JP5543941B2 - Absorption heat pump - Google Patents

Description

  The present invention relates to an absorption heat pump that uses exhaust heat energy as a heat source and obtains a high-temperature fluid from the heat source.

  In the conventional absorption heat pump, a refrigerant pump is provided in the condenser, the refrigerant liquid condensed in the condenser is transferred to the evaporator, the refrigerant liquid is sprayed on the heater of the evaporator, and refrigerant vapor is generated from the refrigerant liquid. It was composed. In addition, a dedicated refrigerant pump is provided in the evaporator, the refrigerant liquid accumulated in the lower part of the evaporator is taken out of the evaporator, supplied to the evaporator again, circulated and distributed to the heater, and the flow rate of the refrigerant liquid supplied to the evaporator The refrigerant vapor is generated from the refrigerant liquid supplied by the evaporator (for example, Patent Document 1).

  In the case of two-stage temperature rise, a refrigerant pump is provided in the low-pressure condenser, the refrigerant liquid condensed in the low-pressure condenser is transferred to the low-pressure evaporator, and the refrigerant liquid is sprayed on the heater of the low-pressure evaporator, A refrigerant vapor is generated from the refrigerant liquid, a refrigerant pump is provided in the high-pressure condenser, the refrigerant liquid condensed in the high-pressure condenser is transferred to the high-pressure evaporator, and the refrigerant liquid is sprayed on the heater of the high-pressure evaporator. The refrigerant liquid is generated from the refrigerant liquid. In addition, a dedicated refrigerant pump is provided for each of the low-pressure and high-pressure evaporators, the refrigerant liquid accumulated in the lower part of the low-pressure and high-pressure evaporators is taken out, supplied again to the low-pressure and high-pressure evaporators, and circulated and sprayed to the heaters respectively. The flow rate of the refrigerant liquid supplied to the evaporator was increased, and the refrigerant vapor was generated from the refrigerant liquid by the evaporator (for example, Patent Document 1).

Japanese Patent Publication No.58-49780

  In such an absorption heat pump, the refrigerant liquid is transferred from the condenser to the evaporator, and the refrigerant liquid is further taken out from the evaporator and returned to the evaporator to be circulated to the heating unit of the evaporator. Therefore, the flow of the refrigerant liquid to be transferred to the evaporator and the other flow of the refrigerant liquid to be returned to the evaporator are generated by separate refrigerant pumps. There has been a demand for an absorption heat pump having a configuration.

  Therefore, the present invention generates the flow of the refrigerant liquid that transfers the refrigerant liquid to the evaporation section and the flow of the refrigerant liquid that is circulated back to the evaporation section after taking out the refrigerant liquid from the evaporation section by the same refrigerant pump, An object is to provide an absorption heat pump having a simple configuration.

  In order to achieve the above object, the absorption heat pump 101 according to the first aspect of the invention includes, for example, as shown in FIG. 1, condensing units C and 5A that condense the refrigerant vapor CS into the refrigerant liquid CL; An evaporating section E that evaporates the refrigerant liquid CL supplied from C and 5A under a single pressure to generate refrigerant vapor CS, and returns excess refrigerant liquid CL that does not evaporate to the condensing sections C and 5A; And a refrigerant boosting means 4 that boosts the refrigerant liquid CL condensed at 5A and supplies the refrigerant liquid CL to the evaporation section E.

  If comprised in this way, since a refrigerant | coolant liquid is pressure | voltage-risen by a refrigerant | coolant pressure | voltage rise means and is supplied to an evaporation part from a condensation part, the pressure of an evaporation part can be made higher than the pressure of a condensation part. Therefore, the excess refrigerant liquid that does not evaporate can be returned from the evaporating part to the condensing part due to the pressure difference between the evaporating part and the condensing part, and the refrigerant liquid returned to the condensing part is supplied to the evaporating part by the refrigerant boosting means. The refrigerant boosting means can generate a flow of the refrigerant liquid that circulates between the evaporation unit and the condensation unit. Since the refrigerant liquid evaporates at a single pressure in the evaporating unit, the refrigerant liquid evaporates at a single temperature in the evaporating unit. The evaporating part of the absorption heat pump evaporates the refrigerant liquid under a single pressure means that the evaporating part of the absorption heat pump is not a multistage pressure increase. The refrigerant booster is typically a refrigerant pump.

Further, for example, as shown in FIG. 1, the absorption heat pump 101 includes a refrigerant liquid CL supplied from the condensing units C and 5A to the evaporation unit E and a refrigerant liquid CL returned from the evaporation unit E to the condensing units C and 5A. You may provide with refrigerant | coolant heat exchanger X11 which performs heat exchange between.
If comprised in this way, since the heat exchange is performed between the refrigerant liquid supplied to the evaporation part from the condensation part and the refrigerant liquid returned to the condensation part from the evaporation part, the temperature of the refrigerant liquid returned to the condensation part is lowered. Therefore, the generation of steam is suppressed to prevent heat loss, and when the refrigerant boosting means is a refrigerant pump, it is useful for preventing cavitation of the refrigerant pump.

  In order to achieve the above object, the absorption heat pump 102 according to the second aspect of the present invention is supplied with condensing parts C and 5A, for example, as shown in FIG. An evaporating part EL for evaporating the refrigerant liquid CL to generate the refrigerant vapor CS; and a refrigerant boosting means 4 for increasing the pressure of the refrigerant liquid CL condensed in the condensing parts C and 5A and supplying the refrigerant liquid CL to the evaporating part EL; 5A has a refrigerant supply line 5A for supplying the condensed refrigerant liquid CL to the refrigerant pressure increasing means 4, and the evaporation section EL is configured to return the excess refrigerant liquid CL that does not evaporate to the refrigerant supply line 5A. .

  If comprised in this way, since a refrigerant | coolant liquid is pressurized by the refrigerant | coolant pressure | voltage rise means and is supplied to the evaporation part with a high pressure from a condensation part, the pressure of an evaporation part can be made higher than the pressure of a condensation part. Therefore, due to the pressure difference between the evaporator and the condenser, excess refrigerant liquid that does not evaporate can be returned from the evaporator to the refrigerant supply line of the condenser, and the refrigerant liquid that has returned to the refrigerant supply line is evaporated by the refrigerant boosting means. Since the refrigerant is supplied to the section, the refrigerant pressure circulating means can generate a flow of the refrigerant liquid that circulates between the evaporation section and the refrigerant supply pipe.

  In order to achieve the above object, the absorption heat pump 103 according to the third aspect of the invention includes, for example, as shown in FIG. 5, condensing units C and 5A that condense the refrigerant vapor CS into the refrigerant liquid CL; High-pressure evaporation section EH that evaporates refrigerant liquid CL supplied from C and 5A to generate refrigerant vapor CS; refrigerant liquid CL supplied from condensation sections C and 5A, and excess refrigerant that does not evaporate in high-pressure evaporation section EH The refrigerant liquid CL that is the liquid CL and is returned from the high-pressure evaporation section EH is evaporated at a lower pressure than the high-pressure evaporation section EH, generates the refrigerant vapor CS, and returns the excess refrigerant liquid CL that does not evaporate to the condensation sections C and 5A. A low-pressure evaporating unit EL; and a refrigerant pressurizing unit 4 that pressurizes the refrigerant liquid CL condensed in the condensing units C and 5A and supplies it to the high-pressure evaporating unit EH and the low-pressure evaporating unit EL.

  With this configuration, the refrigerant liquid is boosted by the refrigerant boosting means and is supplied from the condensing unit to the high-pressure evaporation unit and the low-pressure evaporation unit. In the low-pressure evaporation unit, the refrigerant liquid is evaporated at a lower pressure than the high-pressure evaporation unit. Can be increased in the order of the high-pressure evaporator, the low-pressure evaporator, and the condenser. Therefore, surplus refrigerant liquid that does not evaporate can be returned from the high-pressure evaporator to the low-pressure evaporator due to the pressure difference between the high-pressure evaporator and the low-pressure evaporator, and excess refrigerant that does not evaporate due to the pressure difference between the low-pressure evaporator and the condenser. The liquid can be returned from the low-pressure evaporation unit to the condensation unit, and the refrigerant liquid returned to the condensation unit is supplied to the high-pressure evaporation unit and the low-pressure evaporation unit by the refrigerant boosting unit. It is possible to generate a flow of refrigerant liquid that circulates from the low-pressure evaporator to the condenser, and from the condenser to the high-pressure evaporator and the low-pressure evaporator.

  Further, for example, as shown in FIG. 5, the absorption heat pump 103 is a refrigerant liquid CL supplied from the condensing units C and 5A, and is supplied to the high-pressure evaporation unit EH without being supplied to the low-pressure evaporation unit EL. , A high-temperature refrigerant heat exchanger X12 that exchanges heat with the refrigerant liquid CL returned to the low-pressure evaporator EL from the high-pressure evaporator EH; and supplied from the condenser C to the high-pressure evaporator EH and the low-pressure evaporator EL You may make it provide at least one of the low-temperature refrigerant | coolant heat exchanger X11 which performs heat exchange between the refrigerant | coolant liquid CL and the refrigerant | coolant liquid CL returned to the condensation part C from the low pressure evaporation part EH.

  If comprised in this way, the heat exchange between the refrigerant | coolant liquid supplied to a high voltage | pressure evaporation part from a condensation part and the refrigerant | coolant liquid returned to a low voltage | pressure evaporation part from a high voltage | pressure evaporation part, and a high voltage | pressure evaporation part and a low voltage | pressure evaporation part from a condensation part At least one of the heat exchanges between the refrigerant liquid supplied to the refrigerant liquid and the refrigerant liquid returned from the low-pressure evaporator to the condenser, so that the heat retained in the refrigerant liquid from the high-pressure evaporator escapes to the low-pressure evaporator Can be achieved, or at least one of preventing the heat retained in the refrigerant liquid from the low-pressure evaporation section from escaping to the condensation section can be achieved, and heat loss can be reduced.

  In order to achieve the above object, the absorption heat pump 104 according to the fourth aspect of the invention includes, for example, as shown in FIG. 6, condensing units C and 5A that condense the refrigerant vapor CS into the refrigerant liquid CL; A high-pressure evaporation section EH that evaporates the refrigerant liquid CL supplied from C and 5A to generate refrigerant vapor CS and returns excess refrigerant liquid CL that does not evaporate to the condensation sections C and 5A; The refrigerant liquid CL is evaporated at a lower pressure than the high-pressure evaporation section EH to generate the refrigerant vapor CS, and the excess refrigerant liquid not evaporated is returned to the condensing section; and condensed in the condensing sections C and 5A There is provided a refrigerant boosting means 4 that pressurizes the refrigerant liquid CL and supplies it to the high-pressure evaporator EH and the low-pressure evaporator EL.

  With this configuration, the refrigerant liquid is boosted by the refrigerant boosting means and is supplied from the condensing unit to the high-pressure evaporation unit and the low-pressure evaporation unit. In the low-pressure evaporation unit, the refrigerant liquid is evaporated at a lower pressure than the high-pressure evaporation unit. Can be increased in the order of the high-pressure evaporator, the low-pressure evaporator, and the condenser. Therefore, the excess refrigerant liquid that does not evaporate can be returned from the high pressure evaporation part to the condensation part due to the pressure difference between the high pressure evaporation part and the condensation part, and the excess refrigerant liquid that does not evaporate due to the pressure difference between the low pressure evaporation part and the condensation part. The refrigerant liquid returned to the condensing unit can be returned from the low pressure evaporating unit, and is supplied to the high pressure evaporating unit and the low pressure evaporating unit by the refrigerant boosting unit. It is possible to generate a circulating refrigerant liquid flow and a refrigerant liquid flow circulating between the low-pressure evaporator and the condenser.

  Further, for example, as shown in FIG. 6, the absorption heat pump 104 includes a refrigerant liquid CL supplied from the condensing units C and 5A to the high-pressure evaporation unit EH, and a refrigerant liquid CL returned from the high-pressure evaporation unit EH to the condensing units C and 5A. A high-temperature refrigerant heat exchanger X12 that exchanges heat with the refrigerant; a refrigerant liquid CL that is supplied from the condensers C and 5A to the low-pressure evaporator EL; and a refrigerant liquid that is returned from the low-pressure evaporator EL to the condensers C and 5A At least one of the low-temperature refrigerant heat exchanger X13 that exchanges heat with the heat exchanger may be provided.

  If comprised in this way, the heat exchange between the refrigerant | coolant liquid supplied to a high pressure evaporation part from a condensation part, and the refrigerant | coolant liquid returned to a condensation part from a high pressure evaporation part, and the refrigerant | coolant supplied to a low pressure evaporation part from a condensation part Since at least one of the heat exchanges between the liquid and the refrigerant liquid returned from the low-pressure evaporation unit to the condensation unit is performed, it is possible to prevent the retained heat of the refrigerant liquid from the high-pressure evaporation unit from escaping to the condensation unit, or At least one of preventing the retained heat of the refrigerant liquid from the evaporation section from escaping to the condensation section can be achieved, and heat loss can be reduced.

