Cold generation system

Abstract

To provide a cold generation system that can effectively use exhaust heat of steam turbine driving.SOLUTION: A cold generation system 1000A comprises: a steam turbine device 100 for generating power by using a Rankine cycle 110 for receiving heat from a heat source 10; an adsorption refrigeration device 700 for outputting cold to a cold load 501 by using an adsorption refrigeration cycle using exhaust heat discharged by a first condenser 102 constituting the Rankine cycle 110, as an operation heat source, and discharging refrigeration exhaust heat Q4; and heat balance control mechanisms 320 and 601 for controlling heat balance of the steam turbine device and the adsorption refrigeration device so that a condensation temperature of a first heat medium in the Rankine cycle 110 is kept within a first predetermined temperature range.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to a cold generating system. [Background technology]

[0002] The total amount of waste heat (unused thermal energy) from power plants, factories, etc. in Japan is 1 trillion kWh per year, which is equivalent to the total annual electricity generation in Japan (see Non-Patent Document 1). Furthermore, the majority of this unused thermal energy is waste heat below 200°C. The main sources of this waste heat are the steel industry, petrochemical industry, paper and pulp industry, cement industry, and other material industries (see Non-Patent Document 1).

[0003] Heat is an energy that, if not used, cools down and is lost, and cannot be transported far. Therefore, if the time when heat is generated differs from the time when it is needed, or if the heat source is far from the demand destination, the heat is ultimately wasted because it is not effective enough to meet demand.

[0004] On the other hand, electricity is always in demand and can be easily transported through the power grid. Therefore, the best way to fill the gaps in time and distance mentioned above is to convert heat into electricity, i.e., generate electricity. In fact, large amounts of high-temperature industrial waste heat, exceeding several hundred degrees Celsius, can be efficiently converted into electricity using steam turbines. Naturally, Japan's industrial sector has long been working to streamline energy use through waste heat power generation, and is currently at a level where there is no room for further improvement. Therefore, the above-mentioned industrial waste heat below 200 degrees Celsius can be considered to be waste heat that has already been used to generate electricity, or unused heat because the temperature and quantity are not high enough to be used for power generation using normal methods. [Prior art documents] [Non-patent literature]

[0005] [Non-Patent Document 1] Industrial Structure Council, Industrial Technology Subcommittee, "Preliminary Assessment Report on Research and Development of Innovative Technologies for Utilizing Unused Thermal Energy," Ministry of Economy, Trade and Industry, June 2012 [Non-Patent Document 2] Energy Conservation Center, "Study on Energy Systems for Factories," FY2000 Report, Ministry of Economy, Trade and Industry Summary of the Invention [Problem to be solved by the invention]

[0006] For the reasons mentioned above, the technology for utilizing industrial waste heat below 200°C is also biased toward power conversion, and various technologies have been developed, including the organic Rankine cycle (binary power generation) using an organic solvent instead of water as the working fluid, thermoelectric conversion using the Seebeck effect, and other technologies. However, as is self-evident from the small heat drop that can be used in the first place, the theoretical upper limit of the power generation efficiency of these methods is low, and in reality, this theoretical upper limit is not reached due to various losses (about 5% for the organic Rankine cycle, and less than 1% for thermoelectric conversion), and they have not been widely used in terms of cost-effectiveness. In other words, it has not been possible to effectively utilize the exhaust heat (waste heat) from steam turbine power generation, which accounts for the majority of unused heat. This issue is also common to forms that use the rotational power of a steam turbine to drive other devices.

[0007] The present disclosure has been made to solve the above-mentioned problems, and aims to provide a cold energy generation system that can effectively utilize the waste heat generated by driving a steam turbine. [Means for solving the problem]

[0008] In order to achieve the above-mentioned object, a cold energy generation system according to one aspect of the present disclosure includes a steam turbine device that generates power using a Rankine cycle that receives heat from a heat source, an adsorption refrigeration device that outputs cold energy to a cold energy load and releases refrigeration exhaust heat using an adsorption refrigeration cycle in which exhaust heat released by a first condenser that constitutes the Rankine cycle is used as a working heat source, and a heat balance control mechanism that controls the heat balance of the steam turbine device and the adsorption refrigeration device so that the condensation temperature of a first heat medium in the Rankine cycle is maintained within a first predetermined temperature range.

[0009] According to another aspect of the present disclosure, a cold energy generating system includes a steam turbine device that generates power using a Rankine cycle that receives heat from a heat source, and an adsorption refrigeration device that outputs cold energy to a cold energy load and discharges refrigeration waste heat using an adsorption refrigeration cycle in which exhaust heat discharged by a first condenser constituting the Rankine cycle is used as a working heat source, the adsorption refrigeration device including three or more adsorbers each accommodating an adsorbent, a refrigerant circulation path that constitutes the adsorption refrigeration cycle and circulates a refrigerant through a second evaporator and a second condenser, a second heat medium circulation path that circulates a second heat medium through the first condenser, and a third heat medium that circulates a third heat medium through the second condenser. and a third heat medium circulation path that circulates the hot heat obtained in the second condenser through a condenser and a radiator so as to be radiated in the radiator, and the cold heat generation system includes an adsorption regeneration control mechanism that controls operation of the adsorption refrigeration device to sequentially perform an adsorption regeneration operation for the three or more adsorbers, in which in an adsorption operation, each of the adsorbers is connected to the second evaporator and is interposed between the radiator and the second condenser in the third heat medium circulation path so that the adsorbent adsorbs a refrigerant, and in a regeneration operation, each of the adsorbers is connected to the second condenser and is interposed in the second heat medium circulation path so that the adsorbent releases the refrigerant for regeneration. Effects of the Disclosure

[0010] The present disclosure has an effect of providing a cold heat generation system capable of effectively utilizing exhaust heat generated by driving a steam turbine. [Brief description of the drawings]

[0011] [Figure 1] FIG. 1 is a diagram illustrating an example of an outline of hardware of a cold heat generating system according to a first embodiment of the present disclosure. [Diagram 2] FIG. 2 is a functional block diagram showing an example of the configuration of a control system of the cold generating system of FIG. [Diagram 3] FIG. 3 is a diagram showing a first process in an example of the adsorption regeneration operation of the cold generating system of FIG. [Figure 4] FIG. 4 is a diagram showing a second process in an example of the adsorption regeneration operation of the cold generating system of FIG. [Diagram 5] FIG. 5 is a diagram illustrating an example of an outline of hardware of a cold heat generating system according to a modification of the first embodiment of the present disclosure. [Figure 6] FIG. 6 is a functional block diagram showing an example of the configuration of a control system of a cold generating system according to the second embodiment of the present disclosure. [Figure 7] FIG. 7 is a functional block diagram showing an example of the configuration of a control system of a cold generating system according to the third embodiment of the present disclosure. [Figure 8] FIG. 8 is a functional block diagram showing an example of the configuration of a control system of a cold generating system according to the fourth embodiment of the present disclosure. [Figure 9] FIG. 9 is a flowchart showing an example of heat balance control of the cold generating system of FIG. [Figure 10] FIG. 10 is a functional block diagram showing an example of the configuration of a control system of a cold generating system according to the fifth embodiment of the present disclosure. [Figure 11] FIG. 11 is a diagram illustrating an example of an outline of hardware of a cold heat generating system according to a sixth embodiment of the present disclosure. [Figure 12] FIG. 12 is a graph showing an example of the temperature change of each adsorbent and the discharge temperature change of the second heat medium when the number of adsorbers is two. [Figure 13] FIG. 13 is a graph showing an example of the temperature change of each adsorbent and the discharge temperature change of the second heat medium in the cold generating system of FIG. [Figure 14]FIG. 14 is a diagram illustrating an example of an outline of hardware of a cold generating system according to a seventh embodiment of the present disclosure. [Figure 15] FIG. 15 is a graph showing an example of the temperature change of each adsorbent and the discharge temperature change of the second heat medium in the cold generating system of FIG. [Figure 16] FIG. 16 is a diagram illustrating an example of an outline of hardware of a cold generating system according to the eighth embodiment of the present disclosure. [Figure 17] FIG. 17 is a graph showing an example of a change in discharge temperature of the second heat medium and a change in return temperature of the second heat medium of each refrigerator in the cold generating system of FIG. [Figure 18] FIG. 18 is a diagram illustrating an example of an outline of hardware of a cold heat generating system according to the ninth embodiment of the present disclosure. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0012] (The knowledge that led to this disclosure) <Thermal Refrigeration Machine> The inventors have focused on thermal chillers that generate cold heat using heat as a power source to effectively utilize the exhaust heat from steam turbine power generation. A typical electric chiller is a mechanical compression type that operates by compressing and transporting a refrigerant using an electric compressor, whereas a thermal chiller is a thermal compression type that operates by compressing and transporting a refrigerant using heat. Among thermal chillers, adsorption chillers are known to be able to operate by supplying hot water of 55°C or 85°C as a heat source.

[0013] Specifically, Japanese Patent No. 4,565,539 discloses that the supply hot water temperature and thermal COP of a single-effect adsorption refrigerator using silica gel as an adsorbent are about 85°C and about 0.6, respectively. Japanese Patent Publication No. 2002-372332 discloses the composition and chemical structure of synthetic zeolite, whose adsorption equilibrium state changes significantly in a narrow relative vapor pressure range compared to silica gel, and states that this characteristic is suitable for the adsorbent of an adsorption refrigerator. Japanese Patent No. 4,669,914 discloses design information for an adsorbent that uses the above synthetic zeolite and can be regenerated with hot water at 55°C, and an adsorption refrigerator using the same. Japanese Patent No. 5,850,051 discloses data showing that the thermal COP of this refrigerator is about 0.6. Furthermore, Japanese Patent Publication No. 2018-128242 discloses that adsorption chillers, like absorption chillers, can also be made double-effect, and that when the driving hot water temperature is around 85°C, the theoretical thermal COP is around 1.0, along with the specific configuration of the chiller.

[0014] <Cold energy conversion efficiency instead of power generation efficiency> Although it is not possible to simply compare power generation efficiency and cold energy conversion efficiency, the thermal COP of an adsorption chiller that uses waste heat below 100°C is 0.6 to 1.0, which is comparable to the value obtained when generating electricity at the same temperature with a power generation efficiency of 20% and converting it into cold energy using an electric chiller with a power COP of 3 to 5. In this way, the technology itself for efficiently converting unused heat below 100°C, which is the largest volume among industrial waste heat, into cold energy is publicly known.

[0015] Here, the thermal COP (thermal coefficient of performance) is defined by (Equation 1). (Formula 1): Thermal COP = Cooling output of the refrigerator (kW) / Heat consumption of the refrigerator (kW) Moreover, the power COP (power coefficient of performance) is defined by (Equation 2). (Formula 2): Power COP = Cooling output of the refrigerator (kW) / Power consumption of the refrigerator (kW)

[0016] <Ideal heat load> Incidentally, in order to effectively utilize the exhaust heat from steam turbine power generation by converting it into cold energy instead of into electricity, it is necessary to fill the time gap between heat generation and heat demand, as well as the distance gap between the heat source and the demand destination, just as in the case of electricity.

[0017] Therefore, the present inventors have focused on one such example, in which unused heat is converted into cold heat by a thermal refrigerator to cool a data center (hereinafter referred to as DC), which is an information and communication facility.

[0018] First, we will discuss the actual energy usage of data centers, which are essential facilities for the information and communications industry. The PUE value defined by (Equation 3) is commonly used as an indicator of the power usage efficiency of a data center.

[0019] (Equation 3): PUE = DC power consumption (kW) / Computer power consumption (kW) In other words, if a computer with a power consumption of 1000kW is operated and the DC's power consumption is 2000kW, the PUE is 2.0, and the closer this value is to 1, the more power efficient the DC is. The PUE of the average DC in Japan is around 1.5 as of 2020, and it requires auxiliary power that is about half the power consumed by the computer. The largest part of this auxiliary power is the power required to cool the computer.

[0020] Although input power to a computer is output as information (calculated solutions), the computer does not perform any physical work on the outside, and so in terms of energy, all input power is converted into heat. Therefore, a computer that constantly consumes 1000kW of power cannot achieve heat balance and operate continuously unless it constantly cools at 1000kW. If we ignore power supplies and other losses and simplify the calculation by assuming that all of the incidental power of the above PUE of 1.5 is due to cooling power, then 500kW of cooling power is used to cool 1000kW, so the power COP of the chiller, as defined in (Equation 2), is 2.0. This is considered to be the effective cooling power required when air-cooling a computer in Japan.

[0021] Therefore, energy can be rationalized by introducing equipment to discharge waste heat into the DC and using this waste heat to replace the cooling with a power COP of 2.0 performed by an electric refrigerator with cooling with a power COP of 3 to 5 performed by an adsorption refrigerator. In addition, since there is always a demand for information and communication, there is always a demand for cold heat in the DC, and there is no time gap between the generation of heat and the demand for heat, and since information can be easily transported through communication lines, there is no distance gap between the heat source and the demand destination. Therefore, the conversion of hot heat to cold heat by cooling the DC with an adsorption refrigerator is considered to be the second best method of utilizing unused heat after power conversion. In addition, in this method of utilizing unused heat, the DC can be said to be an ideal heat load.

[0022] Therefore, the present inventors have conceived of a cold energy generation system in which exhaust heat from steam turbine power generation is converted into cold energy by an adsorption refrigerator to cool the DC.

[0023] <The first challenge in utilizing waste heat from steam turbines> However, this cold energy generation system has the following first problem.

[0024] Regardless of whether it is a gas turbine or a steam turbine, the expansion ratio of a turbine is a number defined by Equation 4.

[0025] (Equation 4): Turbine expansion ratio = Turbine inlet pressure / Turbine outlet pressure A gas turbine is a device that has a compressor turbine and an expansion turbine connected coaxially, uses the rotational force obtained by the expansion turbine to perform the air compression work of the compressor turbine, injects fuel into this high-temperature, high-pressure compressed air to cause it to explode, and expands this combustion gas in the expansion turbine to obtain rotational force.To reduce the air compression work of the compressor turbine and increase efficiency, it is common to have a preheating heat exchanger that exchanges heat between the waste combustion gas discharged from the expansion turbine and the intake air of the compressor turbine, and regenerate energy by preheating (heating and compressing) the intake air with the waste combustion gas. Therefore, the expansion ratio defined by (Equation 4) is the ratio between the combustion gas pressure at the turbine inlet and the exhaust combustion gas pressure before entering the preheater heat exchanger, and the exhaust combustion gas after leaving the preheater is usually at atmospheric pressure. Therefore, no matter what type of heat recovery configuration is used for the driven device connected to the latter stage, the effect of the driven device on the expansion ratio is minor as long as the pressure loss is not significantly high.

[0026] On the other hand, condensing turbines, which account for the majority of steam turbines, are devices based on the operating principle of cooling and condensing (condensing) the turbine outlet steam in order to reduce the turbine outlet pressure (turbine back pressure) and increase the expansion ratio.In other words, the lower the condensation temperature (condensation temperature), which has a one-to-one relationship with the turbine back pressure, the higher the expansion ratio and the higher the efficiency.

