heat source fluid RS out.SELECTED DRAWING: Figure 1

Description

  The present invention relates to absorption heat exchange systems, and more particularly to an absorption heat exchange system that transfers heat using an absorption heat pump.

  As a heat source machine for transferring heat from a low temperature heat source to a high temperature heat source, there is an absorption heat pump. In the absorption heat pump, a heat-raising type-type 1 absorption heat pump that extracts more thermal energy than the heat energy of the driving heat source, and a temperature-raising-type second absorption that There is a heat pump. As a second-class absorption heat pump, exhaust heat is introduced as a driving heat source, and there is one that takes out a fluid to be heated at a temperature higher than the introduced exhaust heat (see, for example, Patent Document 1).

JP, 2006-207882, A

  In the absorption heat pump described in Patent Document 1, it is possible to introduce exhaust heat and take it out as a high-temperature fluid having higher utility value. However, when it is intended to use waste heat from steelworks or power plants etc. in residences etc., the positions of both are generally separated, so the energy required for fluid transport is no matter which absorption heat pump is installed It will be bulky.

  SUMMARY OF THE INVENTION In view of the above problems, the present invention has an object to provide an absorption heat exchange system capable of reducing the energy required for fluid transportation even when the place for supplying heat (exhaust heat) and the place using heat are separated. I assume.

  In order to achieve the above object, the absorption heat exchange system according to the first aspect of the present invention is operated by an absorption heat pump cycle of an absorption liquid and a refrigerant as shown in FIG. 1 (FIG. 10), for example. Heat-up absorption heat pump X1 (X2) whose evaporation pressure is higher than the condensation pressure of the refrigerant; and a heat-up absorption heat pump operated by the absorption heat pump cycle of absorption liquid and refrigerant, the evaporation pressure of the refrigerant is lower than the condensation pressure of the refrigerant Y1 (Y2) and; temperature increase target fluid flow path 81 leading the temperature increase target fluid RP heated by the temperature increase absorption heat pump X1 (X2) to the heat increase absorption heat pump Y1 (Y2); and heat increase absorption heat pump Y1 (Y2) And the low temperature heat source fluid channel 82 for leading the low temperature heat source fluid GP which has flowed out to the temperature rising absorption heat pump X1 (X2); the heat buildup absorption heat pump Y1 (Y2) Heat that consumes heat, the heat-increasing target fluid TS heated in the heat-increasing fluid intake part Y56 for introducing the heat-increasing target fluid TS to be heated by the heat pump Y1 (Y2) and the heat-absorption absorption heat pump Y1 (Y2) Heat-up absorption heat pump X1 (X2) has a temperature rising drive heat source for driving an absorption heat pump cycle in temperature rising absorption heat pump X1 (X2). The temperature rising driving heat source fluid inflow section X56 which introduces the fluid RS from the heat supply section HSF supplying heat, and the temperature rising driving heat source fluid RS which drives the absorption heat pump cycle in the temperature rising absorption heat pump X1 (X2) And a thermal drive heat source fluid outlet X58.

  According to this structure, the fluid to be heated which is heated by the heat possessed by the fluid to be heated which is raised in temperature than the temperature rising drive heat source fluid introduced to the temperature rising absorption heat pump is supplied to the heat consuming portion When the heat consuming part and the heat supplying part are separated, the temperature difference between the fluid to be heated and the low temperature heat source fluid is increased, the flow rate of both is reduced, and the energy required for fluid transportation is reduced. it can.

  The absorption heat exchange system according to the second aspect of the present invention is, for example, as shown in FIG. 1 (FIG. 10), in the absorption heat exchange system 1 (1A) according to the first aspect of the present invention. The temperature-increase target fluid flow path 81 is a heat-increase absorption heat pump Y1 so as to supply the temperature-increase target fluid RP to a portion where the heat-increase driving heat source fluid HP for driving the absorption heat pump cycle flows in the heat-absorption absorption heat pump Y1 (Y2). The low temperature heat source fluid flow channel 82 is connected to a portion of the temperature rising absorption heat pump X1 (X2) through which the low temperature heat source fluid GP flows.

  According to this structure, it is possible to supply heat to the heat consuming portion by increasing the temperature of the temperature raising target fluid whose temperature has been increased by the temperature rising absorption heat pump.

  The absorption heat exchange system according to the third aspect of the present invention is, for example, as shown in FIG. 1 (FIG. 10), an absorption heat exchange system according to the first aspect or the second aspect of the present invention. In 1 (1A), the first pump 91 that causes the low temperature heat source fluid GP to flow directly or indirectly; and the second pump 92 that causes the heat-increase target fluid TA (TS) to flow directly or indirectly. Here, to indirectly flow is typically moving the fluid at the site by moving the fluid in the portion in communication with the site.

  With this configuration, the low temperature heat source fluid and the fluid to be heated can be stably flowed.

  The absorption heat exchange system according to the fourth aspect of the present invention is, for example, as shown in FIG. 1 (FIG. 10), in any one of the first to third aspects of the present invention. In the absorption heat exchange system 1 (1A), an expansion tank 98 connected to the low temperature heat source fluid channel 82 or a channel communicating with the low temperature heat source fluid channel 82 is provided. Here, the flow path communicating with the low temperature heat source fluid flow path is a flow path in which the influence of the pressure fluctuation of the low temperature heat source fluid flow path typically appears.

  With this configuration, pressure fluctuations in the low temperature heat source fluid flow channel can be appropriately alleviated.

  The absorption heat exchange system according to the fifth aspect of the present invention is, for example, as shown in FIG. 2, an absorption heat according to any one of the first to fourth aspects of the present invention. In the heat exchange system, the temperature rising absorption heat pump X1 removes the latent heat of vaporization required when the liquid XVf of the refrigerant evaporates and becomes the vapor XVe of the refrigerant from the temperature rising drive heat source fluid RS, and the refrigerant XVe Heat is necessary to heat the dilute solution XSw, which is the absorbing solution with reduced concentration, to desorb the refrigerant XVg from the dilute solution XSw to form the concentrated solution XSa with increased concentration from the temperature rising driving heat source fluid RS The concentrated solution XSa is introduced by introducing the concentrated solution XSa and the absorbed heat released when the concentrated solution XSa absorbs the vapor XVe of the refrigerant generated in the temperature-rising evaporation unit X20 and becomes the dilute solution XSw. Evaporation unit X20 and A temperature rising absorption part which heats a temperature rising target fluid RP by introducing a part of the temperature rising driving heat source fluid branched from the temperature rising driving heat source fluid RA before being introduced into the temperature regeneration unit X30 as a temperature rising target fluid RP X10 and a temperature rising / condensing portion X40 for heating the low temperature heat source fluid GP by condensation heat released when the refrigerant vapor XVg condenses and becomes liquid refrigerant VXf, and is heated by the temperature rising / condensing portion X40 The low temperature heat source fluid GP is configured to merge with the temperature rising driving heat source fluid RS that has flowed out from the temperature rising and evaporating unit X20 and the temperature rising and reproducing unit X30.

  With this configuration, while simplifying the system configuration, the temperature of the temperature rising fluid that has flowed out of the temperature rising absorption unit is greater than the temperature of the temperature rising driving heat source fluid before being introduced into the temperature rising evaporation unit and the temperature rising regeneration unit. Can also be high.

  The absorption heat exchange system according to the sixth aspect of the present invention is, for example, as shown in FIG. 11, an absorption heat according to any one of the first to fourth aspects of the present invention. In the heat exchange system, the temperature rising absorption heat pump X2 removes the latent heat of vaporization required when the liquid XVf of the refrigerant evaporates and becomes the vapor XVe of the refrigerant from the temperature rising drive heat source fluid RS, and the refrigerant XVe Heat is necessary to heat the dilute solution XSw, which is the absorbing solution with reduced concentration, to desorb the refrigerant XVg from the dilute solution XSw to form the concentrated solution XSa with increased concentration from the temperature rising driving heat source fluid RS The temperature rising and driving heat source fluid RQ branched from the temperature rising driving heat source fluid RA before being introduced into the temperature rising and reproducing unit X30 and the temperature rising and evaporating unit X20 and the temperature rising and reproducing unit X30 X20 and temperature rise regeneration unit X30 The temperature rising drive heat source fluid bypass flow path X53 for bypassing and joining the temperature rising drive heat source fluid RS after flowing out from the temperature rising evaporation unit X20 and the temperature rising regeneration unit X30, and the refrigerant vapor XVg condenses as a refrigerant The temperature rising condensation part X40 which heats the low temperature heat source fluid GP by condensation heat released when becoming the liquid XVf, the low temperature heat source fluid GP heated by the temperature rising condensation part X40, and the temperature rising driving heat source fluid bypass flow path X53 The concentrated solution XSa is introduced by introducing the temperature rising heat exchanger X71 which exchanges heat with the flowing temperature rising driving heat source fluid RQ, and the concentrated solution XSa absorbs the vapor XVe of the refrigerant generated in the temperature rising evaporator X20 to dilute the dilute solution XSw The low temperature heat source fluid GP heated by the temperature rising heat exchanger X71 is introduced as a temperature rising target fluid RP by the absorption heat released at the time of temperature That.

  According to this structure, the temperature of the temperature-rising fluid flowing out of the temperature-raising and absorbing portion can be made higher than the temperature of the temperature-rising driving heat-source fluid flowing into the temperature-rising portion and the temperature-rising portion.

  The absorption heat exchange system according to the seventh aspect of the present invention is, for example, as shown in FIG. 13, an absorption heat according to any one of the first to fourth aspects of the present invention. In the heat exchange system, the temperature rising absorption heat pump X2A removes the latent heat of vaporization required when the liquid XVf of the refrigerant evaporates and becomes the vapor XVe of the refrigerant from the temperature rising drive heat source fluid RS, and the refrigerant XVe Heat is necessary to heat the dilute solution XSw, which is the absorbing solution with reduced concentration, to desorb the refrigerant XVg from the dilute solution XSw to form the concentrated solution XSa with increased concentration from the temperature rising driving heat source fluid RS A temperature rising regeneration section X30 which takes away, a temperature rising condensation section X40 which heats the low temperature heat source fluid GP by condensation heat released when the refrigerant vapor XVg condenses and turns into a liquid XVf of the refrigerant, and a temperature rising condensation section X40 heats Low temperature A concentrated solution XSa is introduced by means of a temperature rising heat exchanger X71 for heat exchange between the source fluid GP and the temperature rising driving heat source fluid RS that has flowed out of the temperature rising evaporating section X20 and the temperature rising reproducing section X30. The low temperature heat source fluid GP heated by the temperature rising heat exchanger X71 is introduced as a temperature rising target fluid RP by the absorption heat released when the concentrated solution XSa absorbs the vapor XVe of the refrigerant generated in the above to form a dilute solution XSw. And the temperature rising absorption part X10 which heats the temperature rising object fluid RP.

  According to this structure, the temperature of the temperature-rising fluid flowing out of the temperature-raising and absorbing portion can be made higher than the temperature of the temperature-rising driving heat-source fluid flowing into the temperature-rising portion and the temperature-rising portion.

  The absorption heat exchange system according to the eighth aspect of the present invention is, for example, as shown in FIG. 3, an absorption heat according to any one of the first to seventh aspects of the present invention. In the heat exchange system, the heat-accumulation absorption heat pump Y1 is a heat-accumulation condensation unit Y40 that heats the fluid to be heat-increased by condensation heat released when the refrigerant vapor YVg condenses and becomes the liquid YVf of the refrigerant, The heat transfer evaporation part Y20 which deprives the low temperature heat source fluid GP of the latent heat of vaporization necessary when the liquid YVf of the refrigerant is introduced from the part Y40 and the introduced liquid YVf of the refrigerant evaporates to become the refrigerant vapor YVe Heat transfer to heat the fluid to be heated TS by absorbing heat released by introducing the refrigerant vapor YVe from the part Y20 and absorbing the absorbed refrigerant vapor YVe into the dilute solution YSw whose concentration has been reduced. Absorber Y10 The heat necessary for increasing the concentration of the concentrated solution YSw by heating the diluted solution YSw introduced by introducing the diluted solution YSw from the heat absorption section Y10 and separating the refrigerant YVg from the diluted solution YSw to increase the concentration, A part of the heat increase target fluid branched from the heat increase target fluid TA before being introduced into the heat increase condensation part Y40 and the heat increase absorption part Y10, which has the heat increase regeneration part Y30 deprived of the driving heat source fluid HP The low-temperature heat source fluid GP is configured to be introduced into the heat buildup evaporation unit Y20; the heat generation driving heat source fluid HP that has been deprived of heat by the heat buildup regeneration unit Y30 flows out from the heat buildup absorption unit Y10 and the heat buildup condensation unit Y40. It is comprised so that it may join to the heat-generation object fluid TS.

  According to this structure, the temperature of the low-temperature heat source fluid flowing out of the heat-increasing evaporator can be lowered, and the output of the heat-accumulation heat pump can be increased.

  The absorption heat exchange system according to the ninth aspect of the present invention is, for example, as shown in FIG. 12, an absorption heat according to any one of the first to seventh aspects of the present invention. In the heat exchange system, the heat buildup absorption heat pump Y2 is a heat buildup condensation unit Y40 that heats the fluid to be heat-increased by condensation heat released when the refrigerant vapor YVg condenses and becomes the liquid YVf of the refrigerant; The heat transfer evaporation part Y20 which deprives the low temperature heat source fluid GP of the latent heat of vaporization necessary when the liquid YVf of the refrigerant is introduced from the part Y40 and the introduced liquid YVf of the refrigerant evaporates to become the refrigerant vapor YVe Heat transfer to heat the fluid to be heated TS by absorbing heat released by introducing the refrigerant vapor YVe from the part Y20 and absorbing the absorbed refrigerant vapor YVe into the dilute solution YSw whose concentration has been reduced. Absorber Y1 Then, the dilute solution YSw is introduced from the heat buildup absorbing portion Y10, and the introduced dilute solution YSw is heated to separate the refrigerant YVg from the dilute solution YSw to increase the heat necessary to obtain the concentrated solution YSa having an increased concentration. Heat-generating heat source heat sink deprived of heat by the heat-increase regenerating part Y30, the heat-increase target fluid TS flowing out of the heat-increased heat regenerating part Y30 which is deprived from the heat-driven heat source fluid HP A heat transfer heat exchanger Y72 for exchanging heat with the fluid HP, and the heat generation driving heat source fluid HP flowing out from the heat transfer heat exchanger Y72 is introduced as a low temperature heat source fluid GP into the heat transfer evaporation section Y20. It is configured.

  According to this structure, it is possible to supply heat to the heat consuming apparatus by effectively using the heat held by the fluid to be heated which is introduced into the heat buildup absorption heat pump.

  The absorption heat exchange system according to the tenth aspect of the present invention is, for example, as shown in FIG. 4, an absorption heat according to any one of the first to ninth aspects of the present invention. In the exchange system 2, the heat absorption absorption heat pump Y1 is different from the first heat absorption absorption heat pump Y1A for flowing out the fluid to be heated TA toward the first heat consumption unit HCF1, and the first heat consumption unit HCF1 And a second heat-absorption absorption heat pump Y1B for flowing out the fluid to be heated TA toward the second heat-consuming part HCF2.

  According to this configuration, it is possible to supply the heat-increase target fluid to the plurality of heat consuming units.

  The absorption heat exchange system according to the eleventh aspect of the present invention is, for example, as shown in FIG. 5, in the absorption heat exchange system 3 according to the eighth aspect or the ninth aspect of the present invention. The heat absorption heat pump Y1C temporarily discharges the heat generation driving heat source fluid HP flowing out from the heat generation regeneration unit Y30 out of the heat absorption absorption heat pump Y1C toward the first additional heat consuming unit HCFA that consumes heat. The first heat-generation driving heat source fluid for introducing the heat-generation driving heat source fluid HP in which the heat possessed by the heat generation driving heat source fluid outflow portion Y39a and the heat generation driving heat source fluid HP is consumed by the first additional consumption portion HCFA And an introductory portion Y39b.

  With this configuration, heat can be efficiently consumed according to the characteristics of the heat consuming unit.

  The absorption heat exchange system according to the twelfth aspect of the present invention is, for example, as shown in FIG. 6, an increase in the absorption heat exchange system 4 according to the eighth aspect or the ninth aspect of the present invention. The heat absorption heat pump Y1 is a second additional heat consuming part HCFA that consumes heat from a part of the heat generation driving heat source fluid HP branched from the heat generation driving heat source fluid HP before being introduced to the heat generation regeneration part Y30. The second heat-accumulation drive heat-source fluid outflow portion 487, which temporarily flows out of the heat-accumulation absorption heat pump Y1, and the heat held by the heat-accumulation drive heat-source fluid HP is consumed by the second additional consumer HCFA And a second heat generation driving heat source fluid introducing portion 488 for introducing the heat driving heat source fluid HP.

  With this configuration, heat can be efficiently consumed according to the characteristics of the heat consuming unit.

  In addition, as shown in FIG. 7, for example, as shown in FIG. 7, the absorption heat exchange system according to the thirteenth aspect of the present invention is the absorption heat according to any one of the first to twelfth aspects of the present invention. The exchange system 5 includes a first secondary heat device 61 that heats a part of the low temperature heat source fluid GP branched from the low temperature heat source fluid GP before being introduced into the temperature rising absorption heat pump X1 with a first secondary heat source AS. The low temperature heat source fluid GP heated by the first auxiliary heat device 61 is joined to the temperature raising target fluid RP.

  With this configuration, heat can be recovered from the first auxiliary heat device, which results in energy saving.

  The absorption heat exchange system according to the fourteenth aspect of the present invention is, for example, as shown in FIG. 8, an absorption heat according to any one of the first to thirteenth aspects of the present invention. The exchange system 6 includes a second auxiliary heat device 61 that heats the temperature raising target fluid RP heated by the temperature rising absorption heat pump X1 with the second auxiliary heat source AS.

  With this configuration, heat can be recovered from the second auxiliary heat device, and the temperature-raising target fluid can recover the temperature lost due to heat radiation.

  The absorption heat exchange system according to the fifteenth aspect of the present invention is, for example, as shown in FIG. 9, an absorption heat according to any one of the first to fourteenth aspects of the present invention. In the exchange system 7, the temperature rising absorption heat pump X1 is different from the first temperature rising absorption heat pump X1A for introducing the temperature rising drive heat source fluid RA from the first heat supply portion HSF1 and the first heat supply portion HSF1. And a second temperature rising absorption heat pump X1B for introducing a temperature rising drive heat source fluid RA from the second heat supply unit HSF2.

  With this configuration, heat can be recovered from the plurality of heat supply units.

  According to the present invention, the fluid to be heated which is heated by the heat held by the fluid to be heated which is raised in temperature than the temperature rising drive heat source fluid introduced into the temperature rising absorption heat pump is supplied to the heat consuming portion When the heat consuming part and the heat supplying part are separated, the temperature difference between the fluid to be heated and the low temperature heat source fluid is increased, the flow rate of both is reduced, and the energy required for fluid transportation is reduced. it can.

It is a typical systematic diagram of an absorption-type heat exchange system concerning a 1st embodiment of the present invention. It is a typical systematic diagram of a temperature rising absorption heat pump with which an absorption-type heat exchange system concerning a 1st embodiment of the present invention is provided. It is a typical systematic diagram of a heat buildup absorption heat pump with which an absorption type heat exchange system concerning a 1st embodiment of the present invention is provided. It is a typical systematic diagram of an absorption-type heat exchange system concerning a 2nd embodiment of the present invention. It is a typical systematic diagram of the absorption-type heat exchange system concerning a 3rd embodiment of the present invention. It is a typical systematic diagram of an absorption-type heat exchange system concerning a 4th embodiment of the present invention. It is a typical systematic diagram of the absorption-type heat exchange system concerning a 5th embodiment of the present invention. It is a typical systematic diagram of an absorption-type heat exchange system concerning a 6th embodiment of the present invention. It is a typical systematic diagram of the absorption type heat exchange system concerning a 7th embodiment of the present invention. It is a typical systematic diagram of the absorption type heat exchange system concerning the modification of the 1st embodiment of the present invention. It is a typical systematic diagram of a temperature rising absorption heat pump with which an absorption-type heat exchange system concerning a modification of a 1st embodiment of the present invention is provided. It is a typical systematic diagram of a heat-accumulation absorption heat pump with which the absorption type heat exchange system concerning the modification of the 1st embodiment of the present invention is provided. It is a typical systematic diagram of the modification of the temperature rising absorption heat pump with which the absorption type heat exchange system concerning the modification of a 1st embodiment of the present invention is provided.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each of the drawings, the same or corresponding members are denoted by the same or similar reference numerals, and the redundant description will be omitted.