  In order to achieve the above object, the absorption heat pump 105 according to the fifth aspect of the invention includes, for example, as shown in FIG. 7, a refrigerant boosting means 47 that boosts the refrigerant liquid CL; and evaporates the supplied refrigerant liquid CL. A low-pressure evaporation unit EL that generates a refrigerant vapor CS and an excess refrigerant liquid CL that does not evaporate is taken out by the refrigerant boosting means 47; and evaporates the supplied refrigerant liquid CL at a higher pressure than the low-pressure evaporation unit EL. A high-pressure evaporation section EH that generates CS and supplies an excess refrigerant liquid CL that does not evaporate to the low-pressure evaporation section EL; the refrigerant liquid CL taken out from the low-pressure evaporation section EL is Or is supplied to the high pressure evaporator EH and the low pressure evaporator EL.

  With this configuration, since the refrigerant liquid evaporates at a higher pressure than the low pressure evaporator in the high pressure evaporator, there is a pressure difference between the high pressure evaporator and the low pressure evaporator. Excess refrigerant liquid CL that does not evaporate can be supplied to the low-pressure evaporation part EL, and the refrigerant liquid CL taken out from the low-pressure evaporation part EL is supplied to the high-pressure vapor part EH by the refrigerant pressure raising means 4 or the low-pressure evaporation part EH and the low-pressure evaporation part EH. It can supply to the evaporation part EL. Therefore, it is possible to generate a flow of the refrigerant liquid circulating between the high-pressure evaporation section and the low-pressure evaporation section by the refrigerant boosting means, and a flow of the refrigerant liquid taken out from the low-pressure evaporation section and returning to the low-pressure evaporation section.

  Further, for example, as shown in FIG. 7, the absorption heat pump 105 is extracted from the low-pressure evaporation unit EL and supplied to the high-pressure evaporation unit EH, and is extracted from the high-pressure evaporation unit EH and supplied to the low-pressure evaporation unit EL. You may make it provide the high temperature refrigerant | coolant heat exchanger X15 which heat-exchanges with the refrigerant | coolant liquid which becomes.

  If comprised in this way, since heat exchange is performed as mentioned above, it can prevent that the retention heat | fever of the refrigerant | coolant liquid from a high pressure evaporation part escapes to a low pressure evaporation part, and can reduce a heat loss.

  According to the absorption heat pump of the present invention, since the condensing unit, the evaporating unit, and the refrigerant pressurizing unit are provided as described above, the refrigerant liquid is pressurized by the refrigerant pressurizing unit and supplied from the condensing unit to the evaporating unit. The pressure of the evaporation unit can be made higher than the pressure of the condensation unit, and due to the pressure difference between the evaporation unit and the condensation unit, excess refrigerant liquid that does not evaporate can be taken out from the evaporation unit and returned to the condensation unit, and returned to the condensation unit. Since the refrigerant liquid thus supplied is supplied to the evaporation section by the refrigerant boosting means, the refrigerant boosting means can generate a flow of the refrigerant liquid that circulates between the evaporation section and the condensation section. Therefore, the flow of the refrigerant liquid for supplying the refrigerant liquid to the evaporation unit and the flow of the refrigerant liquid to be circulated back to the evaporation unit after the refrigerant liquid is taken out from the evaporation unit are generated by the same refrigerant boosting means, An absorption heat pump with a simple structure can be obtained.

It is a flow sheet which shows the composition of the absorption heat pump concerning a 1st embodiment of the present invention. It is a diagram which shows the state of the absorption liquid on the flow sheet of FIG. It is a flow sheet which shows the composition of the absorption heat pump concerning a 2nd embodiment of the present invention. It is a diagram which shows the state of the absorption liquid on the flow sheet of FIG. It is a flow sheet which shows the composition of the absorption heat pump concerning a 3rd embodiment of the present invention. It is a flow sheet which shows the composition of the absorption heat pump concerning a 4th embodiment of the present invention. It is a flow sheet which shows the composition of the absorption heat pump concerning a 5th embodiment of the present invention.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, in each figure, the same code | symbol is attached | subjected to the mutually same or equivalent member, and the overlapping description is abbreviate | omitted.

  FIG. 1 is a flow sheet showing the configuration of the absorption heat pump 101 according to the first embodiment. The absorption heat pump 101 includes a single absorber A as an absorption unit in which the refrigerant vapor CS (the refrigerant is water, for example) is absorbed by the absorption liquid ALi (for example, lithium bromide aqueous solution), and the refrigerant vapor CS from the absorption liquid ALi. One regenerator G as a regenerating unit for evaporating and regenerating the absorbing liquid ALi, one evaporator E as an evaporating unit for generating the refrigerant vapor CS from the refrigerant liquid CL, and the refrigerant liquid by condensing the refrigerant vapor CS And one condenser C as a condensing part to be CL. The absorber A, the regenerator G, the evaporator E, and the condenser C are each under one pressure, the pressure of the evaporator E and the pressure of the absorber A are practically equal, and the pressure of the regenerator G and the condenser C The pressure is practically equal.

  The absorber A includes (1) an absorbent liquid spray 22 for transferring (supplying) the absorbent liquid ALi, which is a concentrated solution, and spraying the transferred absorbent liquid ALi inside the absorber A, and (2) makeup water W1. Heated pipe 23 in which transferred replenishment water W1 is heated by absorption liquid ALi which is transferred and absorbs refrigerant vapor CS, and (3) installed in the lower part of absorber A, in absorber A And a liquid level sensor L1 for detecting the liquid level of the absorbing liquid ALi accumulated therein. The liquid level sensor L1 is installed below the heated pipe 23 in the vertical direction.

  In the evaporator E, (1) the refrigerant liquid CL is transferred, and the refrigerant liquid spray 44 for spraying the transferred refrigerant liquid CL inside the evaporator E, and (2) the warm water WH1 having exhaust heat is transferred and evaporated. A heating pipe 28 for heating the refrigerant liquid CL transferred to the evaporator E; and (3) a liquid level sensor that is installed at the lower part of the evaporator E and detects the liquid level of the refrigerant liquid CL accumulated in the evaporator E. L2. The liquid level sensor L2 is installed below the heating pipe 28 in the vertical direction. The absorption heat pump 101 is configured such that the refrigerant vapor CS evaporated by the evaporator E is sent to the absorber A.

  The regenerator G includes (1) an absorbing liquid spray 25 in which the absorbing liquid ALi which is a dilute solution is transferred, and the transferred absorbing liquid ALi is sprayed inside the regenerator G, and (2) hot water WH2 having exhaust heat. The absorption liquid ALi sprayed by the transferred warm water WH2 is heated, the refrigerant vapor CS is generated from the absorption liquid ALi, and the heating pipe 26 using the absorption liquid ALi as a concentrated solution is provided. The absorption heat pump 101 is configured such that the refrigerant vapor CS separated from the absorption liquid ALi by the regenerator G is sent to the condenser C.

  The condenser C includes a cooling pipe 30 to which the cooling water WC is transferred and the refrigerant vapor CS sent from the regenerator G to the condenser C is cooled. The temperature of the cooling water WC is, for example, 32 ° C. at the inlet of the cooling pipe 30 and 37 ° C. at the outlet.

  The absorption heat pump 101 includes (1) a gas-liquid separator 11, (2) a makeup water transfer pipe 7 that is connected to the gas-liquid separator 11 and transports makeup water W1 to the gas-liquid separator 11, and (3) gas A makeup water transfer conduit 6 for transporting makeup water W1 from the liquid separator 11 to the heated tube 23 of the absorber A; and (4) transporting the makeup water W1 from the heated tube 23 to the gas-liquid separator 11 and returning it. A makeup water transfer line 10 and (5) a steam supply line 8 connected to a steam header (not shown) and supplying steam S (for example, 175 ° C.) generated in the gas-liquid separator 11 to the steam header. Prepare. Hereinafter, the heated pipe 23 of the absorber A, the makeup water transfer pipes 7, 6, 10, and the gas-liquid separator 11 are referred to as a steam generation unit 14.

  The absorption heat pump 101 further (6) connects the regenerator G and the absorber A, and absorbs the absorption liquid ALi, which is a concentrated solution regenerated by the regenerator G, to the absorption liquid spray 22 of the absorber A. Absorption liquid transfer pipe for connecting the absorption line ALi, which is a dilute solution accumulated in the absorber A, to the absorption liquid spray 25 of the regenerator G by connecting the pipe line 2 and (7) the absorber A and the regenerator G 3 and (8) a refrigerant liquid transfer line 5 that connects the condenser C and the evaporator E and transfers the refrigerant liquid CL condensed in the condenser C to the evaporator E.

  The refrigerant liquid transfer pipe 5 includes a refrigerant supply pipe 5A on the upstream side of the refrigerant pump 4 described later and a refrigerant liquid transfer pipe 5B on the downstream side of the refrigerant pump 4. Condensing part of this invention is comprised including the condenser C and 5 A of refrigerant | coolant supply pipe lines.

The absorption heat pump 101 further (9) connects the evaporator E and the refrigerant supply line 5A, and transfers the excess refrigerant liquid CL accumulated in the evaporator E to the refrigerant supply line 5A. And (10) the absorption liquid transfer pipe 3 (specifically, upstream of the heat exchanger X2 to be described later of the absorption liquid transfer pipe 3), and again the absorption liquid transfer pipe 3 (specifically, And an absorption liquid transfer pipe line 52 returning to the absorption liquid transfer pipe line 3 downstream of the heat exchanger X2.

The absorption heat pump 101 further transfers (11) the absorption liquid ALi that is a concentrated solution transferred to the heated side through the absorption liquid transfer pipe 2 and the heating liquid through the absorption liquid transfer pipe 52. Refrigerant heat exchanger X1 that exchanges heat with the absorbing liquid ALi that is a dilute solution, (12) makeup water W1 that is transferred to the heated side through the makeup water transfer pipe 7, and an absorption liquid transfer pipe A heat exchanger X2 for exchanging heat with the absorbing liquid ALi, which is a dilute solution transferred to the heating side through the path 3, and (13) transferred to the heated side through the refrigerant liquid transfer line 5. And a refrigerant heat exchanger X11 that performs heat exchange between the refrigerant liquid CL and the refrigerant liquid CL that is transferred to the heating side through the refrigerant liquid transfer pipe 51.
The heat exchanger X2 and the refrigerant heat exchanger X1 are arranged in parallel. In addition, a throttle 61 is installed on the downstream side of the refrigerant heat exchanger X11 in the refrigerant liquid transfer pipe 51.

  The absorption heat pump 101 further includes a heat exchanger X3 in which warm water WH3 having exhaust heat is transferred to the heating side, and makeup water W1 is transferred to the heated side through the makeup water transfer pipe 7 to perform heat exchange. .

  A solution pump 1 is installed in the absorption liquid transfer pipe 2, and the solution pump 1 transfers the absorption liquid ALi regenerated by the regenerator G to the absorber A. The solution pump 1 is installed on the upstream side of the refrigerant heat exchanger X1. The refrigerant liquid transfer pipe 5 is provided with a refrigerant pump 4 as a refrigerant boosting means, and the refrigerant pump 4 transfers the refrigerant liquid CL condensed by the condenser C to the evaporator E. A water supply pump 12 is installed in the make-up water transfer pipe 7, and the water supply pump 12 transfers make-up water W <b> 1 to the gas-liquid separator 11 of the steam generation unit 14. A check valve 37 is installed immediately downstream of the feed water pump 12 in the makeup water transfer pipe 7 to prevent the makeup water W1 from flowing back. A water supply pump 13 is installed in the make-up water transfer pipe 6, and the water supply pump 13 transfers make-up water W 1 from the gas-liquid separator 11 to the heated pipe 23, and further through the make-up water transfer pipe 7 to be heated. It is transferred from the tube 23 to the gas-liquid separator 11 and returned to circulate the makeup water W1.

  A refrigerant supply valve V <b> 3 that adjusts the flow rate of the refrigerant liquid CL to be transferred to the evaporator E is installed downstream of the refrigerant heat exchanger X <b> 11 in the refrigerant liquid transfer line 5.

  The gas-liquid separator 11 of the steam generating unit 14 is provided with a pressure sensor P for detecting the pressure of the steam generating unit 14, and a liquid level sensor L3 for detecting the liquid level of the makeup water W1 accumulated in the lower part. is set up. The steam supply pipe 8 is provided with a steam valve V1 that adjusts the pressure of the steam S to be supplied. As shown in the figure, a check valve 38 for preventing the backflow of steam from a steam header (not shown) may be installed in the steam supply line 8. When the check valve 38 is installed, the backflow of steam from the steam header can be surely prevented regardless of the operation of the steam valve V1. The temperature of the hot water WH1, WH2, and WH3 may be, for example, 90 ° C. at the inlet and 85 ° C. at the outlet.