[0027] In typical plant designs, the condensation temperature when a water-cooled condenser is used is 32°C (turbine back pressure 0.05 atm), and the condensation temperature when an air-cooled condenser is used is 65°C (0.3 atm). Therefore, for example, if the steam at the turbine inlet is 300°C saturated steam (steam pressure 65 atm), the expansion ratio is 1300 (65 / 0.05) when a water-cooled condenser is used, and 216 (65 / 0.3) when an air-cooled condenser is used. In this way, with a steam turbine, the expansion ratio changes greatly depending on the condensation temperature, and so does the efficiency.

[0028] This means that when considering the effective use of the waste heat from the power generation of a steam turbine, the efficiency of the steam turbine is affected by the operating temperature of the driven device driven by the waste heat. This is the peculiarity of the use of waste heat from a steam turbine, and the problem of the above-mentioned cold energy generation system arises from this peculiarity.

[0029] <First finding> To solve this problem, the steam turbine device and the adsorption chiller can be thermally balanced so that the condensing temperature of the steam turbine is maintained within a predetermined temperature range. In this case, from the perspective of a business that utilizes waste heat, it is necessary to prioritize meeting the cold demand and maintain the cold output to the cold load so as to meet the cold demand. The heat balance between the steam turbine device and the adsorption chiller under this constraint can be achieved by adjusting the amount of heat received from the heat source of the steam turbine device, if possible. If this is not possible, it can be achieved by controlling the thermal COP of the adsorption chiller. As a result, a cold generation system can be provided that can effectively utilize the waste heat from driving the steam turbine.

[0030] This is the first finding.

[0031] <Second finding> From the first finding, the amount of heat received from the heat source of the steam turbine device or the thermal COP of the adsorption chiller can also be adjusted over a wide range. In this way, even if the cold heat demand of the heat load varies over a wide range, the thermal COP of the adsorption chiller can be adjusted over a wide range in response to the wide range of cold heat demand of the heat load, thereby achieving thermal balance between the steam turbine device and the adsorption chiller so that the condensing temperature of the steam turbine is maintained within a predetermined temperature range. If this is the case, the cold heat load can be a general cold heat load with a wide range of cold heat demand, in addition to a DC where a constant cold heat demand is expected. In other words, according to the cold heat generation system based on the second finding, the cold heat load is not particularly limited.

[0032] <The second challenge in utilizing waste heat from steam turbines> In the course of examining the first problem, the present inventors have realized that a second problem exists when an adsorption refrigeration device is used to utilize the waste heat of a steam turbine.

[0033] That is, when an adsorption refrigeration system is used to utilize the exhaust heat of a steam turbine, the exhaust heat of the condenser of the steam turbine is input to the adsorption refrigeration system as hot water (heat medium for heating). Meanwhile, an adsorption refrigeration system generally includes a pair of adsorber, and an adsorption regeneration control mechanism controls the adsorption regeneration operation of the pair of adsorber so that while one adsorber performs an adsorption operation, the other adsorber performs a regeneration operation.

[0034] In this case, when one of the adsorbers is in regeneration operation, at the beginning of the regeneration operation, the adsorber has been cooled by cooling water (cooling heat medium) in the immediately preceding adsorption operation, so that the hot water introduced into the adsorption refrigeration system is discharged after consuming heat to a temperature close to that of the cooling water (30°C, for example). Thereafter, as the one of the adsorbers is heated by the hot water, the discharge temperature of the hot water rises, and at the point when the one of the adsorbers is completely regenerated, there is almost no heat consumption, so the hot water is discharged at a temperature close to the temperature at which it was introduced (55°C, for example). Thereafter, when the one of the adsorbers switches to adsorption operation, the other adsorber switches to regeneration operation, and when the other adsorber is in regeneration operation, the same thing happens as with the adsorber of the one of the adsorbers. Therefore, even if hot water of a constant temperature is introduced into the adsorption refrigeration system, the discharge temperature of the hot water will not be constant, and a sudden and large temperature change occurs, particularly at the timing of switching between the adsorption operation and the regeneration operation in each adsorber. This sudden and large temperature change in the hot water causes a pressure shock in the back pressure of the steam turbine, which can damage the turbine blades.

[0035] <Third finding> As a third insight, the inventors have discovered that in order to solve the second problem, the adsorption refrigeration device must be equipped with three or more adsorption units, and the adsorption regeneration control mechanism must control the operation of the adsorption refrigeration device so that the adsorption regeneration operation is performed sequentially for the three or more adsorption units.

[0036] In this case, the adsorption and regeneration operations of at least two adsorber units are shifted and partially overlap, which equalizes the hot water discharge temperature and suppresses the pressure shock of the steam turbine back pressure, thereby reducing the possibility of damage to the turbine blades.

[0037] <Fourth finding> The above-mentioned Japanese Patent No. 4,669,914 states that certain zeolite-based adsorbents can be regenerated at 55° C. under optimal operating conditions. As mentioned above, JP 2002-372332 A discloses that the equilibrium state of this particular synthetic zeolite changes significantly within a narrow range of relative vapor pressures (in an adsorption refrigerator, this is the relative ratio of the evaporator vapor pressure to the adsorber vapor pressure during adsorption operation, and the relative ratio of the adsorber vapor pressure to the condenser vapor pressure during regeneration operation).Furthermore, the above-mentioned Japanese Patent No. 4,669,914 discloses that this particular zeolite-based adsorbent can be regenerated at 55°C under optimal operating conditions.

[0038] In order to verify the practical value of the descriptions in these patent documents, the inventors experimentally confirmed that the adsorption capacity of the zeolite adsorbent changes from 0% to 100% while changing the regeneration temperature from 40°C to 65°C under the condition that the cooling water temperature and the cold water temperature are normal temperatures taking into account seasonal variations. Therefore, the inventors obtained a fourth finding that the efficiency of the adsorption chiller can be controlled by controlling the temperature of the hot water fed into the adsorption chiller, that this is the main mechanism for adjusting the heat balance of the cold energy generation system, and that when the hot water temperature is within this range, it is possible to suppress the condensation temperature (condensation temperature) to 70°C or less by rationally designing the condenser.

[0039] The above first to fourth findings of the present disclosure can also be applied to a configuration in which a steam turbine generates power to drive other devices.

[0040] (Content of this disclosure) The present disclosure has been conceived based on the above first to fourth findings.

[0041] A cold energy generation system according to one aspect of the present disclosure includes a steam turbine device that generates power using a Rankine cycle that receives heat from a heat source, an adsorption refrigeration device that outputs cold energy to a cold energy load and releases refrigeration exhaust heat using an adsorption refrigeration cycle in which exhaust heat released by a first condenser that constitutes the Rankine cycle is used as a working heat source, and a heat balance control mechanism that controls the heat balance of the steam turbine device and the adsorption refrigeration device so that the condensation temperature of a first heat medium in the Rankine cycle is maintained within a first predetermined temperature range.

[0042] According to this configuration, the heat balance control mechanism controls the heat balance of the steam turbine device and the adsorption refrigeration device so that the condensation temperature of the first heat medium in the Rankine cycle is maintained within a first predetermined temperature range, so that the outlet pressure of the steam turbine (turbine back pressure) can be maintained within a range corresponding to the first predetermined temperature range of the condensation temperature of the first heat medium, and thus the compression ratio of the steam turbine can be maintained within a constant range. As a result, it is possible to prevent a decrease in the efficiency of the steam turbine, while utilizing the exhaust heat generated by driving the steam turbine to generate cold energy for a cold energy load, and thus a cold energy generation system capable of effectively utilizing the exhaust heat generated by driving the steam turbine can be provided.

[0043] The heat balance control mechanism may include a heat reception quantity acquisition device that acquires heat reception from the heat source, a cold heat quantity acquisition device that acquires a cold heat quantity to be output to the cold heat load, a condensation temperature correlated physical quantity sensor that detects a condensation temperature correlated physical quantity that correlates with the condensation temperature of the first heat medium, and a heat reception quantity control circuit that controls the amount of heat reception from the heat source in accordance with the output of cold heat to the cold heat load based on the amount of heat reception, the amount of cold heat, and the condensation temperature correlated physical quantity as the heat balance control, so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range.

[0044] According to this configuration, the heat reception control circuit controls the amount of heat received from the heat source in accordance with the output of cold heat to the cold heat load so that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range. Therefore, even if the amount of cold heat load of the cold heat load fluctuates, the amount of heat received from the heat source can be controlled to achieve heat balance between the steam turbine device and the adsorption refrigeration device so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range.

[0045] The heat balance control mechanism may include a cold energy quantity acquisition device that acquires the amount of cold energy to be output to the cold energy load, a condensation temperature correlated physical quantity sensor that detects a condensation temperature correlated physical quantity that correlates with the condensation temperature of the first heat medium, and a thermal COP control circuit that controls the thermal COP of the adsorption refrigeration device based on the amount of cold energy and the condensation temperature correlated physical quantity as the control of the heat balance, so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range and the cold energy corresponding to the cold energy load amount of the cold energy load is output.

[0046] According to this configuration, the thermal COP control circuit controls the thermal COP of the adsorption refrigeration device so that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range and cold energy is output according to the cold energy load amount of the cold energy load. Therefore, even if the cold energy load amount of the cold energy load fluctuates, the thermal COP of the adsorption refrigeration device can be controlled to thermally balance the steam turbine device and the adsorption refrigeration device so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range.

[0047] The first condenser may be a working heat source that releases heat by raising the temperature of a second heat medium through heat exchange with the first heat medium, and the adsorption refrigeration device may include a second heat medium circulation path that circulates the heated second heat medium through the first condenser and the adsorber so that the heated second heat medium heats an adsorbent that is contained in an adsorber that constitutes the adsorption refrigeration cycle and has adsorbed a refrigerant, and the thermal COP control circuit may include a second heat medium flow rate control circuit that controls the flow rate of the second heat medium flowing from the first condenser to the adsorber so that a temperature of the second heat medium flowing from the first condenser to the adsorber is maintained within a second predetermined temperature range, as control of the thermal COP.

[0048] Here, the thermal COP of the adsorption refrigerator can be reduced to a desired value by lowering the supply temperature of the second heat medium to the adsorption refrigerator. If the supply temperature of the second heat medium is lowered, the regeneration operation becomes incomplete, and the heat supplied to the adsorption refrigerator is not sufficiently converted into refrigeration output. As can be seen from (Equation 5), the supply temperature of the second heat medium can be reduced by increasing the fluid flow rate relative to the heat transport amount and reducing the temperature difference. The "temperature difference" is the temperature difference of the heat medium before and after receiving the transported heat. The "fluid flow rate" is the flow rate of the fluid per unit time. In the following, the flow rate per unit time will be simply referred to as "flow rate", and when special attention is required, it will be referred to as "flow rate (flow rate per unit time)".

[0049] (Equation 5): Heat transport rate (kJ / min) = fluid specific heat (kJ / kg K) × fluid flow rate (kJ / min) × temperature difference (K) In other words, by increasing the flow rate of the second heat medium flowing through the first condenser (secondary side), the temperature rise (temperature difference (K)) of the second heat medium due to the heat received from the first heat medium becomes smaller, thereby making it possible to lower the temperature of the second heat medium supplied to the adsorption refrigerator while still sufficiently removing the condensation waste heat, which is the heat transport amount, from the first condenser.

[0050] The second predetermined temperature range is set to a temperature range in which the condensation temperature of the first heat medium is maintained within the first predetermined temperature range. Such a second predetermined temperature range can be obtained by simulation, experiment, calculation, etc.

[0051] According to the above configuration, the second heat medium flow control circuit controls the flow rate of the second heat medium so that the temperature of the second heat medium flowing from the first condenser to the adsorber is maintained within the second predetermined temperature range, and therefore the thermal COP of the adsorption refrigerator is appropriately adjusted so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range.

[0052] The steam turbine device includes, as the Rankine cycle, a first evaporator that evaporates the first heat medium in liquid state by heat from the heat source to generate the first heat medium in vapor state, a steam turbine that generates rotational power by the first heat medium in vapor state, a first condenser that condenses the first heat medium in vapor state after rotating the steam turbine by heat exchange with a second heat medium to generate the first heat medium in liquid state, and a first heat medium circulation system that circulates the first heat medium to pass through the evaporator, the steam turbine, and the first condenser in this order. and a path for condensing the vapor refrigerant discharged from the adsorbent accommodated in the adsorber by heat exchange with the third heat medium to generate a liquid refrigerant. The adsorption refrigeration device includes, as the adsorption refrigeration cycle, an adsorber accommodating an adsorbent which adsorbs a vapor refrigerant in a state cooled by a third heat medium having a lowered temperature and which discharges the adsorbed refrigerant as vapor in a state heated by the second heat medium having a higher temperature through heat exchange with the first heat medium in a vapor state, a second condenser which condenses the vapor refrigerant discharged from the adsorbent accommodated in the adsorber by heat exchange with the third heat medium to generate a liquid refrigerant, and a fourth heat medium which condenses the liquid refrigerant by heat exchange with the fourth heat medium. a second evaporator that evaporates the third heat medium by heat exchange to generate the vapor-state refrigerant; a radiator that radiates heat to lower the temperature of the third heat medium that has been heated by heat exchange with the vapor-state refrigerant; a cold heat output device that outputs cold heat of the fourth heat medium that has been lowered by heat exchange with the liquid refrigerant to the cold heat load; a second heat medium circulation path that circulates the second heat medium through the first condenser and the adsorber; a third heat medium circulation path that circulates the third heat medium through the adsorber, the second condenser, and the radiator in this order; a fourth heat medium circulation path that circulates the refrigerant through the second evaporator and the cold heat output device; a refrigerant circulation path that circulates the refrigerant through the second evaporator, the adsorber, and the second condenser in that order; and an adsorption regeneration mechanism that connects the adsorber to the second evaporator and to the third heat medium circulation path during a process in which the adsorber adsorbs the refrigerant, and connects the adsorber to the second condenser and to the second heat medium circulation path during a process in which the adsorber releases the refrigerant and regenerates the refrigerant.

[0053] With this configuration, it is possible to specifically realize a cold energy generation system that can utilize the exhaust heat from the steam turbine to generate cold energy to supply to a cold energy load while preventing a decrease in the efficiency of the steam turbine drive.

[0054] The heat balance control mechanism may include a third heat medium flow control circuit that controls a flow rate of the third heat medium so that a temperature of the third heat medium flowing from the radiator to the adsorber is maintained within a third predetermined temperature range. Also, the heat balance control mechanism may include a fourth heat medium flow control circuit that controls a flow rate of the fourth heat medium so that a temperature of the fourth heat medium flowing from the cold heat output device to the second evaporator is maintained within a fourth predetermined temperature range.

