JP6015123B2 - Combined cold heat generator - Google Patents

Description

  The present invention combines various devices (for example, a fuel cell system, an engine-driven power generation system, an engine-driven heat pump system, etc.) that generate electrical energy and / or air conditioning energy and exhaust heat, and an adsorption heat pump. The present invention relates to a composite cold heat generator.

  The adsorption heat pump includes an adsorption unit that contains an adsorbent (for example, silica gel) from which a working medium (for example, water) can be desorbed, an adsorption condenser that condenses and liquefies the gaseous working medium desorbed from the adsorption unit, And a cooling unit for vaporizing the working medium liquefied by the adsorption condenser. The adsorption heat pump is generally used in combination with a cooling device such as an air conditioner or a refrigerator. In the adsorption condenser of the adsorption heat pump, latent heat of vaporization is generated when the working medium is vaporized. With this latent heat of vaporization, for example, the heat exchange medium of the cooling device can be cooled directly or indirectly. This can improve the cooling efficiency of the air conditioner during the cooling operation or the refrigerator. More specifically, for example, when the cooling device is an air conditioner, the heat exchange medium (refrigerant) discharged from the indoor unit and compressed by the compressor during the cooling operation of the indoor unit is preliminarily stored by the latent heat of vaporization described above. Can be cooled to. The amount of cooling here improves the COP (Coefficient of Performance, coefficient of performance; cooling / heating efficiency per 1 kW of power consumption) of the air conditioner during the cooling operation.

  By the way, in the adsorption heat pump, when the working medium adsorbed by the adsorbent is vaporized and when the working medium condensed by the adsorption condenser and vaporized is vaporized in the cooling unit, thermal energy is required. . Here, various heat exhaust methods have been proposed as necessary heat energy. For example, by combining a cogeneration system having a generator (drive source) and an adsorption heat pump, exhaust heat generated by the generator can be used in the adsorption heat pump. Moreover, the cooling efficiency of the cooler included in the cogeneration system can be improved by the latent heat of vaporization of the adsorption heat pump. For example, in the technique introduced in Patent Document 1, latent heat of vaporization of the adsorption heat pump described above is used as a supercooling source of an engine-driven heat pump system. Then, exhaust heat of the engine (more specifically, heat of engine cooling water) included in the engine-driven heat pump system is used as the above-described heat energy.

  However, an apparatus having a drive source such as a cogeneration system generally includes elements that require exhaust heat in addition to the adsorption heat pump. For example, a water heater. A time zone in which exhaust heat is required in such an element (referred to as an exhaust heat utilization element) may overlap with a time zone in which exhaust heat is required in the adsorption heat pump. For example, in a general household, during the daytime, the driving source is driven for cooling and hot water is supplied by exhaust heat generated by the driving source, while the use of hot water is few. On the other hand, while the demand for cooling is reduced at night, it becomes difficult to stably supply hot water due to exhaust heat, while the demand for hot water for bathing and cooking increases. For this reason, it may be difficult to supply a sufficient amount of exhaust heat to the adsorption heat pump. Alternatively, by supplying a sufficient amount of exhaust heat to the adsorption heat pump, there is a possibility that the heat energy is insufficient in other exhaust heat utilization elements. Even when the generator is driven at night, if there is a high demand for hot water in the waste heat utilization element, it may be difficult to supply sufficient heat to both the adsorption heat pump and other waste heat utilization elements. It was. In other words, in a conventional combined cold / heat generation apparatus having a drive source and an adsorption heat pump, when exhaust heat from the drive source is supplied to the adsorption heat pump, the production and demand of exhaust heat depends on the time and season. The problem was that it was difficult to level the use of exhaust heat throughout the season and time. As a result, there is a problem that it is difficult to level the energy (that is, fuel) required by the driving source through the seasons and time zones, and it is difficult to improve the energy utilization efficiency.

JP 2010-107156 A

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a combined cold / heat generating apparatus that enables leveling of energy use and exhaust heat use.

The combined cold heat generator of the present invention that solves the above problems includes an adsorption mode in which a working medium is adsorbed on an adsorbent and a desorption mode in which the working medium adsorbed on the adsorbent is desorbed from the adsorbent. An adsorption unit that can be executed alternately, a cooling unit that generates a cooling action by latent heat of vaporization of the working medium in accordance with execution of the adsorption mode and the desorption mode, and a desorption from the adsorbent in execution of the desorption mode. An adsorption heat pump having an adsorption heat pump condenser that condenses the separated gaseous working medium, and an adsorption heat pump heat exchanger that exchanges heat with the adsorbent that has generated heat in accordance with the execution of the adsorption mode. ,
A drive source for generating electrical energy and / or air conditioning energy and exhaust heat;
A heating element capable of heating the working medium present in the adsorption part of the adsorption heat pump in the desorption mode directly or indirectly by exhaust heat of the drive source,
The heating element is
The working medium can be directly heated by the exhaust heat of the driving source, or the working medium can be heated by the exhaust heat of the driving source via an exhaust heat recovery medium different from the working medium. A heating unit;
A supplementary heat source having an auxiliary heat source different from the drive source, and capable of heating the working medium and / or the exhaust heat recovery medium by the auxiliary heat source;
A storage tank for temporarily storing the working medium and / or the exhaust heat recovery medium heated in the heating section and / or the additional cooking section.