The absorption heat pump 101 includes a control device 21. A liquid level signal (not shown) representing the liquid level from the liquid level sensor L1 is sent to the control device 21, and a control signal (a control signal for controlling the number of revolutions so as to keep the liquid level at a constant level). (Not shown) is sent to a VVVF inverter (not shown), which controls the power supply of a motor (not shown) that drives the solution pump 1, and the number of revolutions of the solution pump 1 is constant at the liquid level of the absorber A. (However, in the drawing, the control signal is simplified and shown to be sent from the liquid level sensor L1 to the solution pump 1).

A liquid level signal (not shown) representing the liquid level from the liquid level sensor L2 is sent to the control device 21, and the flow rate of the refrigerant liquid CL is controlled by the control device 21 so as to keep the liquid level at a constant level. A control signal (not shown) is sent to the refrigerant supply valve V3 to control the opening of the refrigerant supply valve V3 so that the liquid level of the evaporator E is constant (in the figure, the liquid level sensor L2 is simplified). From the refrigerant supply valve V3).

A liquid level signal (not shown) representing the liquid level from the liquid level sensor L3 is sent to the control device 21, and the flow rate of the makeup water W1 is controlled by the control device 21 so as to keep the liquid level at a constant level. A control signal (not shown) is sent to the feed water pump 12 (actually an inverter not shown) as described above, and the rotation speed of the feed water pump 12 is controlled so that the liquid level of the gas-liquid separator 11 becomes constant. (In the figure, it is simplified so that a signal is sent from the liquid level sensor L3 to the water supply pump 12).

  A pressure signal (a broken line in the figure) representing the pressure from the pressure sensor P is sent to the control device 21, and the supply amount of the steam S is adjusted from the control device 21 so that the pressure of the gas-liquid separator 11 becomes a predetermined value P1. A control signal to be controlled (broken line in the figure) is sent to the steam valve V1, and the opening of the steam valve V1 is controlled so that the pressure of the gas-liquid separator 11 becomes a predetermined value P1. In this case, the steam generation capacity of the absorption heat pump 101 is set by the control device 21 so as to generate, for example, steam S having a rated flow rate (for example, the operating point having the maximum efficiency). The predetermined value P1 may be set to 0.85 MPa, for example, when the steam header pressure (absolute pressure) is 0.8 MPa. In the above description, the hot water WH1, the hot water WH2, and the hot water WH3 have been described as being supplied in parallel. However, the hot water WH1, the hot water WH3, and the hot water WH3 may be supplied in series, or partially in parallel.

Next, the operation of the first embodiment will be described with reference to FIGS. FIG. 2 is a diagram showing states of the absorbing liquid and the refrigerant, in which the vertical axis represents pressure and the horizontal axis represents temperature.
Absorbing liquid ALi which is a dilute solution exiting the absorber A (state is the position of B2 in FIG. 2) is transferred by the absorbing liquid transfer pipe 3 and partly replenished by passing through the heat exchanger X2. It is cooled by the water W1 and the remaining part is branched from the absorbing liquid transfer pipe 3 and transferred by the absorbing liquid transfer pipe 52 and passes through the refrigerant heat exchanger X1, thereby passing through the absorbing liquid transfer pipe 2 and the regenerator. It is cooled by the absorbing liquid ALi which is a concentrated solution transferred from G to the absorber A. Since the branched absorption liquid transfer pipe 52 is joined again to the absorption liquid transfer pipe 3 on the downstream side of the heat exchanger X2, the absorption liquid ALi cooled by the heat exchanger X2 and the refrigerant heat exchanger X1 are cooled. Absorbing liquid ALi joins (
After the merge, the state of the absorption liquid ALi is transferred to the absorption liquid spray 25 of the regenerator G after the merge.

The absorbing liquid ALi is sprayed from the absorbing liquid spray 25 into the regenerator G (the state of the absorbing liquid ALi is a position B5 in FIG. 2), and the sprayed absorbing liquid ALi is supplied to the hot water WH2 through the heating pipe 26. The refrigerant that has been heated and absorbed in the absorption liquid ALi evaporates as refrigerant vapor CS, and the absorption liquid ALi, which is a regenerated concentrated solution, accumulates at the bottom of the regenerator G.

Absorbing liquid ALi that has become a concentrated solution (the state is the position B4 in FIG. 2) is transferred to the absorbing liquid spray 22 of the absorber A through the absorbing liquid transfer pipe 2. While passing through the absorption liquid transfer line 2, the pressure is increased by the solution pump 1, and then the refrigerant heat exchanger X 1 is heated to the absorption liquid ALi which is a dilute solution transferred from the absorber A to the regenerator G (absorption liquid transfer The state of the absorption liquid ALi passing through the pipe line 2 is shown in FIG.
Middle, position B7), and transferred to the absorbent liquid spray 22 of the absorber A.

In the absorber A, the absorption liquid ALi (the state of the absorption liquid ALi is the position B6 in FIG. 2) which is a concentrated solution sprayed into the absorber A from the absorption liquid spray 22 is the refrigerant evaporated in the evaporator E. The vapor CS is absorbed, the make-up water W1 passing through the heated pipe 23 is heated and accumulated at the bottom of the absorber A (absorbing liquid A
The state of Li is the position B2 in FIG.

  The rotation speed of the solution pump 1 is controlled by the control device 21 so as to transfer the absorption liquid ALi having a flow rate so that the liquid level of the absorption liquid ALi accumulated in the absorber A is constant from the regenerator G to the absorber A. The The reason why such control is performed is that the difference in refrigerant vapor pressure between the absorber A and the regenerator G is large, and mixing of the refrigerant vapor CS cannot be prevented by the liquid seal with the absorbing liquid ALi. Absorbing liquid ALi commensurate with the amount of absorbing liquid returning from absorber A to regenerator G is sent to maintain the liquid level of absorber A (the liquid level control of absorbing liquid ALi prevents the outflow of refrigerant vapor CS).

The refrigerant vapor CS evaporated in the regenerator G is sent to the condenser C, and the refrigerant vapor CS is cooled and condensed by the cooling water WC passing through the cooling pipe 30 in the condenser C to be condensed into the refrigerant liquid CL (the state is shown in FIG. D1 position). The refrigerant liquid CL of the condenser C passes through the refrigerant liquid transfer pipe 5 and is transferred from the evaporator E through the refrigerant liquid transfer pipe 51 upstream of the refrigerant pump 4 (in the refrigerant supply pipe 5A). After joining, the pressure is increased by the refrigerant pump 4, heated by the refrigerant liquid CL transferred from the evaporator E through the refrigerant liquid transfer pipe 51 by the refrigerant heat exchanger X11, and then flowed by the refrigerant supply valve V3. And is sent to the evaporator E. The refrigerant liquid CL is transferred from the evaporator E through the refrigerant liquid transfer line 51 to the refrigerant supply line 5A due to a pressure difference between the evaporator E and the refrigerant supply line 5A (condenser C).

  The refrigerant liquid CL sent to the evaporator E is sprayed from the refrigerant liquid spray 44 to the inside of the evaporator E, heated by the hot water WH1 through the heating pipe 28 and evaporated, and the excess refrigerant liquid CL that does not evaporate is placed in the lower part. Accumulate (the state of the refrigerant is the position D2 in FIG. 2). The evaporated refrigerant vapor CS is sent to the absorber A, and is absorbed by the absorber ALi in the absorber A.

  The refrigerant supply valve V3 is opened by the control device 21 so that an amount of the refrigerant liquid CL is transferred from the condenser C to the evaporator E so that the liquid level of the refrigerant liquid CL accumulated in the evaporator E is constant. The degree is controlled. Such control is performed in order to replenish the evaporated amount of the refrigerant liquid. The refrigerant vapor keeps the refrigerant liquid transfer line 51 filled with the refrigerant liquid CL, and the refrigerant pump 4 emits gas. This is to prevent the refrigerant vapor CS from flowing into the condenser C and preventing heat loss from occurring. Although the evaporator is different from that shown in the figure, an immersion type in which the heating tube is immersed in the refrigerant liquid may be used.

  The makeup water W <b> 1 supplied to the makeup water transfer pipe 7 is boosted by the feed water pump 12 and transferred to the gas-liquid separator 11 of the steam generator 14. The makeup water W1 exiting the feed water pump 12 is heated by the hot water WH3 in the heat exchanger X3, and further heated by the absorption liquid ALi transferred from the absorber A to the regenerator G in the heat exchanger X2, and the gas-liquid separator 11 is transferred.

  The flow rate of the makeup water W1 supplied to the steam generator 14 is controlled by the controller 21 so that the level of the makeup water W1 accumulated in the gas-liquid separator 11 is constant. It is adjusted by controlling. The reason why the liquid level of the makeup water W1 of the gas-liquid separator 11 is adjusted to be constant is to replenish the gas-liquid separator 11 with an amount corresponding to the lost makeup water W1 supplied as steam S.

  The make-up water W1 transferred to the gas-liquid separator 11 passes through the make-up water transfer pipe 6 and is boosted by the feed water pump 13 and sent to the heated pipe 23 of the absorber A. The absorber A absorbs the refrigerant vapor CS. Is heated by the absorption heat of the absorbing liquid ALi to generate steam S, returns to the gas-liquid separator 11 through the make-up water transfer pipe 10, and separates the steam and liquid. The generated steam S passes through the steam supply line 8, and the flow rate is adjusted by the steam valve V <b> 1 controlled by the control device 21 so that the pressure of the steam generating unit 14 becomes the first predetermined pressure P <b> 1. (Not shown).

  The steam generator 14 is controlled so that the pressure of the steam generator 14 becomes a predetermined pressure P1 because the pressure of the steam generator 14 is controlled to be higher than the pressure of the steam header (not shown). The pressure is always higher than the pressure of the steam header by a certain pressure so that the steam S generated by the absorption heat pump 101 is always supplied to the steam header so that the steam S is stably supplied to the load (not shown) side. It is to make it.

  The control device 21 performs the following control. That is, when the pressure of the steam generation unit 14 becomes lower than P1, the opening degree of the steam valve V1 is reduced, and the amount of the steam S supplied from the steam generation unit 14 to the steam header (not shown) is decreased, so that the steam generation unit 14 14 so that the pressure rises. On the other hand, when the pressure of the steam generation unit 14 becomes higher than P1, the opening of the steam valve V1 is increased to increase the amount of steam S supplied from the steam generation unit 14 to the steam header, so that the pressure of the steam generation unit 14 is increased. Try to descend.

  Since the absorption heat pump 101 of the present embodiment includes the refrigerant liquid transfer pipe 5 and the refrigerant pump 4, the refrigerant liquid CL of the condenser C can be supplied to the evaporator E through the refrigerant liquid transfer pipe 5. In addition, since the refrigerant liquid transfer pipe 51 that connects the evaporator E and the refrigerant supply pipe 5A (upstream of the refrigerant pump 4 in the refrigerant liquid transfer pipe 5) is provided, the refrigerant C is transferred from the condenser C to the evaporator E. The flow of the refrigerant liquid CL and the flow of the refrigerant liquid CL returned to the evaporator E after taking out the refrigerant liquid CL from the evaporator E can be merged. Therefore, the refrigerant liquid CL can be transferred from the condenser C to the evaporator E by the refrigerant pump 4, and at the same time, the refrigerant liquid CL can be taken out from the evaporator E and returned to the evaporator E to be circulated. It can also serve as a pump (circulation pump) for taking out CL and returning it to the evaporator E for circulation, eliminating the need to provide a circulation pump.

  The absorption heat pump 101 of the present embodiment can generate a flow for supplying the refrigerant liquid CL to the evaporator E by the refrigerant pump 4 and a flow for circulating between the evaporator E and the refrigerant supply pipe 5A. The flow rate of the refrigerant liquid CL supplied to the container E can be increased. Therefore, the heat transfer efficiency of the evaporator E can be raised, the evaporator E can be made compact, and the utilization efficiency of exhaust heat can be increased.

  The absorption heat pump 101 of the present embodiment is supplied with the refrigerant liquid CL transferred from the condenser C to the evaporator E through the refrigerant liquid transfer pipe 5 and the refrigerant supply from the evaporator E through the refrigerant liquid transfer pipe 51. Since heat exchange is performed with the refrigerant liquid CL transferred to the pipe line 5A, heat loss when returning the refrigerant liquid CL from the evaporator E to the condenser C can be reduced, and the heat is supplied to the absorption heat pump 101. Waste heat can be used more effectively.