[0055] Here, in order to stably output cold to the cold load, the heat generated by the cold load must be stably pumped to the refrigeration device, and for this to happen, the heat input from the first condenser as motive power and the pumped up heat must be stably discharged outside the adsorption refrigeration device. The heat exchange that takes place at this time is expressed by the following (Equation 6). The "temperature difference" in (Equation 6) refers to the temperature difference between the things exchanging heat with each other.

[0056] (Equation 6): Heat exchange amount (kJ) = Heat transfer coefficient (KJ / m 2 ·K) x heat exchange area (m 2 )× Temperature difference (K)

[0057] As is clear from (Equation 6), the fourth heat medium that absorbs the heat generated by the cold load and is returned to the adsorption refrigeration device must have a certain temperature difference with respect to the evaporation temperature of the refrigerant in the second evaporator, otherwise the heat generated by the cold load cannot be absorbed by the limited heat exchange area of ​​the evaporator. Similarly, if the temperature of the third heat medium that is discarded in the radiator and returned to the adsorption refrigeration device after refrigeration waste heat is not low enough, the adsorbent does not drop in temperature, causing the adsorption operation to be incomplete, and furthermore, the pressure in the second condenser does not drop sufficiently, preventing the transfer of refrigerant vapor from the adsorbent to the second condenser, causing the regeneration operation to be incomplete, and the adsorption refrigeration device does not fully demonstrate its refrigeration capacity. In other words, the temperature of the return fourth heat medium and the return third heat medium must be stable within a specified range, which is an implicit prerequisite for the heat pump operation of the adsorption refrigeration device. And it is clear from (Equation 5) that these temperatures can basically be maintained within a specified range by controlling the flow rate of the heat medium.

[0058] The third predetermined temperature range is set to a temperature range in which the adsorption and regeneration operations of the adsorber are sufficiently performed. The fourth predetermined temperature range is set to a temperature range in which the second evaporator is sufficiently able to absorb heat from the cold load. Such third and fourth predetermined temperature ranges can be obtained by simulation, experiment, calculation, etc.

[0059] According to the above configuration, the third heat medium flow control circuit controls the flow rate of the third heat medium flowing from the radiator to the adsorber so that the temperature of the third heat medium is maintained within a third predetermined temperature range, so that the adsorber performs adsorption and regeneration operations satisfactorily. Also, the fourth heat medium flow control circuit controls the flow rate of the fourth heat medium flowing from the cold heat output device to the second evaporator so that the temperature of the fourth heat medium is maintained within a fourth predetermined temperature range, so that the second evaporator sufficiently absorbs heat from the cold heat load. As a result, the heat pump operation of the adsorption refrigeration device is stably performed, and thus the adsorption refrigeration device exhibits sufficient refrigeration capacity while appropriately maintaining the heat balance of the cold heat generation system.

[0060] The cold generating system may include any one of temperature sensors or flow rate sensors of i) to ix) below, and the heat balance control mechanism may include a heat balance control circuit that controls the heat balance based on a temperature or flow rate detected by any one of temperature sensors or flow rate sensors of i) to ix) below: i) a temperature sensor that detects a temperature of the first heat medium flowing from the first condenser to the first evaporator, ii) a temperature sensor that detects a temperature of the first heat medium flowing from the first evaporator to the steam turbine, iii) a flow rate sensor that detects a flow rate of the first heat medium flowing from the first condenser to the first evaporator, iv) a temperature sensor that detects a temperature of the second heat medium flowing from the adsorber to the second condenser, v) a flow rate sensor that detects a flow rate of the second heat medium, vi) a temperature sensor that detects a temperature of the third heat medium flowing from the second condenser to the radiator, vii) a flow rate sensor that detects a flow rate of the third heat medium, viii) a temperature sensor that detects a temperature of the fourth heat medium flowing from the second evaporator to the cold output device, and ix) a flow rate sensor that detects a flow rate of the fourth heat medium.

[0061] As is clear from equation (5), the amount of heat transport can be easily calculated from the temperature difference between when a fluid flows into and out of a device and the circulating flow rate of the fluid. The relationship between steam temperature and specific enthalpy is a physical property value summarized in a steam table, and can be stored in the heat balance control circuit.

[0062] Therefore, according to the above configuration, the heat balance control circuit can directly calculate and obtain the heat received from the heat source, the heat supplied to the steam turbine, the heat supplied to the adsorption refrigeration device, the refrigeration waste heat, and the heat generated by the cold load from the stored information and the measured information. Furthermore, the heat balance control circuit can store experimental or theoretical values, such as the relationship between the supply temperature of the second heat medium, the supply temperature of the third heat medium, and the supply temperature of the fourth heat medium of the adsorption refrigeration device and the efficiency of the adsorption refrigeration device, and can also store experimental or theoretical values, such as the relationship between the outside air temperature and the radiator performance, and the relationship between the steam temperature and the power generation efficiency. In addition, the target temperature and flow rate of each heat medium can be instantly calculated for the target heat amount of the above-mentioned received heat, each supply heat, the refrigeration waste heat, and the heat generated by the cold load, and the operation amount of each actuator can be precisely and quickly controlled, thereby enabling high-level control such as maintaining the heat balance of the cold generation system at all times while reducing the auxiliary power of the cold generation system.

[0063] The adsorption refrigeration device may include three or more adsorbers each containing an adsorbent, and a refrigerant circulation path that constitutes the adsorption refrigeration cycle and circulates the refrigerant through a second evaporator and a second condenser, a second heat medium circulation path that circulates a second heat medium through the first condenser, and a third heat medium circulation path that circulates a third heat medium through the second condenser and a radiator so that the hot heat obtained in the second condenser is radiated by the radiator. The cold heat generation system may include an adsorption regeneration control mechanism that controls operation of the adsorption refrigeration device to sequentially perform an adsorption regeneration operation for the three or more adsorbers, in which each of the adsorbers is connected to the second evaporator and interposed between the radiator and the second condenser in the third heat medium circulation path so that the adsorbent adsorbs the refrigerant in an adsorption operation, and each of the adsorbers is connected to the second condenser and interposed in the second heat medium circulation path so that the adsorbent releases the refrigerant for regeneration.

[0064] Here, the adsorption refrigeration system generally includes a pair of adsorber, and an adsorption regeneration control mechanism controls the adsorption regeneration operation of the pair of adsorber so that while one adsorber performs an adsorption operation, the other adsorber performs a regeneration operation. In this case, even if a second heat medium of a constant temperature is fed into the adsorption refrigeration system, the discharge temperature of the second heat medium is not constant, and a sudden and large temperature change occurs, particularly at the timing when each adsorber switches between the adsorption operation and the regeneration operation. This sudden and large temperature change of the second heat medium causes a pressure shock in the back pressure of the steam turbine, and the pressure shock may damage the turbine blades.

[0065] However, according to the above configuration, the adsorption refrigeration system includes three or more adsorbers each containing an adsorbent, and the adsorption regeneration control mechanism controls the operation of the adsorption refrigeration system to sequentially perform the adsorption regeneration operation for the three or more adsorbers, in which each adsorber is connected to the second evaporator and inserted between the radiator and the second condenser in the third heat medium circulation path to adsorb the refrigerant in the adsorption operation, and each adsorber is connected to the second condenser and inserted in the second heat medium circulation path to release the refrigerant for regeneration. Since the adsorption regeneration operations of at least two adsorbers are shifted and partially overlap, the discharge temperature of the second heat medium is equalized and the pressure shock of the back pressure of the steam turbine is suppressed, thereby reducing the possibility of damage to the turbine blades.

[0066] The time Ta required for the adsorption operation for each of the adsorbers and the time Tr required for the regeneration operation may be the same for n adsorbers (n is an integer greater than or equal to 3), and the adsorption regeneration control mechanism may be capable of controlling the operation of the adsorption refrigeration device so that the adsorption regeneration operation for the n adsorbers is performed with a time shift of 1 / n (Tc / n) of the time Tc required for the adsorption regeneration operation (Tc=Ta+Tr).

[0067] According to this configuration, the adsorption regeneration operation for the n adsorber is performed with a shift of 1 / n of the time Tc required for the adsorption regeneration operation (Tc / n), so that the discharge temperature of the second heat medium fluctuates within the shifted time (Tc / n), but is uniformly averaged over the time axis. In addition, since the time Ta required for the adsorption operation and the time Tr required for the regeneration operation are the same, the discharge temperature of the second heat medium fluctuates within the shifted time (Tc / n), but is uniformly averaged over the time axis. As a result, pressure shock of the back pressure of the steam turbine is suitably suppressed.

[0068] The adsorption regeneration control mechanism includes an adsorption regeneration valve system that connects each of the adsorbers to the second evaporator and interposes it between the radiator and the second condenser in the third heat medium circulation path so that the adsorbents adsorb the refrigerant in the adsorption operation, and connects each of the adsorbers to the second condenser and interposes it in the second heat medium circulation path so that the adsorbents release the refrigerant in the regeneration operation, and an adsorption regeneration control circuit that controls the operation of the adsorption regeneration valve system to sequentially perform the adsorption regeneration operation for the three or more adsorbers. The adsorption refrigeration device includes a plurality of adsorption refrigerators, one radiator, and one cold energy output device that outputs the cold energy obtained in the second evaporator to the cold energy load, and each of the adsorption refrigerators connects each of the second evaporator, the third condenser, and the adsorbents to the second condenser and interposes it in the second heat medium circulation path. the adsorption chiller may comprise the above adsorption unit, the second condenser, the refrigerant circulation path, the second heat medium circulation path, the third heat medium circulation path, and the adsorption regeneration valve system, wherein the third heat medium circulation path of each of the plurality of adsorption chillers passes through one of the radiators, the second heat medium circulation path of each of the plurality of adsorption chillers passes through one of the first condensers or through a plurality of the first condensers, and the plurality of first condensers are provided on a plurality of branch paths of the first heat medium circulation path in the Rankine cycle of the steam turbine device, and the adsorption regeneration control circuit may be a control circuit that controls operation of the adsorption regeneration valve system of all of the adsorption chillers so as to sequentially perform the adsorption regeneration operation for the three or more adsorption units of all of the adsorption chillers.

[0069] This configuration can more effectively suppress the back pressure shock of the steam turbine, reduce the possibility of damage to the turbine blades, and can accommodate large-scale heat sources and cooling loads.

[0070] The time Ta required for the adsorption operation for each adsorber of each of the adsorption refrigerators and the time Tr required for the regeneration operation are the same for n (n is an integer of 3 or more) adsorber of m (m is an integer of 1 or more) adsorption refrigerators, and the adsorption regeneration control circuit may be capable of controlling the operation of the adsorption regeneration valve system of the m adsorption refrigerators so as to perform the adsorption regeneration operation for the n adsorber of each of the adsorption refrigerators with a shift of 1 / n time (Tc / n) of the time Tc (Tc=Ta+Tr) required for the regeneration operation, and to control the operation of the adsorption regeneration valve system of the m adsorption refrigerators with a shift of 1 / mn time (Tc / mn) of the time Tc required for the adsorption regeneration operation among the m (m is an integer of 1 or more).

[0071] With this configuration, it is possible to accommodate large-scale heat sources and cold loads, and the discharge temperature of the second heat medium is more evenly leveled over time, the pressure shock of the steam turbine back pressure is more effectively suppressed, and the possibility of damage to the turbine blades is more effectively reduced.

[0072] The adsorption refrigeration cycle may include a plurality of the adsorption refrigeration devices, and the operating heat source of the adsorption refrigeration cycle used by all of the adsorption refrigeration devices may be the first condenser of one of the steam turbine devices, or the first condensers may be provided in a plurality of branch paths of the circulation path of the first heat medium in the Rankine cycle of the steam turbine device, each corresponding to the plurality of adsorption refrigeration devices.

[0073] This configuration provides a cold generation system that can accommodate larger heat sources and cold loads and that better reduces the possibility of damage to the turbine blades.

[0074] A backup heat source for backing up the exhaust heat may be provided in a heat medium path that carries the exhaust heat from the first condenser to the adsorption refrigeration cycle of the adsorption refrigeration device.

[0075] According to this configuration, even if the steam turbine unit stops operating, the adsorption refrigeration unit can be operated using the backup heat source as a working heat source.

[0076] The adsorption refrigeration system may include a radiator for discharging the refrigeration waste heat, and the radiator may include a cooling tower and an electric heat pump.

[0077] With this configuration, the cooling tower can basically provide sufficient heat dissipation capacity, and the cooling tower's heat dissipation capacity, which varies with temperature and humidity, is assisted by the electric heat pump, making it possible to stably release refrigeration waste heat.

[0078] The cold energy generating system may include information and communication equipment, which is the cold energy load.

[0079] According to this configuration, an ideal heat load that always provides a demand for cold can be secured within the cold generating system.

[0080] The steam turbine device may include a generator that generates electricity using power generated using the Rankine cycle, and the generator and the information and communications equipment may be connected so that at least a portion of the electricity generated by the generator can be supplied to the information and communications equipment.

[0081] According to this configuration, it is possible to reduce reverse power flow when selling the generated electricity of the steam turbine device, which is a waste heat utilization facility of a heat source.

[0082] Hereinafter, specific embodiments of the present disclosure will be described with reference to the drawings. In the following, the same or corresponding elements are denoted by the same reference numerals throughout the drawings, and duplicated descriptions thereof will be omitted. In addition, since the following drawings are for explaining the present disclosure, elements unrelated to the present disclosure may be omitted, dimensions may be inaccurate due to exaggeration, or may be simplified, and shapes of corresponding elements in multiple drawings may not match, etc.

[0083] In addition, in the specification and claims of this application, the number of things (components, devices, etc.) will be expressed simply by numbers in order to simplify the expression.

[0084] Furthermore, the present disclosure is not limited to the following embodiments.

[0085] (Embodiment 1) Fig. 1 is a diagram showing an example of an outline of hardware of a cold energy generating system according to a first embodiment of the present disclosure. Fig. 2 is a functional block diagram showing an example of a configuration of a control system of the cold energy generating system of Fig. 1. Note that Fig. 2 shows a simplified view of the entire steam turbine device of Fig. 1, and also shows a simplified view of the adsorption chiller 200 of Fig. 1.

[0086] <Outline of the cold energy generation system 1000A configuration> 1, a cold energy generating system 1000A according to the first embodiment includes a steam turbine device 100, an adsorption refrigeration device 700, and a control device 300. The adsorption refrigeration device 700 includes an adsorption refrigerator 200, a radiator 400, and a cold energy output device 500.

[0087] The steam turbine device 100 is connected to the heat source 10 through a heat transfer structure at the first evaporator 101, and is connected to the adsorption chiller 200 through a second heat medium circulation path 211 at the first condenser 102. The adsorption chiller 200 is connected to the first condenser 102 of the steam turbine device 100 through the second heat medium circulation path 211 at the adsorber 202 described later, is connected to the radiator 400 through a third heat medium circulation path 212 at the adsorber 202 and the second condenser 204, and is connected to the cold heat output device 500 through a fourth heat medium circulation path 214 at the second evaporator 201. The radiator 400 radiates heat to a cooling body 401. The cold heat output device 500 outputs cold to a cold heat load 501. The control device 300 controls the operation of the cold heat generation system 1000A through a control system described later.