The composite cold heat generator of the present invention preferably includes any of the following (1) to (3), and more preferably includes a plurality of (1) to (3).
(1) The auxiliary heat source of the additional cooking portion is at least one selected from a heater, a burner, a solar water heater, and a heat pump.
(2) The drive source is an engine and / or a fuel cell.
(3) A compressor capable of compressing the refrigerant, a heat exchanger for condensing the refrigerant compressed by the compressor by heat exchange, an expansion valve for expanding the condensed refrigerant, and evaporation for evaporating the expanded refrigerant And a cooler having a compressor, and the compressor is driven by the drive source.

  The composite cold heat generator of the present invention uses the exhaust heat generated by the drive source in the adsorption heat pump. When exhaust heat utilization elements such as water heaters do not require exhaust heat from the drive source (for example, during the daytime in summer), cold heat can be generated by exhaust heat from the drive source, and the exhaust heat from the drive source is effectively used. it can. Moreover, the energy required for the drive source can be used effectively.

  In addition, since the heating element has a reheating part, the demand for exhaust heat in the exhaust heat utilization element is increased, for example, in the summer nighttime, and even when the exhaust heat that can be supplied to the adsorption heat pump is relatively small, the adsorption heat pump A sufficient amount of latent heat of vaporization can be obtained by heating (cooking) the working medium.

  Furthermore, since the heating element has a storage tank, for example, exhaust heat that has become surplus during the day can be stored and used at night. The storage tank may contain only the exhaust heat used for the adsorption heat pump (that is, the heated exhaust heat recovery medium and / or the heated working medium) or the exhaust heat (for example, hot water) used in the exhaust heat utilization element. May also be accommodated. Note that if only the heated exhaust heat recovery medium and / or the heated working medium is accommodated, there is no need to make the apparatus particularly large because a large storage tank is not required.

FIG. 3 is an explanatory diagram schematically illustrating the combined cold heat generator when the adsorption heat pump is in the first mode according to the first embodiment. It is explanatory drawing which represents typically the composite-type cold-heat generator when it concerns on Embodiment 1 and an adsorption heat pump is a 2nd mode. FIG. 9 is an explanatory diagram schematically illustrating a combined cold heat generator when the adsorption heat pump is in a first mode according to the second embodiment. FIG. 10 is an explanatory diagram schematically illustrating a combined cold heat generator when the adsorption heat pump is in a first mode according to the third embodiment.

  The combined cold heat generator of the present invention can be embodied as having an adsorption heat pump and a drive source. Examples of the drive source include a gas engine cogeneration system, a fuel cell system, and a gas heat pump. In this case, the cogeneration system or the heat pump system itself is the composite cold heat generator of the present invention. A drive source (for example, an engine, a fuel cell, or the like) in these systems is a drive source in the composite cold heat generator of the present invention. The engine may be any device that obtains power by burning fuel, and may be, for example, an internal combustion engine or an external combustion engine. As the exhaust heat in this case, heat at the time of combustion can be mainly used. When the drive source is a fuel cell, the heat generated by the reaction between the oxidant (oxygen, etc.) of the fuel cell and the fuel (hydrogen, etc.) can be used as exhaust heat. For reference, gas engine cogeneration systems and fuel cell systems generate electrical energy and exhaust heat. The gas heat pump generates air conditioning energy. A gas heat pump with a generator generates air-conditioning energy and electric energy. In a general gas heat pump with a generator, the generated electric energy is used to drive an auxiliary device of the gas heat pump. In addition, when the combined cold heat generator has an auxiliary heating device such as a water heater, the exhaust heat of the heating device may be used together with the exhaust heat of the drive source. For example, exhaust heat generated during and / or after boiling in a water heater may be used. In addition, the auxiliary | assistant heating apparatus here may be the same as the auxiliary | assistant heat source which comprises an additional cooking part, and may differ.

  Hereinafter, the composite type cold heat generator of the present invention will be described with specific examples.

(Embodiment 1)
The composite cold heat generator of Embodiment 1 is a composite of a household cogeneration system and an adsorption heat pump. Hereinafter, the aspect of the composite type cold heat generating apparatus of this embodiment is demonstrated concretely based on FIG.

(Composite type cold heat generator)
The composite cold heat generator of Embodiment 1 includes an air conditioner (hereinafter referred to as an air conditioner 1), an adsorption heat pump 2, a drive source 30, a heating element 4, and an exhaust heat utilization element 5. The cogeneration system combined with the adsorption heat pump 2 in the combined cold heat generator of Embodiment 1 is a gas engine driven power generation system, and the drive source of this gas engine driven power generation system is a gas engine. Therefore, the drive source 30 in the composite cold heat generator of Embodiment 1 is also a gas engine.