  In the present absorption heat pump 101, excess refrigerant liquid CL that does not evaporate in the evaporator E is recovered by the refrigerant heat exchanger X11, and is supplied to the refrigerant supply line 5A on the upstream side of the refrigerant pump 4 in the refrigerant liquid transfer line 5. Since it returns, the refrigerant | coolant liquid CL is not cooled with the condenser C, and a heat energy is not wasted.

  In the above description, the refrigerant liquid transfer pipe 51 is connected to the refrigerant liquid supply pipe 5A on the upstream side of the refrigerant pump 4 of the refrigerant liquid transfer pipe 5, but the refrigerant liquid transfer pipe 51 is connected to the condenser C. The refrigerant liquid CL of the evaporator E may be returned to the condenser C by connection. Even in this case, since the retained heat of the excess refrigerant liquid CL that does not evaporate in the evaporator E is recovered by the refrigerant heat exchanger X11, heat loss can be prevented, and the exhaust heat supplied to the absorption heat pump 101 can be reduced. It can be used more effectively.

  FIG. 3 is a flow sheet showing the configuration of the absorption heat pump 102 of the second embodiment. Hereinafter, the difference in configuration from the absorption heat pump 101 (FIG. 1) will be described, and the description of the same configuration will be omitted except for what is confirmed. In the absorption heat pump 101 (FIG. 1), there is one absorber A (FIG. 1) and one evaporator E (FIG. 1), both under a single pressure. However, in the absorption heat pump 102, the absorber is not under a single pressure, but includes a high pressure absorber AH and a low pressure absorber AL that is under a lower pressure than the high pressure absorber AH. It is not under a single pressure, but includes a high-pressure evaporator EH as a high-pressure evaporator and a low-pressure evaporator EL as a low-pressure evaporator under a lower pressure than the high-pressure evaporator EH.

The high-pressure absorber AH is configured in the same manner as the absorber A (FIG. 1), and includes an absorbing liquid spray 22H, a heated pipe 23H, and a liquid level sensor L1H.
The low-pressure absorber AL is configured in the same manner as the absorber A, and includes an absorbing liquid spray 22L and a liquid level sensor L1L. The low-pressure absorber AL is provided with a heated pipe 23L. However, not the makeup water W1 but the refrigerant liquid CL is transferred from the gas-liquid separator 15 of the high-pressure evaporator EH described later to the heated pipe 23L, and the refrigerant liquid CL is heated by the absorption liquid ALi to generate the refrigerant vapor CS. . That is, the heated side of the heated tube 23L constitutes a part of the high-pressure evaporator EH.

The high-pressure evaporator EH includes the gas-liquid separator 15 and the heated side of the heated tube 23L as described above. The high-pressure evaporator EH has the same configuration as the evaporator E (FIG. 1) in that the gas-liquid separator 15 includes a liquid level sensor L2H, but the refrigerant liquid spray 44 (FIG. 1) and the heating pipe 28 (
1), the baffle plate 39H is provided inside the gas-liquid separator 15, and the refrigerant liquid CL extracted from the gas-liquid separator 15 of the high-pressure evaporator EH is installed in the low-pressure absorber AL. The refrigerant liquid CL transferred from the condenser C to the gas-liquid separator 15 passes through the inside of the heated pipe 23L and is circulated again, and the gas-liquid separator is transferred from below the baffle plate 39H. 15 is different from the configuration of the evaporator E in that it is supplied to 15.

  The refrigerant liquid CL is supplied from the gas-liquid separator 15 to the heated pipe 23L to generate the refrigerant vapor CS. In the present embodiment, in the low pressure evaporator EL, the refrigerant evaporates outside the heating pipe 28L described later, and the outer can body also serves as a gas-liquid separator, whereas in the high pressure evaporator EH, Since the refrigerant vapor CS is generated inside the heating pipe 23L and the internal volume of the heated pipe 23L is small, the gas-liquid separator 15 is configured as a separate container from the heated pipe 23L.

  The low pressure evaporator EL is configured in the same manner as the evaporator E, and includes a refrigerant liquid spray 44, a heating pipe 28L, and a liquid level sensor L2L.

  In the two-stage heat pump of the present embodiment, the steam S is generated from the high-pressure absorber AH having the highest temperature. In the case of a multistage heat pump, it is good to comprise so that a vapor | steam may be taken out from the absorber of the highest temperature among multistage absorbers.

The make-up water transfer line 6 and the make-up water transfer line 10 of the absorption heat pump 102 are connected to the heated pipe 23H of the high-pressure absorber AH. The absorption heat pump 102 (1) connects the regenerator G and the high pressure absorber AH, and transfers the absorption liquid ALi, which is a concentrated solution regenerated by the regenerator G, to the absorption liquid spray 22H of the high pressure absorber AH. The pipeline 2 and (2) the high pressure absorber AH and the low pressure absorber AL are connected, and the intermediate liquid ALi accumulated in the high pressure absorber AH is transferred to the absorption liquid spray 22L of the low pressure absorber AL. Absorbing liquid transfer line 3H, and (3) Absorbing liquid transfer line 3H (absorbing liquid transfer line 3H upstream of heat exchanger X5 described later) and absorbing liquid transfer line 3H (absorbing liquid transfer) Absorption liquid transfer line 53 returning to the downstream side of heat exchanger X5 of pipe line 3H, and (4) Absorption which is a dilute solution accumulated in low pressure absorber AL by connecting low pressure absorber AL and regenerator G. Absorption liquid transfer pipe for transferring liquid ALi to the absorption liquid spray 25 of the regenerator G (3) Absorbing liquid transfer pipe 3L (specifically, upstream of the heat exchanger X2 described later of the absorbing liquid transfer pipe 3L) and again absorbing liquid transfer pipe 3L (specifically, Is provided with an absorption liquid transfer line 52 that returns to the downstream side of the heat exchanger X2 of the absorption liquid transfer line 3L.

The absorption heat pump 102 further includes (6) a refrigerant liquid transfer line 5 that connects the condenser C and the gas-liquid separator 15 and transfers the refrigerant liquid CL condensed in the condenser C to the gas-liquid separator 15; 7) The low-pressure evaporator EL is connected to the refrigerant supply line 5A (upstream side of the refrigerant pump 4 to be described later of the refrigerant liquid transfer line 5), and the refrigerant liquid CL accumulated in the low-pressure evaporator EL is connected to the refrigerant supply line 5A. And (8) branched from the refrigerant liquid transfer pipe 5 (at a place after the refrigerant vapor CS is cooled by the condenser C as described later) and condensed by the condenser C. A refrigerant liquid transfer line 5L for transferring the refrigerant liquid CL to the low-pressure evaporator EL, (9) a gas-liquid separator 15, and a heated pipe 23L installed in the low-pressure absorber AL, on the heated side, the refrigerant liquid The refrigerant liquid accumulated in the gas-liquid separator 15 is connected to the heated pipe 23L that generates the refrigerant vapor CS by heating Refrigerant liquid transfer line 40 that transfers CL to the heated pipe 23L, and (10) the heated pipe 23L installed in the low-pressure absorber AL and the gas-liquid separator 15 are connected, and the refrigerant exits the heated pipe 23L. And a refrigerant liquid transfer pipe 41 for returning the refrigerant vapor CS containing the liquid CL to the gas-liquid separator 15. A throttle 61 is installed downstream of the low-temperature refrigerant heat exchanger X11 in the refrigerant liquid transfer pipe 51.

  The refrigerant liquid transfer line 5 is a refrigerant vapor CS in which the refrigerant liquid CL passing through the refrigerant liquid transfer line 5 is sent from the regenerator G to the condenser C on the upstream side of the branch point where the refrigerant liquid transfer line 5L branches. It is comprised so that it may be heated by. Although the refrigerant vapor CS having the same temperature as the absorption liquid ALi is generated from the absorption liquid ALi heated in the regenerator G, this temperature is higher than the temperature of the condenser C and close to the temperature of the heat source of the regenerator G. Since it is superheated steam, the refrigerant liquid CL that exits the condenser C can be heated. When the refrigerant vapor CS heading from the regenerator G to the condenser C is condensed by the refrigerant liquid CL passing through the refrigerant liquid transfer pipe 5, the refrigerant liquid CL generated by the condensation does not flow to the regenerator G by the baffle plate 43. Condenser C is configured to flow to vessel C.

The absorption heat pump 102 further includes (1) an absorption liquid ALi that is a concentrated solution transferred to the heated side through the absorption liquid transfer pipe 2 and an absorption liquid transfer pipe 52 that branches from the absorption liquid transfer pipe 3L. The refrigerant heat exchanger X1 that exchanges heat with the absorbing liquid ALi that is a dilute solution that is transferred to the heating side through (2) is transferred to the heated side through the makeup water transfer line 7 A heat exchanger X2 for exchanging heat between the replenishing water W1 and the absorbing liquid ALi which is a dilute solution transferred to the heating side through the absorbing liquid transfer pipe 3L; and (3) an absorbing liquid transfer pipe 3H. Between the absorption liquid ALi, which is an intermediate concentration solution transferred through the heating side through the heat exchanger X2, and the replenishing water W1 transferred to the heated side through the replenishing water transfer line 7 after leaving the heat exchanger X2. Heat exchanger X5 for heat exchange, and (4) after passing through the refrigerant heat exchanger X1 and passing through the absorption liquid transfer pipe 2 Between the absorption liquid ALi which is a concentrated solution transferred to the heating side and the absorption liquid ALi which is an intermediate concentration solution transferred to the heating side through the absorption liquid transfer pipe 53 branched from the absorption liquid transfer pipe 3H The refrigerant heat exchanger X4 for exchanging heat, (5) the refrigerant liquid CL transferred to the heated side through the refrigerant liquid transfer line 5, and transferred to the heating side through the refrigerant liquid transfer line 51. A low-temperature refrigerant heat exchanger X11 that exchanges heat with the refrigerant liquid CL.
The heat exchanger X2 and the refrigerant heat exchanger X1 are arranged in parallel, and the heat exchanger X5 and the refrigerant heat exchanger X4 are arranged in parallel.

  The absorption heat pump 102 further includes (6) a heat exchanger X3 in which warm water WH3 is transferred to the heating side, makeup water W1 is transferred to the heated side through the makeup water transfer pipe 7, and heat exchange is performed. 7) Heat exchange in which warm water WH4 having exhaust heat is transferred to the heating side, refrigerant liquid CL supplied to high-pressure evaporator EH through refrigerant liquid transfer pipe 5 is transferred to the heated side, and heat exchange is performed. And a device X6. The temperature of the hot water WH4 may be, for example, an inlet 90 ° C. and an outlet 85 ° C. The makeup water W1 may be heated by the refrigerant vapor CS of the condenser C or the like on the upstream side of the heat exchanger X3.

  The solution pump 1 installed in the absorbing liquid transfer pipe 2 transfers the absorbing liquid ALi regenerated by the regenerator G to the high pressure absorber AH. The refrigerant pump 4 installed in the refrigerant liquid transfer line 5 includes the refrigerant liquid CL condensed in the condenser C and the refrigerant liquid returned to the upstream side of the refrigerant pump 4 in the refrigerant liquid transfer line 5 from the low-pressure evaporator EL. CL is transferred to the high pressure evaporator EH and the low pressure evaporator EL. The feed water pump 13 installed in the make-up water transfer pipe 6 transfers make-up water W1 from the gas-liquid separator 11 to the heated pipe 23H of the high-pressure absorber AH, and generates steam S in the heated pipe 23H. It is transferred to the liquid separator 11 and the makeup water W1 is circulated.

  Downstream of the heat exchanger X5 on the absorbing liquid transfer pipe 3H and further downstream of the place where the absorbing liquid transfer pipe 53 where the refrigerant heat exchanger X4 is installed joins the absorbing liquid transfer pipe 3H. An absorption liquid supply valve V4 for adjusting the flow rate of the absorption liquid ALi transferred to the absorption liquid spray 22L is provided.

A liquid level signal (not shown) representing the liquid level from the liquid level sensor L1H is sent to the control device 21, and a control signal (a control signal for controlling the number of revolutions so as to keep the liquid level at a constant level). (Not shown) is sent to a VVVF inverter (not shown), which controls the power source of a motor (not shown) that drives the solution pump 1, and sets the rotational speed of the solution pump 1 to the liquid level of the high-pressure absorber AH. It is controlled so as to be constant (however, it is simplified in the drawing and described so that a control signal is sent from the liquid level sensor L1H to the solution pump 1).

A liquid level signal (not shown) representing the liquid level from the liquid level sensor L1L is sent to the control device 21, and the liquid level of the absorbing liquid ALi in the low pressure absorber AL is maintained at a constant level from the control device 21. A control signal (not shown) for controlling the flow rate of the absorption liquid ALi transferred from the high pressure absorber AH to the low pressure absorber AL is sent to the absorption liquid supply valve V4 (in the figure, the liquid level sensor L
1L is described so that a signal is sent to the absorption liquid supply valve V4).