[0088] <Overview of operation of cold energy generation system 1000A> 1 and 2, the cold energy generating system 1000A is generally operated as follows under the control of the control device 300. In the following, the heat input to the cold energy generating system 1000A or output from the cold energy generating system 1000A is identified using symbols Q1 to Q5. The "heat quantities" of Q1 to Q5 are identified using symbols (Q1) to (Q5).

[0089] The steam turbine device 100 receives evaporator input heat Q1 from the heat source 10 in the first evaporator 101, and inputs turbine input heat Q2 out of the evaporator input heat Q1 to the steam turbine 103A to generate power. Then, the steam turbine device 100 discharges condensation exhaust heat Q3 that was not used for generating power in the steam turbine 103A to the second heat medium circulation path 211 in the first condenser 102. The adsorption chiller 200 uses the condensation waste heat Q3 discharged to the second heat medium circulation path 211 as a working heat source to cause the adsorber 202 to perform an adsorption and regeneration operation of the refrigerant. In the second evaporator 201, heat generation Q5 of the heating element of the cold heat load 501 is pumped up as cold heat output from the cold heat load 501 via the fourth heat medium circulation path 214 and the cold heat output device 500, and refrigeration waste heat Q4 is discharged to the cooling body 401 in the adsorber 202 and the second condenser 204 via the third heat medium circulation path 212 and the radiator 400.

[0090] The components of the above-mentioned cold generating system 1000A will be described below in the order of the hardware configuration and the control system configuration.

[0091] <Hardware configuration> <Steam turbine device 100> 2, the steam turbine device 100 includes a Rankine cycle 110. The Rankine cycle 110 includes a first evaporator 101, a steam turbine 103A, a first condenser 102, a first heat medium tank 105, and a first heat medium circulation path 106.

[0092] {First evaporator 101} The first evaporator 101 evaporates the liquid first heat medium by the evaporator input heat Q1 received from the heat source 10 to generate the vapor first heat medium. Hereinafter, the amount of heat of the evaporator input heat Q1 may be referred to as the "amount of received heat (Q1)". The first evaporator 101 is not particularly limited as long as it can evaporate the heat medium, and a known heat medium evaporator can be used as the first evaporator 101. For example, a boiler can be used as the first evaporator 101.

[0093] [Heat source 10] The heat source 10 is not particularly limited. Examples of the heat source 10 include a geothermal energy utilization facility, a solar energy utilization facility, a factory, and a waste incineration facility (waste disposal plant). Examples of the factory include a chemical plant, a steel mill, a paper factory, and a general factory. The heat source 10 transmits the amount of heat generated or the amount of exhaust heat to the heat reception amount acquisition unit 340 as heat reception amount data described later. The heat source 10 also has a heat generation amount control unit 11, and receives a heat generation amount control command from the heat reception amount control circuit 320 of the control device 300 of the cold heat generation system 1000A, and controls the amount of heat generated or the amount of exhaust heat based on the command. Note that, as a mechanism for adjusting the amount of exhaust heat from the heat source 10, a mechanism for adjusting the flow rate of the heat medium (for example, a flow rate adjustment valve) may be provided in the flow path of the heat medium that transports the exhaust heat from the heat source 10 to the first evaporator 101.

[0094] [First heat medium] The first heat medium is pure water in a normal Rankine cycle 110, and in rare cases, an organic solvent such as pentane or hexane is used for the purpose of operating with a low-temperature heat source (organic Rankine cycle). The present disclosure is applicable to both the normal Rankine cycle 110 and the organic Rankine cycle.

[0095] {Steam turbine 103A} The steam turbine 103A generates rotational power by a first heat medium in a vapor state. The steam turbine 103A is not particularly limited, and a known steam turbine can be used as the steam turbine 103A. The rotating shaft of the steam turbine 103A is connected to the power unit 103B, and the steam turbine 103A drives the power unit 103B by the rotational power. The steam turbine 103A and the power unit 103B configure the steam turbine unit 103. The power unit 103B is a device that performs work by power, and examples of the power unit include a generator and a machine tool. Here, the power unit 103B is configured by a generator. Hereinafter, the generator as the power unit will be referred to as "generator 103B".

[0096] {First condenser 102} The first condenser 102 condenses the first heat medium in a vapor state after rotating the steam turbine 103A by heat exchange with the second heat medium to generate the first heat medium in a liquid state. The first condenser 102 is composed of a heat exchanger, and the first heat medium flows through a primary flow path and the second heat medium flows through a secondary flow path. A known condenser can be used as the first condenser 102.

[0097] {First heat medium tank 105} The first heat medium tank 105 temporarily stores the first liquid heat medium produced in the first condenser 102. The first heat medium tank 105 is not particularly limited, and a known heat medium tank can be used as the first heat medium tank 105.

[0098] {First heat medium circulation path 106} The first heat medium circulation path 106 includes a first heat medium circulation flow path and a first heat medium pump 104. The first heat medium circulation flow path is a closed flow path that extends from the outlet of the first evaporator 101, passes through the steam turbine 103A, the primary side flow path of the first condenser 102, and the first heat medium tank 105, and returns to the inlet of the first evaporator 101. The first heat medium pump 104 is provided between the first heat medium tank 105 and the first evaporator 101 in the first heat medium circulation flow path. The first heat medium pump 104 pumps the liquid first heat medium toward the first evaporator 101, thereby circulating the first heat medium through the first heat medium circulation flow path. The first heat medium pump 104 is not particularly limited as long as it can pump the fluid while controlling the flow rate, and a known fluid pump can be used as the first heat medium pump 104.

[0099] <Second heat medium circulation path> The second heat medium circulation path 211 includes a second heat medium circulation flow path and a second heat medium pump 221. The second heat medium circulation flow path is a closed flow path that extends from the outlet of the secondary side flow path of the first condenser 102, passes through the first and second adsorbers 202A and 202B arranged in parallel to each other of the adsorption chiller 200, and returns to the inlet of the secondary side flow path of the first condenser 102. The second heat medium pump 221 is provided between the first and second adsorbers 202A and 202B arranged in parallel to each other and the inlet of the first condenser 102 in the second heat medium circulation flow path. The second heat medium pump 221 pumps the second heat medium toward the inlet of the secondary side flow path of the first condenser 102, thereby circulating the second heat medium through the second heat medium circulation flow path. The second heat medium pump 221 is not particularly limited as long as it can pump a fluid while controlling the flow rate, and a known fluid pump can be used as the second heat medium pump 221.

[0100] Due to the operating principle of the adsorption refrigerator 200, the second heat medium and the third heat medium inevitably mix in small amounts during the adsorption and regeneration operations. Therefore, the second heat medium needs to be substantially the same as the third heat medium, and for reasons described below, the third heat medium is water, and therefore the second heat medium is also water.

[0101] <Adsorption refrigerator> The adsorption chiller 200 includes an adsorption refrigeration cycle 210. The adsorption refrigeration cycle 210 includes a second evaporator 201, first and second adsorption devices 202A and 202B, a second condenser 204, a refrigerant circulation path 213, and an adsorption regeneration valve system 209.

[0102] {Second evaporator 201} The second evaporator 201 evaporates the liquid refrigerant through heat exchange with the fourth heat medium to generate a vapor refrigerant. The refrigerant is not particularly limited as long as it is a low-temperature heat medium. Pure water is used as the refrigerant. The second evaporator 201 is not particularly limited as long as it can evaporate the refrigerant, and a known refrigerant evaporator can be used as the second evaporator 201.

[0103] {Adsorber 202} The first and second adsorption devices 202A and 202B are both sealed containers having a refrigerant inlet, a refrigerant outlet, a heating / cooling medium inlet, and a heating / cooling medium outlet, and each accommodates an adsorption body 203A or 203B. In the following (including other embodiments), when the plurality (here, two) of adsorption devices 202A and 202B are collectively referred to, they are referred to as adsorption devices 202. When the plurality (here, two) of adsorption devices 203A and 203B are collectively referred to, they are referred to as adsorption bodies 203. The adsorption body of the i-th adsorption device may be referred to as the i-th adsorption device. i is an integer of 1 or more. In accordance with the principle of the adsorption refrigerator, the number of the adsorption devices 202 is not particularly limited, and may be 1. However, the number of the adsorption devices 202 is usually 2. This is because while one of the first and second adsorption devices 202A and 202B performs an adsorption operation and a regeneration operation, the other can perform a regeneration operation and an adsorption operation, and continuous refrigeration output can be obtained by continuously compressing the refrigerant.

[0104] The adsorbent 203 is made of, for example, a material such as silica gel, zeolite, etc. In particular, zeolite is preferable as a material for forming the adsorbent 203 for the following reasons.

[0105] [Zeolite] As described in the fourth finding, Japanese Patent No. 4,669,914 states that a specific zeolite-based adsorbent can be regenerated at 55°C under optimal operating conditions. The present inventor experimentally confirmed that the adsorption capacity of the zeolite-based adsorbent changes from 0% to 100% while the regeneration temperature changes from 40°C to 65°C under the condition that the temperature of the cooling water (third heat medium) and the temperature of the cold water (fourth heat medium) are normal temperatures taking into account seasonal fluctuations. Therefore, the inventor has found that the control of the temperature of the hot water (second heat medium) input into the adsorption refrigerator is the main adjustment mechanism for the heat balance of the cold generation system, and that when the temperature of the hot water (second heat medium) is in this range, it is possible to suppress the condensate temperature (condensation temperature of the first heat medium) to 70°C or less by rationally designing the condenser (first condenser). Therefore, it is preferable to configure the adsorbent 203 with a material such as zeolite.

[0106] [Adsorbent 203] The adsorbent 203 adsorbs the vapor refrigerant when cooled by the third heat medium whose temperature has been reduced, and releases (desorbs) the adsorbed refrigerant as vapor (gas) when heated by the second heat medium whose temperature has been increased by heat exchange with the first heat medium in the vapor state.

[0107] {Second condenser 204} The second condenser 204 condenses the vapor refrigerant released from the adsorbent 203 through heat exchange with the third heat medium to generate a liquid refrigerant. The second condenser 204 is composed of a heat exchanger, in which the refrigerant flows through a primary flow path and the third heat medium flows through a secondary flow path. A known refrigerant condenser can be used as the second condenser 204.

[0108] {Refrigerant circulation path 213} The refrigerant circulation path 213 includes a refrigerant circulation flow path and a refrigerant pump 223. The refrigerant circulation flow path is a closed flow path formed so as to extend from the outlet of the second evaporator 201, pass through the adsorber 202 and the primary side flow path of the second condenser 204, and return to the inlet of the second evaporator 201. The refrigerant pump 223 is provided between the second condenser 204 and the second evaporator 201 in the refrigerant circulation flow path. The refrigerant pump 223 pumps the liquid refrigerant toward the inlet of the second evaporator 201, thereby circulating the refrigerant through the refrigerant circulation flow path. The refrigerant pump 223 is not particularly limited as long as it can pump the fluid while controlling the flow rate, and a known fluid pump can be used as the refrigerant pump 223.

[0109] {Adsorption regeneration valve system 209} The adsorption regeneration valve system 209, together with the operation control circuit 330, constitutes an adsorption regeneration control mechanism, and under the control of the operation control circuit 330, in an adsorption operation, each of the adsorbers 202A, 202B is connected to the second evaporator 201 and interposed between the radiator 400 and the second condenser 204 in the third heat medium circulation path 212 so that the adsorbents 203A, 203B adsorb the refrigerant, and in a regeneration operation, each of the adsorbers 202A, 202B is connected to the second condenser 204 and interposed in the second heat medium circulation path 211 so that the adsorbents 203A, 203B release the refrigerant to be regenerated.

[0110] Specifically, the adsorption regeneration valve system 209 includes first and second inlet side refrigerant on-off valves 205A, 205B, first and second outlet side refrigerant on-off valves 206A, 206B, first and second inlet side heat medium switching valves 207A, 207B, and first and second outlet side heat medium switching valves 208A, 208B.

[0111] The first and second inlet side refrigerant on-off valves 205A, 205B are both configured as on-off valves, and are respectively interposed between the refrigerant inlets of the first and second adsorption devices 202A, 202B and the second evaporator 201 in the refrigerant circulation flow path.

[0112] The first and second outlet side refrigerant on-off valves 206A, 206B are both configured as on-off valves and are respectively interposed between the refrigerant outlets of the first and second adsorption devices 202A, 202B and the second condenser 204 in the refrigerant circulation flow path.

[0113] The first and second inlet side heat medium switching valves 207A, 207B are both configured as three-way valves, with their first ports connected to the heating / cooling heat medium inlets of the first and second adsorption devices 202A, 202B, respectively, their second ports connected to the outlet of the secondary side flow path of the first condenser 102 via a second heat medium circulation flow path described later, and their third ports connected to the outlet of the radiator via a third heat medium circulation flow path described later.

[0114] The first and second outlet side heat medium switching valves 208A, 208B are both configured as three-way valves, with their first ports connected to the heating / cooling heat medium outlets of the first and second adsorption devices 202A, 202B, respectively, their second ports connected to the inlet of the secondary side flow path of the first condenser 102 via a second heat medium circulation flow path described later, and their third ports connected to the inlet of the second condenser 204 via a third heat medium circulation flow path described later.

[0115] <Radiator 400> The radiator 400 radiates heat from the third heat medium, which has been heated by heat exchange with the vapor-state refrigerant in the second condenser 204, through heat exchange with the cooling body 401, thereby lowering the temperature.

[0116] The radiator 400 is not particularly limited as long as it can exchange heat between the heat medium and the cooling body 401. Examples of the radiator 400 include a cooling tower (open type heat exchanger), an electric heat pump, and a closed type heat exchanger. The cooling body 401 is not particularly limited as long as it can cool the heat medium. Examples of the cooling body 401 include air (atmosphere), water, and the like.

[0117] <Third heat transfer medium circulation route> The third heat medium circulation path 212 includes a third heat medium circulation flow path and a third heat medium pump 222. The third heat medium circulation flow path is a closed flow path that extends from the outlet of the radiator 400, passes through the first and second adsorbers 202A, 202B arranged in parallel with each other of the adsorption chiller 200, and a secondary side flow path of the second condenser 204, and returns to the inlet of the radiator 400. The third heat medium pump 222 is provided in the third heat medium circulation flow path between the outlet of the radiator 400 and the first and second adsorbers 202A, 202B arranged in parallel with each other. The third heat medium pump 222 pumps the third heat medium toward the first and second adsorbers 202A, 202B, thereby circulating the third heat medium through the third heat medium circulation flow path. The third heat medium pump 222 is not particularly limited as long as it can pump a fluid while controlling the flow rate, and a known fluid pump can be used as the third heat medium pump 222.