  First, an absorption heat exchange system 1 according to a first embodiment of the present invention will be described with reference to FIG. FIG. 1 is a schematic system diagram of the absorption type heat exchange system 1. The absorption type heat exchange system 1 is a system for utilizing the heat recovered by the heat source equipment HSF in a heat utilization equipment HCF after raising the temperature and raising the temperature of the heat medium holding the heat. The heat source equipment HSF is equipment that recovers the exhaust heat from, for example, a steel mill or a power plant, and corresponds to a heat supply unit. The heat utilization facility HCF is, for example, a facility that uses the introduced heat for heating, and corresponds to a heat consuming unit. The absorption type heat exchange system 1 is a temperature rising absorption heat pump X1 for raising the temperature of the heat medium holding heat recovered by the heat source equipment HSF, and a heat absorption absorption for raising the temperature of the heat medium raised by the temperature rising absorption heat pump X1. A heat pump Y1, and a temperature increasing fluid pipe 81 and a low temperature heat source pipe 82 that communicate fluid between the temperature rising absorption heat pump X1 and the heat absorption absorption heat pump Y1 are provided.

  The temperature-rising absorption heat pump X1 is a heat source device that operates by an absorption heat pump cycle of an absorption liquid and a refrigerant, and the evaporation pressure of the refrigerant is higher than the condensation pressure. The configuration of the temperature rising absorption heat pump X1 will be described later. The temperature rising absorption heat pump X1 has a heat source fluid inlet X56, a temperature rising fluid outlet X18, a low temperature heat source inlet X17, and a heat source fluid outlet X58. The heat source fluid inlet X56 is a part for introducing the combined heat source fluid RA heated by the heat source equipment HSF, and corresponds to a temperature rising driving heat source fluid inlet. The temperature rising fluid outlet X18 is a portion from which the temperature raising target fluid RP heated by the temperature rising absorption heat pump X1 flows out. The low temperature heat source introduction port X17 is a portion for introducing the low temperature heat source fluid GP which has flowed out of the heat buildup absorption heat pump Y1. The heat source fluid outlet X58 is a part that flows out the combined heat source fluid RA whose temperature is lower than that introduced from the heat source fluid inlet X56, and corresponds to a temperature rising driving heat source fluid outlet. In the present embodiment, the heat source fluid inlet X56 and the heat source facility HSF are connected by a combined heat source outward pipe 84. The heat source fluid outlet X58 and the heat source equipment HSF are connected by a combined heat source return pipe 85. The combined heat source return pipe 85 is provided with a combined heat source pump 93 for flowing the combined heat source fluid RA.

  The heat buildup absorption heat pump Y1 is a heat source device that operates by an absorption heat pump cycle of an absorption liquid and a refrigerant, and the evaporation pressure of the refrigerant is lower than the condensation pressure. The configuration of the heat buildup absorption heat pump Y1 will be described later. The heat buildup absorption heat pump Y1 has a high temperature heat source inlet Y27, a mixed fluid outlet Y58, a mixed fluid inlet Y56, and a low temperature source outlet Y28. The high temperature heat source inlet Y27 is a part for introducing the temperature raising target fluid RP flowing out of the temperature rising absorption heat pump X1 as the high temperature heat source fluid HP. The mixed fluid outlet Y58 is a portion from which the mixed fluid TA heated by the heat buildup absorption heat pump Y1 flows out, and corresponds to a fluid outlet to be heated. The mixed fluid inlet Y56 is a part for introducing the mixed fluid TA whose temperature has been lowered by the heat utilization facility HCF, and corresponds to a fluid introduction target for increasing heat. The low temperature heat source outlet Y28 is a portion from which the low temperature heat source fluid GP whose heat has been used in the heat buildup absorption heat pump Y1 flows out. In the present embodiment, the mixed fluid outlet Y 58 and the heat utilization facility HCF are connected by the mixed heat source transfer pipe 87. The mixed fluid inlet Y56 and the heat utilization facility HCF are connected by a mixed heat source return pipe 88. The mixed heat source return pipe 88 is provided with a mixed fluid pump 92 that causes the mixed fluid TA to flow. The mixed fluid pump 92 corresponds to a second pump.

  The temperature rising fluid pipe 81 connects the temperature rising fluid outlet X18 of the temperature rising absorption heat pump X1 and the high temperature heat source inlet Y27 of the heat buildup absorption heat pump Y1. The temperature rising fluid pipe 81 is a pipe that constitutes a flow path for leading the temperature rising target fluid RP heated by the temperature rising absorption heat pump X1 to the heat buildup absorption heat pump Y1, and corresponds to the temperature rising target fluid flow path. The low temperature heat source pipe 82 connects the low temperature source outlet Y28 of the heat buildup absorption heat pump Y1 and the low temperature source inlet X17 of the temperature rising absorption heat pump X1. The low temperature heat source pipe 82 is a pipe that constitutes a flow path for leading the low temperature heat source fluid GP used in the heat buildup absorption heat pump Y1 and flowing out from the heat buildup absorption heat pump Y1 to the temperature rising absorption heat pump X1. It corresponds to The low temperature heat source pipe 82 is provided with a low temperature heat source pump 91 for flowing the low temperature heat source fluid GP. The low temperature heat source pump 91 corresponds to a first pump. Each of the pumps 91, 92, 93 is preferably disposed at a position where the temperature is the lowest in each system from the viewpoint of preventing cavitation. From this point of view, the low temperature heat source pump 91 is provided in the low temperature heat source pipe 82 through which the low temperature heat source fluid GP having a temperature lower than the temperature of the temperature raising target fluid RP flowing in the temperature raising fluid pipe 81 is mixed. A mixed fluid pump 92 is provided in the mixed heat source return pipe 88 through which the mixed fluid TA having a temperature lower than the temperature of the fluid TA, and the combined heat source fluid RA having a temperature lower than the temperature of the combined heat source fluid RA flowing through the combined heat source forward pipe 84 A combined heat source pump 93 is provided in the flowing combined heat source return pipe 85. Further, each of the pumps 91, 92, 93 may be provided at a lower position in each of the pipes. Further, in the present embodiment, the low temperature heat source pipe 82 is connected to the expansion tank 98. In the absorption type heat exchange system 1, since the heated fluid such as the temperature rising target fluid RP having a temperature change and the heating source fluid such as the driving heat source fluid RS communicate as a whole, one expansion tank 98 should be provided. Although it is sufficient, a plurality may be provided. In the present embodiment, the expansion tank 98 is provided at the suction portion of the low temperature heat source pump 91 where the temperature of the fluid flowing through the pipe in the circulation system is low and the pressure is also low. I'm adjusting the pressure. The expansion tank 98 can be either closed or open, as appropriate. Subsequently, detailed configurations of the temperature-rising absorption heat pump X1 and the heat-accumulation absorption heat pump Y1 constituting the absorption-type heat exchange system 1 will be described.

  FIG. 2 is a schematic diagram of the temperature rising absorption heat pump X1. The temperature rising absorption heat pump X1 is an absorber X10, an evaporator X20, a regenerator X30, and the like, which constitute the main equipment in which the absorption heat pump cycle of the absorption liquid XS (XSa, XSw) and the refrigerant XV (XVe, XVg, XVf) is performed. A condenser X40 is provided. The absorber X10, the evaporator X20, the regenerator X30, and the condenser X40 correspond to a temperature rising absorption portion, a temperature rising evaporation portion, a temperature rising reproduction portion, and a temperature rising condensation portion, respectively.

In the present specification, the absorption liquid in the temperature rising absorption heat pump X1 may be “diluted solution XSw”, “concentrated solution XSa”, etc. according to the property or the position on the heat pump cycle to facilitate distinction on the heat pump cycle. However, when properties and the like are not questioned, they are collectively referred to as “absorbent liquid XS”. Similarly, with regard to the refrigerant in the temperature rising absorption heat pump X1, “evaporator refrigerant vapor XVe”, “regenerator refrigerant vapor XVg”, according to the property or the position on the heat pump cycle, in order to facilitate distinction on the heat pump cycle. It is referred to as "refrigerant liquid XVf" etc., but when the property etc. are unquestioned, they are collectively referred to as "refrigerant XV". In the present embodiment, an LiBr aqueous solution is used as the absorbent XS (a mixture of an absorbent and a refrigerant XV), and water (H ₂ O) is used as the refrigerant XV.

  The absorber X10 internally includes a heat transfer pipe X12 that configures a flow path of the temperature raising target fluid RP, and a concentrated solution supply device X13 that supplies the concentrated solution XSa to the surface of the heat transfer pipe X12. The heat transfer pipe X12 has one end connected to the temperature increasing fluid introduction pipe X51, and the other end connected to the temperature increasing fluid outflow pipe X19. The temperature raising fluid introduction pipe X51 is a pipe that constitutes a flow path for leading the temperature raising target fluid RP to the heat transfer pipe X12. The temperature raising fluid introduction pipe X51 is provided with a temperature raising fluid valve X51v for adjusting the flow rate of the temperature raising target fluid RP flowing inside. The temperature rising fluid outflow pipe X19 is a pipe that constitutes a flow path through which the temperature raising target fluid RP heated by the absorber X10 flows. The other end of the heating fluid outlet pipe X19 is a heating fluid outlet X18. The absorber X10 generates the heat of absorption when the concentrated solution XSa is supplied from the concentrated solution supply device X13 to the surface of the heat transfer tube X12 and the concentrated solution XSa absorbs the evaporator refrigerant vapor XVe and becomes the dilute solution XSw. The absorption heat is received by the temperature raising target fluid RP flowing through the heat transfer pipe X12, and the temperature raising target fluid RP is heated.

  The evaporator X20 has a heat source pipe X22 forming a flow path of the drive heat source fluid RS inside the evaporator can and barrel X21. The evaporator X20 does not have a nozzle for dispersing the refrigerant liquid XVf inside the evaporator can barrel X21. For this reason, the heat source tube X22 is disposed so as to be immersed in the refrigerant liquid XVf stored in the evaporator can and barrel X21 (full liquid type evaporator). A drive heat source introduction pipe X52 is connected to one end of the heat source pipe X22. The driving heat source introduction pipe X52 is a pipe that constitutes a flow path for leading the driving heat source fluid RS to the heat source pipe X22. The drive heat source introduction pipe X52 is provided with a drive heat source valve X52v for adjusting the flow rate of the drive heat source fluid RS flowing inside. The other end of the driving heat source introduction pipe X52 is connected to the heat source fluid inflow pipe X55 together with the other end of the temperature increasing fluid introduction pipe X51. The heat source fluid inflow pipe X55 is a pipe that constitutes a flow path through which the combined heat source fluid RA flows. The other end of the heat source fluid inflow pipe X55 is a heat source fluid inlet X56. The combined heat source fluid RA flowing through the heat source fluid inflow pipe X55 is branched and flows into the temperature raising fluid introduction pipe X51 and the drive heat source introduction pipe X52. That is, the temperature raising target fluid RP flows into the temperature rising fluid introduction pipe X51 of the combined heat source fluid RA, and the driving heat source fluid RS flows into the driving heat source introducing pipe X52 of the combined heat source fluid RA It is a thing. The evaporator X20 is configured such that the refrigerant liquid XVf around the heat source pipe X22 evaporates with the heat of the drive heat source fluid RS flowing in the heat source pipe X22 to generate the evaporator refrigerant vapor XVe. A refrigerant liquid pipe X45 for supplying the refrigerant liquid XVf into the evaporator can barrel X21 is connected to the evaporator can barrel X21.

  The absorber X10 and the evaporator X20 communicate with each other. By communication between the absorber X10 and the evaporator X20, the evaporator refrigerant vapor XVe generated in the evaporator X20 can be supplied to the absorber X10.

  The regenerator X30 has a heat source pipe X32 for flowing therein a drive heat source fluid RS for heating the dilute solution XSw, and a dilute solution supply device X33 for supplying the dilute solution XSw to the surface of the heat source pipe X32. The driving heat source fluid RS flowing in the heat source pipe X32 is the driving heat source fluid RS after flowing in the heat source pipe X22 of the evaporator X20. The heat source pipe X22 of the evaporator X20 and the heat source pipe X32 of the regenerator X30 are connected by a drive heat source communication pipe X25 in which the drive heat source fluid RS flows. A drive heat source outflow pipe X39 is connected to an end opposite to the end to which the drive heat source communication pipe X25 of the heat source pipe X32 of the regenerator X30 is connected. The driving heat source outflow pipe X39 is a pipe that constitutes a flow path for leading the driving heat source fluid RS to the outside of the regenerator X30. In the regenerator X30, the dilute solution XSw supplied from the dilute solution supply device X33 is heated to the driving heat source fluid RS, whereby the refrigerant XV evaporates from the dilute solution XSw to generate a concentrated solution XSa having an increased concentration. Is configured as. The refrigerant XV evaporated from the dilute solution XSw is configured to move to the condenser X40 as a regenerator refrigerant vapor XVg.

  The condenser X40 has a heat transfer pipe X42 in which the low temperature heat source fluid GP flows, inside the condenser can barrel X41. At one end of the heat transfer pipe X42, a low temperature heat source introduction pipe X57 that constitutes a flow path for guiding the low temperature heat source fluid GP to the heat transfer pipe X42 is connected. The other end of the low temperature heat source introduction pipe X57 is a low temperature heat source introduction port X17. The other end of the heat transfer pipe X42 is connected to one end of a low temperature heat source outflow pipe X49 that constitutes a flow path through which the low temperature heat source fluid GP flowing out of the condenser X40 flows. The other end of the low temperature heat source outflow pipe X49 is connected to the heat source fluid outflow pipe X59 together with the other end of the drive heat source outflow pipe X39. The heat source fluid outflow pipe X59 is a pipe constituting a flow path through which the combined heat source fluid RA in which the drive heat source fluid RS flowing through the drive heat source outflow pipe X39 and the low temperature heat source fluid GP flowing through the low temperature heat source outflow pipe X49 join . The other end of the heat source fluid outflow pipe X59 is a heat source fluid outlet X58. The condenser X40 introduces the regenerator refrigerant vapor XVg generated by the regenerator X30, and the low temperature heat source fluid GP flowing in the heat transfer pipe X42 receives the condensation heat released when the refrigerant condenses and becomes the refrigerant liquid XVf. Thus, the low temperature heat source fluid GP is configured to be heated. The regenerator X30 and the condenser X40 are integrally formed with the can barrel of the regenerator X30 and the condenser can barrel X41 so as to communicate with each other. By connecting the regenerator X30 and the condenser X40, the regenerator refrigerant vapor XVg generated by the regenerator X30 can be supplied to the condenser X40.

  The portion of the regenerator X30 where the concentrated solution XSa is stored and the concentrated solution supply device X13 of the absorber X10 are connected by a concentrated solution pipe X35 in which the concentrated solution XSa flows. The concentrated solution tube X35 is provided with a solution pump X35p for pumping the concentrated solution XSa. The portion of the absorber X10 where the dilute solution XSw is stored and the dilute solution supply device X33 are connected by a dilute solution pipe X36 in which the dilute solution XSw flows. The concentrated solution pipe X35 and the diluted solution pipe X36 are provided with a solution heat exchanger X38 for performing heat exchange between the concentrated solution XSa and the diluted solution XSw. The portion of the condenser X40 where the refrigerant liquid XVf is stored and the evaporator can and barrel X21 are connected by a refrigerant liquid pipe X45 through which the refrigerant liquid XVf flows. The refrigerant liquid pipe X45 is provided with a refrigerant pump X46 for pressure-feeding the refrigerant liquid XVf.

  In steady-state operation of the temperature-rising absorption heat pump X1, the pressure and temperature inside the absorber X10 become higher than the pressure and temperature inside the regenerator X30, and the pressure and temperature inside the evaporator X20 are inside the condenser X40 Pressure and temperature. Therefore, as described above, the evaporation pressure of the refrigerant XV becomes higher than the condensation pressure. In the temperature rising absorption heat pump X1, an absorber X10, an evaporator X20, a regenerator X30, and a condenser X40 constitute a type 2 absorption heat pump.

  Next, with reference to FIG. 3, the detailed configuration of the heat absorption absorption heat pump Y1 will be described. FIG. 3 is a schematic system diagram of the heat buildup absorption heat pump Y1. The heat-accumulation absorption heat pump Y1 includes an absorber Y10, an evaporator Y20, a regenerator Y30, and the like, which constitute the main devices in which the absorption heat pump cycle of the absorption liquid YS (YSa, YSw) and the refrigerant YV (YVe, YVg, YVf) is performed. And a condenser Y40. The absorber Y10, the evaporator Y20, the regenerator Y30, and the condenser Y40 correspond to a heat buildup absorption unit, a heat buildup evaporation unit, a heat buildup regeneration unit, and a heat buildup condensation unit, respectively.

In the present specification, with regard to the absorption liquid in the heat-accumulation absorption heat pump Y1, in order to facilitate distinction on the heat pump cycle, “dilute solution YSw”, “concentrated solution YSa”, etc. according to the property or the position on the heat pump cycle. However, when properties and the like are not questioned, they are collectively referred to as “absorbent YS”. Similarly, with regard to the refrigerant in the heat buildup absorption heat pump Y1, “evaporator refrigerant vapor YVe”, “regenerator refrigerant vapor YVg”, according to the property or the position on the heat pump cycle, in order to facilitate discrimination on the heat pump cycle. It is referred to as "refrigerant liquid YVf" etc., but when the property etc. are unquestioned, it is collectively referred to as "refrigerant YV". In the present embodiment, a LiBr aqueous solution is used as the absorbent YS (a mixture of an absorbent and a refrigerant YV), and water (H ₂ O) is used as the refrigerant YV.

  The absorber Y10 internally includes a heat transfer tube Y12 that configures a flow path of the fluid to be heated TS, and a concentrated solution supply device Y13 that supplies the concentrated solution YSa to the surface of the heat transfer tube Y12. The heat transfer pipe Y12 has one end connected to the heat transfer fluid introduction pipe Y51 and the other end connected to the heat transfer fluid communication pipe Y15. The heat transfer fluid introduction pipe Y51 is a pipe that constitutes a flow path for leading the heat transfer target fluid TS to the heat transfer pipe Y12. The heat increasing fluid introduction pipe Y51 is provided with a heat increasing fluid valve Y51v for adjusting the flow rate of the heat enhancement target fluid TS flowing inside. The heat transfer fluid communication pipe Y15 is a pipe that constitutes a flow path for leading the heat-increase target fluid TS heated by the absorber Y10 to the condenser Y40. The absorber Y10 generates the heat of absorption when the concentrated solution YSa is supplied from the concentrated solution supply device Y13 to the surface of the heat transfer tube Y12 and the concentrated solution YSa absorbs the evaporator refrigerant vapor YVe and becomes a dilute solution YSw. The heat to be heated TS flowing through the heat transfer tube Y12 receives this absorbed heat, and the fluid to be heat-increased TS is heated.

  The evaporator Y20 has a heat source pipe Y22 constituting a flow path of the low temperature heat source fluid GP and a refrigerant liquid supply device Y23 for supplying the refrigerant liquid YVf to the surface of the heat source pipe Y22 inside the evaporator can barrel Y21. ing. A low temperature heat source inflow pipe Y52 is connected to one end of the heat source pipe Y22. The low temperature heat source inflow pipe Y52 is a pipe that constitutes a flow path for leading the low temperature heat source fluid GP to the heat source pipe Y22. The low temperature heat source inflow pipe Y52 is provided with a low temperature heat source valve Y52v for adjusting the flow rate of the low temperature heat source fluid GP flowing therein. The other end of the low temperature heat source inflow pipe Y52 is connected to the mixed fluid inflow pipe Y55 together with the other end of the heat transfer fluid introduction pipe Y51. The mixed fluid inflow pipe Y55 is a pipe that constitutes a flow path through which the mixed fluid TA flows. The other end of the mixed fluid inflow pipe Y55 is a mixed fluid inlet Y56. The mixed fluid TA flowing through the mixed fluid inflow pipe Y55 is divided and flows into the heat-increasing fluid introduction pipe Y51 and the low temperature heat source inflow pipe Y52. That is, the heat-increase target fluid TS flows into the heat-up fluid introduction pipe Y51 of the mixed fluid TA, and the low-temperature heat source fluid GP flows into the low-temperature heat source inflow pipe Y52 of the mixed fluid TA. is there. A low temperature heat source outflow pipe Y29 is connected to an end of the heat source pipe Y22 opposite to the end to which the low temperature heat source inflow pipe Y52 is connected. The low temperature heat source outflow pipe Y29 is a pipe constituting a flow path for leading the low temperature heat source fluid GP to the outside of the evaporator Y20. The other end of the low temperature heat source outflow pipe Y29 is a low temperature heat source outlet Y28. In the evaporator Y20, the refrigerant liquid YVf is supplied from the refrigerant liquid supply device Y23 to the surface of the heat source pipe Y22, and the refrigerant liquid YVf around the heat source pipe Y22 is evaporated and evaporated by the heat of the low temperature heat source fluid GP flowing in the heat source pipe Y22. Is configured to generate a refrigerant vapor YVe.