  The heating element 4 has a heating part (20, 31), an additional cooking part (35), and a storage tank 40. The heating unit includes a heating passage 20 of the adsorption heat pump 2 described later and a water heater 31 of the cogeneration system. Accordingly, hot water from the water heater 31 flows through the heating passage 20. The water heater 31 of the cogeneration system also serves as a part of the heating unit and the waste heat utilization element 5. In other words, the hot water of the water heater 31 is a heat exchange medium that is heated by the exhaust heat of the drive source 30, and an exhaust heat recovery medium that heats the working medium by exchanging heat with the working medium of the adsorption heat pump 2. It is. The additional cooking unit includes a solar water heater 35. Specifically, the solar water heater 35 includes a heat collector 350 that obtains solar heat, an auxiliary heating passage 351 that passes through the heat collector 350, and a coolant for solar water heater that flows through the auxiliary heating passage 351. The heat collector 350 corresponds to an auxiliary heat source in the composite cold heat generator of the present invention. The auxiliary heating passage 351 is arranged to be able to exchange heat with the heating passage 20. The coolant for solar water heaters contains additives such as ethylene glycol, propylene glycol, rust preventive and antifoaming agent. For this reason, in the first embodiment, the hot water (water) flowing through the water heater 31 and the coolant for the solar water heater are circulated through different flow paths (the heating passage 20 and the auxiliary heating passage 351) so as not to mix with each other. Yes. The boiling point of the coolant for solar water heaters is higher than the boiling point of water. For this reason, the coolant for solar water heaters heated by sunlight during the day in the solar water heater 35 becomes relatively high temperature. Therefore, the hot water flowing through the heating passage 20 exchanges heat with the solar water heater coolant flowing through the auxiliary heating passage 351 via the three-way valve 32 and the branch passage 20a, and the temperature further rises. The hot water whose temperature has risen joins the heating passage 20. In the combined cold / heat generator of Embodiment 1, the solar water heater 35 is included in the cogeneration system and is connected to the water heater 31. The branch path 20a toward the auxiliary heating path 351 in the heating path 20 can be opened and closed by the three-way valve 32. For example, when it is difficult to supply hot water with the solar water heater 35 at night, the branch path 20a. (That is, heat exchange with the solar water heater 35 is not performed) and flows directly into the storage tank 40 described later. A three-way valve 33 is provided in the heating passage 20 on the downstream side of the branch passage 20a. In the heating passage 20, the downstream portion of the branch passage 20 a is branched into the heating passage 20 and the hot water supply passage 20 b via the three-way valve 33. When the heating passage 20 and the hot water supply passage 20 b are connected by the three-way valve 33, hot water can be used by the exhaust heat utilization element 5. For example, when the cooling operation of the air conditioner 1 is stopped, the heating passage 20 and the hot water supply passage 20b are connected, and the circulation of hot water in the heating passage 20 is cut off (the inflow of hot water into the storage tank 40 is cut off). The three-way valve 33 is switched so that the hot water in the heating passage 20 is used in the exhaust heat utilization element 5. The waste heat utilization element 5 in the first embodiment is a hot water heater 31 and supplies hot water flowing through the hot water supply path 20b to a bath or the like. When the air conditioner 1 is in a cooling operation during the daytime in summer and the exhaust heat utilization element 5 does not use hot water, the three-way valve 33 stops the supply of hot water from the heating passage 20 toward the hot water supply passage 20b. To do. Further, when the cooling operation output by the air conditioner 1 is weak and the amount of exhaust heat used by the exhaust heat utilization element 5 is relatively large, such as at night in the summer, a storage tank described later from the heating passage 20 by the three-way valve 33. The amount of hot water reaching the adsorption heat pump 2 through 40 is reduced, and the amount of hot water supplied from the heating passage 20 through the exhaust heat utilization element 5 is increased. In addition, the timing which supplies warm water to the adsorption heat pump 2 and the waste heat utilization element 5 is not limited to this, and may be set as appropriate according to a change in heat demand during the season or throughout the day. If control is performed so that hot water can be supplied to the adsorption heat pump 2 when the amount of heat required for the exhaust heat utilization element 5 is excessive during the day of the summer as in Embodiment 1 and the demand for cooling increases, combined cold heat It is possible to contribute to optimization of the energy utilization efficiency of the entire generator, and it is possible to level the energy utilization throughout the season or throughout the day.

  At a position upstream of the adsorption portions 21 and 22 of the adsorption heat pump 2 in the heating passage 20 (specifically, a position upstream of a first port 201 described later, a position outside the case 200), a tank-like shape is provided. A storage tank 40 is attached. The storage tank 40 can store hot water before flowing through the heating passage 20 and exchanging heat with the working medium in the adsorption portions 21 and 22. A water inlet 40 a is formed in the upper part of the storage tank 40, and a water outlet 40 b is formed in the lower part of the storage tank 40. The water outlet 40 b is connected to the heating passage 20 and the reheating passage 240 via the three-way valve 34. The hot water that has passed through the heating passage 20 flows into the storage tank 40 through the water inlet 40a. The hot water whose temperature has decreased in the storage tank 40 flows into the reheating passage 240 through the water outlet 40 b and the three-way valve 34. That is, a constant amount of hot water is always stored in the storage tank 40. The reheating passage 240 joins the upstream side 20x of the drive source 30 in the heating passage 20. Therefore, the hot water flowing out of the storage tank 40 through the water outlet 40b is transported by the drive source 30 and heated again.

  The air conditioner 1 is driven by the electric power obtained by the drive source 30 and is connected to a cooling unit 23 (supercooler) of the adsorption heat pump 2 described later. In addition, since the air conditioner 1 is used in combination with the adsorption heat pump 2, it is only necessary to be able to perform a cooling operation. However, if the air conditioner 1 is capable of heating operation, the exhaust heat (engine exhaust heat) generated by the drive source 30 is used. It can also be used during heating operation.