[0118] The third heat medium is water. This is because a system in which the third heat medium is water, the radiator 400 is a cooling tower (open type heat exchanger), and the cooling body 401 is air (atmosphere), and in which heat is radiated and cooled to the atmosphere using the latent heat of vaporization of the third heat medium, is common and preferable.

[0119] <Cold heat output device 500> The cold energy output device 500 outputs the cold energy of the fourth heat medium, the temperature of which has been lowered by heat exchange with the liquid refrigerant, to the cold energy load 501. The cold energy output device 500 may transmit cold energy amount data to the cold energy amount acquisition unit 350, which will be described later.

[0120] The cold heat output device 500 is not particularly limited as long as it can exchange heat with the heat generating element of the cold heat load 501. A general example of the cold heat output device 500 is a heat exchanger, and a specific example is an indoor unit of an air conditioning facility (regardless of size). Examples of the cold heat load 501 include a DC, a food factory, a general factory, etc. The cold energy load 501 may transmit cold energy amount data, which will be described later, to the cold energy amount acquisition unit 350 .

[0121] <Fourth heat medium circulation route> The fourth heat medium circulation path 214 includes a fourth heat medium circulation flow path and a fourth heat medium pump 224. The fourth heat medium circulation flow path is a closed flow path that extends from the outlet of the secondary side flow path of the second evaporator 201, passes through the cold heat output device 500, and returns to the inlet of the secondary side flow path of the second evaporator 201. The fourth heat medium pump 224 is provided between the cold heat output device 500 and the inlet of the second evaporator 201 in the fourth heat medium circulation flow path. The fourth heat medium pump 224 pumps the fourth heat medium toward the inlet of the secondary side flow path of the second evaporator 201, thereby circulating the fourth heat medium through the fourth heat medium circulation flow path. The fourth heat medium pump 224 is not particularly limited as long as it can pump the fluid while controlling the flow rate, and a known fluid pump can be used as the fourth heat medium pump 224.

[0122] Examples of the fourth heat medium include water and antifreeze liquid. When the fourth heat medium is water, there is a possibility that it is cooled and frozen in the second evaporator 201, but this is not the case with antifreeze liquid, so it is preferable that the fourth heat medium is antifreeze liquid.

[0123] <Control device 300> The control device 300 is disposed at an appropriate location in the cold energy generating system 1000A. The control device 300 includes a computer and a communication device for communicating with each control element. The computer includes a processor Pr and a memory Me. The control device 300 controls the operation of the cold energy generating system 1000A. The control device 300 may be configured as a single control device performing centralized control, or may be configured as multiple control devices performing distributed control. The detailed configuration and operation of the control device 300 will be described below.

[0124] <Control system configuration> Referring to FIG. 2, the control system of the cold generating system 1000A includes a control device 300 and a first heat medium temperature sensor 601.

[0125] <Control device 300> The control device 300 includes a system control circuit 310, a received heat amount acquisition unit 340, and a cold heat amount acquisition unit 350. The control device 300 includes a system control circuit 310, a received heat amount control circuit 320, and an operation control circuit 330. The system control circuit 310, the received heat amount acquisition unit 340, and the cold heat amount acquisition unit 350 each include a communication unit and a processing unit, and receive or transmit data that is to be processed or has been processed by the processing unit via the communication unit.

[0126] The processing units of the system control circuit 310, the received heat amount acquiring unit 340, and the cold heat amount acquiring unit 350 are functional blocks (functional modules) that are realized by the processor Pr reading and executing a dedicated control program stored in the memory Me.

[0127] Examples of a computer including a processor Pr and a memory Me include a microcontroller, an MPU, a field programmable gate array (FPGA), and a programmable logic controller (PLC).

[0128] The functions of the control elements disclosed herein can be performed using circuits or processing circuits, including general purpose processors, special purpose processors, integrated circuits, ASICs (Application Specific Integrated Circuits), conventional circuits, and / or combinations thereof, configured or programmed to perform the disclosed functions. The processor Pr is considered a processing circuit or circuit because it includes transistors and other circuits. In this disclosure, a "circuit", "unit", or "part" is hardware that performs the recited functions or hardware that is programmed to perform the recited functions. The hardware may be hardware disclosed herein or other known hardware that is programmed or configured to perform the recited functions. In the case of the processor Pr, where the hardware is considered a type of circuit, the "circuit", "unit", or "part" is a combination of hardware and software, and the software is used to configure the hardware and / or the processor Pr.

[0129] {Heat reception control circuit 320} The heat reception amount control circuit 320 controls the amount of heat received (Q1) from the heat source 10 according to the output of cold heat to the cold heat load 501 so that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range, based on the condensation temperature of the first heat medium detected by the first heat medium temperature sensor 601, the amount of heat received data acquired by the heat reception amount acquisition unit 340, and the amount of cold heat data acquired by the cold heat amount acquisition unit 350. The heat reception amount control circuit 320 transmits a heat generation amount control command to the heat generation amount control unit 11 of the heat source 10, and controls the heat generation amount (Q1) or the amount of exhaust heat (Q1) of the heat source 10 based on the heat generation amount control command received by the heat generation amount control unit 11.

[0130] The first predetermined temperature range is determined in consideration of the allowable range of efficiency of the steam turbine 103A of the steam turbine device 100. The first predetermined temperature range is, for example, 20°C or more and 70°C or less. If the condensation temperature of the first heat medium is 70°C or less, the decrease in efficiency of the steam turbine 103A can be suppressed within the allowable limit. Also, if the condensation temperature of the first heat medium is 70°C or less, the necessary temperature difference can be set in consideration of the preferable temperature range of the second heat medium (40°C to 65°C), and the first condenser 102 can be designed in a reasonable range of heat transfer area. On the other hand, the lower limit temperature of the first predetermined temperature range is governed by the temperature of the cooling body 401. The reason is as follows. In the adsorption regeneration operation, the adsorbent 203 is heated by the second heat medium and cooled by the third heat medium, so that the temperature of the second heat medium is higher than that of the third heat medium. And, in the adsorption refrigeration cycle, the third heat medium is cooled by the cooling body 401, so that the temperature of the third heat medium is higher than that of the cooling body 401. Therefore, in order to design the temperature of the second heat medium to be low, it is necessary to design the temperature of cooling body 401 to be low.

[0131] The practical lower limit temperature of the cooling body 401 is about 10° C. of groundwater. Therefore, if the first predetermined temperature range is 20° C. or higher, the efficiency of the steam turbine 103A can be maintained at a good level without any practical problems. The heat receiving amount control circuit 320 stores this first predetermined temperature range in the storage unit in advance.

[0132] The heat received amount control circuit 320 is an example of an aspect of the heat balance control circuit in embodiment 1. The heat balance control circuit constitutes a heat balance control mechanism together with the first heat medium temperature sensor 601, the heat received amount acquisition unit 340, and the cold heat amount acquisition unit 350, and controls the heat balance of the steam turbine device 100 and the adsorption refrigeration device 700 so that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range.

[0133] {Operation control circuit 330} The operation control circuit 330 controls operations other than the heat balance of the cold generation system 1000A. In particular, the operation control circuit 330 controls the operation of the adsorption regeneration valve system 209. Therefore, the operation control circuit 330 and the adsorption regeneration valve system 209 constitute an adsorption regeneration control mechanism.

[0134] {Received heat amount acquisition unit 340} In the received heat amount acquisition unit 340, the heat receiving communication unit receives the received heat amount data from the heat source 10, and the received heat amount processing unit appropriately processes the received received heat amount data, such as temporarily storing it.

[0135] The received heat amount data is data indicating the amount of evaporator input heat Q1 discharged from the heat source 10 and received by the first evaporator 101 of the steam turbine device 100. Specifically, for example, if the heat source 10 is a waste incineration facility, the received heat amount data may include the amount of waste input. If the heat source 10 is a factory, the received heat amount data may include the flow rate of a heat medium (e.g., hot water) that carries the exhaust heat from the factory. The received heat amount acquisition unit 340 may use these received heat amount data as the "received heat amount (Q1)" as is, or may convert these received heat amount data into heat amount to use it as the "received heat amount (Q1)".

[0136] {Cold heat amount acquisition unit 350} In the cold energy amount acquiring unit 350, the cold energy communication unit receives cold energy amount data from the cold energy load 501 or the cold energy output device 500, and the cold energy amount processing unit appropriately processes the received cold energy amount data, such as temporarily storing it.

[0137] The cold energy amount data is data indicating the amount of heat of the heat generating body Q5 that the heat generating body of the cold energy load 501 releases in exchange for the cold energy supplied from the cold energy output device 500. In other words, the cold energy amount data is data indicating the amount of heat of the heat generating body Q5 that the cold energy output device 500 pumps up from the cold energy load 501. Therefore, hereinafter, the "amount of heat of the heat generating body Q5" may be referred to as the "amount of cold energy (Q5)". Specifically, for example, when the cold energy load 501 is a DC, the cold energy amount data may include the power consumption of the DC. For example, when the cold energy load 501 is a factory, the cold energy amount data may include the power consumption of the air conditioning equipment as the cold energy output device 500 of the factory. For example, when the cold energy load 501 is a food factory and the cold energy output device 500 is a large-scale refrigeration equipment of the food factory, the cold energy amount data may include the flow rate of the refrigerant of the refrigeration equipment. The cold energy amount acquiring unit 350 may use these cold energy amount data as "cold energy amount (Q5)" as it is, or may convert these cold energy amount data into heat amount (negative heat amount) and use it as "cold energy amount (Q5)".

[0138] {First heat medium temperature sensor 601} The first heat medium temperature sensor 601 is an example of an aspect of the condensation temperature correlated physical quantity sensor in the first embodiment. The first heat medium temperature sensor 601 detects the condensation temperature of the first heat medium of the steam turbine device 100. Specifically, the first heat medium temperature sensor 601 is provided between the steam turbine 103A and the first condenser 102 in the first heat medium flow path. The first heat medium temperature sensor 601 is not particularly limited as long as it is a temperature sensor. Examples of the first heat medium temperature sensor 601 include a resistance temperature detector, a thermocouple, a radiation thermometer such as an infrared sensor, and the like.

[0139] <Operation of cold energy generation system 1000A> <General operation> First, a general operation of the cold generation system 1000A will be described. This operation is performed by the operation control circuit 330 controlling the control elements of the cold generation system 1000A (particularly, the first to fourth heat medium pumps 104, 221, 222, 224 and the adsorption regeneration valve system 209).

[0140] 1 and 2, in the steam turbine device 100, the first evaporator 101 evaporates a first heat medium by the evaporator input heat Q1 received from the heat source 10. The first heat medium circulation path 106 transports the turbine input heat Q2 to the steam turbine 103A by the vaporized first heat medium. The steam turbine 103A rotates the generator 103B to cause the generator 103B to generate electric power E1. The first heat medium circulation path 106 transports the vaporized first heat medium discharged from the steam turbine 103A to the first condenser 102. The first condenser 102 condenses the vaporized first heat medium. The first heat medium circulation path 106 returns the condensed liquid first heat medium to the first evaporator 101 through the first heat medium tank 105 and the first heat medium pump 104.

[0141] Meanwhile, in the adsorption refrigeration system 700, the cold heat output device 500 outputs cold heat to the cold heat load 501, and at that time receives heat Q5 from the heating element from the cold heat load 501 in exchange for the cold heat output. The fourth heat medium circulation path 214 transports this heat Q5 from the heating element to the second evaporator 201 by the fourth heat medium. The second evaporator 201 evaporates the refrigerant by the heat Q5 from the heating element.

[0142] The radiator 400 also exchanges heat between the third heat medium and the cooling body 401 to radiate the refrigeration waste heat Q4, thereby lowering the temperature of the third heat medium. The third heat medium circulation path 212 transports the cooled third heat medium to the first and second adsorption devices 202A, 202B.

[0143] Furthermore, the first condenser 102 exchanges heat between the first heat medium and the second heat medium to condense the first heat medium, thereby discharging condensation waste heat Q3 that has not been used to drive the steam turbine 103A. The second heat medium circulation path 211 transports the condensation waste heat Q3 to the first and second adsorption devices 202A and 202B by the second heat medium.

[0144] Here, the adsorption regeneration valve system 209 causes the first and second adsorption devices 202A, 202B to perform an "adsorption operation" and a "regeneration operation." The "adsorption operation" is an operation in which the adsorbent 203 in the adsorption device 202 adsorbs the refrigerant as vapor from the second evaporator 201, thereby removing the latent heat of vaporization of the vapor from the second evaporator 201 to generate refrigeration output. The "regeneration operation" is an operation in which the adsorbent 203 in the adsorption device 202 releases the refrigerant adsorbed in the adsorption operation as vapor, thereby regenerating the adsorption function of the adsorbent 203.

[0145] The adsorption regeneration valve system 209, for example, opens the first inlet side refrigerant on-off valve 205A and closes the first outlet side refrigerant on-off valve 206A in a first half cycle of the cycle time of the adsorption regeneration operation of the first and second adsorption devices 202A, 202B (hereinafter simply referred to as the “adsorption regeneration operation cycle time”) to connect the first adsorption device 202A to the second evaporator 201, and switches the connection destination of the inlet of the first adsorption device 202A to the third heat medium circulation path 212 by the first inlet side heat medium switching valve 207A, and switches the connection destination of the outlet of the first adsorption device 202A to the third heat medium circulation path 212 by the first outlet side heat medium switching valve 208A, thereby interposing the first adsorption device 202A between the radiator 400 and the second condenser 204 in the third heat medium circulation path 212. As a result, the adsorbent 203A of the first adsorption device 202A is cooled by the third heat medium and adsorbs the vapor-state refrigerant from the second evaporator 201.

[0146] Furthermore, in the first half cycle of the adsorption regeneration operation cycle time, the adsorption regeneration valve system 209 closes the second inlet side refrigerant on-off valve 205B and opens the second outlet side refrigerant on-off valve 206B to connect the second adsorber 202B to the second condenser 204, and switches the connection destination of the inlet of the second adsorber 202B to the second heat medium circulation path 211 by the second inlet side heat medium switching valve 207B and switches the connection destination of the outlet of the second adsorber 202B to the second heat medium circulation path 211 by the second outlet side heat medium switching valve 208B, thereby inserting the second adsorber 202B into the second heat medium circulation path 211. As a result, the adsorbent 203B of the second adsorber 202B is heated by the second heat medium and releases the adsorbed refrigerant.

[0147] Thereafter, in the latter half of the adsorption regeneration operation cycle time, the adsorption regeneration valve system 209 closes the first inlet side refrigerant on-off valve 205A and opens the first outlet side refrigerant on-off valve 206A to connect the first adsorber 202A to the second condenser 204, and switches the connection destination of the inlet of the first adsorber 202A to the third heat medium circulation path 212 by the first inlet side heat medium switching valve 207A and switches the connection destination of the outlet of the first adsorber 202A to the second heat medium circulation path 211 by the first outlet side heat medium switching valve 208A, thereby inserting the first adsorber 202A into the second heat medium circulation path 211. As a result, the adsorbent 203A of the first adsorber 202A is heated by the second heat medium and releases the adsorbed refrigerant.