A liquid level signal (not shown) representing the liquid level from the liquid level sensor L2H is sent to the control device 21, and the flow rate of the refrigerant liquid CL is controlled by the control device 21 so as to keep the liquid level at a constant level. A control signal (not shown) is sent to the refrigerant supply valve V3H, and the degree of opening of the refrigerant supply valve V3H is controlled so that the liquid level of the refrigerant liquid CL of the gas-liquid separator 15 is constant (in the figure, simplified). The signal is sent from the liquid level sensor L2H to the refrigerant supply valve V3H).

A liquid level signal (not shown) representing the liquid level from the liquid level sensor L2L is sent to the control device 21, and the flow rate of the refrigerant liquid CL is controlled by the control device 21 so as to keep the liquid level at a constant level. A control signal (not shown) is sent to the refrigerant supply valve V3L, and the opening of the refrigerant supply valve V3L is controlled so that the liquid level of the refrigerant liquid CL of the low-pressure evaporator EL is constant (in the figure, simplified, The description is such that a signal is sent from the liquid level sensor L2L to the refrigerant supply valve V3L).

Next, the operation of the second embodiment will be described with reference to FIGS. FIG. 4 is a diagram showing the states of the absorbing liquid and the refrigerant, in which the vertical axis represents pressure and the horizontal axis represents temperature.
Absorption liquid ALi (the state is the position of B2H in FIG. 4), which is an intermediate solution that has exited high-pressure absorber AH, is transferred by absorption liquid transfer line 3H, and partly passes through heat exchanger X5, Cooled by make-up water W1 in the exchanger X5, the remaining part is transferred by the absorbent liquid transfer pipe 53 branched from the absorbent liquid transfer pipe 3H, passes through the refrigerant heat exchanger X4, and in the refrigerant heat exchanger X4, The refrigerant heat exchanger X1 exits from the regenerator G and is cooled by the absorbing liquid ALi that is a concentrated solution transferred to the high-pressure absorber AH. Since the branched absorption liquid transfer pipe 53 joins the absorption liquid transfer pipe 3H again on the downstream side of the refrigerant heat exchanger X4, the absorption liquid ALi and the refrigerant heat exchanger X4 that have passed through the heat exchanger X5 have passed. The absorption liquid ALi merges again (the state after the absorption liquid ALi passing through the absorption liquid transfer line 3H is the position B11 in FIG. 4), the flow rate is controlled by the absorption liquid supply valve V4, and the pressure is further reduced. It is transferred to the absorbing liquid spray 22L of the absorber AL. The flow rate control by the absorption liquid supply valve V4 is performed such that a certain level of the absorption liquid ALi accumulates in the low pressure absorber AL.

The absorbing liquid ALi is sprayed from the absorbing liquid spray 22L into the low pressure absorber AL (absorbing liquid AL
The state of i is the position of B6L in FIG. 4), the sprayed absorption liquid ALi absorbs the refrigerant vapor CS evaporated in the low-pressure evaporator EL, and the heated pipe 23L (the heated side of the heated pipe 23L is at a high pressure). Evaporator E
The refrigerant liquid CL that leaves the gas-liquid separator 15 and returns to the gas-liquid separator 15 is heated via H) and is accumulated at the bottom of the low-pressure absorber AL.

Absorbing liquid ALi (state is the position of B2L in FIG. 4), which is a dilute solution that has exited low-pressure absorber AL, is transferred by absorbing liquid transfer pipe 3L, and partly passes through heat exchanger X2. It is cooled by the makeup water W1, and the remaining part is transferred by the absorption liquid transfer line 52 branched from the absorption liquid transfer line 3L, passes through the refrigerant heat exchanger X1, and transferred from the regenerator G to the high pressure absorber AH. It is cooled by the absorption liquid ALi which is a concentrated solution. Since the branched absorption liquid transfer pipe 52 joins the absorption liquid transfer pipe 3L again on the downstream side of the refrigerant heat exchanger X4, the absorption liquid ALi that has passed through the heat exchanger X2 and the refrigerant heat exchanger X1 have passed. Absorbing liquid ALi merges again (absorbing liquid transfer line 3
The state of the absorption liquid ALi passing through L is transferred to the absorption liquid spray 25 of the regenerator G, and the position of B13 in FIG.

The absorbing liquid ALi is sprayed into the regenerator G from the absorbing liquid spray 25 (the state of the absorbing liquid ALi is a position B5 in FIG. 4), and the sprayed absorbing liquid ALi is supplied to the hot water WH2 through the heating pipe 26. The refrigerant that has been heated and absorbed in the absorption liquid ALi evaporates as refrigerant vapor CS, and the absorption liquid ALi, which is a regenerated concentrated solution, accumulates at the bottom of the regenerator G.

The absorption liquid ALi that has become a concentrated solution (the state is the position B4 in FIG. 4) is transferred to the absorption liquid spray 22H of the high-pressure absorber AH through the absorption liquid transfer pipe 2. While passing through the absorption liquid transfer pipe 2, the pressure is increased by the solution pump 1, and then heated by the refrigerant heat exchanger X 1 to the absorption liquid ALi that is a dilute solution transferred from the low pressure absorber AL to the regenerator G (absorption liquid Absorbing liquid ALi passing through transfer line 2
4 is a position B7 in FIG. 4) and is further heated by the refrigerant ALi transferred from the high-pressure absorber AH to the low-pressure absorber AL in the refrigerant heat exchanger X4 (the absorption liquid passing through the absorption liquid transfer line 2). AL
The state i is transferred to the absorbing liquid spray 22H of the high-pressure absorber AH at the position B10 in FIG.

  In the high-pressure absorber AH, the absorption liquid ALi (the state of the absorption liquid ALi is the position of B6H in FIG. 4) which is a concentrated solution sprayed from the absorption liquid spray 22H into the high-pressure absorber AH is the gas-liquid separator 15 The refrigerant vapor CS separated in step 1 is absorbed, the makeup water W1 passing through the heated pipe 23H is heated, and is accumulated at the bottom of the high-pressure absorber AH (the state of the absorbing liquid ALi is the position B2H in FIG. 4).

  The rotation speed of the solution pump 1 is controlled by the controller 21 so as to transfer the absorption liquid ALi having a flow rate from the regenerator G to the high pressure absorber AH so that the liquid level of the absorption liquid ALi accumulated in the high pressure absorber AH is constant. Be controlled. Such control is performed from the high pressure absorber AH to the low pressure absorber AL, and from the regenerator G to the high pressure absorber, the amount of the absorption liquid ALi corresponding to the amount of the absorption liquid ALi decreased by the high pressure absorber AH. This is to transfer to AH.

  The refrigerant vapor CS evaporated in the regenerator G is sent to the condenser C, cooled to the refrigerant liquid CL passing through the refrigerant liquid transfer pipe 5, and further cooled and condensed by the cooling water WC passing through the cooling pipe 30 in the condenser C. The refrigerant liquid CL becomes (the state of the refrigerant liquid CL is a position D1 in FIG. 4). The refrigerant liquid CL of the condenser C passes through the refrigerant liquid transfer pipe 5 and is mixed with the refrigerant liquid CL sent from the low-pressure evaporator EL through the refrigerant liquid transfer pipe 51, and the pressure is increased by the refrigerant pump 4 to lower the temperature. It is heated by the refrigerant liquid CL that passes through the refrigerant heat exchanger X11 and is returned from the low-pressure evaporator EL to the upstream side of the refrigerant pump 4 in the refrigerant liquid transfer pipe 5, and is further introduced into the upper part of the condenser C. Heated by the refrigerant vapor CS sent to the condenser C. A part of the refrigerant liquid CL passing through the refrigerant liquid transfer pipe 5 is further controlled in flow rate by the refrigerant supply valve V3H, heated by the hot water WH4 through the heat exchanger X6, and then sent to the high-pressure evaporator EH, where it remains. Is branched from the refrigerant liquid transfer pipe 5, passes through the refrigerant liquid transfer pipe 5L, is controlled in flow rate by the refrigerant supply valve V3L, and is sent to the low-pressure evaporator EL. The refrigerant liquid CL is transferred from the low-pressure evaporator EL to the refrigerant supply pipe 5A through the refrigerant liquid transfer pipe 51 due to a pressure difference between the low-pressure evaporator EL and the refrigerant supply pipe 5A (condenser C).

  The flow rate of the refrigerant liquid CL sent to the high-pressure evaporator EH is controlled so that the liquid level of the excess refrigerant liquid CL accumulated at the bottom of the gas-liquid separator 15 is constant. The reason for this control is to transfer the refrigerant liquid CL corresponding to the amount of the refrigerant liquid CL evaporated by the high-pressure evaporator EH and sent to the high-pressure absorber AH to the gas-liquid separator 15.

  The flow rate of the refrigerant liquid CL sent to the low-pressure evaporator EL is controlled so that the liquid level of the excess refrigerant liquid CL accumulated at the bottom of the low-pressure evaporator EL is constant. This control is performed in order to transfer the refrigerant liquid CL corresponding to the amount of the refrigerant liquid CL evaporated in the low-pressure evaporator EL and sent to the low-pressure absorber AL to the low-pressure evaporator EL. This is to prevent the refrigerant vapor CS of the condenser EL from flowing out to the condenser C.

The refrigerant liquid CL transferred to the gas-liquid separator 15 enters below the baffle plate 39H of the gas-liquid separator 15 so as not to be accompanied by the refrigerant vapor CS, and accumulates at the bottom (the state of the refrigerant liquid CL is shown in FIG. 4, the position of D2H). The refrigerant liquid CL may be directly supplied into the refrigerant liquid that accumulates at the bottom. The evaporated refrigerant vapor CS is sent to the high-pressure absorber AH and is absorbed by the absorption liquid ALi in the high-pressure absorber AH. The refrigerant liquid CL supplied to the gas-liquid separator 15 is heated by the hot water WH4 in the heat exchanger X6, and is in a supercooled state when viewed from the refrigerant vapor CS. In order to prevent the supplied refrigerant liquid CL from being sent to the heated pipe 23L installed in the low-pressure absorber AL while being supercooled, the refrigerant vapor is expelled to the refrigerant vapor and saturated, and then sent to the heated pipe 23L. It is done.

The refrigerant liquid CL transferred to the low-pressure evaporator EL is heated by the hot water WH1 passing through the heating pipe 28L, and the surplus is accumulated at the bottom of the low-pressure evaporator EL (the state of the refrigerant liquid CL is D2L in FIG. 4). position). The heated refrigerant liquid CL evaporates, and the evaporated refrigerant vapor CS is sent to the low-pressure absorber AL and is absorbed by the absorption liquid ALi in the low-pressure absorber AL.

  The makeup water W <b> 1 supplied to the makeup water transfer pipe 7 is pressurized by the feed water pump 12 and transferred to the gas-liquid separator 11. The makeup water W1 exiting the feed water pump 12 is heated by the hot water WH3 in the heat exchanger X3, and further heated by a part of the absorption liquid ALi transferred from the low pressure absorber AL to the regenerator G in the heat exchanger X2. Furthermore, it is heated by a part of the absorption liquid ALi transferred from the high pressure absorber AH to the low pressure absorber AL in the heat exchanger X5 and transferred to the gas-liquid separator 11.

Since the absorption heat pump 102 of the present embodiment includes the refrigerant liquid transfer pipes 5 and 5L and the refrigerant pump 4, the refrigerant liquid CL of the condenser C passes through the refrigerant liquid transfer pipes 5 and 5L. Since it can be supplied to the low-pressure evaporator EL, and further includes a refrigerant liquid transfer line 51 that connects the low-pressure evaporator EL and the refrigerant supply line 5A (upstream of the refrigerant pump 4 of the refrigerant liquid transfer line 5), The flow of the refrigerant liquid CL transferred from the condenser C to the low-pressure evaporator EL and the flow of the refrigerant liquid CL returned to the low-pressure evaporator EL after taking out the refrigerant liquid CL from the low-pressure evaporator EL may be merged. it can. Therefore, the refrigerant liquid CL can be transferred from the condenser C to the low-pressure evaporator EL by the refrigerant pump 4, and at the same time, the refrigerant liquid CL can be taken out from the low-pressure evaporator EL and returned to the low-pressure evaporator EL for circulation. It can also serve as a pump (circulation pump) for taking out the refrigerant liquid CL from the EL and returning it to the low-pressure evaporator EL for circulation, eliminating the need for a circulation pump.

  The absorption heat pump 101 of the present embodiment can generate a flow for supplying the refrigerant liquid CL to the low-pressure evaporator EL by the refrigerant pump 4 and a flow for circulating between the low-pressure evaporator EL and the refrigerant supply line 5A. The flow rate of the refrigerant liquid CL supplied to the low-pressure evaporator EL can be increased. Therefore, the heat transfer efficiency of the low-pressure evaporator EL can be increased, the low-pressure evaporator EL can be made compact, and the exhaust heat utilization efficiency can be increased.