[Configuration of adsorption heat pump]
Hereinafter, the structure of the adsorption heat pump 2 in the composite cold heat generator of Embodiment 1 will be described.

  The adsorption heat pump 2 is attached to the outdoor unit 1 of the air conditioner 1. The adsorption heat pump 2 includes a case 200, a first adsorption unit 21 and a second adsorption unit 22 provided in the case 200, a cooling unit 23 that generates latent heat of vaporization, a first four-way valve 214, and a second four-way. It has a valve 215 and a first port 201 to an eighth port 208 provided in the case 200. The 1st adsorption part 21 and the 2nd adsorption part 22 have porous adsorbents, such as silica gel, activated carbon, and activated alumina which can adsorb working media, such as water. The first four-way valve 214 and the second four-way valve 215 switch between the first passage 216 on the first adsorption part 21 side and the second passage 217 on the second adsorption part 22 side, respectively. Specifically, by switching the first four-way valve 214 and the second four-way valve 215, it corresponds to a first mode and a second mode to be described later. In the first mode, the first passage 216 on the first adsorption unit 21 side is connected to a heating passage 20 described later, and hot water is circulated through the first passage 216. At this time, the second passage 217 on the second adsorption unit 22 side is connected to a cooling passage 28 described later, and coolant that has passed through an adsorption heat exchanger 29 described later (adsorption coolant, cold water in the first embodiment). Is circulated through the second passage 217. In the second mode, the first passage 216 on the first adsorption portion 21 side is connected to the cooling passage 28, and the adsorption coolant is circulated through the first passage 216. At this time, the second passage 217 on the second adsorption unit 22 side is connected to the heating passage 20, and hot water is circulated through the second passage 217. In addition, warm water and cold water are the same water except for a distribution channel and different temperatures.

  Although it is preferable that the temperature of the hot water is high, it is sufficient if the temperature of the working medium in the first adsorption unit 21 and the second adsorption unit 22 can be heated and evaporated. The temperature of the cold water is preferably lower but may be lower than the temperature of the hot water. Moreover, in Embodiment 1, since the hot water obtained with the water heater 31 of the cogeneration system is used in the adsorption heat pump 2 as described above, water (hot water, cold water) is supplied to the heating passage 20 and the cooling passage 6. Although being distributed, the medium flowing through the heating passage 20 and the cooling passage 6 is not limited to this. For example, similar to the solar water heater 35 described above, a coolant containing some solute may be circulated.

  An adsorption condenser 24 for condensing the gaseous working medium desorbed from the adsorbent is disposed outside the case 200. The cooling unit 23 receives the liquid working medium condensed by the adsorption condenser 24 through the communication path 221 and vaporizes the liquid working medium to generate a cooling action by latent heat of vaporization. The adsorption heat pump 2 is provided with a working medium passage 221 for circulating the working medium. As shown in FIGS. 1 and 2, the working fluid passage 220 in the adsorption heat pump 2 includes a cooling unit 23, a first valve 231, a first adsorption unit 21, a second valve 232, an eighth port 208, an adsorption condenser. 24, the 7th port 207, the 3rd valve 233, the 2nd adsorption part 22, the 4th valve 234, and the cooling part 23 are made to communicate in order. Further, the working medium passage 220 branches in the adsorption agglomerator 24 to form a communication passage 221 that communicates the adsorption condenser 24 and the cooling unit 23 without passing through the first adsorption unit 21 and the second adsorption unit 22. ing. As shown in FIG. 1, the adsorption condenser 24, the storage tank 40, and the cooling unit 23 are arranged in this order from the upper side to the lower side in the vertical direction (gravity direction).

  Cold water flows through the cooling passage 28. The cooling passage 28 alternately cools the first adsorption unit 21 and the second adsorption unit 22 of the adsorption heat pump 2 with cold water. The cooling passage 28 is connected to the inside of the adsorption heat pump 2 via the second port 202 of the adsorption heat pump 2, the adsorption heat exchanger 29 capable of ventilating, the pump 290 (adsorption heat pump coolant conveying means), and the third port 203. To the first passage 216 or the second passage 217.

  The adsorption condenser 24 and the adsorption heat exchanger 29 used for the operation of the adsorption heat pump 2 are cooled by cooling air generated by the blower fans 10a and 10b.

  As shown in FIG. 1, the path 100 that connects the outdoor unit and the indoor unit in the refrigerant flow path of the air conditioner 1 passes through the cooling unit 23 of the adsorption heat pump 2. Specifically, the refrigerant of the air conditioner 1 reaches the cooling unit 23 from the outdoor unit through the fifth port 205. And it cools in the cooling unit 23 and goes to the indoor unit through the port 206. For this reason, the refrigerant of the air conditioner 1 is preliminarily cooled by the adsorption heat pump 2. Note that the refrigerant cooled by the adsorption heat pump 2 may flow into the indoor unit side of the air conditioner 1, for example, may flow into the upstream side of the subcooler 11, or the downstream side of the subcooler 11 and Although it may flow into the upstream side of the expansion valve 12, it may flow into at least the upstream side of the expansion valve 12. In consideration of the cooling performance of the adsorption heat pump 2 and the cooling performance of the air conditioner 1, it is preferable to flow into the upstream side of the subcooler 11. The refrigerant preliminarily cooled by the adsorption heat pump 2 on the indoor unit side of the air conditioner 1 and further cooled (cooled below the saturation temperature) by the subcooler 11 is expanded by the expansion valve 12 and evaporated by the evaporator 13. In this process, the refrigerant generates an indoor cooling action.