  The absorber Y10 and the evaporator Y20 communicate with each other. By communicating the absorber Y10 with the evaporator Y20, the evaporator refrigerant vapor YVe generated in the evaporator Y20 can be supplied to the absorber Y10.

  The regenerator Y30 has a heat source pipe Y32 through which a high-temperature heat source fluid HP for heating the dilute solution YSw flows, and a dilute solution supply device Y33 which supplies the dilute solution YSw to the surface of the heat source tube Y32. At one end of the heat source pipe Y32, a high temperature heat source introduction pipe Y57 that configures a flow path for leading the high temperature heat source fluid HP to the heat source pipe Y32 is connected. The other end of the high temperature heat source introduction pipe Y57 is a high temperature heat source introduction port Y27. The other end of the heat source pipe Y32 is connected to one end of a high temperature heat source outflow pipe Y39 which constitutes a flow path through which the high temperature heat source fluid HP flowing out of the regenerator Y30 flows. In the regenerator Y30, the dilute solution YSw supplied from the dilute solution supply device Y33 is heated to the high-temperature heat source fluid HP to evaporate the refrigerant YV from the dilute solution YSw to generate a concentrated solution YSa having an increased concentration. Is configured as. The refrigerant YV evaporated from the dilute solution YSw is configured to move to the condenser Y40 as a regenerator refrigerant vapor YVg.

  The condenser Y40 includes a heat transfer pipe Y42 through which the fluid to be heated is flowing, inside the condenser can barrel Y41. The heat enhancement target fluid TS flowing through the heat transfer tube Y42 is the heat enhancement target fluid TS after flowing through the heat transfer tube Y12 of the absorber Y10. The heat transfer pipe Y12 of the absorber Y10 and the heat transfer pipe Y42 of the condenser Y40 are connected by a heat increasing fluid communication pipe Y15 in which the heat-increase target fluid TS flows. A heat transfer fluid discharge pipe Y49 is connected to an end of the heat transfer pipe Y42 of the condenser Y40 opposite to the end to which the heat transfer fluid communication pipe Y15 is connected. The heat transfer fluid discharge pipe Y49 is a pipe that constitutes a flow path for leading the heat increase target fluid TS to the outside of the condenser Y40. The other end of the heat transfer fluid outflow pipe Y49 is connected to the mixed fluid outflow pipe Y59 together with the other end of the high temperature heat source outflow pipe Y39. The mixed fluid outflow pipe Y59 is a pipe constituting a flow path in which the mixed fluid TA in which the high temperature heat source fluid HP flowing in the high temperature heat source outflow pipe Y39 and the fluid to be heated TS flowing in the heat increasing fluid outflow pipe Y49 join is there. The other end of the mixed fluid outflow pipe Y59 is a mixed fluid outlet Y58. The condenser Y40 introduces the regenerator refrigerant vapor YVg generated by the regenerator Y30, and condenses the heat of condensation released when the refrigerant condenses and becomes the refrigerant liquid YVf. Then, the fluid TS to be heated is configured to be heated. The regenerator Y30 and the condenser Y40 are integrally formed with the regenerator Y30 so as to communicate with each other. By connecting the regenerator Y30 and the condenser Y40, the regenerator refrigerant vapor YVg generated by the regenerator Y30 can be supplied to the condenser Y40.

  The portion of the regenerator Y30 where the concentrated solution YSa is stored and the concentrated solution supply device Y13 of the absorber Y10 are connected by a concentrated solution pipe Y35 in which the concentrated solution YSa flows. The portion of the absorber Y10 where the dilute solution YSw is stored and the dilute solution supply device Y33 are connected by a dilute solution pipe Y36 in which the dilute solution YSw flows. The dilute solution pipe Y36 is provided with a solution pump Y36p for pressure-feeding the dilute solution YSw. The concentrated solution pipe Y35 and the diluted solution pipe Y36 are provided with a solution heat exchanger Y38 for performing heat exchange between the concentrated solution YSa and the diluted solution YSw. The portion of the condenser Y40 where the refrigerant liquid YVf is stored and the refrigerant liquid supply device Y23 are connected by a refrigerant liquid pipe Y45 through which the refrigerant liquid YVf flows.

  In the heat absorption absorption heat pump Y1, the pressure and temperature inside the absorber Y10 are lower than the pressure and temperature inside the regenerator Y30 during steady operation, and the pressure and temperature inside the evaporator Y20 is inside the condenser Y40 Lower than the pressure and temperature of Therefore, as described above, the evaporation pressure of the refrigerant XV is lower than the condensation pressure. In the heat-accumulation absorption heat pump Y1, the absorber Y10, the evaporator Y20, the regenerator Y30, and the condenser Y40 constitute a first-type absorption heat pump.

  Further, referring additionally to FIGS. 1 to 3, the heat transfer pipe X42 of the condenser X40, the heat source equipment HSF, the heat transfer pipe X12 of the absorber X10, the heat source pipe Y32 of the regenerator Y30, the heat utilization equipment HCF, and the evaporator Y20. The heat source pipe Y22 of the second embodiment constitutes a first circulation path, and the low temperature heat source pump 91 is connected to the low temperature heat source fluid GP or the combined heat source fluid RA or the temperature raising target fluid RP or the high temperature heat source fluid HP or the mixed fluid TA in the first circulation path. It is a pump that circulates The heat transfer pipe Y12 of the absorber Y10, the heat transfer pipe Y42 of the condenser Y40, and the heat utilization facility HCF constitute a second circulation path, and the mixed fluid pump 92 generates a fluid TS to be heated or a mixed fluid in the second circulation path. It is a pump that circulates TA. The heat source equipment HSF, the heat source pipe X22 of the evaporator X20, and the heat source pipe X32 of the regenerator X30 form a third circulation path, and the combined heat source pump 93 generates a third circulation path of the combined heat source fluid RA or the driving heat source fluid RS. It is a pump to circulate. The first circulation path, the second circulation path, and the third circulation path constitute one circulation path as a whole by combining and branching appropriately. From this, it can be understood that in the present embodiment, it is sufficient to provide at least one expansion tank 98 in the entire absorptive heat exchange system 1. In the present embodiment, the low temperature heat source pipe 82 is used as the expansion tank 98 at a mounting position, but instead of the low temperature heat source pipe 82 or together with the low temperature heat source pipe 82, One or more of the mixed heat source return pipe 88, the combined heat source return pipe 84, and the combined heat source return pipe 85 may be used.

  With continuing reference to FIGS. 1 to 3, the operation of the absorptive heat exchange system 1 will be described. First, the operation around the temperature rising absorption heat pump X1 will be described with reference to FIG. 1 and FIG. 2. The combined heat source fluid RA flowing by the start of the combined heat source pump 93 recovers exhaust heat in the heat source facility HSF. The temperature rises, and flows into the temperature rising absorption heat pump X1 from the heat source fluid inlet X56 via the combined heat source forward pipe 84. The combined heat source fluid RA flowing into the temperature rising absorption heat pump X1 flows through the heat source fluid inflow pipe X55, and then the temperature raising target fluid RP entering the temperature raising fluid introduction pipe X51 and the driving heat source fluid RS entering the driving heat source introduction pipe X52 It divides into and. The temperature raising target fluid RP flowing through the temperature raising fluid introduction pipe X51 flows into the heat transfer pipe X12 of the absorber X10, and the temperature rises by obtaining the absorption heat generated when the concentrated solution XSa absorbs the evaporator refrigerant vapor XVe Then, it flows through the temperature rising fluid outlet pipe X19, and the temperature rising absorption heat pump X1 flows out from the temperature rising fluid outlet X18 and reaches the temperature rising fluid pipe 81. In the temperature rising absorption heat pump X1, the low temperature heat source fluid GP having the same flow rate as the flow rate of the temperature rising target fluid RP flowing out from the temperature rising fluid outlet X18 passes from the low temperature heat source pipe 82 through the low temperature heat source inlet X17 It flows into X57. The low temperature heat source fluid GP flowing from the low temperature heat source pipe 82 into the low temperature heat source introduction pipe X57 flows when the low temperature heat source pump 91 is activated. The low temperature heat source fluid GP flowing through the low temperature heat source introduction pipe X57 flows into the heat transfer pipe X42 of the condenser X40, obtains condensation heat released when the regenerator refrigerant vapor XVg condenses, and the temperature rises after the temperature rises. Flow through tube X49.

  On the other hand, the drive heat source fluid RS branched from the combined heat source fluid RA flowing from the heat source equipment HSF into the temperature rising absorption heat pump X1 flows through the drive heat source introduction pipe X52 and flows into the heat source pipe X22 of the evaporator X20, and the refrigerant liquid XVf After the latent heat of vaporization necessary for becoming the evaporator refrigerant vapor XVe is deprived and the temperature decreases, it reaches the driving heat source communication pipe X25. The driving heat source fluid RS flowing through the driving heat source communication pipe X25 flows into the heat source pipe X32 of the regenerator X30, and the temperature is lowered after the heat necessary for separating the regenerator refrigerant vapor XVg is removed from the dilute solution XSw , Driving heat source outflow pipe X39. The driving heat source fluid RS flowing through the driving heat source outflow pipe X39 merges with the low temperature heat source fluid GP flowing through the above-described low temperature heat source outflow pipe X49 to form a merged heat source fluid RA. The combined heat source fluid RA flows through the heat source fluid outlet pipe X59, and flows out from the heat source fluid outlet X58 to the temperature rising absorption heat pump X1 and reaches the combined heat source return pipe 85. The combined heat source fluid RA that has flowed into the combined heat source return pipe 85 flows into the heat source equipment HSF and recovers the exhaust heat to rise in temperature, and then reaches the combined heat source forward pipe 84. Thereafter, the above-described operation is repeated. Hereinafter, absorption heat pump cycles of the absorbent XS and the refrigerant XV that bring about temperature changes of the temperature raising target fluid RP, the low temperature heat source fluid GP, and the driving heat source fluid RS will be described mainly with reference to FIG.

  First, the absorption heat pump cycle on the refrigerant side will be described. In the condenser X40, the regenerator refrigerant vapor XVg evaporated in the regenerator X30 is received, the regenerator refrigerant vapor XVg is cooled and condensed by the fluid flowing through the heat transfer pipe X42 (in the present embodiment, the low temperature heat source fluid GP). It becomes the refrigerant liquid XVf. At this time, the temperature of the fluid flowing through the heat transfer pipe X42 (in the present embodiment, the low temperature heat source fluid GP) rises due to the condensation heat released when the regenerator refrigerant vapor XVg condenses. The condensed refrigerant liquid XVf is sent to the evaporator can and barrel X21 by the refrigerant pump X46. The refrigerant liquid XVf sent to the evaporator can and barrel X21 is heated by the drive heat source fluid RS flowing in the heat source pipe X22, and evaporates to be the evaporator refrigerant vapor XVe. At this time, the heat source fluid RS is deprived of heat by the refrigerant liquid XVf and the temperature thereof is lowered. The evaporator refrigerant vapor XVe generated in the evaporator X20 moves to an absorber X10 in communication with the evaporator X20.

  The solution side absorption heat pump cycle will now be described. In the absorber X10, the concentrated solution XSa is supplied from the concentrated solution supply device X13, and the supplied concentrated solution XSa absorbs the evaporator refrigerant vapor XVe transferred from the evaporator X20. The concentrated solution XSa that has absorbed the evaporator refrigerant vapor XVe is reduced in concentration to become a dilute solution XSw. In the absorber X10, absorption heat is generated when the concentrated solution XSa absorbs the evaporator refrigerant vapor XVe. Due to this absorbed heat, the temperature raising target fluid RP flowing through the heat transfer tube X12 is heated and the temperature rises. In the present embodiment, the temperature raising target fluid RP flowing through the heat transfer tube X12 is originally the same combined heat source fluid RA as the source of the driving heat source fluid RS introduced into the heat source tube X22 of the evaporator X20. Therefore, the temperature-rising target fluid RP flowing through the temperature-rising fluid outlet pipe X19 has a temperature higher than that of the driving heat source fluid RS flowing into the evaporator X20 and the regenerator X30 by the amount heated by the absorber X10. The concentrated solution XSa having absorbed the evaporator refrigerant vapor XVe by the absorber X10 is reduced in concentration to be a dilute solution XSw, and is stored in the lower part of the absorber X10. The stored dilute solution XSw flows through the dilute solution pipe X36 toward the regenerator X30 due to the difference in internal pressure between the absorber X10 and the regenerator X30 and exchanges heat with the concentrated solution XSa in the solution heat exchanger X38 to obtain a temperature It falls to the regenerator X30.

  The dilute solution XSw sent to the regenerator X30 is supplied from the dilute solution supply device X33, is heated by the driving heat source fluid RS flowing through the heat source pipe X32, and the refrigerant in the supplied dilute solution XSw evaporates and the concentrated solution XSa And stored in the lower part of the regenerator X30. At this time, the heat source fluid RS is deprived of heat by the dilute solution XSw and the temperature is lowered. The driving heat source fluid RS flowing through the heat source pipe X32 has passed through the heat source pipe X22 of the evaporator X20. The refrigerant XV evaporated from the dilute solution XSw moves to the condenser X40 as a regenerator refrigerant vapor XVg. The concentrated solution XSa stored in the lower part of the regenerator X30 is pressure-fed by the solution pump X35p to the concentrated solution supply device X13 of the absorber X10 via the concentrated solution pipe X35. The concentrated solution XSa flowing in the concentrated solution pipe X35 exchanges heat with the dilute solution XSw in the solution heat exchanger X38 and rises in temperature, and then flows into the absorber X10 to be supplied from the concentrated solution supply device X13 and thereafter Repeat the same cycle.

  Next, the operation of the heat-accumulation absorption heat pump Y1 will be described with reference to FIG. 1 and FIG. 3. The temperature raising target fluid RP flowing through the temperature raising fluid pipe 81 is heated from the high temperature heat source inlet Y27 as the high temperature heat source fluid HP. It flows into absorption heat pump Y1. Although the temperature raising target fluid RP and the high temperature heat source fluid HP before and after the high temperature heat source inlet Y27 are the same, for convenience of explanation, the one in the temperature rising absorption heat pump X1 and the one in the heat buildup absorption heat pump Y1 are distinguished In order to change the name. The high temperature heat source fluid HP flowing into the heat buildup absorption heat pump Y1 flows through the high temperature heat source introduction pipe Y57, flows into the heat source pipe Y32 of the regenerator Y30, and the heat necessary to separate the regenerator refrigerant vapor YVg from the dilute solution YSw After the temperature is lowered, it reaches the high temperature heat source outflow pipe Y39. The high-temperature heat source fluid HP flowing through the high-temperature heat source outlet pipe Y39 joins the heat-increase target fluid TS flowing through the heat-up fluid outlet pipe Y49 to form a mixed fluid TA. The mixed fluid TA flows through the mixed fluid outlet pipe Y59 and flows out of the heat buildup absorption heat pump Y1 from the mixed fluid outlet Y58 to the mixed heat source transfer pipe 87.

  The mixed fluid TA flowing through the mixed heat source forward pipe 87 flows into the heat utilization facility HCF, reaches the mixed heat source return pipe 88 after the heat is utilized and the temperature drops. The mixed fluid TA of the mixed heat source return pipe 88 flows from the mixed fluid inlet Y56 into the mixed fluid inflow pipe Y55 in the heat buildup absorption heat pump Y1. The mixed fluid TA flowing from the mixed heat source return pipe 88 into the mixed fluid inflow pipe Y 55 flows by activation of the mixed fluid pump 92. The mixed fluid TA flowing through the mixed fluid inflow pipe Y55 is divided into the heat increase target fluid TS entering the heat increasing fluid introduction pipe Y51 and the low temperature heat source fluid GP entering the low temperature heat source inflow pipe Y52. The fluid to be heated TS flowing through the heat transfer fluid introduction pipe Y51 flows into the heat transfer pipe Y12 of the absorber Y10, and the temperature rises by obtaining the absorption heat generated when the concentrated solution YSa absorbs the evaporator refrigerant vapor YVe Then, the heat transfer fluid communication pipe Y15 is reached. The fluid to be heated TS flowing through the heat transfer fluid communication tube Y15 flows into the heat transfer tube Y42 of the condenser Y40, obtains condensation heat released when the regenerator refrigerant vapor YVg condenses, and increases after the temperature rises. It flows through the thermal fluid outflow pipe Y49. The heat enhancement target fluid TS flowing through the heat transfer fluid outlet pipe Y49 is mixed with the high temperature heat source fluid HP flowing through the above-mentioned high temperature heat source outlet pipe Y39 to form a mixed fluid TA and flows through the mixed fluid outlet pipe Y59 as described above Head towards the heat utilization facility HCF.

  On the other hand, the low temperature heat source fluid GP branched from the mixed fluid TA flowing from the heat utilization facility HCF into the heat buildup absorption heat pump Y1 flows through the low temperature heat source inflow pipe Y52 and flows into the heat source pipe Y22 of the evaporator Y20, and the refrigerant liquid YVf After the latent heat of vaporization necessary for becoming the evaporator refrigerant vapor YVe is taken and the temperature decreases, it flows through the low temperature heat source outflow pipe Y29. The low temperature heat source fluid GP flowing through the low temperature heat source outflow pipe Y29 flows out from the low temperature heat source outflow Y28 to the low temperature heat source pipe 82 through the heat buildup absorption heat pump Y1. The low temperature heat source fluid GP of the low temperature heat source pipe 82 flows as the low temperature heat source pump 91 is activated as described above, and travels to the temperature rising absorption heat pump X1. Hereinafter, absorption heat pump cycles of the absorbent YS and the refrigerant YV that bring about temperature changes of the high temperature heat source fluid HP, the heat increase target fluid TS, and the low temperature heat source fluid GP will be described mainly with reference to FIG.

  First, the absorption heat pump cycle on the solution side will be described. In the absorber Y10, the concentrated solution YSa is supplied from the concentrated solution supply device Y13, and the supplied concentrated solution YSa absorbs the evaporator refrigerant vapor YVe transferred from the evaporator Y20. The concentrated solution YSa that has absorbed the evaporator refrigerant vapor YVe has a reduced concentration and becomes a dilute solution YSw. In the absorber Y10, absorption heat is generated when the concentrated solution YSa absorbs the evaporator refrigerant vapor YVe. The heat to be heated TS flowing through the heat transfer tube Y12 is heated by the absorbed heat, and the temperature of the heat increasing target fluid TS rises. The concentrated solution YSa having absorbed the evaporator refrigerant vapor YVe by the absorber Y10 is reduced in concentration to be a dilute solution YSw, and is stored in the lower part of the absorber Y10. The stored dilute solution YSw is pressure-fed to the solution pump Y36p, flows through the dilute solution pipe Y36 toward the regenerator Y30, exchanges heat with the concentrated solution YSa in the solution heat exchanger Y38, and the temperature rises. It reaches to Y30.

  The dilute solution YSw sent to the regenerator Y30 is supplied from the dilute solution supply device Y33, is heated by the high-temperature heat source fluid HP flowing through the heat source pipe Y32, and the refrigerant in the supplied dilute solution YSw evaporates and the concentrated solution YSa And stored in the lower part of the regenerator Y30. At this time, the high-temperature heat source fluid HP loses its heat by the dilute solution YSw and its temperature decreases. The refrigerant YV evaporated from the dilute solution YSw moves to the condenser Y40 as a regenerator refrigerant vapor YVg. The concentrated solution YSa stored in the lower part of the regenerator Y30 reaches the concentrated solution supply device Y13 of the absorber Y10 through the concentrated solution pipe Y35 due to the difference in internal pressure between the regenerator Y30 and the absorber Y10. The concentrated solution YSa flowing in the concentrated solution pipe Y35 exchanges heat with the dilute solution YSw in the solution heat exchanger Y38, and then the temperature is lowered before it flows into the absorber Y10 and is supplied from the concentrated solution supply device Y13. Repeat the cycle of the absorbent YS.