  In the absorption heat pump 102 of the present embodiment, in addition to the effects of the absorption heat pump 101 (FIG. 1), the absorber includes a high-pressure absorber AH and a low-pressure absorber AL, and the evaporator includes a high-pressure evaporator EH and a low-pressure absorber. Since it is configured to include the evaporator EL, it has an effect that the steam S having a higher temperature can be generated as compared with the absorption heat pump 101 (FIG. 1).

  The absorption heat pump 102 of the present embodiment includes a low-temperature refrigerant heat exchanger X11, and is a refrigerant liquid CL that has exited the condenser C, and is boosted by the refrigerant pump 4 and transferred to the high-pressure evaporator EH and the low-pressure evaporator EL. Since the heat exchange is performed between the refrigerant liquid CL and the refrigerant liquid CL returned to the upstream side of the refrigerant pump 4 from the low-pressure evaporator EL, the heat is sent from the condenser C to the high-pressure evaporator EH and the low-pressure evaporator EL. The temperature of the refrigerant liquid CL can be raised, and the exhaust heat supplied to the absorption heat pump 102 can be used more effectively.

  In the above description, the refrigerant liquid transfer line 51 is connected to the refrigerant supply line 5A. However, the refrigerant liquid transfer line 51 is connected to the condenser C, and the refrigerant liquid CL of the low-pressure evaporator EL is connected to the condenser C. You may make it return. Even in this case, similarly, the temperature of the refrigerant liquid CL sent from the condenser C to the high-pressure evaporator EH and the low-pressure evaporator EL can be raised, and the exhaust heat supplied to the absorption heat pump 102 can be used more effectively. can do.

FIG. 5 is a flow sheet showing the configuration of the absorption heat pump 103 of the third embodiment. Hereinafter, the difference in configuration from the absorption heat pump 102 (FIG. 3) will be described, and the description of the same configuration will be omitted except for what is confirmed.
The absorption heat pump 103 is different from the absorption heat pump 102 in that it additionally includes a high-temperature refrigerant heat exchanger X12, which will be described later, and in the configuration of the refrigerant liquid transfer conduit. This will be specifically described below.

  The absorption heat pump 103 does not transfer the refrigerant liquid CL accumulated in the lower part of the gas-liquid separator 15 of the high-pressure evaporator EH to the heated pipe 23L. Instead, the refrigerant liquid transfer pipe 5 has a different route from the refrigerant liquid transfer pipe 5 (FIG. 3) of the absorption heat pump 102 after the downstream side of the heat exchanger X6. That is, the refrigerant liquid transfer pipe 5 on the downstream side of the heat exchanger X6 is not directly connected to the gas-liquid separator 15, but is connected to the heated pipe 23L, and is connected to the low pressure absorber via the heated pipe 23L. The refrigerant liquid CL passing through the refrigerant liquid transfer pipe 5 is heated by the absorption heat at AL, and the refrigerant liquid transfer pipe 5 ahead is connected to the heated pipe 23L and the gas-liquid separator 15 and heated. The refrigerant liquid CL thus transferred is transferred to the gas-liquid separator 15.

  The absorption heat pump 103 connects the gas-liquid separator 15 and the downstream side of the refrigerant supply valve V3L of the refrigerant liquid transfer line 5L, and the excess refrigerant liquid CL accumulated in the gas-liquid separator 15 is supplied from the condenser C to the refrigerant liquid. A refrigerant liquid transfer line 45 is provided which is mixed with the refrigerant liquid CL transferred via the transfer line 5 and the refrigerant liquid transfer line 5L and transferred to the low-pressure evaporator EL after mixing.

  The absorption heat pump 103 includes a refrigerant liquid CL that is transferred to the heating side through the refrigerant liquid transfer pipe 45 and a refrigerant liquid CL that passes through the refrigerant liquid transfer pipe 5 and is heated after leaving the heat exchanger X6. A high-temperature refrigerant heat exchanger X12 that performs heat exchange with the refrigerant liquid CL that is transferred to the heated side toward the pipe 23L is further provided.

Next, the operation of the absorption heat pump 103 of the present embodiment will be described. Differences from the operation of the absorption heat pump 102 (FIG. 3) will be described, and the description of the same points will be omitted except for what is confirmed.
The refrigerant liquid CL that exits the condenser C and passes through the refrigerant liquid transfer line 5 exits the heat exchanger X6, then passes through the high-temperature refrigerant heat exchanger X12, and passes through the high-pressure evaporator EH in the high-temperature refrigerant heat exchanger X12. Heated by the refrigerant liquid CL transferred from the liquid separator 15 to the low-pressure evaporator EL, further passes through the heated pipe 23L, and the absorbing liquid ALi absorbs the refrigerant vapor CS in the low-pressure absorber EL via the heated pipe 23L. It is heated by the absorption heat and then transferred to the gas-liquid separator 15.

  Excess refrigerant liquid CL accumulated at the bottom of the gas-liquid separator 15 exits the gas-liquid separator 15, passes through the refrigerant liquid transfer line 45, is transferred to the high-temperature refrigerant heat exchanger X 12, and is then supplied to the high-temperature refrigerant heat exchanger X 12. Then, it is cooled to the refrigerant liquid CL transferred from the condenser C to the gas-liquid separator 15, transferred to the downstream side of the refrigerant supply valve V3L of the refrigerant liquid transfer line 5L, and transferred from the condenser C to the low-pressure evaporator EL. Is mixed with the refrigerant liquid CL and further transferred to the low-pressure evaporator EL. The refrigerant liquid CL passes from the gas-liquid separator 15 through the refrigerant liquid transfer line 45 due to the pressure difference between the gas-liquid separator 15 and the refrigerant liquid transfer line 5L (low pressure evaporator EL), and flows through the refrigerant liquid transfer line 5L. It is transferred to.

  In the low pressure absorber AL, the absorbing liquid ALi is sprayed from the absorbing liquid spray 22L into the low pressure absorber AL, and the sprayed absorbing liquid ALi absorbs the refrigerant vapor CS evaporated in the low pressure evaporator EL, and the heated pipe 23L The refrigerant liquid CL leaving the condenser C and transferred to the gas-liquid separator 15 is heated and accumulated at the bottom of the low-pressure absorber AL.

  The refrigerant liquid CL returned from the low-pressure evaporator EL to the upstream side of the refrigerant pump 4 is merged with the refrigerant liquid CL that has exited the condenser C. After the merge, the refrigerant liquid CL is pressurized to the refrigerant pump 4, and the low-temperature refrigerant heat exchanger X11, refrigerant After passing through the supply valve V3L, the refrigerant liquid CL that exits the gas-liquid separator 15 and passes through the high-temperature refrigerant heat exchanger X12 further joins and is transferred to the low-pressure evaporator EL.

Since the absorption heat pump 103 of the present embodiment includes the refrigerant liquid transfer pipes 5 and 5L and the refrigerant pump 4, the refrigerant liquid CL of the condenser C is passed through the refrigerant liquid transfer pipes 5 and 5L and the refrigerant liquid CL is supplied. Since it can be supplied to the low-pressure evaporator EL, and further includes a refrigerant liquid transfer line 51 that connects the low-pressure evaporator EL and the refrigerant supply line 5A (upstream of the refrigerant pump 4 of the refrigerant liquid transfer line 5), The flow of the refrigerant liquid CL transferred from the condenser C to the low-pressure evaporator EL and the flow of the refrigerant liquid CL returned to the low-pressure evaporator EL after taking out the refrigerant liquid CL from the low-pressure evaporator EL may be merged. it can. Therefore, the refrigerant liquid CL can be transferred from the condenser C to the low-pressure evaporator EL by the refrigerant pump 4, and at the same time, the refrigerant liquid CL can be taken out from the low-pressure evaporator EL and returned to the low-pressure evaporator EL for circulation. It can also serve as a pump (circulation pump) for taking out the refrigerant liquid CL from the EL and returning it to the low-pressure evaporator EL for circulation, eliminating the need for a circulation pump.

Since the absorption heat pump 103 of the present embodiment includes the refrigerant liquid transfer pipe 5 and the refrigerant pump 4, the refrigerant liquid CL of the condenser C passes through the refrigerant liquid transfer pipe 5 and passes through the high-pressure evaporator EH (gas-liquid separation). 15), and further includes a refrigerant liquid transfer line 45 that connects the high pressure evaporator EH and the refrigerant liquid transfer line 5L, so that the refrigerant liquid CL transferred from the condenser C to the high pressure evaporator EH is provided. And the flow of the refrigerant liquid CL taken out from the high-pressure evaporator EH and then transferred to the low-pressure evaporator EL and returned from the low-pressure evaporator EL to the high-pressure evaporator EH can be merged. Therefore, the refrigerant liquid CL is transferred from the condenser C to the high-pressure evaporator EH by the refrigerant pump 4, and at the same time, the refrigerant liquid CL is taken out from the high-pressure evaporator EL, transferred to the low-pressure evaporator EL, and taken out from the low-pressure evaporator EL again. The refrigerant liquid CL can be taken out from the high-pressure evaporator EH and returned to the high-pressure evaporator EH through the low-pressure evaporator EL and circulated back to the high-pressure evaporator EH (circulation pump). There is no need to provide a circulation pump.

  The absorption heat pump 103 of the present embodiment can generate a flow for supplying the refrigerant liquid CL to the low-pressure evaporator EL by the refrigerant pump 4 and a flow for circulating between the low-pressure evaporator EL and the refrigerant supply line 5A. Further, the refrigerant liquid CL is supplied to the high-pressure evaporator EH (gas-liquid separator 15), circulates between the refrigerant supply line 5A via the high-pressure evaporator EH (gas-liquid separator 15) and the low-pressure evaporator EL. Since the flow can be generated, the flow rate of the refrigerant liquid CL supplied to the low-pressure evaporator EL and the flow rate of the refrigerant liquid CL supplied to the high-pressure evaporator EH can be increased. Therefore, the heat transfer efficiency of the low pressure evaporator EL and the high pressure evaporator EH can be increased, the compactness of the low pressure evaporator EL and the high pressure evaporator EH can be achieved, and the utilization efficiency of exhaust heat can be increased. .

The absorption heat pump 103 of the present embodiment includes a high-temperature refrigerant heat exchanger X12, and is a refrigerant liquid CL that has exited the condenser C. After being pressurized by the refrigerant pump 4, the high-pressure evaporator EH (gas-liquid separator 15 ) And the refrigerant liquid CL transferred from the gas-liquid separator 15 back to the low-pressure evaporator EL, heat exchange is performed between the condenser C and the high-pressure evaporator EH (gas-liquid separator). The temperature of the refrigerant liquid CL sent only to 15) can be raised, and the exhaust heat supplied to the absorption heat pump 103 can be used more effectively.

  In addition, the absorption heat pump 103 of this Embodiment is equipped with the low-temperature refrigerant | coolant heat exchanger X11 similarly to the absorption heat pump 102 (FIG. 5), is the refrigerant | coolant liquid CL which went out of the condenser C, Comprising: Heat exchange between the refrigerant liquid CL transferred to the high-pressure evaporator EH (gas-liquid separator 15) and the low-pressure evaporator EL and the refrigerant liquid CL returned to the upstream side of the refrigerant pump 4 from the low-pressure evaporator EL. Therefore, the temperature of the refrigerant liquid CL sent from the condenser C to the high-pressure evaporator EH (gas-liquid separator 15) and the low-pressure evaporator EL can be raised, and the exhaust heat supplied to the absorption heat pump 103 is more effective. Can be used.

FIG. 6 is a flow sheet showing the configuration of the absorption heat pump 104 of the fourth embodiment. Hereinafter, the difference in configuration from the absorption heat pump 103 (FIG. 5) will be described, and the description of the same configuration will be omitted except for what is confirmed.
The absorption heat pump 104 does not include the refrigerant liquid transfer line 45 and the low-temperature refrigerant heat exchanger X11, but includes a refrigerant liquid transfer line 48 and a refrigerant heat exchanger X13 described later, the refrigerant liquid transfer line 5L, and the refrigerant liquid transfer. It differs from the absorption heat pump 103 in the configuration of the pipe 51 and the refrigerant liquid transfer pipe 5. This will be specifically described below.

  The refrigerant liquid transfer line 5 connects the condenser C and the gas-liquid separator 15 of the high-pressure evaporator EH, and transfers the refrigerant liquid CL condensed in the condenser C to the gas-liquid separator 15. Since the apparatus X11 does not exist, it is not connected to the low-temperature refrigerant heat exchanger X11. The refrigerant liquid transfer line 51 connects the low-pressure evaporator EL and the refrigerant supply line 5A (upstream side of the refrigerant pump 4 described later of the refrigerant liquid transfer line 5), and surplus refrigerant accumulated in the low-pressure evaporator EL. The liquid CL is transferred to the refrigerant liquid transfer pipe 5, but since the low-temperature refrigerant heat exchanger X11 does not exist, it is not connected to the low-temperature refrigerant heat exchanger X11.