[Operation of adsorption heat pump]
The operation of the adsorption heat pump 2 will be described. First, the first mode for executing the desorption mode of the first adsorption unit 21 and the adsorption mode of the second adsorption unit 22 will be described.

(First mode)
As shown in FIG. 1, in the first mode, the first valve 231 and the third valve 233 are closed, and the second valve 232 and the fourth valve 234 are opened. In this state, the control unit 9 controls the first four-way valve 214 and the second four-way valve 215. Specifically, the first four-way valve 214 connects the first passage 216 in the adsorption heat pump 2 to the downstream side of the storage tank 40 in the heating passage 20, and the second passage 217 is connected to the cooling passage 28. Hot water is stored in the storage tank 40. This hot water is warm water of a water heater and is heated by the drive source 30. In some cases, the hot water is further heated by exchanging heat with the coolant for the solar water heater circulating in the solar water heater 35. This high-temperature coolant is supplied to the first passage 216 via the heating passage 20, the first port 201, and the second four-way valve 215, and is adsorbed in the first adsorption portion 21 via the first passage 216. Heat the agent. Then, it further joins the heating passage 20 via the first four-way valve 214 and the fourth port 204, further passes through the driving source 30 via the pump 300, is heated by the exhaust heat of the driving source 30, and returns to the water heater 31. To do. Thus, the 1st adsorption | suction part 21 is heated with a high temperature coolant, and desorption mode is performed. Further, since the pump 290 operates, the low-temperature coolant (cold water) cooled by the adsorption heat exchanger 29 is discharged from the adsorption heat exchanger 29, and the cooling passage 28, the pump 290, the second port 202, the second The adsorbent supplied to the second passage 217 via the two-way valve 215 and accommodated in the second adsorption portion 22 via the second passage 217 is cooled. At this time, the coolant is heated by the heat of the second adsorbing portion 22 and is further returned to the adsorption heat exchanger 29 via the second passage 217, the first four-way valve 214, the third port 203, and the cooling passage 28, and the fan It is cooled by the cooling air generated in 10b. Since the second adsorption unit 22 is cooled by the coolant and performs the adsorption mode in this manner, the overheating of the second adsorption unit 22 is suppressed, and the adsorption of the gaseous working medium in the second adsorption unit 22 continues. .

  In the first mode, since the first adsorption unit 21 is heated as described above, the working medium (generally water) adsorbed by the adsorbent of the first adsorption unit 21 is removed from the first adsorption unit 21. The gas is separated, passes through the second valve 232 and the eighth port 208 while flowing through the working medium passage 220, moves to the outside of the case 200, and further moves to the adsorption condenser 24. And in the condenser 24 for adsorption | suction, it cools with the cooling air produced with the fan 10a, and condenses. Thereby, the working medium is liquefied in the adsorption condenser 24. At this time, the adsorption condenser 24 releases heat of condensation. In this case, since the first valve 231 and the third valve 233 are closed, the gaseous working medium (generally water vapor) desorbed from the first adsorption unit 21 is cooled by the cooling unit 23 and the second adsorption unit. Do not move to 22. The liquid working medium (generally water) condensed in the adsorption condenser 24 moves to the cooling unit 23 via the communication path 221 by gravity.

  In the first mode, the second adsorbing portion 22 is cooled by the coolant flowing from the cooling passage 28 to the second passage 217, so that the pressure of the second adsorbing portion 22 decreases. Here, since the first valve 231 and the third valve 233 are closed and the fourth valve 234 is opened, the pressure of the cooling unit 23 decreases as the pressure of the second adsorption unit 22 decreases. Therefore, vaporization of the liquid working medium accommodated in the cooling unit 23 proceeds. The gaseous working medium (generally water) in the cooling unit 23 moves to the second adsorption unit 22 through the open fourth valve 234 and is adsorbed by the second adsorption unit 22. At this time, since the first valve 231 and the third valve 233 are closed, the gaseous working medium in the cooling unit 23 does not move to the first adsorption unit 21 and the adsorption condenser 24. By the way, the adsorption action in which the adsorbent adsorbs the working medium in the second adsorption unit induces heat generation. As a result, the second adsorption unit 22 that adsorbs the gaseous working medium is heated. In this case, the second adsorbing portion 22 is cooled by the coolant flowing through the second passage 217. Therefore, excessive temperature rise of the second adsorption unit 22 is prevented, and the adsorption performance of the second adsorption unit 22 is maintained.