  Next, the absorption heat pump cycle on the refrigerant side will be described. In the condenser Y40, the regenerator refrigerant vapor YVg evaporated in the regenerator Y30 is received, the regenerator refrigerant vapor YVg is cooled and condensed by the heat-increase target fluid TS flowing through the heat transfer pipe Y42, and becomes refrigerant liquid YVf. At this time, the temperature of the heat-increase target fluid TS rises due to the heat of condensation released when the regenerator refrigerant vapor YVg condenses. The fluid to be heated TS flowing through the heat transfer tube Y42 has passed through the heat transfer tube Y12 of the absorber Y10. The condensed refrigerant liquid YVf flows through the refrigerant liquid pipe Y45 to reach the evaporator Y20 due to the difference in internal pressure between the condenser Y40 and the evaporator Y20. The refrigerant liquid YVf sent to the evaporator Y20 is supplied from the refrigerant liquid supply device Y23, is heated by the low-temperature heat source fluid GP flowing in the heat source pipe Y22, and evaporates to become the evaporator refrigerant vapor YVe. At this time, the low temperature heat source fluid GP flowing through the heat source pipe Y22 is deprived of heat by the refrigerant liquid YVf and the temperature is lowered. The evaporator refrigerant vapor YVe generated by the evaporator Y20 moves to the absorber Y10 in communication with the evaporator Y20, and the same cycle is repeated thereafter.

  Again referring to FIG. 1 mainly, of the fluid circulating through the temperature rising absorption heat pump X1, the heat absorption absorption heat pump Y1, the heat source equipment HSF, and the heat utilization equipment HCF in the absorption type heat exchange system 1 performing the above-described function. The changes in temperature and flow rate will be described using specific examples. The combined heat source fluid RA flowing out of the heat source equipment HSF and flowing into the temperature rising absorption heat pump X1 and flowing through the heat source fluid inflow pipe X55 has a temperature of 95 ° C. and a flow rate of 60 t / h. The temperature raising target fluid RP and the driving heat source fluid RS which are branched from the heat source fluid inflow pipe X55 to the heating fluid introducing pipe X51 and the driving heat source introducing pipe X52 have a temperature of 95 ° C. and a flow rate of 30 t / h. When the driving heat source fluid RS of 95 ° C. and 30 t / h flowing through the driving heat source introduction pipe X52 flows through the heat source pipe X22 of the evaporator X20, heat is taken away by the refrigerant liquid XVf and reaches the driving heat source communication pipe X25 The temperature drops to 88 ° C. Thereafter, when the driving heat source fluid RS flowing through the driving heat source communication pipe X25 flows through the heat source pipe X32 of the regenerator X30, heat is taken away by the dilute solution XSw, and the temperature reaches 80 ° C. when it reaches the driving heat source outflow pipe X39. descend. The flow rate of the drive heat source fluid RS reaching the drive heat source outflow pipe X39 remains at 30 t / h.

  On the other hand, when the temperature-raising target fluid RP having a temperature of 95 ° C. and a flow rate of 30 t / h flowing through the temperature-rising fluid introduction pipe X51 flows through the heat transfer pipe X12 of the absorber X10, the concentrated solution XSa is the evaporator refrigerant vapor XVe The temperature rises to 100.degree. C. when it reaches the temperature rising fluid outlet pipe X19. The flow rate of the temperature raising target fluid RP reaching the temperature rising fluid outlet pipe X19 remains at 30 t / h. The temperature increase target fluid RP of 100 ° C. and 30 t / h flowing through the temperature rising fluid outflow pipe X19 flows out of the temperature rising absorption heat pump X1, flows through the temperature rising fluid pipe 81, and the temperature and flow rate substantially remain unchanged. It flows into the heat buildup absorption heat pump Y1 as a fluid HP. Strictly speaking, the temperature of the high-temperature heat source fluid HP that has flowed into the heat-accumulation absorption heat pump Y1 is lower than 100 ° C. due to heat dissipation when flowing through the temperature-rising fluid pipe 81. It is assumed that the temperature of the high-temperature heat source fluid HP flowing into the heat-accumulation absorption heat pump Y1 is 100.degree.

  The high temperature heat source fluid HP flowing into the heat buildup absorption heat pump Y1 and flowing through the high temperature heat source introduction pipe Y57 at a temperature of 100 ° C. and having a flow rate of 30 t / h flows into the heat source pipe Y32 of the regenerator Y30, and heats the diluted solution YSw. The temperature drops to 90 ° C. when reaching the high temperature heat source outflow pipe Y39. The high temperature heat source fluid HP of 90 ° C. flowing through the high temperature heat source outlet pipe Y 39 is mixed with the fluid to be heated TS with a flow rate of 75 t / h at a temperature of 48 ° C. flowing through the heat transfer fluid outlet pipe Y 49, 60 t C, 105 t / h The mixed fluid TA flows in the mixed fluid outlet pipe Y59. The mixed fluid TA at 60 ° C. and 105 t / h flowing through the mixed fluid outflow pipe Y59 flows out from the heat-accumulating absorption heat pump Y1 and flows into the heat utilization facility HCF to utilize heat to reduce the temperature. It is assumed that the temperature of the mixed fluid TA flowing into the heat buildup absorption heat pump Y1 decreases at the heat utilization facility HCF and the flow rate is 105 t / h at 40 ° C. The mixed fluid TA of 40 ° C. and 105 t / h flowing into the mixed heat inflow pipe Y 55 flowing into the heat absorption and absorption heat pump Y1 is branched, and the 40 ° C. and 75 t / h heat transfer target fluid TS is a heat increasing fluid introduction pipe It flows into Y51, and the low temperature heat source fluid GP of 40 ° C. and 30 t / h flows into the low temperature heat source inflow pipe Y52. The concentrated solution YSa was generated by absorbing the evaporator refrigerant vapor YVe when flowing through the heat transfer tube Y12 of the absorber Y10 at 40 ° C. and 75 t / h of the heat increase target fluid TS flowing through the heat increase fluid introduction tube Y51. The heat of absorption is obtained, and the temperature rises to 44 ° C. when reaching the heat transfer fluid communication pipe Y15. Thereafter, when the fluid to be heated TS flowing through the heat transfer fluid communication pipe Y15 flows through the heat transfer pipe Y42 of the condenser Y40, the condensation heat released when the regenerator refrigerant vapor YVg condenses and becomes the refrigerant liquid YVf The temperature rises to 48 ° C. when reaching the heat-up fluid outlet pipe Y49. The flow rate of the heat-increase target fluid TS reaching the heat-accumulation fluid discharge pipe Y49 remains at 75 t / h. As described above, the 48 ° C., 75 t / h heat-up target fluid TS flowing through the heat-up fluid outflow pipe Y49 joins the 90 ° C., 30 t / h high-temperature heat source fluid HP flowing through the high-temperature heat source outflow pipe Y39 The mixed fluid TA of 105 t / h is allowed to flow through the mixed fluid outlet pipe Y59.

  On the other hand, when the low temperature heat source fluid GP of 40 ° C. and 30 t / h flowing through the low temperature heat source inflow pipe Y52 flows through the heat source pipe Y22 of the evaporator Y20, heat is taken away by the refrigerant liquid YVf and the low temperature heat source outflow pipe Y29 The temperature drops to 30 ° C. The flow rate of the heat-increase target fluid TS reaching the low temperature heat source outflow pipe Y29 remains at 30 t / h. The low temperature heat source fluid GP at 30 ° C. and 30 t / h flowing in the low temperature heat source outflow pipe Y 29 flows out the heat buildup absorption heat pump Y 1 and flows in the low temperature heat source pipe 82. Flow into Strictly speaking, the temperature of the low-temperature heat source fluid GP that has flowed into the temperature-rising absorption heat pump X1 is lower than 30 ° C. due to heat radiation when flowing through the low-temperature heat source pipe 82. It is assumed that the temperature of the low temperature heat source fluid GP which has flowed into the temperature rising absorption heat pump X1 is 30 ° C., assuming that it is not present.

  The low temperature heat source fluid GP which flows into the temperature rising absorption heat pump X1 and flows through the low temperature heat source introduction pipe X57 at a temperature of 30 ° C. and a flow rate of 30 t / h flows through the heat transfer pipe X42 of the condenser X40. The heat of condensation obtained when XVg condenses and becomes refrigerant liquid XVf is obtained, and the temperature rises to 40 ° C. when it reaches the low temperature heat source outflow pipe X49. The flow rate of the low temperature heat source fluid GP that has reached the low temperature heat source outflow pipe X49 remains at 30 t / h. The low temperature heat source fluid GP at 40 ° C. and 30 t / h flowing through the low temperature heat source outflow pipe X49 merges with the 80 ° C. and 30 t / h driving heat source fluid RS flowing through the driving heat source outflow pipe X39 and merges at 60 ° C. and 60 t / h It becomes the heat source fluid RA, flows through the heat source fluid outflow pipe X59, and flows out from the temperature rising absorption heat pump X1. The 60 ° C., 60 t / h combined heat source fluid RA flowing out of the temperature rising absorption heat pump X1 flows through the combined heat source return pipe 85 and flows into the heat source facility HSF, recovers the exhaust heat, and the temperature rises. The combined heat source fluid RA whose temperature has risen in the heat utilization facility HCF flows into the temperature rising absorption heat pump X1 at 95 ° C. and 60 t / h, and the above flow is repeated thereafter.

  An overview of the heat flow of the absorption heat exchange system 1 described above can be seen as follows. The heat source equipment HSF applies heat to the combined heat source fluid RA to heat the combined heat source fluid RA, and the combined heat source fluid RA supplies the amount of heat obtained by heating to the temperature rising absorption heat pump X1. In the temperature-rising absorption heat pump X1, the driving heat-source fluid RS branched from the combined heat-source fluid RA gives heat to the low-temperature heat source fluid GP and the temperature-rising fluid RP via the absorption heat pump cycle The heat source fluid GP and the temperature raising target fluid RP are heated. At this time, the low temperature heat source fluid GP that has flowed out of the condenser X40 flows into the absorber X10 as a temperature raising target fluid RP after being heated by the heat source facility HSF as described above as a part of the combined heat source fluid RA. Therefore, looking at the amount of heat input and output to the temperature rising absorption heat pump X1, the amount of heat input to the temperature rising absorption heat pump X1 is the combined heat source fluid RA whose temperature flowing out is reduced from the amount of heat brought in It can be regarded as the amount of heat deducted from the amount of heat carried away. The heat output from the temperature rising absorption heat pump X1 is the amount of heat given to the low temperature heat source fluid GP by the condenser X40, and the low temperature heat source fluid GP flowing out of the condenser X40 becomes the temperature rising target fluid RP flowing into the absorber X10. The amount of heat given by heating to the amount of heat given to the temperature raising target fluid RP by the absorber X10, in other words, the amount of heat carried by the low-temperature heat source fluid GP flowing into the condenser X40, flows out from the absorber X10 It can be regarded as the amount of heat deducted from the amount of heat carried out by the temperature raising target fluid RP. That is, the temperature-rising absorption heat pump X1 converts the low-temperature heat source fluid GP into the temperature-rising target fluid RP by applying the amount of heat given from the combined heat source fluid RA to the low-temperature heat source fluid GP to heat the low-temperature heat source fluid GP. The temperature raising target fluid RP gives the heat amount obtained by being heated by the temperature rising absorption heat pump X1 to the heat buildup absorption heat pump Y1. In the heat-accumulation absorption heat pump Y1, the high-temperature heat source fluid HP whose name is changed from the temperature raising target fluid RP and the low-temperature heat source fluid GP heat the heat-increase target fluid TS via the absorption heat pump cycle of the absorbing liquid and the refrigerant. To heat the fluid TS to be heated. At this time, the high temperature heat source fluid HP that has flowed out of the regenerator Y30 flows into the evaporator Y20 as a low temperature heat source fluid GP after heat is taken away by the heat utilization facility HCF as a part of the mixed fluid TA. Therefore, looking at the amount of heat input and output to the heat buildup absorption heat pump Y1, the heat input to the heat buildup absorption heat pump Y1 is the amount of heat taken from the high temperature heat source fluid HP by the regenerator Y30 and the high temperature heat source fluid HP that has flowed out It is the sum of the amount of heat removed and cooled by the low temperature heat source fluid GP flowing into the evaporator Y20 and the amount of heat removed by the low temperature heat source fluid GP by the evaporator Y20, in other words, the temperature flowing into the regenerator Y30 is It can be considered as the amount of heat obtained by subtracting the amount of heat carried out by the low temperature heat source fluid GP obtained by lowering the temperature flowing out of the evaporator Y20 from the amount of heat carried by the high temperature raising target fluid RP. The heat output from the heat-increasing absorption heat pump Y1 can be regarded as the heat obtained by subtracting the heat carried by the mixed fluid TA having a low temperature flowing from the heat carried by the mixed fluid TA having a high temperature flowing out. That is, the heat-accumulation absorption heat pump Y1 provides the mixed fluid TA with the heat amount given by the high-temperature heat source fluid HP whose name is changed from the temperature raising target fluid RP changing to the low-temperature heat source fluid GP to heat the mixed fluid TA. ing. The mixed fluid TA gives the heat amount obtained by heating to the heat utilization facility HCF. That is, in the absorption type heat exchange system 1, the mixed fluid TA gives the heat utilization facility HCF the amount of heat that the heat source facility HSF has given to the combined heat source fluid RA. Thus, the absorption-type heat exchange system 1 constitutes a system for transporting heat from the heat source equipment HSF to the heat utilization equipment HCF.

  As described above, according to the absorption type heat exchange system 1 according to the present embodiment, the temperature difference (in the present embodiment, 35 ° C.) of the combined heat source fluid RA flowing into and out of the heat source facility HSF Since the temperature difference (70 ° C. in the present embodiment) between the temperature-rising target fluid RP flowing out of the temperature-raising absorption heat pump X1 and the low-temperature heat source fluid GP flowing in can be increased, The flow rates of the heat target fluid RP and the low temperature heat source fluid GP flowing through the low temperature heat source pipe 82 can be reduced to reduce the energy required for fluid transportation. The effect is more remarkable as the distance between the temperature-rising absorption heat pump X1 and the heat-accumulation absorption heat pump Y1 increases. Further, the fluid to be heated (the fluid to be heated RP, the low temperature heat source fluid GP) and the heating source fluid (combined heat source fluid RA, the driving heat source fluid RS) in the temperature rising absorption heat pump X1, and the heat in the heat buildup absorption heat pump Y1 A fluid RP to be heated between the fluid (mixed fluid TA, fluid to be heated up TS) and the heating source fluid (high temperature heat source fluid HP, low temperature heat source fluid GP), the temperature rising absorption heat pump X1 and the heat absorption rising heat pump Y1 The low temperature heat source fluid GP, the combined heat source fluid RA between the temperature rising absorption heat pump X1 and the heat source equipment HSF, and the mixed fluid TA between the heat absorption absorption heat pump Y1 and the heat utilization equipment HCF communicate as a whole. Since one circulation path is configured, the pressure fluctuation in the flow path can be appropriately alleviated by providing at least one expansion tank 98 throughout the absorption heat exchange system 1. Kill. Further, since the flow paths communicate with each other to configure one circulation path, the control target of the properties and the amount of the fluid in each flow path is only one fluid, and management becomes easy. When the low temperature heat source pipe 82 extends a long distance since the temperature rising absorption heat pump X1 and the heat buildup absorption heat pump Y1 are separated, the low temperature heat source pipe 82 is provided with a plurality of low temperature heat source pumps 91 at predetermined intervals The fluid GP may be pumped, or the low temperature heat source fluid 91 may be pumped by connecting a plurality of low temperature heat source pumps 91 in series to increase the discharge pressure. Alternatively, similarly to the low temperature heat source pump 91 provided in the low temperature heat source pipe 82, a pump corresponding to a fluid having a high temperature may be provided in the temperature raising fluid pipe 81.

  Next, with reference to FIG. 4, an absorption heat exchange system 2 according to a second embodiment of the present invention will be described. FIG. 2 is a schematic system diagram of the absorption type heat exchange system 2. In the following description, FIG. 2 is appropriately referred to when the configuration of the temperature-rising absorption heat pump X1 is referred to, and FIG. 3 is appropriately referred to when the configuration of the heat-accumulation absorption heat pump Y1 is referred to. The absorption-type heat exchange system 2 differs from the absorption-type heat exchange system 1 (see FIG. 1) in the following points. In the absorption type heat exchange system 2, two heat transfer absorption heat pumps Y1A and Y1B are provided so that the mixed fluid TA of 60 ° C. and 105 t / h can be supplied to the two heat utilization facilities HCF1 and HCF2, respectively. There is. The two heat buildup absorption heat pumps Y1A and Y1B both have the same configuration as the heat buildup absorption heat pump Y1 (see FIG. 3). The temperature raising fluid pipe 81 is branched into a first temperature raising fluid pipe 81A and a second temperature raising fluid pipe 81B on the opposite side of the temperature raising fluid outlet X18, and the other end of the first temperature raising fluid pipe 81A is The other end of the second temperature-rising fluid pipe 81B is connected to the high-temperature heat source inlet Y27 of the heat-accumulating absorption heat pump Y1B. The low temperature heat source pipe 82 is branched to a first low temperature heat source pipe 82A and a second low temperature heat source pipe 82B on the opposite side of the low temperature heat source inlet X17, and the other end of the first low temperature heat source pipe 82A is The other end of the second low temperature heat source pipe 82B is connected to the low temperature source outlet Y28 of the heat buildup absorption heat pump Y1B. The first low temperature heat source pipe 82A is provided with a first low temperature heat source pump 91A for flowing the internal fluid, and the second low temperature heat source pipe 82B is provided with a second low temperature heat source pump 91B for flowing the internal fluid. It is arranged. The first low-temperature heat source pump 91A includes a heat transfer pipe X42 of a condenser X40, a heat source equipment HSF, a heat transfer pipe X12 of an absorber X10, a heat source pipe Y32 of a regenerator Y30 of a heat buildup heat pump Y1A, a heat utilization plant HCF1, The heat source pipe Y22 of the evaporator Y20 of the heat pump Y1A is a pump for circulating the low temperature heat source fluid GP or the combined heat source fluid RA or the temperature raising target fluid RP or the high temperature heat source fluid HP or the mixed fluid TA. The second low-temperature heat source pump 91B includes the heat transfer pipe X42 of the condenser X40, the heat source equipment HSF, the heat transfer pipe X12 of the absorber X10, the heat source pipe Y32 of the regenerator Y30 of the heat absorption absorption heat pump Y1B, and the heat utilization equipment HCF2 The heat source pipe Y22 of the evaporator Y20 of the heat pump Y1B is a pump for circulating the low temperature heat source fluid GP or the combined heat source fluid RA or the temperature raising target fluid RP or the high temperature heat source fluid HP or the mixed fluid TA. A low temperature heat source pump 91 is disposed in the low temperature heat source pipe 82 on the downstream side of the connection portion between the first low temperature heat source pipe 82A and the second low temperature heat source pipe 82B as in the absorption heat exchange system 1 (see FIG. 1). It is done. The low temperature heat source pump 91 functions as a combination of the first low temperature heat source pump 91A and the second low temperature heat source pump 91B. The expansion tank 98 is connected to the first low temperature heat source pipe 82A on the upstream side of the first low temperature heat source pump 91A in the present embodiment, but may be connected to any pipe in communication therewith. The heat buildup absorption heat pump Y1A and the heat utilization equipment HCF1 are connected by a first mixed heat source forward pipe 87A and a first mixed heat source return pipe 88A. The heat absorption absorption heat pump Y1A corresponds to a first heat absorption absorption heat pump, and the heat utilization facility HCF1 corresponds to a first heat consuming unit. A first mixed fluid pump 92A is disposed in the first mixed heat source return pipe 88A. The heat buildup absorption heat pump Y1B and the heat utilization equipment HCF2 are connected by a second mixed heat source forward pipe 87B and a second mixed heat source return pipe 88B. The heat absorption absorption heat pump Y1B corresponds to a second heat absorption absorption heat pump, and the heat utilization facility HCF2 corresponds to a second heat consumption unit. A second mixed fluid pump 92B is disposed in the second mixed heat source return pipe 88B. The configuration of the absorption heat exchange system 2 other than the above is the same as that of the absorption heat exchange system 1 (see FIG. 1).