[0148] Further, in the latter half of the adsorption regeneration operation cycle time, the adsorption regeneration valve system 209 opens the second inlet side refrigerant on-off valve 205B and closes the second outlet side refrigerant on-off valve 206B to connect the second adsorber 202B to the second evaporator 201, and switches the connection destination of the inlet of the second adsorber 202B to the third heat medium circulation path 212 by the second inlet side heat medium switching valve 207B and switches the connection destination of the outlet of the second adsorber 202B to the third heat medium circulation path 212 by the second outlet side heat medium switching valve 208B, thereby interposing the second adsorber 202B between the radiator 400 and the second condenser 204 in the third heat medium circulation path 212. As a result, the adsorbent 203B of the second adsorber 202B is cooled by the third heat medium and adsorbs the vapor-state refrigerant from the second evaporator 201.

[0149] The second condenser 204 exchanges heat with a third heat medium to condense the vapor refrigerant released from the adsorbent 203A of the first adsorber 202A or the adsorbent 203B of the second adsorber 202B. The refrigerant circulation path 213 sends the condensed liquid refrigerant to the second evaporator 201 by the refrigerant pump 223.

[0150] Further, the third heat medium circulation path 212 transports heat obtained by the third heat medium cooling the adsorbent 203A of the first adsorber 202A or the adsorbent 203B of the second adsorber 202B and exchanging heat with the refrigerant in the second condenser 204 to the radiator 400 by the third heat medium. The radiator 400 radiates the transported heat to the cooling body 401 as refrigeration waste heat Q4.

[0151] In this way, the adsorption chiller 200 uses the condensation waste heat Q3 discharged to the second heat medium circulation path 211 as a working heat source to cause the adsorber 202 to perform refrigerant adsorption and regeneration operation. In the second evaporator 201, heat generation Q5 of the heating element of the cold heat load 501 is pumped up as cold heat output from the cold heat load 501 via the fourth heat medium circulation path 214 and the cold heat output device 500, and refrigeration waste heat Q4 is discharged to the cooling body 401 in the adsorber 202 and the second condenser 204 via the third heat medium circulation path 212 and the radiator 400.

[0152] <Heat balance control> Next, the heat balance control will be described. This heat balance control is performed by a heat reception amount control circuit 320 which is an example of the heat balance control circuit according to the first embodiment.

[0153] {The principle of heat balance} Referring to FIG. 2, the first heat medium circulation path 106 is a Rankine cycle circuit that receives evaporator input heat Q1 from the heat source 10, inputs turbine input heat Q2 out of the evaporator input heat Q1 to the steam turbine 103A, and discharges condensation exhaust heat Q3 that is not used for generating power in the steam turbine 103A from the first condenser 102.

[0154] The second heat medium circulation path 211 is a circuit that circulates a second heat medium for heating used in the regeneration operation of the adsorption refrigeration device 700. The second heat medium is heated by condensation exhaust heat Q3 in the first condenser 102 and supplied to the adsorption refrigeration device 700, and after heat consumption in the adsorption refrigeration device 700, returns to the first condenser 102.

[0155] The third heat medium circulation path 212 is a circuit that circulates the third heat medium for cooling used in the adsorption operation of the adsorption refrigeration device 700. The third heat medium is heated by the adsorption refrigeration device 700, and then the third heat medium is radiated by the radiator 400 as refrigeration waste heat Q4.

[0156] The fourth heat medium circulation path 214 is a circuit that circulates the fourth heat medium that carries the cold energy of the adsorption refrigeration device 700. The fourth heat medium outputs the cold energy generated in the second evaporator 201 to the cold energy load 501 in the cold energy output device 500, and at the same time, receives heat energy Q5 from the heating element of the cold energy load 501 in exchange for the cold energy, and carries this heat energy back to the second evaporator 201.

[0157] In the cold heat generation system 1000A, a series of Rankine cycle operations are performed by the heat transfer through these four types of heat medium circulation paths 106, 211, 212, 214, in which the steam turbine 103A of the primary cycle drives the power unit (here, the generator) 103B using the turbine input heat Q2 from the first evaporator 101 as power, and the first condenser 102 discharges condensation waste heat Q3, and the adsorption refrigeration device 700 of the secondary cycle generates refrigeration output using the condensation waste heat Q3 from the first condenser 102 as a working heat source, and this refrigeration output is used to pump up heat generation Q5 from the heating element of the cold heat load 501, and the refrigeration waste heat Q4 is discharged outside the system, thereby performing a series of heat pump operations.

[0158] When the overall utilization efficiency of the cold energy generation system 1000A is ε1, the energy efficiency of the power unit 103B (here, the power generation efficiency of the turbine generator) is ε2, and the thermal COP of the adsorption refrigeration unit 700 is ε3, the following relationship holds for the evaporator input heat Q1, the turbine input heat Q2, the condensation waste heat Q3, the refrigeration waste heat Q4, and the heat generation amount Q5 of the heating element when the cold energy generation system 1000A is in thermal balance. Here, (Equation 10) is the law of conservation of energy in the operation of the heat pump. In the following formulas, more precisely, Q1 to Q5 represent the heat quantities of the evaporator input heat Q1, the turbine input heat Q2, the condensation waste heat Q3, the refrigeration waste heat Q4, and the heat generation amount Q5 of the heating element, respectively.

[0159] (Formula 7): Q1×ε1=Q2

[0160] (Equation 8): Q2×(1-ε2)=Q3

[0161] (Formula 9): Q3×ε3=Q5

[0162] (Equation 10): Q3+Q5=Q4 To summarise,

[0163] (Formula 11): Q1×ε1×(1-ε2)×ε3=Q5

[0164] (Formula 12): Q1×ε1×(1-ε2)×(1+ε3)=Q4 Here, ε1 is about 0.8 (80%) in normal cogeneration facilities, ε2 is about 10% in geothermal power generation and waste incineration plants, (1-ε2) is about 0.9 (90%), and ε3 is about 0.6 (60%) when the chiller is operating optimally. From (Equation 11), it can be seen that unless these efficiencies (ε1 to ε3) change significantly, the heat balance cannot be maintained unless the amount of heat generated by the heating element Q5 is changed according to the amount of heat input heat Q1 to the evaporator from the heat source 10, or conversely, the amount of heat input heat Q1 to the evaporator is changed according to the amount of heat generated by the heating element Q5.

[0165] The condensation temperature (turbine back pressure) is a barometer of the heat balance state. That is, assuming that the adsorption refrigeration system 700 is operating optimally and ε3 is in the normal range, if the heat generated by the heating element Q5 is too small compared to the evaporator input heat Q1, the adsorption refrigeration system 700 performs only refrigeration work that balances the heat generated by the heating element Q5, so the heat consumption of the adsorption refrigeration system 700 also decreases accordingly, and the condensation waste heat Q3 that should be removed cannot be removed, so the condensation temperature (turbine back pressure) rises. Conversely, if the heat generated by the heating element Q5 is excessive compared to the evaporator input heat Q1, excessive cooling work is loaded relative to the amount of heat input to the adsorption refrigeration system 700, so that the adsorbents 203A and 203B of the adsorption refrigeration system 700 do not rise to a sufficient temperature, and as a result, the temperature of the second heat medium heading toward the first condenser 102 drops, resulting in a drop in the condensation temperature (turbine back pressure).

[0166] Therefore, in the first embodiment, the heat quantity of the evaporator input heat Q1 is controlled relative to the heat quantity of the heat generated by the heat generating element Q5 so that the condensation temperature of the first heat medium in the first condenser 102 falls within a predetermined appropriate range (here, a first predetermined temperature range). Note that, from the viewpoint of a business that utilizes waste heat, it is necessary to prioritize meeting the cold heat demand and to maintain the cold heat output to the cold heat load 501 so as to meet the cold heat demand. Therefore, in the first embodiment, it is not assumed that the heat balance of the cold heat generating system 1000A will be appropriately maintained by controlling the heat quantity of the heat generated by the heat generating element Q5 relative to the heat quantity of the evaporator input heat Q1.

[0167] {Heat balance control} Next, the heat balance control will be described.

[0168] The heat balance control is performed by the heat reception control circuit 320 as follows.

[0169] The heat receiving amount acquiring unit 340 acquires heat receiving amount data from the heat source 10, and obtains the heat receiving amount (Q1) from the heat receiving amount data. Also, the cold heat amount acquiring unit 350 acquires cold heat amount data from the cold heat output device 500 or the cold heat load 501, and obtains the cold heat amount (Q5) from the cold heat amount data.

[0170] The heat reception amount control circuit 320 acquires the amount of received heat from the heat reception amount acquisition unit 340 and acquires the amount of cold heat (Q5) from the cold heat amount acquisition unit 350. The heat reception amount control circuit 320 also acquires the condensation temperature of the first heat medium from the first heat medium temperature sensor 601. Then, based on the acquired amount of received heat (Q1) and amount of cold heat (Q5), the heat reception amount control circuit 320 generates a heat generation control command such that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range, and transmits this to the heat generation amount control unit 11 of the heat source 10.

[0171] Then, the heat generation amount control unit 11 of the heat source 10 controls the heat generation amount or the heat exhaust amount of the heat source 10 based on the received heat generation amount control command.

[0172] Thus, the heat balance of the cold generating system 1000A is controlled such that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range.

[0173] (Modification) FIG. 5 is a diagram showing an example of an outline of hardware of a cold generating system 1000B according to a modification of the first embodiment of the present disclosure.

[0174] Referring to FIG. 5, in this modification, a turbine back pressure sensor 610 that detects the back pressure of the steam turbine 103A is used as the condensation temperature-correlated physical quantity sensor. The rest of the basic configuration is the same as that of the above-mentioned embodiment 1. The turbine back pressure sensor 610 is provided between the steam turbine 103A and the first condenser 102 in the first heat medium flow path. Examples of the turbine back pressure sensor 610 include a diffusion type semiconductor sensor and a metal thin film type sensor. The back pressure of the steam turbine 103A corresponds one-to-one to the condensation temperature of the first heat medium. Therefore, in this modification, the heat receiving amount control circuit 320 controls the heat receiving amount (Q1) according to the cold energy amount (Q5) so that the turbine back pressure detected by the turbine back pressure sensor 610 is maintained within a predetermined pressure range of the turbine back pressure corresponding to a first predetermined temperature range of the condensation temperature of the first heat medium. As a result, the amount of heat received (Q1) is controlled according to the amount of cold heat (Q5) so that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range, and ultimately, the heat balance of the cold heat generation system 1000A is controlled so that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range.

[0175] As described above, according to the first embodiment, the heat balance control mechanism (the heat receiving amount control circuit 320 and the condensation temperature correlation physical quantity sensor (the first heat medium temperature sensor 601 or the turbine back pressure sensor 610)) controls the heat balance of the steam turbine device 100 and the adsorption refrigeration device 700 so that the condensation temperature of the first heat medium in the Rankine cycle is maintained within the first predetermined temperature range. Therefore, the outlet pressure (turbine back pressure) of the steam turbine 103A can be maintained within a range corresponding to the first predetermined temperature range of the condensation temperature of the first heat medium, and the compression ratio of the steam turbine 103A can be maintained within a certain range. As a result, the exhaust heat of the steam turbine drive can be utilized for generating cold energy for the cold energy load 501 while preventing a decrease in the efficiency of the steam turbine 103A, and thus the cold energy generation systems 1000A and 1000B capable of effectively utilizing the exhaust heat of the steam turbine drive can be provided.

[0176] Furthermore, according to embodiment 1, the heat reception control circuit 320 controls the amount of heat received (Q1) from the heat source 10 in accordance with the output of cold to the cold load 501 so that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range. Therefore, even if the amount of cold load of the cold load 501 fluctuates, the heat reception amount (Q1) from the heat source 10 can be controlled to achieve heat balance between the steam turbine device 100 and the adsorption refrigeration device 700 so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range.

[0177] (Embodiment 2) 6 is a functional block diagram showing an example of the configuration of a control system of a cold energy generation system 1000C according to the second embodiment of the present disclosure. In the cold energy generation system 1000C of the second embodiment, the heat balance control mechanism controls the thermal COP of the adsorption refrigeration device 700 to control the heat balance so that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range and cold energy corresponding to the cold energy load amount of the cold energy load 501 is output. The second embodiment differs from the first embodiment (including the modified example) in this respect, and is similar to the first embodiment (including the modified example) in other respects. The difference will be described in detail below.

[0178] <Configuration> 6, in the second embodiment, the heat balance control mechanism includes a thermal COP control circuit 321 instead of the heat receiving amount control circuit 320 of the first embodiment, and further includes a second heat medium temperature sensor 602. In addition, the control device 300 does not include a heat receiving amount acquisition unit 340. In addition, the thermal COP control circuit 321 includes a second heat medium flow rate control circuit 325.

[0179] The second heat medium temperature sensor 602 is provided in the second heat medium circulation path 211 between the outlet of the first condenser 102 and the first and second adsorbers 202A, 202B of the adsorption chiller 200. The second heat medium temperature sensor 602 detects the supply temperature of the second heat medium supplied from the first condenser 102 to the adsorption chiller 200. As the second heat medium temperature sensor 602, a known temperature sensor can be used, similar to the first heat medium temperature sensor 601.

[0180] <Thermal COP control principle> As described in the first embodiment, in the cold energy generation system 1000C, the evaporator input heat Q1, the turbine input heat Q2, the condensation waste heat Q3, the refrigeration waste heat Q4, and the heat generation element heat Q5 are in heat balance. Therefore, the temperatures of the second to fourth heat media are determined according to the operating conditions of the adsorption refrigeration device 700 so that the cold energy generation system 1000C is in heat balance.

[0181] On the other hand, according to the fourth finding mentioned above, control of the temperature T2 of the second heat medium (hereinafter referred to as the supply temperature of the second heat medium) input to the adsorption refrigerator 200 becomes the main adjustment mechanism for the heat balance of the cold generation system 1000C, and when the supply temperature T2 of the second heat medium is within this range (hereinafter referred to as the second specified temperature range), it is possible to suppress the condensation temperature of the first heat medium to 70°C or below by rationally designing the first condenser 102.

[0182] Furthermore, as described above using (Equation 5), the thermal COP of the adsorption refrigeration device 700 (adsorption refrigerator 200) can be reduced to a desired value by lowering the supply temperature of the second heat medium to the adsorption refrigerator 200, and this reduction in the supply temperature of the second heat medium can be achieved by reducing the flow rate (flow rate per unit time) of the second heat medium flowing through the second heat medium circulation path 211.