(Second mode)
Next, the second mode for executing the desorption mode of the second adsorption unit 22 and the adsorption mode of the first adsorption unit 21 will be described. As shown in FIG. 2, in the second mode, contrary to the first mode, the second valve 232 and the fourth valve 234 are closed, and the first valve 231 and the third valve 233 are opened. In this state, the control unit 9 controls the first four-way valve 214 and the second four-way valve 215 so that the heating passage 20 is connected to the second passage 217 and the cooling passage 28 is connected to the first passage 216. . As a result, the high-temperature coolant heated by the drive source 30 flows from the drive source 30 into the second passage 217 via the heating passage 20, the first port 201, and the second four-way valve 215 by the operation of the pump 300. The second adsorption unit 22 is heated via the second passage 217. Thereafter, the coolant returns to the heating passage 20 via the second passage 217, the first four-way valve 214, and the fourth port 204. Then, the coolant is infused into the pump 300 and returns to the inside of the drive source 30. Further, since the pump 300 is operated, the low-temperature coolant cooled by the adsorption heat exchanger 29 is discharged from the adsorption heat exchanger 29 and passes through the cooling passage 28, the second port 202, and the second four-way valve 215. And supplied to the first passage 216. Then, the coolant cools the first adsorption portion 21 through the first passage 216, returns to the adsorption heat exchanger 29 through the first four-way valve 214, the third port 203, and the cooling passage 28, and exchanges the heat for adsorption. Cooled in a vessel 29.

  At this time, the gaseous working medium is cooled and condensed by the adsorption heat exchanger 29. For this reason, the adsorption heat exchanger 29 releases the heat of condensation. As described above, in the second mode, the second adsorption unit 22 is heated by the high-temperature coolant heated by the drive source 30, so that the working medium adsorbed by the second adsorption unit 22 is adsorbed by the second adsorption unit 22. Desorbs from the agent and becomes gaseous. The gaseous working medium flows out to the working medium passage 220 through the open third valve 233, moves to the adsorption condenser 24 through the seventh port 207, and is cooled by the adsorption condenser 24. Condensate. Therefore, the working medium becomes liquid in the adsorption condenser 24, and the adsorption condenser 24 releases heat of condensation. At this time, since the fourth valve 234 and the second valve 232 are closed, the gaseous working medium generated in the second adsorption unit 22 does not move to the cooling unit 23.

  In the second mode, the pump 290 operates and the first adsorption unit 21 is cooled by the coolant (adsorption coolant), so the pressure of the first adsorption unit 21 decreases. At this time, since the second valve 232 is closed and the first valve 231 is opened, the pressure of the cooling unit 23 is reduced, and vaporization of the working medium proceeds in the cooling unit 23. For this reason, the cooling unit 23 is cooled by vaporization latent heat. The gaseous working medium of the cooling unit 23 moves to the first adsorption unit 21 via the first valve 231 and is adsorbed by the first adsorption unit 21. At this time, the first adsorption portion 21 generates heat due to adsorption heat. However, since the coolant flows through the first passage 216, the first adsorption unit 21 is cooled by the coolant, and the excessive temperature rise of the first adsorption unit 21 is suppressed.

  As described above, the first adsorption unit 21 and the second adsorption unit 22 in the adsorption heat pump 2 adsorb the working medium to the adsorbent to generate heat, and remove the working medium adsorbed by the adsorbent from the adsorbent. The desorption mode to be released is alternately executed every predetermined time. The predetermined time is appropriately set according to the type and amount of the adsorbent and the working medium. As described above, the adsorption heat pump 2 is operated during the cooling operation, and the cooling unit 23 is cooled in the first mode and the second mode. For this reason, the refrigerant for the air conditioner 1 condensed in the outdoor heat exchanger 7 and flowing into the cooling unit 23 is precooled by the cooling unit 23. For this reason, according to the air conditioner 1 of the embodiment, the cooling efficiency during the cooling operation can be improved. During the cooling operation, that is, when the adsorption heat pump 2 is operated, the adsorption condenser 24 and the adsorption heat exchanger 29 are heated. In the first embodiment, the refrigerant flowing through the refrigeration cycle (compression, condensation, expansion, and evaporation cycle) circuit is cooled by the cooling unit 23. However, the composite cold heat generator of the present invention is not limited to this, and various types are available. The refrigerant circulating in the refrigerant circuit can be cooled. For example, the refrigerant (cooling water) in a simple cooling water circulation type refrigerant circuit that does not involve a change in the state of the refrigerant may be cooled.

  In the first embodiment, the adsorbing portions 21 and 22 of the adsorption heat pump 2 are heated by the hot water of the water heater 31 obtained by collecting the exhaust heat of the drive source 30 (gas engine). For this reason, since the refrigerant | coolant of the air conditioner 1 can be pre-cooled with the cold obtained by the adsorption heat pump 2, the cooling efficiency of the air conditioner 1 can be improved.

  Moreover, since the hot water used for the adsorption heat pump 2 is stored in the storage tank 40, the adsorption heat pump 2 (when the exhaust heat of the drive source 30 is mainly supplied to the exhaust heat utilization element 5 (for example, the water heater 31). That is, the exhaust heat can be used also in the air conditioner 1). Depending on the amount of exhaust heat required by the exhaust heat utilization element 5, hot water may be supplied to both the exhaust heat utilization element 5 and the adsorption heat pump 2.