  In the absorption type heat exchange system 2 configured as described above, the combined heat source fluid RA flowing out of the heat source equipment HSF and flowing into the temperature rising absorption heat pump X1 and flowing through the heat source fluid inflow pipe X55 has a temperature of 95 ° C. Is 120 t / h. The temperature raising target fluid RP and the driving heat source fluid RS which are branched from the heat source fluid inflow pipe X55 to the temperature increasing fluid introducing pipe X51 and the driving heat source introducing pipe X52 have a temperature of 95 ° C. and a flow rate of 60 t / h. The drive heat source fluid RS flowing from the drive heat source introduction pipe X52 to the heat source pipe X22 of the evaporator X20, the drive heat source communication pipe X25, the heat source pipe X32 of the regenerator X30, and the drive heat source outflow pipe X39 in this order As in the case of the temperature rising absorption heat pump X1 of the replacement system 1 (see FIG. 1), the flow rate remains at 60 t / h. On the other hand, the temperature raising target fluid RP having a temperature of 95 ° C. and a flow rate of 60 t / h flowing through the temperature raising fluid introduction pipe X51 flows through the heat transfer pipe X12 of the absorber X10 and the temperature rises to 100 ° C. Through the outflow pipe X19, the temperature rising absorption heat pump X1 flows out at 100 ° C., 60 t / h, and flows through the temperature rising fluid pipe 81.

  The temperature raising target fluid RP of 100.degree. C. and 60 t / h flowing through the temperature raising fluid pipe 81 is divided into 100.degree. C. and 30 t / h for the first temperature raising fluid pipe 81A and the second temperature raising fluid pipe 81B respectively. The temperature raising target fluid RP flows in. The temperature raising target fluid RP of 100 ° C. and 30 t / h flowing in the first temperature raising fluid pipe 81A flows into the heat buildup absorption heat pump Y1A as the high temperature heat source fluid HP, and flows at 100 ° C. and 30 t flowing in the second temperature raising fluid pipe 81B. The temperature raising target fluid RP of / h flows into the heat-accumulation absorption heat pump Y1B as the high-temperature heat source fluid HP. Changes in the temperature and flow rate of the high-temperature heat source fluid HP, the heat-increase target fluid TS, the mixed fluid TA, and the low-temperature heat source fluid GP in each of the heat absorption absorption heat pump Y1A and the heat utilization equipment HCF1, the heat absorption absorption heat pump Y1B and the heat utilization equipment HCF2 Is the same as in the case of the heat absorption absorption heat pump Y1 of the absorption heat exchange system 1 (see FIG. 1). Therefore, each of the low temperature heat source fluid GP that has flowed out of the heat buildup absorption heat pump Y1A to the first low temperature heat source pipe 82A and the low temperature heat source fluid GP that has flowed out of the heat buildup absorption heat pump Y1B to the second low temperature heat source pipe 82B is 30 ° C. The flow rate is 30 t / h. The low temperature heat source fluid GP of 30 ° C. and 30 t / h flowing through the first low temperature heat source pipe 82A and the low temperature heat source fluid GP of 30 ° C. and 30 t / h flowing through the second low temperature heat source pipe 82B merge to 30 ° C. and 60 t / h. The low temperature heat source fluid GP as h is flowed through the low temperature heat source pipe 82 and flows into the temperature rising absorption heat pump X1.

  The low temperature heat source fluid GP which flows into the temperature rising absorption heat pump X1 and flows through the low temperature heat source introduction pipe X57 at 30 ° C. and 60 t / h flows through the heat transfer pipe X42 of the condenser X40 and rises in temperature to 40 ° C., The low temperature heat source outflow pipe X49 flows, and the driving heat source outflow pipe X39 flows at 80 ° C. and joins with the 60 t / h driving heat source fluid RS to become 60 ° C. and 120 t / h combined heat source fluid RA. It flows out of the temperature rising absorption heat pump X1. The combined heat source fluid RA of 60 ° C. and 120 t / h flowing out of the temperature rising absorption heat pump X1 flows through the combined heat source return pipe 85 and flows into the heat source facility HSF, recovers the exhaust heat and raises the temperature, 95 ° C., After flowing into the temperature rising absorption heat pump X1 at 120 t / h, the above-mentioned flow is repeated. The absorption-type heat exchange system 2 acting in this way is, for example, a secondary hot water (mixed fluid) from a large-capacity heat source (heat source facility HSF) to two hot water supply facilities (heat utilization facilities HCF1 and HCF2) for home heating. It is suitable when supplying TA). Even if the first low temperature heat source pump 91A is not provided, the low temperature heat source fluid GP secures a predetermined flow rate and flows through the first low temperature heat source pipe 82A, and the temperature raising target fluid RP secures a predetermined flow rate to achieve the first temperature rise When flowing through the fluid pipe 81A, the first low temperature heat source pump 91A may not be provided. Similarly, even without the second low temperature heat source pump 91B, the low temperature heat source fluid GP secures a predetermined flow rate and flows through the second low temperature heat source pipe 82B, and the temperature raising target fluid RP secures a predetermined flow rate to raise the second temperature When flowing through the warm fluid pipe 81B, the second low temperature heat source pump 91B may be omitted. Alternatively, even if the low temperature heat source pump 91 is not provided, the low temperature heat source fluid GP secures a predetermined flow rate and flows through the low temperature heat source pipe 82, and the temperature raising fluid RP secures a predetermined flow rate and flows through the temperature rising fluid pipe 81 , The low temperature heat source pump 91 may not be necessary. Further, in the absorption type heat exchange system 2, the temperature of the mixed fluid TA sent to the heat utilization facility HCF1 and the temperature of the mixed fluid TA sent to the heat utilization facility HCF2 are the same, but may be different. In addition, the heat utilization facility HCF and the heat-accumulation absorption heat pump Y1 may each be three or more.

  Next, with reference to FIG. 5, an absorption heat exchange system 3 according to a third embodiment of the present invention will be described. FIG. 5 is a schematic system diagram of the absorption type heat exchange system 3. In the following description, FIG. 2 is appropriately referred to when the configuration of the temperature-rising absorption heat pump X1 is referred to, and FIG. 3 is appropriately referred to when the configuration of the heat-accumulation absorption heat pump Y1 is referred to. The absorption heat exchange system 3 differs from the absorption heat exchange system 1 (see FIG. 1) in the following points. In the absorption type heat exchange system 3, the heat buildup absorption heat pump Y1C is provided instead of the heat buildup absorption heat pump Y1 (see FIG. 1). The heat buildup absorption heat pump Y1C is configured such that the high temperature heat source fluid HP flowing through the high temperature heat source discharge pipe 39 flows out of the heat buildup absorption heat pump Y1C and then flows in again. In the absorption type heat exchange system 3, the high temperature heat source fluid HP that has flowed out of the heat absorption absorption heat pump Y1C is heated again after the heat is utilized in the additional heat utilization facility HCFA as a first additional heat consumption unit. It is designed to flow into absorption heat pump Y1C. The high temperature heat source outflow pipe Y39 has an intermediate outlet Y39a for flowing the high temperature heat source fluid HP out of the heat buildup absorption heat pump Y1C, and an intermediate for the high temperature heat source fluid HP to flow from outside the heat buildup absorption heat pump Y1C An inlet Y39b is provided. The middle outlet Y39a corresponds to a first heat generation driving heat source fluid outflow portion, and the middle inlet Y39b corresponds to a first heat generation driving heat source fluid introduction portion. The middle outlet Y 39 a and the additional heat utilization facility HCFA are connected by a high temperature outlet pipe 387. The additional heat utilization facility HCFA and the intermediate inlet Y 39 b are connected by a high temperature outflow return pipe 388. The high temperature outflow return pipe 388 is provided with a high temperature outflow pump 392 for flowing the high temperature heat source fluid HP therein. The configuration of the absorption heat exchange system 3 other than the above is the same as that of the absorption heat exchange system 1 (see FIG. 1).

  In the absorption type heat exchange system 3 configured as described above, the combined heat source fluid RA flows out from the temperature rising absorption heat pump X1 and flows into the heat source facility HSF, and after the temperature rises in the heat source facility HSF, from the heat source facility HSF The temperature change and the flow rate at the time of flowing out and flowing into the temperature rising absorption heat pump X1 are the same as in the absorption type heat exchange system 1 (see FIG. 1). Further, the temperature change and the flow rate change of the combined heat source fluid RA, the temperature raising target fluid RP, the driving heat source fluid RS, and the low temperature heat source fluid GP in the temperature rising absorption heat pump X1 are in the absorption heat exchange system 1 (see FIG. 1). The same as in the case of the temperature rising absorption heat pump X1. The temperature raising target fluid RP that has flowed out the temperature rising absorption heat pump X1 at 100 ° C. and 30 t / h flows into the heat buildup absorption heat pump Y1C as the high temperature heat source fluid HP via the temperature rising fluid pipe 81. Regarding the high-temperature heat source fluid HP that has flowed into the heat-accumulation absorption heat pump Y1C, the changes in temperature and flow rate through the regenerator Y30 to the high-temperature heat source outflow pipe Y39 are the same as in the case of the heat-absorption absorption heat pump Y1 (see FIG. 1) It is. Thereafter, in the heat absorption absorption heat pump Y1C, the high temperature heat source fluid HP reaching 90 ° C. and 30 t / h that has reached the high temperature heat source discharge pipe Y39 temporarily flows out the heat absorption absorption heat pump Y1C from the intermediate outlet 39a, and the high temperature outflow pipe 387 Through the additional heat utilization facility HCFA. The high temperature heat source fluid HP that has flowed into the additional heat utilization facility HCFA uses heat to lower the temperature to 60 ° C., and flows again from the high temperature outflow return pipe 388 to the heat absorption absorption heat pump Y1C.

  60 ° C, 30t / h high temperature heat source fluid HP returned to high temperature heat source outflow pipe Y39 in heat buildup absorption heat pump Y1C, temperature flowing at heat increaser fluid outflow pipe Y49 is 48 ° C and heat flow target is 75t / h The fluid TS is mixed with the fluid TS to form a mixed fluid TA of 51.5 ° C. and 105 t / h, which flows through the mixed fluid outflow pipe Y59. The mixed fluid TA of 51.5 ° C. and 105 t / h flowing through the mixed fluid outflow pipe Y59 flows out of the heat-accumulating absorption heat pump Y1C and flows into the heat utilization facility HCF to utilize the heat and reduce the temperature. The temperature of the mixed fluid TA flowing into the heat absorption absorption heat pump Y1C at the heat utilization facility HCF and flowing into the heat absorption absorption heat pump Y1C is 40 ° C. and the flow rate is 105 t / h, as in the absorption heat exchange system 1 (see FIG. 1) Do. The subsequent temperature change and flow rate change of the fluid to be heat-increased TS and the low-temperature heat source fluid GP in the heat-up absorption heat pump Y1C are the same as in the case of the heat-up absorption heat pump Y1 (see FIG. 1). The low-temperature heat source fluid GP having a temperature of 30 ° C. and 30 t / h that has flowed out of the heat-accumulation absorption heat pump Y1C flows into the temperature-rising absorption heat pump X1 via the low-temperature heat source pipe 82, and repeats the above flow. The absorption type heat exchange system 3 acting in this way can make the temperature on the heat utilization side taken out by the additional heat utilization equipment HCFA higher than the temperature on the heat utilization side taken out by the heat utilization equipment HCF. Also, when the temperature of the high temperature heat source fluid HP that has flowed out of the additional heat utilization facility HCFA is the same as or higher than the temperature of the fluid to be heated TS that has flowed out of the condenser Y40, the high temperature heat source fluid that has flowed out of the additional heat utilization facility HCFA By setting the temperature of the mixed fluid TA in which HP and target fluid TS are mixed to be equal to or higher than the temperature of target fluid TS before mixing, in the heat utilization facility HCF, indirectly from the high temperature heat source fluid HP Can take more heat. Further, even if the high temperature outflow pump 392 is not provided, the high temperature outflow pump 392 may be omitted if the high temperature heat source fluid HP secures a predetermined flow rate and flows through the high temperature outflow forward pipe 387 and the high temperature outflow return pipe 388.

  Next, an absorption heat exchange system 4 according to a fourth embodiment of the present invention will be described with reference to FIG. FIG. 6 is a schematic system diagram of the absorption type heat exchange system 4. In the following description, FIG. 2 is appropriately referred to when the configuration of the temperature-rising absorption heat pump X1 is referred to, and FIG. 3 is appropriately referred to when the configuration of the heat-accumulation absorption heat pump Y1 is referred to. The absorption heat exchange system 4 differs from the absorption heat exchange system 1 (see FIG. 1) in the following points. In the absorption type heat exchange system 4, a part of the high temperature heat source fluid HP before being introduced into the heat buildup regenerator 30 of the heat buildup absorption heat pump Y1 is branched and temporarily flow out of the heat buildup absorption heat pump Y1, and the second addition After the heat is utilized in the additional heat utilization facility HCFA as a heat consuming part, it is mixed with the mixed fluid TA. In the absorption type heat exchange system 4, one end of the branch outflow pipe 487 is connected to the high temperature heat source introduction pipe Y57 of the heat absorption absorption heat pump Y1, and the other end of the branch outflow pipe 487 is connected to the additional heat utilization facility HCFA It is done. The branch outflow forward pipe 487 is a pipe constituting a flow path for leading the high-temperature heat source fluid HP before flowing into the regenerator Y30 to the additional heat utilization facility HCFA outside the heat-accumulation absorption heat pump Y1, and the second heat-up It corresponds to a driving heat source fluid outlet. One end of the branched outflow pipe 487 may be connected to the temperature raising fluid pipe 81 instead of the high temperature heat source introduction pipe Y57. Further, one end of a branch outflow return pipe 488 is connected to the mixed fluid outflow pipe Y59 of the heat buildup absorption heat pump Y1, and the other end of the branch outflow return pipe 488 is connected to the additional heat utilization facility HCFA. The branch outflow return pipe 488 is a pipe constituting a flow path for leading a part of the high-temperature heat source fluid HP whose temperature has been reduced by the use of heat in the additional heat utilization facility HCFA to the mixed fluid outflow pipe Y59. It corresponds to a heat generation driving heat source fluid introduction unit. One end of the branched outflow return pipe 488 may be connected to the mixed heat source outward pipe 87 instead of the mixed fluid outflow pipe Y59. The branch outflow return pipe 488 is provided with a branch outflow pump 492 that causes the high temperature heat source fluid HP inside to flow. The structure of the absorption heat exchange system 4 other than the above is the same as that of the absorption heat exchange system 1 (see FIG. 1).

  In the absorption type heat exchange system 4 configured as described above, the actions around the temperature rising absorption heat pump X1 and the heat source equipment HSF include absorption heat exchange including changes in the temperature and flow rate of the heated fluid and the heating source fluid It is similar to the systems 1 (see FIG. 1) and 3 (see FIG. 5). The temperature raising target fluid RP that has flowed out the temperature rising absorption heat pump X1 at 100 ° C. and 30 t / h flows into the heat buildup absorption heat pump Y1 as the high temperature heat source fluid HP via the temperature rising fluid pipe 81. A part (5 t / h in the present embodiment) of the high-temperature heat source fluid HP flowing into the heat-accumulation absorption heat pump Y1 from the high-temperature heat source inlet Y27 flows into the branch outflow pipe 487, and the rest (25 t in the present embodiment) / H) continues to flow through the high temperature heat source introduction pipe Y57. The temperature of the high-temperature heat source fluid HP flowing through the high-temperature heat source introduction pipe Y57 at 100 ° C. and 25 t / h decreases at the regenerator Y30 and drops to 89 ° C. when reaching the high-temperature heat source outflow pipe Y39. On the other hand, the high temperature heat source fluid HP of 100 ° C. and 5 t / h which has flowed into the branch outflow pipe 487 temporarily flows out of the heat buildup absorption heat pump Y1 and flows into the additional heat utilization facility HCFA, and this additional heat utilization facility HCFA The heat is utilized to reduce the temperature to 60.degree. C., and flows through the branch outflow return pipe 488 toward the mixed fluid outflow pipe Y59 of the heat absorption absorption heat pump Y1. 89 ° C., 25 t / h high temperature heat source fluid HP flowing through high temperature heat source outflow pipe Y 39, 60 ° C. 5 t / h high temperature heat source fluid HP flowing through branch outflow return pipe 488, 49 ° C. flowing through heat transfer fluid outflow pipe Y 49 And 65 t / h of the heat-increased target fluid TS join together to form a mixed fluid TA at 60 ° C. and 95 t / h and flow through the mixed fluid outflow pipe Y59. Thereafter, the temperature change and the flow rate change of the heat-increase target fluid TS and the low-temperature heat source fluid GP in the heat utilization facility HCF and the heat-increase absorption heat pump Y1 are 49 t C and 65 t / h, respectively. Except for this point, it is the same as the absorption heat exchange systems 1 (see FIG. 1) and 3 (see FIG. 5). The low temperature heat source fluid GP at 30 ° C. and 30 t / h that has flowed out the heat buildup absorption heat pump Y1 flows into the temperature rising absorption heat pump X1 via the low temperature heat source pipe 82, and the above flow is repeated thereafter. The absorption type heat exchange system 4 acting in this way can make the temperature on the heat utilization side taken out by the additional heat utilization equipment HCFA higher than the temperature on the heat utilization side taken out by the heat utilization equipment HCF. In FIG. 6, the temperature of the high temperature heat source fluid HP which is the heating source fluid in the additional heat utilization facility HCFA is higher than the temperature of the high temperature heat source fluid HP which is the heating source fluid in the additional heat utilization facility HCFA in FIG. The temperature of the medium to be heated taken out by the additional heat utilization facility HCFA in FIG. 6 can be made higher than in the case of FIG. 5. Further, even if the high temperature outflow pump 492 is not provided, the high temperature outflow pump 492 may be omitted if the high temperature heat source fluid HP ensures a predetermined flow rate and flows through the branched outflow pipe 487 and the branched outflow return pipe 488.

  Next, with reference to FIG. 7, an absorption heat exchange system 5 according to a fifth embodiment of the present invention will be described. FIG. 7 is a schematic system diagram of the absorption type heat exchange system 5. In the following description, FIG. 2 is appropriately referred to when the configuration of the temperature-rising absorption heat pump X1 is referred to, and FIG. 3 is appropriately referred to when the configuration of the heat-accumulation absorption heat pump Y1 is referred to. The absorption heat exchange system 5 differs from the absorption heat exchange system 1 (see FIG. 1) in the following points. The absorption type heat exchange system 5 includes a secondary heat device 61 for recovering heat from a secondary heat source AS (corresponding to a first secondary heat source) which is a heat source different from the heat source equipment HSF, and flows through the low temperature heat source pipe 82 A part of the low temperature heat source fluid GP bypasses the temperature rising absorption heat pump X1 and the heat source equipment HSF, is heated by the auxiliary heating device 61, and then merges with the temperature rising fluid pipe 81. The secondary heat device 61 is a device for performing heat exchange between part of the low temperature heat source fluid GP and the secondary heat source AS, and corresponds to a first secondary heat device. A high temperature liquid such as warm water or a high temperature gas such as an exhaust gas can be used as the auxiliary heat source AS. One end of a bypass forward pipe 62 is connected to the low temperature heat source pipe 82 on the downstream side of the low temperature heat source pump 91, and the other end of the bypass forward pipe 62 is connected to the heated fluid inlet 61 a of the secondary heat device 61 There is. The bypass forward pipe 62 is a pipe constituting a flow path for guiding a part of the low temperature heat source fluid GP flowing through the low temperature heat source pipe 82 to the sub-heat device 61. The bypass forward pipe 62 is provided with a low temperature bypass pump 66 for flowing the low temperature heat source fluid GP therein. One end of a bypass return pipe 63 is connected to the heated fluid outlet 61 b of the auxiliary heating device 61, and the other end of the bypass return pipe 63 is connected to the temperature increasing fluid pipe 81. The bypass return pipe 63 is a pipe that constitutes a flow path for leading the fluid flowing out of the auxiliary heating device 61 to the temperature raising fluid pipe 81. In addition, a secondary heat bypass pipe 64 is provided to bypass the flow of the low temperature heat source fluid GP into the secondary heat device 61. One end of the secondary heat bypass pipe 64 is connected to the bypass forward pipe 62 downstream of the low temperature bypass pump 66, and the other end is connected to the bypass return pipe 63. The bypass heat pipe 62 and / or the bypass return pipe 63 between the both ends of the auxiliary heat bypass pipe 64 and the auxiliary heat bypass pipe 64 are each provided with a valve so that the low temperature heat source fluid GP flows through the auxiliary heat device 61. It is configured to be able to switch between flowing through the auxiliary heat bypass pipe 64. The configuration of the absorption-type heat exchange system 5 other than the above is the same as that of the absorption-type heat exchange system 1 (see FIG. 1).