  The absorption heat pump 104 includes a refrigerant liquid CL that is transferred to the heated side through the refrigerant liquid transfer pipe 5L branched from the refrigerant liquid transfer pipe 5, and a refrigerant that is transferred to the heating side through the refrigerant liquid transfer pipe 51. A refrigerant heat exchanger X13 that performs heat exchange with the liquid CL is provided. Therefore, the upstream side of the refrigerant supply valve V3L of the refrigerant liquid transfer pipe line 5L is connected to the heated side of the refrigerant heat exchanger X13, and the refrigerant liquid transfer pipe 51 is connected to the heating side of the refrigerant heat exchanger X13.

  Similarly to the absorption heat pump 103 (FIG. 5), the absorption heat pump 104 is a refrigerant liquid CL that is transferred to the heating side through the refrigerant liquid transfer pipe 48 and a refrigerant liquid CL that passes through the refrigerant liquid transfer pipe 5. And a high-temperature refrigerant heat exchanger X12 that performs heat exchange with the refrigerant liquid CL that is transferred to the heated side toward the heated pipe 23L after leaving the heat exchanger X6.

  The absorption heat pump 104 connects the gas-liquid separator 15 of the high-pressure evaporator EH and the refrigerant supply pipe 5A, and transfers the excess refrigerant liquid CL accumulated in the gas-liquid separator 15 to the refrigerant supply pipe 5A. A transfer pipe 48 is provided, and a throttle 62 is installed on the refrigerant liquid transfer pipe 48 downstream of the high-temperature refrigerant heat exchanger X12.

Next, the operation of the absorption heat pump 104 of the present embodiment will be described. Differences from the operation of the absorption heat pump 103 (FIG. 5) will be described, and the description of the same points will be omitted except for what is confirmed.
The refrigerant liquid CL of the condenser C is mixed with the refrigerant liquid CL sent from the low-pressure evaporator EL through the refrigerant liquid transfer pipe 51 through the refrigerant liquid transfer pipe 5, and is pressurized by the refrigerant pump 4. It is introduced into the upper part of the condenser C and heated by the refrigerant vapor CS sent from the regenerator G to the condenser C.

A part of the refrigerant liquid CL passing through the refrigerant liquid transfer pipe 5 is further controlled in flow rate by the refrigerant supply valve V3H, passes through the heat exchanger X6, is heated by the hot water WH4 in the heat exchanger X6, and then is heated. The liquid ALi is heated by the absorption heat absorbing the refrigerant vapor CS in the low-pressure absorber AL through the heated pipe 23L, and then transferred to the gas-liquid separator 15 of the high-pressure evaporator EH.
The remaining part of the refrigerant liquid CL passing through the refrigerant liquid transfer pipe 5 branches from the refrigerant liquid transfer pipe 5 and passes through the refrigerant liquid transfer pipe 5L, and passes through the refrigerant heat exchanger X13 upstream of the refrigerant supply valve V3L. As described above, the refrigerant heat exchanger X13 is heated by the refrigerant liquid CL returned from the low pressure evaporator EL to the refrigerant supply pipe 5A, and then the flow rate is controlled by the refrigerant supply valve V3L to be sent to the low pressure evaporator EL.

  The refrigerant liquid CL accumulated in the lower part of the high-pressure evaporator EH passes through the refrigerant liquid transfer line 48 and passes through the high-temperature refrigerant heat exchanger X12, and then passes through the high-temperature refrigerant heat exchanger X12 and then from the condenser C. The refrigerant liquid CL sent to the gas-liquid separator 15 of the evaporator EL, which has been heated by the refrigerant vapor CS sent from the regenerator G to the condenser C in the condenser C, is then heated. The refrigerant is returned to the refrigerant supply line 5A. The refrigerant liquid CL is supplied from the gas-liquid separator 15 through the refrigerant liquid transfer line 48 due to the pressure difference between the gas-liquid separator 15 (high pressure evaporator EH) and the refrigerant supply line 5A (condenser C). It is transferred to the pipeline 5A.

  The refrigerant liquid CL accumulated in the lower portion of the low-pressure evaporator EL passes from the condenser C to the low-pressure evaporator via the refrigerant heat exchanger X13 when passing through the refrigerant liquid transfer pipe 51 and passing through the refrigerant heat exchanger X13. The refrigerant liquid CL sent to the EL is heated in the condenser C by the refrigerant vapor CS sent from the regenerator G to the condenser C, and then returned to the refrigerant supply line 5A. . The refrigerant liquid CL is transferred from the low-pressure evaporator EL to the refrigerant supply pipe 5A through the refrigerant liquid transfer pipe 51 due to a pressure difference between the low-pressure evaporator EL and the refrigerant supply pipe 5A (condenser C).

Since the absorption heat pump 104 of the present embodiment includes the refrigerant liquid transfer lines 5 and 5L and the refrigerant pump 4, the low-pressure evaporator EL passes the refrigerant liquid CL of the condenser C through the refrigerant liquid transfer lines 5 and 5L. And further includes a refrigerant liquid transfer pipe 51 that connects the low pressure evaporator EL and the refrigerant supply pipe 5A, so that the refrigerant liquid CL is transferred from the condenser C to the low pressure evaporator EL. And the flow of the refrigerant liquid CL returned to the low-pressure evaporator EL after the refrigerant liquid CL is taken out from the low-pressure evaporator EL can be merged. Therefore, the refrigerant liquid CL can be transferred from the condenser C to the low-pressure evaporator EL by the refrigerant pump 4, and at the same time, the refrigerant liquid CL can be taken out from the low-pressure evaporator EL and returned to the low-pressure evaporator EL for circulation. It can also serve as a pump (circulation pump) for taking out the refrigerant liquid CL from the EL and returning it to the low-pressure evaporator EL for circulation, eliminating the need for a circulation pump.

  Since the absorption heat pump 104 of the present embodiment includes the refrigerant liquid transfer pipe 5 and the refrigerant pump 4, the refrigerant liquid CL of the condenser C is supplied to the high-pressure evaporator EH through the refrigerant liquid transfer pipe 5. Furthermore, since the refrigerant liquid transfer pipe 48 connecting the high pressure evaporator EH and the refrigerant supply pipe 5A is provided, the flow of the refrigerant liquid CL transferred from the condenser C to the high pressure evaporator EH, and the high pressure evaporator EH After the refrigerant liquid CL is taken out of the refrigerant liquid CL, the refrigerant liquid CL returned to the high-pressure evaporator EH can be joined again. Therefore, the refrigerant liquid CL can be transferred from the condenser C to the high-pressure evaporator EH by the refrigerant pump 4, and at the same time, the refrigerant liquid CL can be taken out from the high-pressure evaporator EH and returned to the high-pressure evaporator EH for circulation. It can also serve as a pump (circulation pump) for taking out the refrigerant liquid CL from the EH and returning it to the high-pressure evaporator EH for circulation, eliminating the need to provide a circulation pump.

  The absorption heat pump 104 of the present embodiment can generate a flow for supplying the refrigerant liquid CL to the low-pressure evaporator EL by the refrigerant pump 4 and a flow for circulating between the low-pressure evaporator EL and the refrigerant supply line 5A. The flow rate of the refrigerant liquid CL supplied to the low-pressure evaporator EL can be increased. Therefore, the heat transfer efficiency of the low-pressure evaporator EL can be increased, the low-pressure evaporator EL can be made compact, and the exhaust heat utilization efficiency can be increased. Further, the absorption heat pump 104 can generate a flow for supplying the refrigerant liquid CL to the high-pressure evaporator EH by the refrigerant pump 4 and a flow for circulating between the high-pressure evaporator EH and the refrigerant supply line 5A. The flow rate of the refrigerant liquid CL supplied to the container EH can be increased. Therefore, the heat transfer efficiency of the high-pressure evaporator EH can be increased, the high-pressure evaporator EH can be made compact, and the exhaust heat utilization efficiency can be increased.

  The absorption heat pump 104 of the present embodiment includes a refrigerant heat exchanger X13, and is a refrigerant liquid CL that has exited the condenser C and is transferred only to the low-pressure evaporator EL after being pressurized by the refrigerant pump 4. Since heat exchange is performed between CL and the refrigerant liquid CL returned to the condenser C from the low-pressure evaporator EL, the temperature of the refrigerant liquid CL sent only from the condenser C to the low-pressure evaporator EL can be increased, The exhaust heat supplied to the absorption heat pump 104 can be used more effectively.

  Similarly to the absorption heat pump 103 (FIG. 5), the absorption heat pump 104 of the present embodiment includes a high-temperature refrigerant heat exchanger X12 and is a refrigerant liquid CL that has exited the condenser C and has been boosted by the refrigerant pump 4. Heat exchange between the refrigerant liquid CL which is later transferred only to the high-pressure evaporator EH (gas-liquid separator 15) and the refrigerant liquid CL returned from the high-pressure evaporator EH (gas-liquid separator 15) to the low-pressure evaporator EL. Therefore, the temperature of the refrigerant liquid CL sent only from the condenser C to the high-pressure evaporator EH (gas-liquid separator 15) can be raised, and the exhaust heat supplied to the absorption heat pump 104 can be used more effectively. Can do.

FIG. 7 is a flow sheet showing the configuration of the absorption heat pump 105 of the fifth embodiment. Hereinafter, the difference in configuration from the absorption heat pump 104 (FIG. 6) will be described, and the description of the same configuration will be omitted except for what is confirmed.
The absorption heat pump 105 includes a refrigerant liquid transfer line 54, a refrigerant liquid transfer line 55, a refrigerant liquid transfer line 56, a refrigerant heat exchanger X14, and a high temperature refrigerant heat exchanger X15, a high temperature refrigerant heat exchanger X12 (FIG. 6) The refrigerant heat exchanger X13 (FIG. 6), the refrigerant liquid transfer pipe 5 (FIG. 6), the refrigerant liquid transfer pipe 5L (FIG. 6), and the refrigerant liquid transfer pipe 51 (FIG. 6) are not provided. This is different from the absorption heat pump 104. This will be specifically described below.

  The absorption heat pump 105 (1) connects the condenser C and the low-pressure evaporator EL, transfers the refrigerant liquid CL condensed in the condenser C to the low-pressure evaporator EL, and (2) low-pressure evaporation. A refrigerant liquid transfer line 55 that connects the evaporator EL and the gas-liquid separator 15 of the high-pressure evaporator EH and transfers the excess refrigerant liquid CL accumulated at the bottom of the low-pressure evaporator EL to the gas-liquid separator 15; ) A refrigerant liquid transfer line 56 that is separated from the refrigerant liquid transfer line 55 and circulates the refrigerant liquid CL of the low pressure evaporator EL back to the low pressure evaporator EL.

  The refrigerant liquid transfer line 45 is configured to return the refrigerant liquid CL accumulated at the bottom of the gas-liquid separator 15 to the refrigerant liquid transfer line 56 via a high-temperature refrigerant heat exchanger X15 described later. The refrigerant liquid transfer pipe 54 is further configured such that the refrigerant liquid CL passing through the refrigerant liquid transfer pipe 54 is heated by the refrigerant vapor CS sent from the regenerator G to the condenser C. The refrigerant liquid transfer conduit 54 is configured to supply the refrigerant liquid CL to the low-pressure evaporator EL from above the refrigerant liquid CL accumulated at the bottom.

  In the absorption heat pump 105, (1) hot water WH5 having exhaust heat is transferred to the heating side, and the refrigerant liquid CL transferred from the low-pressure evaporator EL to the gas-liquid separator 15 through the refrigerant liquid transfer line 55 is heated. The refrigerant heat exchanger X14 that is transferred to the side and performs heat exchange, and (2) the refrigerant liquid CL that is transferred from the gas-liquid separator 15 through the refrigerant liquid transfer pipe 45 is transferred to the heating side, and the refrigerant liquid The refrigerant liquid CL passing through the transfer line 55, which is transferred to the heated pipe 23L after leaving the refrigerant heat exchanger X14, is transferred to the heated side, and heat exchange is performed. And an exchanger X15. The temperature of the hot water WH5 may be, for example, an inlet 90 ° C and an outlet 85 ° C.