  Furthermore, since the working medium is additionally cooked by the auxiliary heat source (solar water heater 35), the working medium can be further heated, and the cooling efficiency by the air conditioner 1 can be further improved. That is, the temperature of the coolant that exchanges heat with the adsorbent in the adsorption portions 21 and 22 in the desorption mode and the coolant that exchanges heat with the adsorbent in the adsorption portions 21 and 22 in the adsorption mode due to the characteristics of the adsorption heat pump 2. If the difference is small, the cooling efficiency decreases. However, in the first embodiment, an auxiliary heat source (for example, a solar water heater 35) is used to recapture the coolant that exchanges heat with the adsorbent in the adsorbing units 21 and 22 in the desorption mode. Thereby, the temperature difference of the above-mentioned coolant can be increased, and the cooling efficiency of the adsorption heat pump can be improved. As a result, it can contribute to the improvement of the cooling efficiency by the air conditioner 1. In the first embodiment, the coolant for the solar water heater circulating through the solar water heater 35 and the exhaust heat recovery medium (water) are different types of coolant, but the same type of coolant may be used. In this case, the exhaust heat recovery medium itself may be distributed to the heat collector 350 of the solar water heater 35. In the first embodiment, the working medium of the adsorbing units 21 and 22 is heated by circulating the exhaust heat recovery medium (water) through the heating passage 20, but the working medium is cooled by cooling water or exhaust gas of the drive source 30, for example. You may heat. In this case, if the cooling water or the like flowing out from the drive source 30 is circulated through the heating passage 20, the working medium is directly heated by the exhaust heat. Cooling water or the like is circulated through the storage tank 40 and can be temporarily stored in the storage tank 40. The cooling water or the like that has flowed out of the storage tank 40 may be circulated through the water heater 31 to recover the exhaust heat. Further, the cooling water or the like can be supplementarily heated by an auxiliary heat source such as a gas burner. When the working medium is heated by the exhaust heat recovery medium, the exhaust heat recovery medium may be a gas or a solid, but considering the heat conduction performance, the exhaust heat recovery medium is a fluid. preferable. Furthermore, in consideration of downsizing the storage tank 40 and keeping the exhaust heat recovery medium warm in the storage tank 40, it is preferable that the exhaust heat recovery medium is liquid at least in the storage tank 40.

(Embodiment 2)
FIG. 3 is a diagram schematically illustrating the composite cold heat generator according to the second embodiment. More specifically, the adsorption heat pump 2 shown in FIG. 3 is in the first mode, and the first adsorption unit 1 is heated using the exhaust heat (warm heat) derived from the drive source 30 to desorb the working medium. I am letting. Moreover, the 2nd adsorption | suction part 22 is cooled using the cold heat originating in the heat exchanger for adsorption | suction. As shown in FIG. 3, in the second embodiment, a gas burner 36 is used as an auxiliary heat source in place of the solar water heater. The gas burner 36 constitutes a part of the cogeneration system, and is used for reheating hot water from the water heater 31. Similar to the first embodiment, the water heater 31 collects the exhaust heat of the drive source 30 to obtain hot water from water. The gas burner 36 directly heats the hot water of the water heater using the same gas as the drive source 30 as fuel.

  The storage tank 40 is disposed on the downstream side of the water heater 31 and on the upstream side of the first port 201. In the composite cold heat generator of Embodiment 2, the tank wall of the storage tank 40 has a heat insulating layer (such as a vacuum layer). For this reason, the temperature change of the warm water accommodated in the storage tank 40 is suppressed. That is, the temperature of the hot water stored in the storage tank 40 is difficult to decrease. The water outlet 40 b of the storage tank 40 communicates with the upstream side of the drive source 30 in the heating passage 20 as in the first embodiment. Therefore, also in the second embodiment, a constant amount of warm water is always stored in the storage tank 40, and the warm water flowing out of the storage tank 40 through the water outlet 40 b is heated again by the drive source 30.

  The other elements in the composite type cold heat generator of Embodiment 2 are substantially the same as those of the composite type cold heat generator of Embodiment 1. Therefore, also in the composite type cold heat generating device of the second embodiment, similarly to the composite type cold heat generating device of the first embodiment, cold heat is generated by the adsorption heat pump 2 using the exhaust heat of the drive source 30, and the air conditioner is generated by this cold heat. By pre-cooling one refrigerant, the cooling efficiency of the air conditioner 1 can be improved. Moreover, since the hot water used for the adsorption heat pump 2 is stored in the storage tank, the cooling operation by the air conditioner 1 can be performed efficiently even when the exhaust heat required for the exhaust heat utilization element 5 is relatively large. . Furthermore, since additional cooking is performed by an auxiliary heat source that does not use exhaust heat (that is, the gas burner 36), there is an advantage that the air-conditioning apparatus 1 can efficiently perform the cooling operation regardless of the operation state of the exhaust heat utilization element 5. If the hot water stored in the storage tank 40 is sufficiently hot, the three-way valve 32 is switched so that the hot water does not flow to the gas burner 36 side. For this reason, the energy required for cooling operation can be reduced. In the second embodiment, the gas burner 36 is used as an auxiliary heat source for directly heating the exhaust heat recovery medium. However, other auxiliary heat sources such as an electric heater may be used.

(Embodiment 3)
FIG. 4 is a diagram schematically showing the composite cold heat generator of the third embodiment. More specifically, the adsorption heat pump 2 shown in FIG. 4 is in the first mode.