  In the absorption type heat exchange system 5 configured as described above, the functions of the heat buildup absorption heat pump Y1 and the heat utilization facility HCF are the same as those of the heated fluid and the heat source fluid except for the temperature and flow rate of the heated fluid and the heat source fluid. It is the same as the absorption type heat exchange system 1 (see FIG. 1), including fluid flow (including merging and branching), absorption heat pump cycle and the like. In the absorption type heat exchange system 5, the low temperature heat source fluid GP at 30 ° C. and 33 t / h flows out to the low temperature heat source pipe 82 from the heat absorption absorption heat pump Y 1. A portion (3 t / h in this embodiment) of the low temperature heat source fluid GP flowing through the low temperature heat source pipe 82 at 30 ° C. and 33 t / h flows into the bypass forward pipe 62, and the rest (30 t / h in this embodiment) ) Continue to flow through the low temperature heat source pipe 82. Subsequently, the low temperature heat source fluid GP flowing through the low temperature heat source pipe 82 flows into the temperature rising absorption heat pump X1 at 30 ° C., 30 t / h, and the subsequent operation around the temperature rising absorption heat pump X1 and the heat source equipment HSF is the fluid to be heated and heating Similar to the absorption heat exchange system 1 (see FIG. 1), including changes in temperature and flow rate of the source fluid. Therefore, the temperature raising target fluid RP of 100 ° C. and 30 t / h flows out to the temperature rising fluid pipe 81 from the temperature rising absorption heat pump X1. Returning a little, the low temperature heat source fluid GP of 30 ° C. and 3 t / h which has flowed into the bypass forward pipe 62 flows into the sub-heater 61, receives heat from the sub-heat source AS in the sub-heater 61, and the temperature becomes 100 ° C. After rising, it flows through the bypass return pipe 63 and flows into the temperature raising fluid pipe 81. As a result, the temperature raising target fluid RP of 100 ° C. and 33 t / h flows in the temperature raising fluid pipe 81 on the downstream side of the connection with the bypass return pipe 63. The temperature raising target fluid RP of 100.degree. C. and 33 t / h flows into the heat buildup absorption heat pump Y1 as the high temperature heat source fluid HP.

  The temperature of the high-temperature heat source fluid HP flowing into the heat-accumulation absorption heat pump Y1 at 100 ° C. and 33 t / h decreases to 90 ° C. when passing through the regenerator Y30. The high temperature heat source fluid HP at 90 ° C. and 33 t / h flowing through the high temperature heat source outflow pipe Y39 is mixed with the 48.5 ° C. and 77 t / h heat enhancement target fluid TS flowing through the heat transfer fluid outflow pipe Y49, 61 ° C. and 110 t / H mixed fluid TA and flows in the mixed fluid outflow pipe Y59. The mixed fluid TA at 61 ° C. and 110 t / h flowing in the mixed fluid outflow pipe Y59 flows out from the heat absorption absorption heat pump Y1, and heat is utilized in the heat utilization facility HCF to reduce the temperature to 40 ° C. It flows into heat pump Y1. The mixed fluid TA at 40 ° C. and 110 t / h flowing through the mixed fluid inflow pipe Y 55 flowing into the heat absorption and absorption heat pump Y1 is branched, and the temperature-increased target fluid TS at 40 ° C. 77 t / h It flows into Y51, and the low temperature heat source fluid GP of 40 ° C. and 33 t / h flows into the low temperature heat source inflow pipe Y52. The temperature increase of 40 ° C. and 77 t / h of the heat-up target fluid TS flowing through the heat-up fluid introducing pipe Y51 when it passes through the absorber Y10 and the condenser Y40 increases to 48.5 ° C. It leads to the fluid outflow pipe Y49. The flow rate of the 48.5 ° C., 77 t / h heat-up target fluid TS flowing through the heat-up fluid outflow pipe Y49 merges with the 90 ° C., 33 t / h high-temperature heat source fluid HP flowing through the high-temperature heat source outflow pipe Y39 as described above. Then, it becomes a mixed fluid TA of 61 ° C. and 110 t / h and flows through the mixed fluid outlet pipe Y59. On the other hand, the temperature of the low temperature heat source fluid GP flowing through the low temperature heat source inflow pipe Y52 at 40 ° C. and 33 t / h drops to 30 ° C. when passing through the evaporator Y20 and passes through the low temperature heat source outflow pipe Y29 Flows out as the low temperature heat source fluid GP at 30 ° C. and 33 t / h, and a part thereof flows into the bypass forward pipe 62 halfway through, and the above flow is repeated thereafter. The absorption type heat exchange system 5 acting in this manner can effectively use a plurality of heat sources. When the temperature of the secondary heat source AS of the secondary heat device 61 is higher than the temperature of the temperature rising target fluid RP flowing out of the temperature rising absorption heat pump X1, the temperature of the low temperature heat source fluid GP flowing through the bypass return pipe 63 is increased. The temperature of the temperature-rising fluid RP after joining with the low-temperature heat source fluid GP that can be higher than the temperature of the temperature-rising fluid RP flowing out of the heat absorption heat pump X1 and merged with the low-temperature heat source fluid GP It may be higher than the temperature of the fluid RP. Further, even if the low temperature bypass pump 66 is not provided, the low temperature bypass pump 66 may be omitted if the low temperature heat source fluid GP secures a predetermined flow rate and flows through the bypass forward pipe 62 and the bypass return pipe 63. The secondary heat source AS may be a high temperature gas such as an exhaust gas, as well as a high temperature liquid such as warm water. Also, there may be a plurality of secondary heat devices 61.

  Next, an absorption heat exchange system 6 according to a sixth embodiment of the present invention will be described with reference to FIG. FIG. 8 is a schematic system diagram of the absorption type heat exchange system 6. In the following description, FIG. 2 is appropriately referred to when the configuration of the temperature-rising absorption heat pump X1 is referred to, and FIG. 3 is appropriately referred to when the configuration of the heat-accumulation absorption heat pump Y1 is referred to. The absorption heat exchange system 6 differs from the absorption heat exchange system 5 (see FIG. 7) in the following points. In the absorption type heat exchange system 6, the fluid introduced into the auxiliary heat device 61 is not a part of the low temperature heat source fluid GP before being introduced into the temperature rising absorption heat pump X1, and the temperature rise heated by the temperature rising absorption heat pump X1 It is part of the target fluid RP. Due to the difference in the configuration, a branch bypass outward pipe 65 is connected to the heated fluid inflow port 61a instead of the bypass outward pipe 62 (see FIG. 7) in the absorption heat exchange system 5 (see FIG. 7) . The other end of the branch bypass forward pipe 65 is connected to the temperature raising fluid pipe 81 on the upstream side of the connection with the bypass return pipe 63. A branch bypass pump 67 for flowing the temperature raising target fluid RP inside is disposed in the branch bypassing return pipe 65. In addition, in the absorption type heat exchange system 6, the secondary heat device 61 corresponds to a second secondary heat device, and the secondary heat source AS corresponds to a second secondary heat source. The structure of the absorption heat exchange system 6 other than the above is the same as that of the absorption heat exchange system 5 (see FIG. 7).

  In the absorption type heat exchange system 6 configured as described above, the functions of the heat buildup absorption heat pump Y1 and the heat utilization facility HCF are the same as the temperatures and flow rates of the fluid to be heated and the heat source fluid. It is the same as the absorption type heat exchange system 5 (see FIG. 7) including fluid flow (including merging and branching), absorption heat pump cycle and the like. In the absorption type heat exchange system 6, the low temperature heat source fluid GP of 30 ° C. and 30 t / h flows out to the low temperature heat source pipe 82 from the heat buildup absorption heat pump Y1, and flows into the temperature rising absorption heat pump X1. The operation around the temperature rising absorption heat pump X1 and the heat source equipment HSF is the same as that of the absorption heat exchange system 5 (see FIG. 7), including changes in the temperature and flow rate of the heated fluid and the heating source fluid. Therefore, the temperature raising target fluid RP of 100 ° C. and 30 t / h flows out to the temperature rising fluid pipe 81 from the temperature rising absorption heat pump X1. A part (5 t / h in the present embodiment) of the temperature raising target fluid RP that has flowed out to the temperature raising fluid pipe 81 flows into the branch bypass return pipe 65, and the remaining (25 t / h in the present embodiment) continues. It flows through the temperature raising fluid pipe 81. The temperature rising target fluid RP of 100 ° C. and 5 t / h flowing into the branch bypass forward pipe 65 flows into the sub-heater 61, receives heat from the sub-heat source AS in the sub-heater 61, and the temperature rises to 118 ° C. Then, it flows through the bypass return pipe 63 and flows into the temperature raising fluid pipe 81. As a result, the temperature raising target fluid RP of 103 ° C. and 30 t / h flows in the temperature raising fluid pipe 81 on the downstream side of the connection with the bypass return pipe 63. The temperature raising target fluid RP of 103 ° C. and 30 t / h flows into the heat buildup absorption heat pump Y1 as the high temperature heat source fluid HP.

  The high-temperature heat source fluid HP flowing into the heat-accumulation absorption heat pump Y1 at 103 ° C. and 30 t / h lowers in temperature when passing through the regenerator Y30, and reaches 92 ° C. The high temperature heat source fluid HP at 92 ° C. and 30 t / h flowing through the high temperature heat source outflow pipe Y 39 is mixed with the 48.5 ° C. and 74.3 t / h heat increasing target fluid TS flowing through the heat transfer fluid outflow pipe Y 49, 61 ° C. , 104.3 t / h of the mixed fluid TA and flows through the mixed fluid outlet pipe Y59. The mixed fluid TA of 104.3 t / h flowing through the mixed fluid outflow pipe Y59 flows out from the heat absorption absorption heat pump Y1, and the heat is utilized in the heat utilization facility HCF to lower the temperature to 40 ° C. and increase it. It flows into the heat absorption heat pump Y1. The mixed fluid TA at 40 ° C. and 104.3 t / h flowing into the mixed heat inflow pipe Y 55 flowing into the heat absorption and absorption heat pump Y1 is branched, and the temperature-increased target fluid TS at 40 ° C. and 74.3 t / h increases. The low temperature heat source fluid GP having a temperature of 40 ° C. and 30 t / h flows into the low temperature heat source inflow pipe Y52. The temperature increase of 40.degree. C. and 74.3 t / h of the heat-increased fluid TS flowing through the heat-up fluid introducing pipe Y51 respectively reaches 48.5.degree. C. when passing through the absorber Y10 and the condenser Y40. It leads to the heat transfer fluid outflow pipe Y49. As described above, the flow rate of 48.5 ° C., 74.3 t / h heat-increase target fluid TS flowing through the heat-up fluid outflow pipe Y49 is 92 ° C., 30 t / h high-temperature heat source fluid flowing through the high-temperature heat source outflow pipe Y39. It flows into the mixed fluid outflow pipe Y59 as a mixed fluid TA at 61 ° C. and 104.3 t / h in combination with the HP. On the other hand, the temperature of the low temperature heat source fluid GP flowing through the low temperature heat source inflow pipe Y52 at 40 ° C. and 30 t / h drops to 30 ° C. when passing through the evaporator Y20 and passes through the low temperature heat source outflow pipe Y29 Flows out of the low temperature heat source pipe 82 as a low temperature heat source fluid GP of 30.degree. C. and 30 t / h, and the above flow is repeated thereafter. Thus, when the temperature of the auxiliary heat source AS of the auxiliary heat device 61 is higher than the temperature of the temperature rising target fluid RP flowing out of the temperature rising absorption heat pump X1, the temperature of the temperature rising target fluid RP flowing through the bypass return pipe 63 The temperature of the temperature raising target fluid RP before being branched to the branch bypassing return pipe 65, and flows into the partial temperature rising target fluid RP heated through the auxiliary heating device 61 and flows into the branch bypass bypassing pipe 65 The temperature of the temperature raising target fluid RP where the remaining temperature raising target fluid RP which has not been joined may be made higher than the temperature of the temperature rising target fluid RP before the joining. In the absorption type heat exchange system 6 that acts in this way, when the temperature of the temperature raising target fluid RP falls due to heat dissipation before flowing into the heat buildup absorption heat pump Y1 because the entire length of the temperature raising fluid pipe 81 is long, By heating the warm target fluid RP, it is possible to recover the temperature lost due to heat radiation. When the temperature raising fluid pipe 81 extends over a long distance, the auxiliary heating device 61 is disposed at a predetermined distance at which the temperature of the temperature raising fluid RP decreases to compensate for the temperature lost by the temperature raising fluid RP due to heat dissipation. It is good to provide more than one. In FIG. 8, the secondary heat device 61 is disposed in parallel with the temperature raising fluid pipe 81 by providing a bypass circuit (branch bypass bypass pipe 65 and bypass return pipe 63), but the branch bypass bypass pipe 65 is the temperature raising fluid pipe The temperature increasing fluid pipe 81 between the portion connected to 81 and the portion where the bypass return pipe 63 is connected to the temperature increasing fluid pipe 81 is removed, and the auxiliary heating device 61 is incorporated in series in the flow path of the temperature increasing fluid pipe 81 May be. Further, even if the branch bypass pump 67 is not provided, the branch bypass pump 67 may be omitted if the temperature raising target fluid RP secures a predetermined flow rate and flows through the branch bypass forward pipe 65 and the bypass return pipe 63. Also in the case of the present embodiment, the auxiliary heat source AS may be a high temperature gas such as an exhaust gas as well as a high temperature liquid such as warm water.

  Next, with reference to FIG. 9, an absorption heat exchange system 7 according to a seventh embodiment of the present invention will be described. FIG. 9 is a schematic system diagram of the absorptive heat exchange system 7. In the following description, FIG. 2 is appropriately referred to when the configuration of the temperature-rising absorption heat pump X1 is referred to, and FIG. 3 is appropriately referred to when the configuration of the heat-accumulation absorption heat pump Y1 is referred to. The absorption heat exchange system 7 differs from the absorption heat exchange system 1 (see FIG. 1) in the following points. The absorption type heat exchange system 7 includes two temperature rising absorption heat pumps X1A and X1B so that each of the combined heat source fluid RA whose heat is recovered from the two heat source equipment HSF1 and HSF2 can be heated. . The two temperature rising absorption heat pumps X1A and X1B both have the same configuration as the temperature rising absorption heat pump X1 (see FIG. 2). The temperature rising absorption heat pump X1A and the heat source equipment HSF1 are connected by a combined heat source forward pipe 84A and a combined heat source return pipe 85A in which a combined heat source pump 93A is disposed. The temperature rising absorption heat pump X1A corresponds to a first temperature rising absorption heat pump, and the heat source equipment HSF1 corresponds to a first heat supply unit. The temperature rising absorption heat pump X1B and the heat source equipment HSF2 are connected by a combined heat source outward pipe 84B and a combined heat source return pipe 85B in which a combined heat source pump 93B is disposed. The temperature rising absorption heat pump X1B corresponds to a second temperature rising absorption heat pump, and the heat source equipment HSF2 corresponds to a second heat supply unit.

  The temperature raising fluid pipe 81 is branched into a first temperature raising fluid pipe 81A and a second temperature raising fluid pipe 81B on the opposite side of the high temperature heat source inlet Y27, and the other end of the first temperature raising fluid pipe 81A is raised. The other end of the second temperature rising fluid pipe 81B is connected to the temperature rising fluid outlet X18 of the temperature rising absorption heat pump X1B. The low temperature heat source pipe 82 is branched into a first low temperature heat source pipe 82A and a second low temperature heat source pipe 82B on the opposite side of the low temperature heat source outlet Y28, and the other end of the first low temperature heat source pipe 82A is a temperature rising absorption heat pump X1A The other end of the second low temperature heat source pipe 82B is connected to the low temperature heat source inlet X17 of the temperature rising absorption heat pump X1B. The first low temperature heat source pipe 82A is provided with a first low temperature heat source pump 91A that causes the fluid inside to flow. The second low temperature heat source pipe 82B is provided with a second low temperature heat source pump 91B that causes the fluid inside to flow. In the low temperature heat source pipe 82, a low temperature heat source pump 91 and an expansion tank 98 are disposed similarly to the absorption type heat exchange system 1 (see FIG. 1). The structure of the absorption heat exchange system 7 other than the above is the same as that of the absorption heat exchange system 1 (see FIG. 1).

  In the absorption-type heat exchange system 7 configured as described above, the functions of the heat buildup absorption heat pump Y1 and the heat utilization facility HCF are the same as those of the heated fluid and the heat source fluid except for the temperature and flow rate of the heated fluid and the heat source fluid. It is the same as the absorption type heat exchange system 1 (see FIG. 1), including fluid flow (including merging and branching), absorption heat pump cycle and the like. In the absorption type heat exchange system 7, the low temperature heat source fluid GP at 30 ° C. and 42.9 t / h flows out to the low temperature heat source pipe 82 from the heat buildup absorption heat pump Y 1. The low temperature heat source fluid GP having a temperature of 30 ° C. and 42.9 t / h flowing through the low temperature heat source pipe 82 is divided, and in the present embodiment, 12.9 t / h flows into the first low temperature heat source pipe 82A. It is assumed that 30 t / h flows into the pipe 82B. The 30.degree. C., 12.9 t / h low temperature heat source fluid GP flowing into the first low temperature heat source pipe 82A flows into the temperature rising absorption heat pump X1A, and the temperature rises to 33.5.degree. C. when passing through the condenser X40. , Low temperature heat source outlet pipe X49. 33.5 ° C. and 12.9 t / h low-temperature heat source fluid GP flowing through low-temperature heat source outflow pipe X49 merges with 80 ° C. and 17.1 t / h driving heat source fluid RS flowing through driven heat source outflow pipe X39, 60 ° C. , 30 t / h of the combined heat source fluid RA and flows through the heat source fluid outflow pipe X59 and flows out of the temperature rising absorption heat pump X1A. Thereafter, the combined heat source fluid RA is heated when passing through the heat source equipment HSF1, and its temperature rises to 90 ° C., and flows into the temperature rising absorption heat pump X1A. The combined heat source fluid RA of 90 ° C. and 30 t / h flowing through the heat source fluid inflow pipe X55 of the temperature rising absorption heat pump X1A is 90 ° C. and 12.9 t / h of the temperature raising target fluid RP flowing into the temperature rising fluid introduction pipe X51. , 90.degree. C. flowing into the driving heat source introduction pipe X52, and 17.1 t / h of the driving heat source fluid RS. When passing through the temperature rising absorber 10, the temperature rising target fluid RP of 90 ° C. and 12.9 t / h flowing through the temperature rising fluid introduction pipe X51 rises to 100 ° C., and passes through the temperature rising fluid outflow pipe X19. Flows out from the temperature rising absorption heat pump X1A and flows through the first temperature rising fluid pipe 81A. At 90 ° C. and 17.1 t / h of the drive heat source fluid RS flowing through the drive heat source introduction pipe X52, the temperature drops to 80 ° C. when passing through the evaporator X20 and the regenerator X30, and reaches the drive heat source outflow pipe X39. The 80.degree. C., 17.1 t / h driving heat source fluid RS flowing through the driving heat source outflow pipe X39 combines the 33.5.degree. C., 12.9 t / h low temperature heat source fluid GP flowing through the low temperature heat source outflow pipe X49 as described above Then, it becomes a combined heat source fluid RA at 60 ° C. and 30 t / h, and flows through the heat source fluid outlet pipe X59, and the above flow is repeated thereafter.