  A refrigerant pump 46 is installed in the refrigerant liquid transfer line 54, and the refrigerant pump 46 transfers the refrigerant liquid CL condensed by the condenser C to the low-pressure evaporator EL through a refrigerant supply valve V3L described later. A refrigerant pump 47 is installed in the refrigerant liquid transfer pipe 55, and the refrigerant pump 47 partially circulates the refrigerant liquid CL accumulated at the bottom of the low-pressure evaporator EL back to the low-pressure evaporator EL, and the remaining refrigerant liquid. CL is transferred to the gas-liquid separator 15 via a refrigerant supply valve V3H, a refrigerant heat exchanger X14, a high-temperature refrigerant heat exchanger X15, and a heated pipe 23L which will be described later.

  The refrigerant liquid transfer pipe 55 includes a refrigerant supply pipe 55 </ b> A on the upstream side of the refrigerant pump 46 and a refrigerant liquid transfer pipe 55 </ b> B on the downstream side of the refrigerant pump 4. The low pressure evaporator according to the present invention is configured including the low pressure evaporator EL and the refrigerant supply line 55A.

  The refrigerant liquid transfer line 54 is transferred from the condenser C to the low-pressure evaporator EL downstream of the portion where the refrigerant liquid CL is heated by the refrigerant vapor CS from the regenerator G to the condenser C in the condenser C. A refrigerant supply valve V3L for adjusting the flow rate of the refrigerant liquid CL is installed. Refrigerant transferred from the low pressure evaporator EL to the gas-liquid separator 15 downstream of the branch point where the refrigerant transfer line 56 of the refrigerant liquid transfer line 55 branches and upstream of the refrigerant heat exchanger X14. A refrigerant supply valve V3H for adjusting the flow rate of the liquid CL is provided. A throttle 63 is installed on the upstream side of the refrigerant liquid transfer pipe 56 where the refrigerant liquid transfer pipe 45 is connected.

A liquid level signal (not shown) indicating the liquid level of the refrigerant liquid CL from the liquid level sensor L2H of the gas-liquid separator 15 is sent to the control device 21, and the liquid level is set to a constant level from the control device 21. A control signal (not shown) for controlling the flow rate of the refrigerant liquid CL is sent to the refrigerant supply valve V3H so as to maintain the opening of the refrigerant supply valve V3H, and the liquid level of the refrigerant liquid CL of the gas-liquid separator 15 becomes constant. (In the figure, it is simplified and described so that a signal is sent from the liquid level sensor L2H to the refrigerant supply valve V3H).

A liquid level signal (not shown) indicating the liquid level of the refrigerant liquid CL from the liquid level sensor L2L of the low-pressure evaporator EL is sent to the control device 21, and the liquid level is maintained at a constant level from the control device 21. A control signal (not shown) for controlling the flow rate of the refrigerant liquid CL is sent to the refrigerant supply valve V3L, and the opening of the refrigerant supply valve V3L is controlled so that the liquid level of the refrigerant liquid CL in the low-pressure evaporator EL becomes constant. (In the figure, it is simplified so that a signal is sent from the liquid level sensor L2L to the refrigerant supply valve V3L).

  The refrigerant liquid transfer line 45 may return the refrigerant liquid CL accumulated at the bottom of the gas-liquid separator 15 to the refrigerant supply line 55A.

Next, the operation of the absorption heat pump 105 of the present embodiment will be described. Differences from the operation of the absorption heat pump 104 (FIG. 6) will be described, and the description of the same points will be omitted except for what is confirmed.
The refrigerant liquid CL that exits the condenser C and passes through the refrigerant liquid transfer pipe 54 is boosted by the refrigerant pump 46, heated in the condenser C by the refrigerant vapor CS from the regenerator G to the condenser C, and is supplied to the refrigerant supply valve V3L. The flow rate is adjusted so that the refrigerant liquid level of the low-pressure evaporator EL becomes constant, and the low-pressure evaporator EL is transferred to the low-pressure evaporator EL.

  The surplus refrigerant liquid CL accumulated at the bottom of the low-pressure evaporator EL exits the low-pressure evaporator EL, passes through the refrigerant liquid transfer line 54, and is boosted by a refrigerant pump 47 as a refrigerant boosting means. The flow rate is adjusted so that the refrigerant liquid level of the gas-liquid separator 15 becomes constant by the refrigerant supply valve V3H, and the remainder is heated by the hot water WH5 via the refrigerant heat exchanger X14. Further, the refrigerant is heated by the refrigerant liquid CL returned to the low-pressure evaporator EL from the gas-liquid separator 15 via the high-temperature refrigerant heat exchanger X15, and further, by the absorbed heat generated in the low-pressure absorber AL via the heated pipe 23L. Heated and supplied to the gas-liquid separator 15.

  Excess refrigerant liquid CL accumulated at the bottom of the gas-liquid separator 15 exits the gas-liquid separator 15 and passes through the refrigerant liquid transfer line 45, and is then discharged from the low-pressure evaporator EL to the high-temperature refrigerant heat exchanger X15. The refrigerant liquid CL transferred to 15 is heated, reaches the refrigerant liquid transfer line 56, joins with the refrigerant liquid CL circulated from the bottom of the low pressure evaporator EL through the refrigerant liquid transfer line 56, and the low pressure evaporator EL It is transferred to. The refrigerant liquid CL passes from the high-pressure evaporator EH through the refrigerant liquid transfer line 45 due to the pressure difference between the high-pressure evaporator EH and the refrigerant liquid transfer line 5L (low-pressure evaporator EL). 63 downstream).

  The absorption heat pump 105 of this embodiment is configured so that the refrigerant pump 47 supplies the refrigerant liquid CL to the low-pressure evaporator EL, the refrigerant supply line through the high-pressure evaporator EH (gas-liquid separator 15) and the low-pressure evaporator EL. Since a flow circulating between 55A can be generated, the flow rate of the refrigerant liquid CL supplied to the high-pressure evaporator EH and the low-pressure evaporator EL can be increased. Therefore, the heat transfer efficiency of the high-pressure evaporator EH and the low-pressure evaporator EL can be increased, the high-pressure evaporator EH and the low-pressure evaporator EL can be made compact, and the utilization efficiency of exhaust heat can be increased. .

The absorption heat pump 105 of the present embodiment includes a high-temperature refrigerant heat exchanger X15, and is a refrigerant liquid CL that has exited the low-pressure evaporator EL. After being pressurized by the refrigerant pump 47, the high-pressure evaporator EH (gas-liquid separator) 15) and the refrigerant liquid CL transferred only to the high-pressure evaporator EH (gas-liquid separator 15) and the refrigerant liquid CL returned to the low-pressure evaporator EL, heat exchange is performed between the low-pressure evaporator EL and the high-pressure evaporator EL. The temperature of the refrigerant liquid CL sent to the evaporator EL (gas-liquid separator 15) can be raised, and the exhaust heat supplied to the absorption heat pump 105 can be used more effectively.

The absorption heat pump according to the second to fifth embodiments described above has a two-stage temperature rise, and the evaporator is assumed to be composed of a high-pressure evaporator (second stage) and a low-pressure evaporator (first stage). However, if the temperature rises to 3 or more stages and N (natural number) stages, the N-stage evaporator (1 stage, 2 stages,
May be configured. In this case, for example, the evaporators in the third and higher stages are respectively supplied from the condenser or the lower stage evaporator (in the case of the N stage, the N-1 stage, the N-2 stage,...) Respectively. The excess refrigerant liquid that has not been evaporated from the third and higher stages of evaporators is supplied to the lower stage (typically, the last lower stage may be used), and / or the condenser. The heat exchange may be performed between the supplied refrigerant liquid and the returned refrigerant liquid. If it does in this way, the temperature of the refrigerant | coolant liquid supplied to the 3rd or more stage | paragraph evaporator can be raised, and the waste heat supplied to the absorption heat pump 105 can be utilized more effectively.

1, 46, 47 Solution pump 2, 3 Absorbing liquid transfer line 4 Refrigerant pump (refrigerant boosting means)
5, 5B, 5L, 40, 41, 45, 51, 54, 55, 56 Refrigerant liquid transfer line 5A Refrigerant supply line 7 Makeup water transfer line 8 Steam supply line 11 Gas-liquid separator 12, 13 Water supply pump 15 Gas-liquid separator 21 Control device 101,102,103,104,105 Absorption heat pump A Absorber (absorption part)
AH high pressure absorber (absorption part)
AL Low pressure absorber (absorption part)
ALi Absorbent C Condenser (Condenser)
CS Refrigerant vapor CL Refrigerant liquid E Evaporator (evaporator)
EH high pressure evaporator (evaporation part)
EL Low pressure evaporator (evaporation part)
G regenerator (reproduction unit)
L1, L2, L3, L1H, L1L, L2H, L2L Liquid level sensor P Pressure sensor S Steam V1 Steam valve V2, V3, V3H, V3L Refrigerant supply valve V4 Absorbing liquid supply valve W1 Supply water WC Cooling water WH1, WH2, WH3, WH4, WH5 Hot water X1, X4, X13, X14 Refrigerant heat exchanger X11 Refrigerant heat exchanger, low temperature refrigerant heat exchanger X12, X15 High temperature refrigerant heat exchanger X2, X3, X5, X6 Heat exchanger

Claims (4)

A condensing part that condenses the refrigerant vapor into a refrigerant liquid;
An evaporation section having a heating pipe for evaporating the refrigerant liquid supplied from the condensing section and a refrigerant liquid spray for spraying the supplied refrigerant liquid on the heating pipe, evaporating the supplied refrigerant liquid. An evaporating section that generates refrigerant vapor and returns the excess refrigerant liquid that does not evaporate to the condensing section;
A single refrigerant pump that pressurizes the refrigerant liquid condensed in the condensing unit and supplies the refrigerant liquid to the refrigerant liquid spray of the evaporation unit from the condensing unit;
The condensing unit has a refrigerant supply line that supplies the refrigerant liquid condensed by the condensing unit to the single refrigerant pump;
A first refrigerant liquid transfer line connecting the single refrigerant pump and the refrigerant liquid spray;
A second refrigerant liquid transfer line for returning the excess refrigerant liquid that does not evaporate to the condensing part, connecting the evaporation part and the refrigerant supply line, and removing the excess refrigerant liquid that does not evaporate to the refrigerant A second refrigerant liquid transfer line returning to the supply line;
A surplus refrigerant liquid that is not evaporated and returned to the refrigerant supply pipe from the evaporation section and is transferred through the second refrigerant liquid transfer pipe; and a refrigerant liquid that is supplied from the condensation section to the refrigerant liquid spray. A heat exchanger for exchanging heat with the refrigerant liquid transferred through the first refrigerant transfer line ;
The single refrigerant pump supplies the condensed refrigerant liquid to the refrigerant liquid spray via the refrigerant supply line and the first refrigerant liquid transfer line;
Absorption heat pump. The evaporating unit has a liquid level sensor that detects a level of refrigerant liquid accumulated in the evaporating unit;
A refrigerant supply valve for adjusting a flow rate of the refrigerant liquid supplied to the refrigerant liquid spray is installed in the first refrigerant liquid transfer pipe;
And a control device that receives the signal of the detected liquid level from the liquid level sensor and controls the opening of the refrigerant supply valve so as to keep the liquid level of the evaporation unit constant;
The absorption heat pump according to claim 1. The evaporator is a low pressure evaporator;
A high-pressure evaporation unit that generates refrigerant vapor by evaporating the refrigerant liquid supplied from the condensing unit at a higher pressure than the low-pressure evaporation unit;
The heating pipe of the low-pressure evaporation section evaporates the refrigerant liquid that is an excess refrigerant liquid that does not evaporate in the high-pressure evaporation section and is returned from the high-pressure evaporation section;
The refrigerant liquid spray of the low-pressure evaporation unit is configured to spray the refrigerant liquid returned from the high-pressure evaporation unit to the heating pipe;
The low-pressure evaporation section evaporates the refrigerant liquid returned from the high-pressure evaporation section, generates refrigerant vapor, and returns excess refrigerant liquid that does not evaporate in the low-pressure evaporation section to the condensing section;
The single refrigerant pump pressurizes the refrigerant liquid condensed in the condensing unit and supplies the refrigerant liquid from the condensing unit to the high-pressure evaporation unit;
The absorption heat pump according to claim 1 or 2. The evaporator is a low pressure evaporator;
A high-pressure evaporation unit that generates refrigerant vapor by evaporating the refrigerant liquid supplied from the condensing unit at a higher pressure than the low-pressure evaporation unit;
The high-pressure evaporating unit returns excess refrigerant liquid that does not evaporate in the high-pressure evaporating unit to the condensing unit;
The low-pressure evaporation unit evaporates the refrigerant liquid supplied from the condensing unit, generates refrigerant vapor, and returns excess refrigerant liquid that does not evaporate in the low-pressure evaporation unit to the condensing unit;
The single refrigerant pump pressurizes the refrigerant liquid condensed in the condensing unit and supplies the refrigerant liquid from the condensing unit to the high-pressure evaporation unit;
The absorption heat pump according to claim 1 or 2.

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