[0183] Therefore, in the second embodiment, the thermal COP control circuit 321 controls the thermal COP of the adsorption refrigeration device 700 so that the condensation temperature of the first heat medium is maintained within a first predetermined temperature range and cold energy corresponding to the cold load amount of the cold load 501 is output. During this thermal COP control, the second heat medium flow control circuit 325 controls the flow rate of the second heat medium flowing through the second heat medium circulation path 211 so that the supply temperature of the second heat medium is maintained within a second predetermined temperature range. Here, the second predetermined temperature range is set to a temperature range in which the condensation temperature of the first heat medium is maintained within the first predetermined temperature range. Such a second predetermined temperature range can be obtained by simulation, experiment, calculation, etc. The thermal COP control circuit 321 stores the first and second predetermined temperature ranges in a storage unit in advance.

[0184] <Operation> The thermal COP control circuit 321 acquires the cold energy amount (Q5) from the cold energy amount acquisition unit 350 and acquires the supply temperature of the second heat medium from the second heat medium temperature sensor 602. Then, the thermal COP control circuit 321 including the second heat medium flow rate control circuit 325 controls the operation amount P2 of the second heat medium pump 221 according to the cold energy amount (Q5) so that the supply temperature of the second heat medium is maintained within a second predetermined temperature range. This controls the thermal COP of the adsorption refrigeration device 700 so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range and cold energy according to the cold energy load amount of the cold energy load 501 is output. However, since the second predetermined temperature range is set on the premise that the received heat amount (Q1) is in heat balance with the cold energy amount (Q5), if the heat balance is lost due to a change in one or both of the cold energy amount (Q5) and the received heat amount (Q1), the condensation temperature of the first heat medium falls outside the first predetermined temperature range. In such a case, the thermal COP control circuit 321 controls the operating amount P2 of the second heat medium pump 221 based on the condensation temperature of the first heat medium detected by the first heat medium temperature sensor 601 so that the condensation temperature of the first heat medium is within a first predetermined temperature range.

[0185] As described above, according to the second embodiment, the thermal COP control circuit 321 controls the thermal COP of the adsorption refrigeration device 700 so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range and cold energy is output according to the cold energy load amount of the cold energy load 501. Therefore, even if the cold energy load amount fluctuates, by controlling the thermal COP of the adsorption refrigeration device 700, the steam turbine device 100 and the adsorption refrigeration device 700 can be thermally balanced so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range.

[0186] Furthermore, in controlling the thermal COP, the second heat medium flow control circuit 325 controls the flow rate of the second heat medium flowing from the first condenser 102 to the adsorber 202 so that the supply temperature of the second heat medium is maintained within a second predetermined temperature range. As a result, the thermal COP of the adsorption refrigerator 200 is suitably adjusted so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range.

[0187] (Embodiment 3) FIG. 7 is a functional block diagram showing an example of the configuration of a control system of a cold generating system 1000D according to the third embodiment of the present disclosure.

[0188] 7, the cold generation system 1000D of the third embodiment includes a heat balance control mechanism including additional control circuits and temperature sensors, compared with the cold generation system 1000C of the second embodiment. Specifically, the heat COP control circuit 321 includes third and fourth heat medium flow control circuits 326 and 327, and the temperature sensor group includes third and fourth heat medium temperature sensors 603 and 604 in addition to the first and second heat medium temperature sensors 601 and 602. The third embodiment differs from the second embodiment in these respects, and is similar to the second embodiment in other respects. The differences will be described in detail below.

[0189] <Configuration> The third heat medium temperature sensor 603 is provided between the radiator 400 and the first and second adsorption devices 202A, 202B in the third heat medium circulation path 212. The third heat medium temperature sensor 603 detects the temperature of the third heat medium flowing from the radiator 400 to the first and second adsorption devices 202A, 202B.

[0190] The fourth heat medium temperature sensor 604 is provided between the cold heat output device 500 and the inlet of the second evaporator 201 in the fourth heat medium circulation path 214. The fourth heat medium temperature sensor 604 detects the temperature of the fourth heat medium flowing from the cold heat output device 500 to the second evaporator 201.

[0191] The third heat medium flow control circuit 326 controls the flow rate of the third heat medium so that the temperature of the third heat medium flowing from the radiator 400 to the adsorber 202 is maintained within a third predetermined temperature range. The third predetermined temperature range is set to a temperature range in which the adsorption and regeneration operations of the adsorber 202 are performed sufficiently. This third predetermined temperature range is determined by simulation, experiment, calculation, etc.

[0192] The fourth heat medium flow control circuit 327 controls the flow rate of the fourth heat medium so that the temperature of the fourth heat medium flowing from the cold heat output device 500 to the second evaporator 201 is maintained within a fourth predetermined temperature range. The fourth predetermined temperature range is set to a temperature range in which the second evaporator 201 can sufficiently absorb the heat Q5 of the cold heat load 501. The fourth predetermined temperature range is determined by simulation, experiment, calculation, etc.

[0193] <Operation> The COP control circuit 321 including the second heat medium flow control circuit 325 performs the thermal COP control of the second embodiment. In this thermal COP control, the third heat medium flow control circuit 326 controls the operation amount of the third heat medium pump 222 based on the temperature of the third heat medium detected by the third heat medium temperature sensor 603 so that the temperature of the third heat medium is maintained within a third predetermined temperature range. This allows the adsorber 202 to perform adsorption and regeneration operations sufficiently. In addition, the fourth heat medium flow control circuit 327 controls the operation amount of the fourth heat medium pump 224 based on the temperature of the fourth heat medium detected by the fourth heat medium temperature sensor 604 so that the temperature of the fourth heat medium is maintained within a fourth predetermined temperature range. This allows the second evaporator 201 to sufficiently absorb the heat Q5 of the cooling load 501.

[0194] Therefore, according to the third embodiment, the heat pump operation of the adsorption refrigeration apparatus 700 is performed stably, and the adsorption refrigeration apparatus 700 exerts a sufficient refrigeration capacity while appropriately maintaining the heat balance of the cold generation system 1000D.

[0195] (Embodiment 4) FIG. 8 is a functional block diagram showing an example of the configuration of a control system of a cold generating system 1000E according to the fourth embodiment of the present disclosure.

[0196] 8, the cold generating system 1000E of the embodiment 4 includes a heat balance control mechanism including an additional control circuit, a temperature sensor group, and a flow rate sensor group, and the heat balance control circuit 323 performs a higher level of heat balance control, compared with the cold generating system 1000D of the embodiment 3. The embodiment 4 is different from the embodiment 3 in these points, and is similar to the embodiment 3 in other points. The difference will be described in detail below.

[0197] <Configuration> First, the configuration of the cold heat generating system 1000E will be described.

[0198] In the fourth embodiment, the temperature sensor group includes three first heat medium temperature sensors 601a-601c, two second heat medium temperature sensors 602a, 602b, two third heat medium temperature sensors 603a, 603b, and two fourth heat medium temperature sensors 604a, 604b. The flow rate sensor group includes first to fourth heat medium flow rate sensors 611-614.

[0199] The first heat medium temperature sensor 601a is provided between the outlet of the first evaporator 101 in the first heat medium circulation path 106 and the steam turbine 103A, and detects the temperature of the first heat medium flowing from the first evaporator 101 to the steam turbine 103A.

[0200] The first heat medium temperature sensor 601b is configured as the first heat medium temperature sensor 601 of the third embodiment, and detects the condensation temperature T1 of the first heat medium flowing from the first evaporator 101 to the steam turbine 103A.

[0201] The first heat medium temperature sensor 601c is provided between the first heat medium tank 105 and the inlet of the first evaporator 101 in the first heat medium circulation path 106, and detects the temperature of the first heat medium flowing from the first condenser 102 to the first evaporator 101.

[0202] The second heat medium temperature sensor 602a is configured by the second heat medium temperature sensor 602 of the third embodiment, and detects the supply temperature T2 of the second heat medium flowing from the first condenser 102 to the first and second adsorption devices 202A, 202B of the adsorption chiller 200.

[0203] The second heat medium temperature sensor 602b is provided between the first and second adsorption devices 202A, 202B of the adsorption refrigerator 200 and the first condenser 102 in the second heat medium circulation path 211, and detects the temperature of the second heat medium flowing from the first and second adsorption devices 202A, 202B to the first condenser 102.

[0204] The third heat medium temperature sensor 603a is provided between the second condenser 204 and the radiator 400 of the adsorption chiller 200 in the third heat medium circulation path 212, and detects the temperature of the third heat medium flowing from the second condenser 204 to the radiator 400.

[0205] The third heat medium temperature sensor 603b is configured as the third heat medium temperature sensor 603 of the third embodiment, and detects the supply temperature T3 of the third heat medium flowing from the radiator 400 to the first and second adsorption devices 202A, 202B of the adsorption chiller 200.

[0206] The fourth heat medium temperature sensor 604a is provided between the second evaporator 201 of the adsorption refrigerator 200 and the cold heat output device 500 in the fourth heat medium circulation path 214, and detects the temperature of the fourth heat medium flowing from the second evaporator 201 to the cold heat output device 500.

[0207] The fourth heat medium temperature sensor 604 b is configured as the fourth heat medium temperature sensor 604 in the third embodiment, and detects the supply temperature T 4 of the fourth heat medium flowing from the cold heat output device 500 to the second evaporator 201 of the adsorption chiller 200 .

[0208] The first heat medium flow sensor 611 is provided between the first heat medium tank 105 and the first evaporator 101 in the first heat medium circulation path 106, and detects the flow rate of the first heat medium flowing from the first condenser 102 to the first evaporator 101.

[0209] The second heat medium flow rate sensor 612 is provided at an appropriate position in the second heat medium circulation path 211 and detects the flow rate of the second heat medium.

[0210] The third heat medium flow rate sensor 613 is provided at an appropriate position in the third heat medium circulation path 212, and detects the flow rate of the third heat medium.

[0211] The fourth heat medium flow rate sensor 614 is provided at an appropriate position in the fourth heat medium circulation path 214, and detects the flow rate of the fourth heat medium.

[0212] As described above, the first to fourth heat medium temperature sensors 601a to 601c, 602a, 602b, 603a, 603b, 604a, and 604b can be configured with known temperature sensors. The first to fourth heat medium flow rate sensors 611 to 614 can be, for example, known flow meters.

[0213] Moreover, the control device 300 includes the received heat amount acquiring unit 340 of the first embodiment, and the heat balance control circuit 323 has the functions of the received heat amount control circuit 320 of the first embodiment and the thermal COP control circuit 321 of the third embodiment.

[0214] As is clear from (Equation 5), the amount of heat transport can be easily calculated from the temperature difference between when the fluid flows into and out of a device and the circulating flow rate of the fluid. The relationship between the steam temperature and the specific enthalpy is a physical property value summarized in a steam table, and can be stored in the heat balance control circuit 323.

[0215] Therefore, the heat balance control circuit 323 directly calculates the heat received from the heat source 10 (Q1), the heat supplied to the steam turbine 103A (Q2), the heat supplied to the adsorption refrigeration device 700 (Q3), the refrigeration waste heat (Q4), and the heat generated by the cold load 501 (Q5) from stored information such as the above (Equation 5) and a steam table, detection data from the first to fourth heat medium temperature sensors 601a to 601c, 602a, 602b, 603a, 603b, 604a, 604b, and detection data from the first to fourth heat medium flow sensors 611 to 614. Furthermore, the heat balance control circuit 323 prestores experimental or theoretical values ​​of, for example, the relationship between the efficiency of the adsorption refrigeration device 700 and the supply temperature T2 of the second heat medium, the supply temperature T3 of the third heat medium, and the supply temperature T4 of the fourth heat medium of the adsorption refrigeration device 700, and also prestores experimental or theoretical values ​​of the relationship between the outside air temperature and the performance of the radiator 400, and the relationship between the steam temperature and the power generation efficiency. Furthermore, the heat balance control circuit 323 instantaneously calculates the target temperatures T1 to T4 and flow rates of the first to fourth heat media for the target heat quantities of the received heat (Q1), the supplied heat (Q2, Q3), the refrigeration waste heat (Q4), and the generated heat (Q5), and precisely and quickly controls the operating amounts P1 to P4 of the first to fourth heat medium pumps 104, 221, 222, 224 corresponding to the first to fourth heat media, respectively.

[0216] <Operation> Next, the basic operation of the cold generating system 1000E configured as above will be described with reference to FIG.

[0217] Fig. 9 is a flow chart showing an example of the heat balance control of the cold generating system 1000E of Fig. 8. This heat balance control is performed by the heat balance control circuit 323.

[0218] 8 and 9, the heat balance control circuit 323 first determines whether there is room to vary the amount of heat received (Q1) (step S1). Specifically, if the amount of heat received (Q1) exceeds the amount of cold heat (Q5), the heat balance control circuit 323 determines that there is room to vary the amount of heat received (Q1) (YES in step S) and proceeds to step S2, and if not, determines that there is no room to vary the amount of heat received (Q1) (NO in step S1) and proceeds to step S10.

[0219] In step 2, the heat balance control circuit 323 determines whether the supply temperature T3 of the third heat medium is appropriate. Specifically, if the supply temperature T3 of the third heat medium is within the third predetermined temperature range (YES in step S2), the heat balance control circuit 323 proceeds to step S4, and if the supply temperature T3 of the third heat medium is not within the third predetermined temperature range (NO in step S2), the heat balance control circuit 323 controls the operation amount P3 of the third heat medium pump 222 until the supply temperature T3 of the third heat medium is within the third predetermined temperature range (YES in steps S3 and S2).

[0220] In step S4, the heat balance control circuit 323 determines whether the supply temperature T4 of the fourth heat medium is appropriate. Specifically, if the supply temperature T4 of the fourth heat medium is within a fourth predetermined temperature range (YES in step S4), the heat balance control circuit 323 proceeds to step S6, and if the supply temperature T4 of the fourth heat medium is not within the fourth predetermined temperature range (NO in step S4), the heat balance control circuit 323 controls the operation amount P4 of the fourth heat medium pump 224 until the supply temperature T4 of the fourth heat medium is within the fourth predetermined temperature range (YES in step S5 and step S4).

[0221] In step S6, the heat balance control circuit 323 determines whether the supply temperature T2 of the second heat medium is appropriate. Specifically, if the supply temperature T2 of the second heat medium is within the second predetermined temperature range (YES in step S2), the heat balance control circuit 323 proceeds to step S8, and if the supply temperature T2 of the second heat medium is not within the second predetermined temperature range (NO in step 6), the heat balance control circuit 323 controls the operating amount P2 of the second heat medium pump 221 until the supply temperature T2 of the second heat medium is within the second predetermined temperature range (YES in steps S7 and S6).

[0222] In step S8, the heat balance control circuit 323 determines whether the condensation temperature T1 of the first heat medium is appropriate. Specifically, if the condensation temperature T1 of the first heat medium is within the first predetermined temperature range (YES in step S8), the heat balance control circuit 323 returns to step S1, and if the condensation temperature T1 of the first heat medium is not within the first predetermined temperature range (NO in step S8), the heat balance control circuit 323 controls the amount of received heat (Q1), i.e., the amount of heat generated or the amount of heat exhausted from the heat source 10, until the condensation temperature T1 of the first heat medium is within the first predetermined temperature range (YES in steps S9 and S8).