  On the other hand, the low temperature heat source fluid GP at 30 ° C. and 30 t / h that has flowed into the second low temperature heat source pipe 82B flows into the temperature rising absorption heat pump X1B. The actions around the temperature rising absorption heat pump X1B and the heat source equipment HSF2 include changes in the temperature and flow rate of the fluid to be heated and the heating source fluid, and the temperature rising absorption heat pump X1 and the heat source in the absorption heat exchange system 1 (see FIG. 1) It is similar to the operation around the facility HSF. Therefore, from the temperature rising absorption heat pump X1B, the temperature rising target fluid RP of 100 ° C. and 30 t / h flows out to the second temperature rising fluid pipe 81B. The temperature raising target fluid RP of 100 ° C. and 30 t / h flowing through the second temperature raising fluid pipe 81B merges with the temperature raising target fluid RP of 12.9 t / h and 100 ° C. flowing through the first temperature raising fluid pipe 81A described above. Then, it becomes a temperature raising target fluid RP of 100 ° C. and 42.9 t / h, flows through the temperature rising fluid pipe 81, flows into the heat-accumulation absorption heat pump Y1, and thereafter repeats the above-mentioned flow. The absorption type heat exchange system 7 acting in this manner can raise the temperature of the temperature rising target fluid RP that mediates the heat recovered from the two heat source equipment HSF1 and HSF2, and transfers it to the heat absorption absorption heat pump Y1. The flow rate of the warm target fluid RP can be reduced, and the transfer power can be suppressed. In particular, it is suitable in the case where the temperature raising target fluid RP is taken out from two heat sources having different temperatures and / or flow rates. In the example shown in FIG. 9, the combined heat source fluid RA flowing into the temperature rising absorption heat pump X1A is 90 ° C., and the combined heat source fluid RA flowing into the temperature rising absorption heat pump X1B is 95 ° C., but flows out from the temperature rising absorption heat pump X1A The temperature of the temperature rising target fluid RP and the temperature of the temperature rising target fluid RP flowing out of the temperature rising absorption heat pump X1B are both 100.degree. Although two heat sources (heat source equipment HSF) are provided in the example illustrated in FIG. 9, it is preferable to expand the temperature-rising absorption heat pump X1 according to the number of heat sources also in the case of three or more heat sources. Further, even without the first low temperature heat source pump 91A, the low temperature heat source fluid GP secures a predetermined flow rate and flows through the first low temperature heat source pipe 82A, and the temperature raising target fluid RP secures a predetermined flow rate to perform the first temperature rise When flowing through the fluid pipe 81A, the first low temperature heat source pump 91A may not be provided. Similarly, even without the second low temperature heat source pump 91B, the low temperature heat source fluid GP secures a predetermined flow rate and flows through the second low temperature heat source pipe 82B, and the temperature raising target fluid RP secures a predetermined flow rate to raise the second temperature When flowing through the warm fluid pipe 81B, the second low temperature heat source pump 91B may be omitted. Further, even if the low temperature heat source pump 91 is not provided, the low temperature heat source fluid GP secures a predetermined flow rate and flows through the low temperature heat source pipe 82, and the temperature raising fluid RP secures a predetermined flow rate and flows through the temperature rising fluid pipe 81 , The low temperature heat source pump 91 may not be necessary.

  Next, with reference to FIG. 10, an absorption-type heat exchange system 1A according to a modification of the first embodiment of the present invention will be described. FIG. 10 is a schematic diagram of the absorption-type heat exchange system 1A. In the absorption type heat exchange system 1A, a temperature rising absorption heat pump X2 is provided instead of the temperature rising absorption heat pump X1 (see FIG. 2), and a heat buildup absorption heat pump Y2 is provided instead of the heat buildup absorption heat pump Y1 (see FIG. 3) Differs from the absorption heat exchange system 1 (see FIG. 1) in that In the temperature-rising absorption heat pump X2, the edges of the temperature-rising target fluid RP, the low-temperature heat source fluid GP, and the driving heat-source fluid RS are not joined but divided and the heat transfer heat pump Y2 is The edges of the high temperature heat source fluid HP and the low temperature heat source fluid GP are disconnected without merging or branching. With this configuration, in the absorption type heat exchange system 1A, in addition to the expansion tank 98 provided in the low temperature heat source pipe 82, an expansion tank 97 is provided in the combined heat source return pipe 85 on the upstream side of the combined heat source pump 93 An expansion tank 99 is provided in the mixed heat source return pipe 88 on the upstream side of the fluid pump 92. Each system is preferably provided with at least one expansion tank, and each system may be provided with a plurality of expansion tanks. The configuration other than the above of the absorption type heat exchange system 1A includes a temperature rising fluid pipe 81 connecting the temperature rising absorption heat pump X2 and the heat absorption absorption heat pump Y2 and a low temperature heat source pipe 82, a temperature rising absorption heat pump X2 and A combined heat source forward pipe 84 and a combined heat source return pipe 85 for connecting the heat source equipment HSF, a mixed heat source forward pipe 87 and a mixed heat source return pipe 88 for connecting the heat buildup heat pump Y2 to the heat utilization facility HCF It is the same as the absorption type heat exchange system 1 (see FIG. 1), including the included points. The detailed configurations of the temperature-rising absorption heat pump X2 and the heat-accumulation absorption heat pump Y2 will be described below.

  FIG. 11 is a schematic diagram of the temperature rising absorption heat pump X2. The temperature rising absorption heat pump X2 is different from the temperature rising absorption heat pump X1 (see FIG. 2) in the following points. In the temperature rising absorption heat pump X2, instead of the temperature rising fluid introduction pipe X51 (see FIG. 2), one end of the heat source fluid bypass pipe X53 is connected to the connecting portion between the heat source fluid inflow pipe X55 and the driving heat source introduction pipe X52 There is. The other end of the heat source fluid bypass pipe X53 is connected to the connection portion between the driving heat source outflow pipe X39 and the heat source fluid outflow pipe X59. The low temperature heat source outflow pipe X49 (see FIG. 2) is not provided in the temperature rising absorption heat pump X2. The heat source fluid bypass pipe X53 bypasses the evaporator X20 and the regenerator X30 to be a drive heat source outflow pipe X39 by bypassing the branch heat source fluid RQ which is a part branched from the combined heat source fluid RA flowing through the heat source fluid inflow pipe X55. It is a pipe | tube which comprises the flow path made to merge with flowing drive heat-source fluid RS, and is corresponded to a temperature rising drive heat-source fluid bypass flow path. The heat source fluid bypass pipe X53 is provided with a heat source fluid bypass valve X53v capable of blocking the flow path. Further, in the temperature rising absorption heat pump X2, the end of the heat transfer pipe X42 of the condenser X40 opposite to the end connected to the low temperature heat source introduction pipe X57, and the temperature rising fluid outflow pipe X19 of the heat transfer pipe X12 of the absorber X10. And the end opposite to the connected side are connected by the heating fluid communication pipe X15. The temperature rising heat exchange pipe X15 and the heat source fluid bypass pipe X53 are provided with a temperature rising heat exchanger X71 for performing heat exchange between the low temperature heat source fluid GP and the branch heat source fluid RQ. In the temperature rising absorption heat pump X2, the low temperature heat source fluid GP that has flowed out the temperature rising heat exchanger X71 is referred to as the temperature rising target fluid RP, and the low temperature heat source fluid GP heated by the temperature rising heat exchanger X71 is used as the temperature rising target fluid RP. It is comprised so that it may introduce into absorber X10. The configuration other than the above of the temperature rising absorption heat pump X2 is the same as the temperature rising absorption heat pump X1 (see FIG. 2).

  Next, with reference to FIG. 12, the detailed configuration of the heat buildup absorption heat pump Y2 will be described. FIG. 12 is a schematic system diagram of the heat buildup absorption heat pump Y2. The heat buildup absorption heat pump Y2 is different from the heat buildup absorption heat pump Y1 (see FIG. 3) in the following points. In the heat absorption absorption heat pump Y2, the heat transfer fluid inlet pipe Y51 (see FIG. 3) and the low temperature heat source inlet pipe Y52 (see FIG. 3) are not provided, and the mixed fluid inlet pipe Y55 is a heat transfer tube Y12 of the absorber Y10. The heat transfer fluid communication pipe Y15 is connected to the end opposite to the connected side. In addition, the heat-accumulation absorption heat pump Y2 is not provided with the heat-accumulation fluid outflow pipe Y49 (see FIG. 3), and the mixed fluid outflow pipe Y59 is connected to the heat transfer fluid communication pipe Y15 of the heat transfer pipe Y42 of the condenser Y40. It is connected to the end opposite to the side where it was made. In the heat absorption absorption heat pump Y2, it is the mixed fluid inflow pipe Y55 and the mixed fluid outflow pipe Y59 that is not the mixed fluid TA (see FIG. 3) but the heat increase target fluid TS, but the heat absorption absorption heat pump Y1 (figure For convenience of comparison with the configuration of 3), the designations "mixed fluid inflow pipe Y55" and "mixed fluid outflow pipe Y59" are used. Further, in the heat buildup absorption heat pump Y2, the other end of the high temperature heat source outflow pipe Y39 is not one end of the mixed fluid outflow pipe Y59, but opposite to the side of the heat source pipe Y22 of the evaporator Y20 to which the low temperature heat source outflow pipe Y29 is connected Connected to the end of the side. The high-temperature heat source outflow pipe Y39 and the mixed fluid outflow pipe Y59 are provided with a heat-increase heat exchanger Y72 that performs heat exchange between the high-temperature heat source fluid HP and the heat-increase target fluid TS. In the heat buildup absorption heat pump Y2, the high temperature heat source fluid HP that has flowed out the heat transfer heat exchanger Y72 is referred to as the low temperature heat source fluid GP, and the high temperature heat source fluid HP that has flowed out the heat buildup heat exchanger Y72 is evaporated as the low temperature heat source fluid GP. It is comprised so that it may introduce into container Y20. The configuration other than the above of the heat buildup absorption heat pump Y2 is the same as that of the heat buildup absorption heat pump Y1 (see FIG. 3).

  10 to 12, the heat transfer pipe X42 of the condenser X40, the heating fluid communication pipe X15, the heat transfer pipe X12 of the absorber X10, the heat source pipe Y32 of the regenerator Y30, and the high temperature heat source outflow pipe Y39. The heat source pipe Y22 of the evaporator Y20 constitutes a first circulation path, and the low temperature heat source pump 91 is a pump for circulating the low temperature heat source fluid GP or the temperature raising target fluid RP or the high temperature heat source fluid HP in the first circulation path. is there. The heat transfer pipe Y12 of the absorber Y10, the heat transfer pipe Y42 of the condenser Y40, the heat transfer fluid communication pipe Y15, and the heat utilization facility HCF constitute a second circulation path, and the mixed fluid pump 92 is increased to the second circulation path. It is a pump for circulating the heat target fluid TS. The heat source equipment HSF, the heat source pipe X22 of the evaporator X20, the heat source pipe X32 of the regenerator X30, the drive heat source communication pipe X25, and the heat source fluid bypass pipe X53 constitute a third circulation path, and the combined heat source pump 93 is a combined heat source fluid It is a pump which circulates RA or driving heat-source fluid RS or branch heat-source fluid RQ to a 3rd circulation path. The first circulation path, the second circulation path, and the third circulation path are independent circulation paths that are neither joined nor branched.

  Continuing to refer to FIGS. 10-12, the operation of the absorptive heat exchange system 1A will be described. First, the operation around the temperature rising absorption heat pump X2 will be described with reference to FIG. 10 and FIG. 11. The combined heat source fluid RA flowing by activation of the combined heat source pump 93 recovers exhaust heat in the heat source facility HSF. The temperature rises and flows into the temperature rising absorption heat pump X2 from the heat source fluid inlet X56 via the combined heat source forward pipe 84. The combined heat source fluid RA that has flowed into the temperature rising absorption heat pump X2 flows through the heat source fluid inflow pipe X55 and then enters the drive heat source introduction pipe X52, the drive heat source fluid RS, and the branch heat source fluid RQ that enters the heat source fluid bypass pipe X53; Diverted to The driving heat source fluid RS flowing through the driving heat source introduction pipe X52 flows into the heat source pipe X22 of the evaporator X20, and the temperature drops after the refrigerant liquid XVf loses the evaporation latent heat necessary for becoming the evaporator refrigerant vapor XVe , Driving heat source communication pipe X25. The driving heat source fluid RS flowing through the driving heat source communication pipe X25 flows into the heat source pipe X32 of the regenerator X30, and the temperature is lowered after the heat necessary for separating the regenerator refrigerant vapor XVg is removed from the dilute solution XSw , Driving heat source outflow pipe X39. On the other hand, the branched heat source fluid RQ branched from the combined heat source fluid RA flows through the heat source fluid bypass pipe X53 and exchanges heat with the low temperature heat source fluid GP in the temperature rising heat exchanger X71 to lower the temperature. It joins with the flowing driving heat source fluid RS. The combined drive heat source fluid RS and the branch heat source fluid RQ become combined heat source fluid RA and flow through the heat source fluid outlet pipe X59, and flow out the temperature rising absorption heat pump X1 from the heat source fluid outlet X58. Lead to The combined heat source fluid RA that has flowed into the combined heat source return pipe 85 flows into the heat source equipment HSF and recovers the exhaust heat to rise in temperature, and then reaches the combined heat source forward pipe 84. Thereafter, the above-described operation is repeated.

  On the other hand, the low temperature heat source fluid GP flowing through the low temperature heat source pipe 82 flows into the low temperature heat source inlet pipe X57 through the low temperature source inlet X17 in the temperature rising absorption heat pump X2. The low temperature heat source fluid GP flowing from the low temperature heat source pipe 82 into the low temperature heat source introduction pipe X57 flows when the low temperature heat source pump 91 is activated. The low temperature heat source fluid GP flowing through the low temperature heat source introduction pipe X57 flows into the heat transfer pipe X42 of the condenser X40, obtains condensation heat released when the regenerator refrigerant vapor XVg condenses, and the temperature rises after the temperature rises It leads to the communication pipe X15. The low temperature heat source fluid GP flowing through the temperature rising fluid communication pipe X15 exchanges heat with the branch heat source fluid RQ in the temperature rising heat exchanger X71 and rises in temperature, and then flows into the heat transfer pipe X12 of the absorber X10 as a temperature rising target fluid RP. The temperature rises by obtaining the absorption heat generated when the concentrated solution XSa absorbs the evaporator refrigerant vapor XVe, and then flows through the temperature rising fluid outflow pipe X19, and the temperature rising absorption heat pump X1 from the temperature rising fluid outlet X18 To the temperature raising fluid pipe 81. In the temperature rising absorption heat pump X2, the absorption heat pump cycle of the absorption liquid XS and the refrigerant XV that brings about temperature changes of the driving heat source fluid RS and the low temperature heat source fluid GP and the temperature rising target fluid RP as described above is the temperature rising absorption heat pump X1. It is similar to the absorption heat pump cycle in (see FIG. 2).

  Next, the operation of the heat-accumulation absorption heat pump Y2 will be described with reference to FIG. 10 and FIG. 12. The temperature raising target fluid RP flowing through the temperature raising fluid pipe 81 is heated as the high temperature heat source fluid HP from the high temperature heat source inlet Y27. It flows into absorption heat pump Y2. The high-temperature heat source fluid HP flowing into the heat-accumulation absorption heat pump Y2 flows through the high-temperature heat source inlet pipe Y57, flows into the heat source pipe Y32 of the regenerator Y30, and heat necessary to separate the regenerator refrigerant vapor YVg from the dilute solution YSw After the temperature is lowered, it reaches the high temperature heat source outflow pipe Y39. The high-temperature heat source fluid HP flowing through the high-temperature heat source outflow pipe Y39 exchanges heat with the heat-increase target fluid TS in the heat-up heat exchanger X72 and drops in temperature, and then flows into the heat source pipe Y22 of the evaporator Y20 as a low-temperature heat source fluid GP. The refrigerant liquid YVf loses its latent heat of vaporization necessary for becoming the evaporator refrigerant vapor YVe, and after the temperature drops, it flows through the low temperature heat source outflow pipe Y29. The low temperature heat source fluid GP flowing through the low temperature heat source outflow pipe Y29 flows out the heat buildup absorption heat pump Y2 from the low temperature heat source outflow port Y28 and reaches the low temperature heat source pipe 82. The low temperature heat source fluid GP of the low temperature heat source pipe 82 flows as the low temperature heat source pump 91 is activated as described above, and travels to the temperature rising absorption heat pump X2.

  On the other hand, the fluid to be heated TS that has flowed out of the heat utilization facility HCF flows into the heat transfer pipe Y12 of the absorber Y10 via the mixed heat source return pipe 88 and the mixed fluid inflow pipe Y55. The heat-increase target fluid TS flowing from the mixed heat source return pipe 88 into the mixed fluid inflow pipe Y 55 flows by activation of the mixed fluid pump 92. The temperature-increasing fluid communication pipe Y15 receives the heat of absorption generated when the concentrated solution YSa absorbs the evaporator refrigerant vapor YVe and the temperature rises, as the heat-increase target fluid TS that has flowed into the heat transfer pipe Y12 of the absorber Y10 Lead to The fluid to be heated TS flowing through the heat transfer fluid communication tube Y15 flows into the heat transfer tube Y42 of the condenser Y40, obtains the condensation heat released when the regenerator refrigerant vapor YVg condenses, and further rises in temperature, It flows through the mixed fluid outflow pipe Y59. The fluid to be heated TS flowing through the mixed fluid outflow pipe Y59 exchanges heat with the high temperature heat source fluid HP in the heat transfer heat exchanger X72 and rises in temperature, and then the heat absorbing absorption heat pump Y2 flows out from the mixed fluid outlet Y58. Flow through the mixed heat source forward pipe 87 and into the heat utilization facility HCF, the heat is utilized and the temperature drops, and then the heat utilization facility HCF flows out from the heat utilization facility HCF and flows through the mixed heat source return pipe 88. repeat. In the heat absorption absorption heat pump Y2, as described above, the absorption heat pump cycle of the absorption liquid YS and the refrigerant YV that brings about temperature change of the high temperature heat source fluid HP and the low temperature heat source fluid GP and the heat increase target fluid TS It is similar to the absorption heat pump cycle in (see FIG. 3).

  Referring again to FIG. 10, mainly of the fluid circulating through the temperature rising absorption heat pump X2, the heat absorption absorption heat pump Y2, the heat source equipment HSF, and the heat utilization equipment HCF in the absorption heat exchange system 1A performing the above-described function. The temperature and flow rate will be described by way of specific examples. In the absorption type heat exchange system 1A, in the temperature rising absorption heat pump X2, the temperature raising target fluid RP and the low temperature heat source fluid GP, and the driving heat source fluid RS become a system independent of each other without mixing, In the absorption heat pump Y2, the high-temperature heat source fluid HP and the low-temperature heat source fluid GP and the heat-increase target fluid TS do not mix, and are independent systems. In the absorption type heat exchange system 1A, the driving heat source fluid RS circulates between the temperature rising absorption heat pump X2 and the heat source facility HSF at a flow rate of 60 t / h, and the temperature flows out of the heat source facility HSF at 95 ° C. and rises. It flows into the heat absorption heat pump X2, flows out from the temperature rising absorption heat pump X2 at 60 ° C., and flows into the heat source equipment HSF. Further, the temperature raising target fluid RP and the low temperature heat source fluid GP circulate at a flow rate of 30 t / h between the temperature rising absorption heat pump X2 and the heat buildup absorption heat pump Y2 (in the heat buildup absorption heat pump Y, the high temperature heat source fluid HP is called Although it is called, the substance is the fluid to be heated (RP), flows out from the temperature rising absorption heat pump X2 at 100 ° C, flows into the heat absorption absorption heat pump Y2, flows out from the heat expansion absorption heat pump Y2 at 30 ° C It flows into the temperature rising absorption heat pump X2. The fluid TS to be heated circulates between the heat absorption absorption heat pump Y2 and the heat utilization facility HCF at a flow rate of 105 t / h, flows out from the heat absorption absorption heat pump Y2 at 60 ° C, and flows into the heat utilization equipment HCF. It flows out from the heat utilization facility HCF at 40 ° C. and flows into the heat absorption absorption heat pump Y2.

  According to the absorption type heat exchange system 1A which acts as described above, the temperature rising absorption heat pump X2 is used as the temperature difference (35.degree. C. in this embodiment) of the combined heat source fluid RA flowing into and out of the heat source equipment HSF. Since the temperature difference (70 ° C. in this embodiment) of the low temperature heat source fluid GP and the temperature raising target fluid RP flowing in and out can be increased, the temperature raising target flowing through the temperature rising fluid pipe 81 and the low temperature heat source pipe 82 The flow rates of the fluid RP and the low temperature heat source fluid GP can be reduced to reduce the energy required for fluid transportation. The effect is more remarkable as the distance between the temperature-rising absorption heat pump X2 and the heat-accumulation absorption heat pump Y2 increases.