  The combined cold heat generator of Embodiment 3 distributes the same coolant as the solar water heater coolant of Embodiment 1 as a waste heat recovery medium that separates the heating passage 20 from the water heater 31 and distributes it inside the heating passage 20. The storage tank 40 is disposed upstream of the auxiliary heat source (gas burner 36), the path from the heating passage 20 to the drive source 30 (heating branch path 25) is branched, and the heating path 20 and the heating branch path 25 Are connected to each other by the three-way valve 35, and the reheating passage 240 from the storage tank 40 to the drive source 30 is not provided, and is the same as the combined cold heat generator of the second embodiment.

  In the combined cold heat generator of Embodiment 3, the operation of the adsorption heat pump 2 and the coolant circulation in the heating passage 20 are synchronized. That is, while the adsorption heat pump 2 is stopped, the coolant flow is also stopped. When the exhaust heat usage amount in the exhaust heat utilization element 5 is very large, the passage from the heating path 20 to the heating branch path 25 is blocked by the three-way valve 35, and the coolant is not circulated to the drive source 30. Therefore, in this case, the adsorption heat pump 2 does not use the exhaust heat of the drive source 30 and can use the exhaust heat only by the exhaust heat utilization element 5. In this case, the adsorption heat pump 2 is heated by the coolant accommodated in the storage tank 40. In the first mode shown in FIG. 4, the coolant that has passed through the adsorption heat pump 2 (that is, the coolant that has been cooled by exchanging heat with the working medium) passes through the first adsorption unit 21, the first four-way valve 214, and the fourth port 204. It flows into the heating channel 20 and is returned to the storage tank 40. For this reason, the temperature of the coolant in the storage tank 40 falls. However, since the gas burner 36 is provided on the downstream side of the storage tank 40, the coolant that has flowed out of the storage tank 40 can be heated by the gas burner 36, and high-temperature coolant can be supplied to the adsorption heat pump 2. Therefore, even when exhaust heat cannot be used (or the amount of available exhaust heat is small), the cooling operation of the air conditioner 1 can be performed efficiently.

(Other)
The present invention is not limited to the embodiments described above and shown in the drawings, and can be implemented with appropriate modifications within the scope not departing from the gist. For example, three or more adsorption units may be provided, or an auxiliary heat source 350 or an exhaust heat utilization element 5 of the additional cooking unit, an exhaust heat recovery medium, or the like other than those mentioned in the above embodiment is used. You can also The composite cold heat generator of the present invention can be installed stationary in various buildings, or can be installed in various vehicles, ships, and the like.

1 is an air conditioner, 2 is an adsorption heat pump, 20 is a heating passage, 21 is a first adsorption portion, 22 is a second adsorption portion, 23 is a cooling portion, 28 is a cooling passage, 29 is an adsorption heat exchanger, and 214 is First four-way valve, 215 is a second four-way valve, 216 is a first passage, 217 is a second passage, 221 is a communication passage, 30 is a drive source, 31 is a hot water heater, 35 is a solar water heater, and 350 is a heat collector. , 36 indicates a gas burner.

Claims (3)

A first adsorption unit and a first adsorption unit capable of alternately executing an adsorption mode for adsorbing the working medium on the adsorbent and a desorption mode for desorbing the working medium adsorbed on the adsorbent from the adsorbent at predetermined time intervals . An adsorption unit having two adsorption units; a cooling unit that generates a cooling action by latent heat of vaporization of the working medium in accordance with execution of the adsorption mode and the desorption mode; and desorption from the adsorbent in accordance with execution of the desorption mode. An adsorption heat pump having an adsorption heat pump condenser that condenses the separated gaseous working medium, and an adsorption heat pump heat exchanger that exchanges heat with the adsorbent that has generated heat in accordance with the execution of the adsorption mode. ,
A drive source for generating electrical energy and / or air conditioning energy and exhaust heat;
A heating element capable of directly or indirectly heating the working medium present in the adsorption portion of the adsorption heat pump in the desorption mode by exhaust heat of the drive source;
An exhaust heat utilization element having a heat exchange medium heated by the exhaust heat of the drive source ,
The heating element is
The working medium can be directly heated by the exhaust heat of the driving source, or the working medium can be heated by the exhaust heat of the driving source via an exhaust heat recovery medium different from the working medium. A heating unit;
A supplementary heat source having an auxiliary heat source different from the drive source, and capable of heating the working medium and / or the exhaust heat recovery medium by the auxiliary heat source;
E Bei and a reservoir for temporarily accommodating the working medium and / or the waste heat recovery medium heated in the heating unit and / or the reheating portion,
When there is a demand for exhaust heat in the exhaust heat utilization element and the exhaust heat that can be supplied to the adsorption heat pump is insufficient, the working medium of the adsorption heat pump is heated by the additional cooking unit, and combined cold heat generation apparatus.   The combined cold / heat generating apparatus according to claim 1, wherein one type selected from a fuel cell system, an engine-driven power generation system, and an engine-driven heat pump system as the drive source is combined with the adsorption heat pump. A compressor capable of compressing the refrigerant; a heat exchanger for condensing the refrigerant compressed by the compressor by heat exchange; an expansion valve for expanding the condensed refrigerant; an evaporator for evaporating the expanded refrigerant; Have a cooler with
The combined cold / heat generating apparatus according to claim 1 , wherein the compressor is driven by the driving source and the refrigerant is precooled by the adsorption heat pump .

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