  A temperature rising absorption heat pump X2A according to a modification shown in FIG. 13 may be provided instead of the temperature rising absorption heat pump X2 (see FIG. 11) in the absorption type heat exchange system 1A (see FIG. 10). FIG. 13 is a schematic diagram of the temperature rising absorption heat pump X2A. The temperature rising absorption heat pump X2A differs from the temperature rising absorption heat pump X2 (see FIG. 11) in the following points. In the temperature rising absorption heat pump X2A, the heat source fluid bypass pipe X53 (see FIG. 11) is not provided, and all of the combined heat source fluid RA flowing through the heat source fluid inflow pipe X55 flows into the driving heat source introduction pipe X52 as the driving heat source fluid RS. It is supposed to Further, in the temperature rising absorption heat pump X2A, the temperature rising heat exchanger X71 is replaced by the temperature rising fluid communication pipe X15 and the heat source fluid bypass pipe X53 (see FIG. 11), and It is provided. The driving heat source fluid RS flowing out of the temperature rising heat exchanger X71 and flowing through the driving heat source outflow pipe X39 is all configured to flow through the heat source fluid outflow pipe X59 as a combined heat source fluid RA. In the temperature rising absorption heat pump X2A, the combined heat source fluid RA flowing through the heat source fluid inflow pipe X55 is the same as the driving heat source fluid RS flowing through the driving heat source introduction pipe X52, and the combined heat source fluid RA flowing through the heat source fluid outflow pipe X59 is The same as the driving heat source fluid RS flowing through the driving heat source outflow pipe X39, but the fluid flowing through the heat source fluid inflow pipe X55 and the heat source fluid outflow pipe X59 for the sake of comparison with the configuration of the temperature rising absorption heat pump X2 (see FIG. 11). The term “combined heat source fluid RA” is used. The configuration other than the above of the temperature rising absorption heat pump X2A is the same as that of the temperature rising absorption heat pump X2 (see FIG. 11). Also in the temperature rising absorption heat pump X2A configured in this way, the driving heat source fluid RS circulates between the temperature rising absorption heat pump X2A and the heat source equipment HSF at a flow rate of 60 t / h, and the temperature is 95 ° C. It can flow out of the HSF and flow into the temperature rising absorption heat pump X2A, and flow out of the temperature rising absorption heat pump X2A at 60 ° C. and flow into the heat source equipment HSF. Further, the temperature raising target fluid RP and the low temperature heat source fluid GP are circulated at a flow rate of 30 t / h between the temperature rising absorption heat pump X2A and the heat buildup absorption heat pump Y2, and flow out from the temperature rising absorption heat pump X2A at 100 ° C. It can flow into the heat buildup absorption heat pump Y2, flow out of the heat buildup absorption heat pump Y2 at 30 ° C., and flow into the temperature rising absorption heat pump X2A.

  The temperature rising absorption heat pump X2 (see FIG. 11) and the heat absorption absorption heat pump Y2 (see FIG. 12) in the absorption heat exchange system 1A (see FIG. 10) respectively include the absorption heat exchange system 2 (see FIG. 4) In the heat exchange system 7 (see FIG. 9), the heat-up absorption heat pump X1 (see FIG. 2) and the heat-accumulation absorption heat pump Y1 (see FIG. 3) can be used instead. Moreover, it can replace with temperature rising absorption heat pump X2 (refer FIG. 11), and temperature rising absorption heat pump X2A (refer FIG. 13) can also be applied. In the absorption heat exchange system 2 (see FIG. 4) to the absorption heat exchange system 7 (see FIG. 9), the temperature rising absorption heat pump X1 (see FIG. 2) is a temperature rising absorption heat pump X2 (see FIG. 11) When replacing with the heat pump X2A (see FIG. 13) and replacing the heat-accumulation absorption heat pump Y1 (see FIG. 3) with the heat-absorption absorption heat pump Y2 (see FIG. 12), temperature rising absorption in the absorption heat exchange system 1 (see FIG. 1) The heat pump X1 and the heat-accumulation absorption heat pump Y1 may be replaced by a temperature-rising absorption heat pump X2 and a heat-accumulation absorption heat pump Y2 to construct an absorption type heat exchange system 1A (see FIG. 10).

  Further, in the absorption heat exchange system 1 (see FIG. 1) to the absorption heat exchange system 7 (see FIG. 9), the heat absorption absorption heat pump Y1 is used as the heat absorption absorption heat pump Y2 (FIG. 12) without replacing the temperature rising absorption heat pump X1. (Refer to the reference), or replacing the temperature rising absorption heat pump X1 with the temperature rising absorption heat pump X2 (see FIG. 11) or the temperature rising absorption heat pump X2A (see FIG. 13) without replacing the heat absorption absorption heat pump Y1. It may be

  In the absorption type heat exchange system 1A described above, a combined heat source fluid RA circulating the heat source equipment HSF and the temperature rising absorption heat pump X2 (or the temperature rising absorption heat pump X2A), the temperature rising absorption heat pump X2 (X2A) and the heat absorption The heat-up target fluid RP circulating through the heat pump Y2 and the low-temperature heat source fluid GP, and the heat-up target fluid TS circulating through the heat buildup absorption heat pump Y2 and the heat utilization facility HCF It may apply. When a liquid having a boiling point higher than that of water is applied, it is not necessary to pressurize the temperature-raising target fluid RP to suppress boiling. In particular, in the absorption type heat exchange system 1A, the combined heat source fluid RA circulating the heat source equipment HSF and the temperature rising absorption heat pump X2 (X2A), the temperature rising absorption heat pump X2 (X2A) and the heat absorption absorption heat pump Y2 circulating The heat target fluid RP and the low temperature heat source fluid GP, and the heat enhancement target fluid TS circulating in the heat buildup absorption heat pump Y2 and the heat utilization facility HCF constitute independent circulation paths that are not mixed with each other. Therefore, if general water is used for the combined heat source fluid RA and the fluid to be heated TS, and if a liquid having a boiling point higher than that of the water is applied to the temperature rising fluid RP etc. whose temperature is high, the temperature is raised to suppress boiling. It is not necessary to pressurize the target fluid RP, and the amount of use of a liquid having a high boiling point can be reduced, so that the cost of equipment can be suppressed. As described above, a heat transfer fluid or chemical liquid having a boiling point higher than that of water is applied to the fluid in which the temperature of the fluid flowing through each circulation flow path is higher than the boiling point (100 ° C.) of water at atmospheric pressure. Say. Also, the fluid used in the factory manufacturing process may be introduced into the combined heat source fluid RA as it is for heat utilization.

  In the above description, the heat source equipment HSF is shown to be composed of one heat source except for the absorption type heat exchange system 7 (see FIG. 9), but it is composed of a plurality of heat sources different in temperature It is also good. For example, there are many cases where there are various heat sources having different temperatures in steelworks, power plants and the like, and such a case can be applied. In this case, the combined heat source fluid RA passing through the heat source equipment HSF may be configured to sequentially pass from the low temperature heat source to the high temperature heat source.

  In the above description, the combined heat source fluid RA flowing through the combined heat source return pipe 85 is introduced into the heat source facility HSF, but may be discharged out of the system without being introduced into the heat source facility HSF. In this case, the combined heat source fluid RA, which is a medium of heat recovered by the heat source equipment HSF, is separately introduced from outside the system. Further, in the above description, the mixed fluid TA flowing through the mixed heat source return pipe 88 or the fluid to be heated up is the one that has flowed out of the heat utilization facility HCF. It may be made to flow into the pipe 88, and the mixed fluid TA or the fluid T for heat increase whose temperature has decreased after heat utilization in the heat utilization facility HCF may be discharged out of the system. In the absorption heat exchange systems 1, 1A and 2-7, the flow rate of the temperature raising target fluid RP flowing through the temperature raising fluid pipe 81 and the flow rate of the low temperature heat source fluid GP flowing through the low temperature heat source pipe 82 are the same. The balance is maintained, and heat transfer is performed from the temperature rising absorption heat pump X1 (X2, X2A) to the heat absorption absorption heat pump Y1 (Y2).

  In the above description, in the temperature rising absorption heat pumps X1, X2, X2A, the driving heat source fluid RS flows in series from the evaporator X20 to the regenerator X30, but the flow direction is reversed and evaporation from the regenerator X30 It may flow in series to the vessel X20, or may flow in parallel to the evaporator X20 and the regenerator X30.

  In the above description, in the temperature rising absorption heat pumps X1, X2 and X2A, the evaporator X20 is full liquid type, but it may be falling liquid film type. When the evaporator is a falling liquid film type, a refrigerant liquid supply device for supplying the refrigerant liquid XVf is provided in the upper part in the evaporator can barrel X21, and in the case of full liquid type, it is connected to the evaporator can barrel X21 The end portion of the refrigerant liquid pipe X45 may be connected to the refrigerant liquid supply device. Moreover, you may provide piping and a pump which supply the refrigerant liquid XVf of the lower part of evaporator can-cylinder X21 to a refrigerant liquid supply apparatus.

1, 1 A, 2, 3, 4, 5, 6, 7 absorption heat exchange system X1, X1 A, X1 B, X2, X2 A temperature rising absorption heat pump X10 absorber X20 evaporator X30 regenerator X40 condenser X53 heat source fluid bypass pipe X56 Heat source fluid inlet X58 Heat source fluid outlet X71 Temperature rising heat exchanger Y1, Y1A, Y1B, Y1C, Y2 Heat absorption absorption heat pump Y10 Absorber Y20 Evaporator Y30 Regenerator Y39a Intermediate outlet Y39b Intermediate inlet Y40 Condenser Y56 Mixing Fluid inlet Y 58 Mixed fluid outlet Y 72 Heat transfer heat exchanger 61 Secondary heating device 81 Heating fluid pipe 82 Low temperature heat source pipe 91 Low temperature heat source pump 92 Mixed fluid pump 98 Expansion tank 487 Branch outflow pipe 488 Branch outflow return pipe AS Heat source GP Low temperature heat source fluid HCF Heat utilization equipment HSF Heat source equipment HP High temperature heat source fluid RP Body RS Drive heat source fluid RQ Branch heat source fluid TA Mixed fluid TS Heat up target fluid XSa, YSa Concentrated solution XSw, YSw Dilute solution XVe, YVe Evaporator refrigerant vapor XVf, YVf refrigerant liquid XVg, YVg Regenerator refrigerant vapor

Claims (15)

A temperature rising absorption heat pump which is operated by an absorption heat pump cycle of an absorption liquid and a refrigerant, and the evaporation pressure of the refrigerant is higher than the condensation pressure of the refrigerant;
A heat-accumulation absorption heat pump which is operated by an absorption heat pump cycle of an absorbing liquid and a refrigerant, and the evaporation pressure of the refrigerant is lower than the condensation pressure of the refrigerant;
A temperature increase target fluid flow path for guiding the temperature increase target fluid heated by the temperature increase absorption heat pump to the heat buildup absorption heat pump;
A low temperature heat source fluid channel for leading a low temperature heat source fluid flowing out of the heat buildup absorption heat pump to the temperature rising absorption heat pump;
The heat-accumulation absorption heat pump consumes heat as a heat-increasing fluid introduction portion for introducing a heat-increased target fluid to be heated by the heat-accumulation absorption heat pump, and the fluid to be heat-increased by the heat-absorption absorption heat pump A fluid outlet to be heated which flows out toward the heat consumer;
The temperature rising absorption heat pump includes a temperature rising driving heat source fluid inflow portion for introducing a temperature rising driving heat source fluid that drives the absorption heat pump cycle in the temperature rising absorption heat pump from a heat supply portion that supplies heat; A temperature rising drive heat source fluid outflow portion for flowing out the temperature rise driving heat source fluid that has driven the absorption heat pump cycle in a heat pump;
Absorption heat exchange system. The temperature rising target fluid flow path is connected to the heat rising absorption heat pump so as to supply the temperature rising target fluid to a portion where the heat generation driving heat source fluid driving the absorption heat pump cycle flows in the heat rising absorption heat pump;
The low temperature heat source fluid flow path is connected to a portion of the temperature rising absorption heat pump where the low temperature heat source fluid flows.
The absorption heat exchange system according to claim 1. A first pump that causes the low temperature heat source fluid to flow directly or indirectly;
And a second pump that causes the fluid to be heated to flow directly or indirectly;
The absorption heat exchange system according to claim 1 or 2. An expansion tank connected to the low temperature heat source fluid flow channel or a flow channel in communication with the low temperature heat source fluid flow channel;
The absorption-type heat exchange system according to any one of claims 1 to 3. The temperature rising absorption heat pump is
A temperature rising evaporation section which deprives the temperature rising drive heat source fluid of the latent heat of vaporization necessary when the liquid of the refrigerant evaporates to become the vapor of the refrigerant;
The temperature rising driving heat source fluid is heat necessary for heating the dilute solution which is the absorption liquid which has absorbed the refrigerant and having lowered the concentration to separate the refrigerant from the dilute solution to form the concentrated solution having the increased concentration. With temperature rise reproduction department which deprives from,
The concentrated solution is introduced, the heat of evaporation generated when the concentrated solution absorbs the vapor of the refrigerant generated in the temperature-rising evaporation unit, and is released when the concentrated solution becomes the temperature-rising evaporation unit and the temperature-raising regeneration A temperature rising and absorbing section for introducing a part of the temperature rising driving heat source fluid branched from the temperature rising driving heat source fluid before being introduced into the section as the temperature rising target fluid and heating the temperature rising target fluid;
And a temperature raising / condensing portion that heats the low temperature heat source fluid by condensation heat released when the vapor of the refrigerant condenses and becomes liquid of the refrigerant,
The low-temperature heat source fluid heated by the temperature rising and condensing unit is configured to merge with the temperature rising driving heat source fluid that has flowed out from the temperature rising and evaporating unit and the temperature rising and reproducing unit;
The absorption-type heat exchange system according to any one of claims 1 to 4. The temperature rising absorption heat pump is
A temperature rising evaporation section which deprives the temperature rising drive heat source fluid of the latent heat of vaporization necessary when the liquid of the refrigerant evaporates to become the vapor of the refrigerant;
The temperature rising driving heat source fluid is heat necessary for heating the dilute solution which is the absorption liquid which has absorbed the refrigerant and having lowered the concentration to separate the refrigerant from the dilute solution to form the concentrated solution having the increased concentration. With temperature rise reproduction department which deprives from,
A part of the temperature raising driving heat source fluid branched from the temperature raising driving heat source fluid before being introduced into the temperature raising evaporating part and the temperature raising reproducing part, the temperature raising evaporating part and the temperature raising reproducing part A temperature rising drive heat source fluid bypass flow path for bypassing and joining the temperature rise driving heat source fluid after flowing out from the temperature rising evaporation unit and the temperature rising regeneration unit;
A temperature rising condensation part which heats the low temperature heat source fluid by condensation heat released when the vapor of the refrigerant condenses and becomes liquid of the refrigerant;
A temperature rising heat exchanger that exchanges heat between the low temperature heat source fluid heated by the temperature rising condensation part and the temperature rising driving heat source fluid flowing through the temperature rising driving heat source fluid bypass channel;
The concentrated solution is introduced, and the heat of the temperature rising heat exchanger is generated by the heat of absorption released when the concentrated solution absorbs the vapor of the refrigerant generated in the temperature rising evaporation section and becomes the dilute solution. A temperature rising and absorbing section for introducing a low temperature heat source fluid as the temperature raising fluid to heat the temperature raising fluid;
The absorption-type heat exchange system according to any one of claims 1 to 4. The temperature rising absorption heat pump is
A temperature rising evaporation section which deprives the temperature rising drive heat source fluid of the latent heat of vaporization necessary when the liquid of the refrigerant evaporates to become the vapor of the refrigerant;
The temperature rising driving heat source fluid is heat necessary for heating the dilute solution which is the absorption liquid which has absorbed the refrigerant and having lowered the concentration to separate the refrigerant from the dilute solution to form the concentrated solution having the increased concentration. With temperature rise reproduction department which deprives from,
A temperature rising condensation part which heats the low temperature heat source fluid by condensation heat released when the vapor of the refrigerant condenses and becomes liquid of the refrigerant;
A temperature rising heat exchanger that exchanges heat between the low temperature heat source fluid heated by the temperature rising condensation section and the temperature rising driving heat source fluid that has flowed out to the temperature rising evaporation section and the temperature rising regeneration section;
The concentrated solution is introduced, and the heat of the temperature rising heat exchanger is generated by the heat of absorption released when the concentrated solution absorbs the vapor of the refrigerant generated in the temperature rising evaporation section and becomes the dilute solution. A temperature rising and absorbing section for introducing a low temperature heat source fluid as the temperature raising fluid to heat the temperature raising fluid;
The absorption-type heat exchange system according to any one of claims 1 to 4. The heat absorption absorption heat pump is
A heat buildup condenser that heats the fluid to be heated by the heat of condensation released when the vapor of the refrigerant condenses to become a liquid of the refrigerant;
A heat-increasing evaporation section which introduces the liquid of the refrigerant from the heat-accumulating condensation section and deprives the low-temperature heat source fluid of the latent heat of vaporization necessary when the introduced liquid of the refrigerant evaporates to become the vapor of the refrigerant;
The vapor of the refrigerant is introduced from the heat buildup evaporation section, and the absorption liquid releases the introduced refrigerant vapor to heat the fluid to be heated by the absorption heat released when it becomes a dilute solution whose concentration is reduced. Heat absorption section,
The heat necessary for introducing the dilute solution from the heat buildup absorbing part, heating the introduced dilute solution, and leaving the refrigerant from the dilute solution to form a concentrated solution having an increased concentration And a heat recovery unit to take away from it,
A part of the heat-increase target fluid branched from the heat-increase target fluid before being introduced into the heat-accumulation portion and the heat-increase absorption portion is introduced into the heat-increase evaporation portion as the low-temperature heat source fluid Configured;
The heat generation driving heat source fluid deprived of heat in the heat generation regeneration unit is configured to join the heat generation target fluid flowing out from the heat generation absorption unit and the heat generation condensation unit;
The absorption heat exchange system according to any one of claims 1 to 7. The heat absorption absorption heat pump is
A heat buildup condenser that heats the fluid to be heated by the heat of condensation released when the vapor of the refrigerant condenses to become a liquid of the refrigerant;
A heat-increasing evaporation section which introduces the liquid of the refrigerant from the heat-accumulating condensation section and deprives the low-temperature heat source fluid of the latent heat of vaporization necessary when the introduced liquid of the refrigerant evaporates to become the vapor of the refrigerant;
The vapor of the refrigerant is introduced from the heat buildup evaporation section, and the absorption liquid releases the introduced refrigerant vapor to heat the fluid to be heated by the absorption heat released when it becomes a dilute solution whose concentration is reduced. Heat absorption section,
The heat necessary for introducing the dilute solution from the heat buildup absorbing part, heating the introduced dilute solution, and leaving the refrigerant from the dilute solution to form a concentrated solution having an increased concentration With the heat recovery section that takes away from the
A heat transfer heat exchanger that exchanges heat between the heat-increasing fluid and the heat-increasing heat source fluid that has been deprived of heat by the heat-up regeneration unit, and the heat-up target fluid that has flowed out from the heat transfer unit Have
The heat-increasing driving heat-source fluid flowing out of the heat-increasing heat exchanger is introduced as the low-temperature heat-source fluid to the heat-increasing evaporator;
The absorption heat exchange system according to any one of claims 1 to 7. The heat buildup absorption heat pump includes a first heat buildup absorption heat pump for flowing out the fluid to be heated toward the first heat consuming unit, and a second heat consuming unit other than the first heat consuming unit. A second heat absorption absorption heat pump which discharges the fluid to be heated toward the target;
An absorption heat exchange system according to any one of claims 1 to 9. The heat buildup absorption heat pump temporarily flows out of the heat buildup heat pump toward the first additional heat consuming unit that consumes the heat generation driving heat source fluid that has flowed out of the heat buildup regeneration unit. A heat generation driving heat source fluid outflow portion, and a first heat generation driving heat source fluid introduction for introducing the heat generation driving heat source fluid in which the heat held by the heat generation driving heat source fluid is consumed by the first additional consumption portion Have a department;
The absorption heat exchange system according to claim 8 or 9. The heat-accumulation absorption heat pump is a second additional heat-consuming unit that consumes heat from a part of the heat-production-driven heat source fluid branched from the heat-production-driven heat source fluid before being introduced into the heat generation regeneration unit. A second heat generation driving heat source fluid outflow portion which temporarily flows out to the outside of the heat absorption absorption heat pump, and the heat held by the heat generation driving heat source fluid is consumed by the second additional consumption portion And a second heat generation driving heat source fluid introducing unit for introducing a heat driving heat source fluid;
The absorption heat exchange system according to claim 8 or 9. A first secondary heat device for heating a part of the low temperature heat source fluid branched from the low temperature heat source fluid before being introduced into the temperature rising absorption heat pump with a first auxiliary heat source;
The low temperature heat source fluid heated by the first auxiliary heat device is configured to be merged with the temperature raising fluid;
An absorption heat exchange system according to any one of claims 1 to 12. A second auxiliary heat device for heating the temperature-raising target fluid heated by the temperature-raising absorption heat pump with a second auxiliary heat source;
The absorption-type heat exchange system according to any one of claims 1 to 13. The temperature rising absorption heat pump includes a first temperature rising absorption heat pump for introducing the temperature rising driving heat source fluid from the first heat supply unit, and a second heat supply unit different from the first heat supply unit. And a second temperature rising absorption heat pump for introducing the temperature rising driving heat source fluid;
An absorption heat exchange system according to any one of the preceding claims.

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