[0223] On the other hand, in step S10, the heat balance control circuit 323 determines whether the supply temperature T3 of the third heat medium is appropriate. Specifically, if the supply temperature T3 of the third heat medium is within the third predetermined temperature range (YES in step S10), the heat balance control circuit 323 proceeds to step S12, and if the supply temperature T3 of the third heat medium is not within the third predetermined temperature range (NO in step S10), the heat balance control circuit 323 controls the operation amount P3 of the third heat medium pump 222 until the supply temperature T3 of the third heat medium is within the third predetermined temperature range (YES in steps S11 and S10).

[0224] In step S12, the heat balance control circuit 323 determines whether the supply temperature T4 of the fourth heat medium is appropriate. Specifically, if the supply temperature T4 of the fourth heat medium is within a fourth predetermined temperature range (YES in step S12), the heat balance control circuit 323 proceeds to step S14, and if the supply temperature T4 of the fourth heat medium is not within the fourth predetermined temperature range (NO in step S12), the heat balance control circuit 323 controls the operation amount P4 of the fourth heat medium pump 224 until the supply temperature T4 of the fourth heat medium is within the fourth predetermined temperature range (YES in steps S13 and S12).

[0225] In step S14, the heat balance control circuit 323 determines whether the condensation temperature T1 of the first heat medium is appropriate. Specifically, if the condensation temperature T1 of the first heat medium is within the first predetermined temperature range (YES in step S14), the heat balance control circuit 323 returns to step S1, and if the condensation temperature T1 of the first heat medium is not within the first predetermined temperature range (NO in step S14), the heat balance control circuit 323 controls the operation amount P2 of the second heat medium pump 221 until the condensation temperature T1 of the first heat medium falls within the first predetermined temperature range (YES in step S15 and step S14).

[0226] In addition to this basic control, the heat balance control circuit 323 may precisely and quickly control the operation amounts P1 to P4 of the first to fourth heat medium pumps 104, 221, 222, 224 corresponding to the first to fourth heat media, respectively, as described above.

[0227] As described above, according to the fourth embodiment, it is possible to perform advanced control such as reducing the auxiliary power of the cold generation system 1000E while maintaining the heat balance of the cold generation system 1000E at all times.

[0228] (Embodiment 5) FIG. 10 is a functional block diagram showing an example of the configuration of a control system of a cold generating system 1000F according to the fifth embodiment of the present disclosure.

[0229] Referring to FIG. 10, the cold energy generating system 1000F of the fifth embodiment is different from the cold energy generating system 1000E of the fourth embodiment in the following points. That is, the radiator 400 is composed of a cooling tower 401a and an electric heat pump 401b. In addition, a backup heat source 216 is provided between the outlet of the first condenser 102 in the second heat medium circulation path 211 and the temperature measurement position of the second heat medium temperature sensor 602a. As the backup heat source 216, for example, a heavy oil-fired or gas-fired hot water boiler can be mentioned. In addition, the cold energy load is DC501A, and power equipment for information and communication equipment including an uninterruptible power supply 503 and a backup generator 504 is added to this DC501A. The cold energy generating system 1000F of the fifth embodiment is similar to the cold energy generating system 1000E of the fourth embodiment in other points.

[0230] Specifically, the cooling tower 401a and the electric heat pump 401b are provided in series with each other in the third heat medium circulation path 212.

[0231] The DC 501A is connected to a communication line 502. The DC 501A, the uninterruptible power supply 503, the backup generator 504, and the electric heat pump 401b are connected in parallel to the generator 103B connected to the steam turbine 103A, and constitute a microgrid powered by the generator 103B. This microgrid is connected to a commercial power grid 505. The cold energy generation system 1000F includes this microgrid.

[0232] According to the fifth embodiment, the following effects can be obtained.

[0233] An ideal heat load, DC501A, which always has a demand for cold energy, can be secured within the cold energy generation system. Also, the electric power E1 obtained from the steam turbine unit 103 can be used to power the computer server or control accessories of DC501A. Diversifying the power supply source is particularly recommended for information and communication facilities in terms of ensuring redundancy. Also, in general, waste-to-energy generation often has a low selling price because the amount of electricity generated is small or unstable, but the cold energy generation system 1000F always consumes more power than it can generate and receives commercial electricity, so it can solve the problem of selling price.

[0234] In addition, since the radiator 400 is composed of the cooling tower 401a and the electric power heat pump 401b, the following advantages are obtained. That is, a cooling tower is usually used for the radiator 400. However, the heat dissipation capacity of the cooling tower varies depending on the temperature and humidity, and there is a risk that the heat dissipation capacity will be insufficient during the hottest hours of the summer. In this case, the adsorption operation of the adsorption refrigeration device 700 will become insufficient, and the cooling capacity will be lost. However, in this embodiment 5, the electric power heat pump 401b is used in combination as an auxiliary to cool the third heat medium so that the temperature of the return third heat medium does not exceed a certain value, so that the DC501A can be operated stably.

[0235] In addition, since the backup heat source 216 is provided in the section of the second heat medium circulation path 211 from when the second heat medium flows out of the first condenser 102 to when the temperature is measured by the second heat medium temperature sensor 602a, even if the Rankine cycle 110 of the steam turbine device 100 stops due to a malfunction, accident, or other reason, the second heat medium can be heated to an appropriate temperature to maintain the cooling capacity and ensure stable operation of the DC501A.

[0236] (Embodiment 6) A sixth embodiment of the present disclosure is an embodiment based on the above-mentioned third finding. Fig. 11 is a diagram showing an example of an outline of hardware of a cold generating system 2000A according to the sixth embodiment.

[0237] 11, the cold energy generation system 2000A of the sixth embodiment is different from the cold energy generation system 1000A of the first embodiment in the number of adsorber 202, the number of components of the adsorption regeneration valve system 209, and the configuration of the control device 300, but is otherwise similar to the cold energy generation system 1000A of the first embodiment. These differences will be described in detail below.

[0238] <Configuration> In the sixth embodiment, the adsorption chiller 200 includes first to fourth adsorbers 202A-202D. The adsorption regeneration valve system 209 includes first to fourth inlet side refrigerant on-off valves 205A-205D, first to fourth outlet side refrigerant on-off valves 206A-206D, first to fourth inlet side heat medium switching valves 207A-207D, and first to fourth outlet side heat medium switching valves 208A-208D. The number of the adsorbers 202 and the number of the corresponding elements of the adsorption regeneration valve system 209 are four here, but may be three or more.

[0239] The first to fourth adsorption devices 202A to 202D are connected in parallel to the second heat medium circulation flow path, the third heat medium circulation flow path, and the refrigerant circulation flow path, respectively, via the adsorption regeneration valve system 209. The connection manner is the same as in the first embodiment, and therefore a detailed description thereof will be omitted.

[0240] The control device 300 includes a heat balance control circuit 323, an adsorption regeneration control circuit 324, and an operation control circuit 330. The adsorption regeneration control circuit 324 controls the operation of the adsorption regeneration valve system 209. The adsorption regeneration valve system 209 and the adsorption regeneration control circuit 324 constitute an adsorption regeneration control mechanism. The control device 300 and the heat balance control circuit 323 cooperate to perform the functions of the received heat amount acquisition unit 340, the cold heat amount acquisition unit 350, and the received heat amount control circuit 320 of the first embodiment, or the functions of the cold heat amount acquisition unit 350 and the thermal COP control circuit 321 of the third embodiment. Note that, for example, in an application in which the evaporator input heat Q1 from the heat source 10 and the heat generation amount Q5 of the heat load 501 are stable, the heat balance control circuit 323 may be omitted.

[0241] <Operation> The adsorption regeneration control mechanism controls the operation of the adsorption refrigeration apparatus 700 so as to sequentially perform adsorption regeneration operations on the first to fourth adsorption devices 202A to 202D, in which, in an adsorption operation, the first to fourth adsorption devices 202A to 202D are respectively connected to the second evaporator 201 and are interposed between the radiator 400 and the second condenser 204 in the third heat medium circulation path 212 so that each of the adsorbents 203A to 203D adsorbs a refrigerant, and in a regeneration operation, the first to fourth adsorption devices 202A to 202D are connected to the second condenser 204 and are interposed in the second heat medium circulation path 211 so that each of the adsorbents 203A to 203D releases the refrigerant to be regenerated.

[0242] The adsorption and regeneration operations of the first to fourth adsorption devices 202A to 202D are similar to the adsorption and regeneration operations of the first and second adsorption devices 202A, 202B described in detail in the first embodiment, so a detailed explanation thereof will be omitted, and only operations that require supplementary explanation will be described below.

[0243] In the cold generation system 2000A, the time Ta required for the adsorption operation and the time Tr required for the regeneration operation for each of the n adsorbers (n is an integer of 3 or more) are the same for each of the n adsorbers, and the adsorption regeneration control mechanism controls the operation of the adsorption refrigeration device 700 so that the adsorption regeneration operations for the n adsorbers are performed with a time shift of 1 / n (Tc / n) of the time required for the adsorption regeneration operation (hereinafter referred to as the cycle time of the adsorption regeneration operation) Tc (Tc=Ta+Tr). This "time shift" between the cycle times of the adsorption regeneration operations for the n adsorbers is hereinafter referred to as a "phase shift."

[0244] Here, for n=4 adsorption devices, the first to fourth adsorption devices 202A to 202D, for example, Ta is set to 180 seconds, Tr is set to 180 seconds, Tc is set to 360 seconds, and the phase shift between the cycle times of the adsorption regeneration operations of the first to fourth adsorption devices 202A to 202D is set to Tc / n=90 seconds.

[0245] Therefore, the adsorption regeneration control mechanism controls the operation of the adsorption refrigeration apparatus 700 so that the adsorption regeneration operations for the first to fourth adsorption devices 202A to 202D, which have a cycle time of 360 seconds, are performed with a phase shift of 90 seconds each.

[0246] <Effects> The effect of the cold generation system 2000A configured as above will be described with reference to Figs. 12 and 13. Fig. 12 is a graph showing an example of the temperature change of each adsorbent and the discharge temperature change of the second heat medium when the number of adsorbers is two. Fig. 13 is a graph showing an example of the temperature change of each adsorbent and the discharge temperature change of the second heat medium in the cold generation system 2000A of Fig. 11. In Figs. 12 and 13, the vertical axis indicates the temperature (°C) of the adsorbent, and the horizontal axis indicates the elapsed time (seconds) of the adsorption regeneration operation. In Fig. 12, the thick solid line indicates the temperature of the first adsorbent 203A, the dashed line indicates the temperature of the second adsorbent 203B, and the thin solid line indicates the temperature of the second heat medium discharged from the adsorption refrigerator 200 (hereinafter referred to as the discharge temperature of the second heat medium). In FIG. 13, the thick solid line indicates the temperature of the first adsorbent 203A, the dashed line indicates the temperature of the second adsorbent 203B, the dotted line indicates the temperature of the third adsorbent 203C, the dashed dotted line indicates the temperature of the fourth adsorbent 203D, and the thin solid line indicates the discharge temperature of the second heat medium.

[0247] In the case of two adsorber, for example, the cycle time of the adsorption regeneration operation is 360 seconds, and the phase shift between the cycle times is 180 seconds.

[0248] 12, in the case where the number of adsorbers 202 is two, when one of the adsorbers (for example, the first adsorber 202A) is in a regenerating operation, the adsorbent 203A has been cooled by the third heat medium in the immediately preceding adsorption operation at the beginning of the regenerating operation, so that the second heat medium introduced into the adsorption refrigerator 200 consumes heat to a temperature close to the temperature of the third heat medium (30°C, for example) that has been lowered by dissipating heat, and is then discharged. Thereafter, as the one of the adsorbers 203A is heated by the second heat medium, the discharge temperature of the second heat medium rises, and at the point when the adsorbent 203A is completely regenerated, there is almost no heat consumption, so that the second heat medium is discharged at a temperature close to the temperature at which it was introduced (55°C, for example). Thereafter, when the one of the adsorber 202A switches to the adsorption operation, the other adsorber (e.g., the second adsorber 202B) switches to the regeneration operation, and when the adsorber 203B is in the regeneration operation, the same thing as the adsorber 203A of the one of the adsorber 202A occurs. Therefore, even if a second heat medium of a constant temperature is fed into the adsorption chiller 200, the discharge temperature of the second heat medium is not constant, and a sudden and large temperature change occurs, particularly at the timing of switching between the adsorption operation and the regeneration operation in each of the adsorber 202A, 202B. This sudden and large temperature change of the second heat medium causes a pressure shock in the back pressure of the steam turbine 103A, and the turbine blades may be damaged by the pressure shock.

[0249] In contrast, when the number of adsorbers 202 is four, referring to FIG. 13, two adsorbers 202 are always in adsorption operation with the third heat medium flowing therethrough, and the remaining two adsorbers are always in regeneration operation with the second heat medium flowing therethrough. However, the two adsorbents 203 in regeneration operation have different temperatures because the phases of the regeneration operations are shifted, and the temperature of the second heat medium discharged from these adsorbents, mixed, and then discharged from the adsorption chiller 200 is approximately the average temperature of both. Therefore, the temperature shock shown in FIG. 12 is mitigated, and the discharge temperature of the second heat medium is leveled. As a result, the possibility of damage to the turbine blades of the steam turbine 103A is reduced.

[0250] (Embodiment 7) FIG. 14 is a diagram showing an example of an outline of hardware of a cold generating system 2000B according to the seventh embodiment of the present disclosure.

[0251] Referring to FIG. 14, compared with the cold energy generation system 2000A of embodiment 6, the cold energy generation system 2000B of embodiment 7 differs from the cold energy generation system 2000A of embodiment 6 in the number of adsorbers 202 and the number of components of the adsorption regeneration valve system 209, but is otherwise similar to the cold energy generation system 2000A of embodiment 6.

[0252] Specifically, the number of adsorbers 202 and the number of components of the adsorption regeneration valve system 209 in the cold energy generation system 2000A of embodiment 6 are four, while the number of adsorbers 202 and the number of components of the adsorption regeneration valve system 209 in the cold energy generation system 2000B of embodiment 7 are six.

[0253] Fig. 15 is a graph showing an example of the temperature change of each adsorbent and the discharge temperature change of the second heat medium in the cold generation system 2000B of Fig. 14. In Fig. 15, the vertical axis indicates the temperature (°C) of the adsorbent, and the horizontal axis indicates the elapsed time (seconds) of the adsorption regeneration operation. The thick solid line indicates the temperature of the first adsorbent 203A, the longer dashed line indicates the temperature of the second adsorbent 203B, the shorter dashed line indicates the temperature of the third adsorbent 203C, the one-dot chain line indicates the temperature of the fourth adsorbent 203D, the two-dot chain line indicates the temperature of the fifth adsorbent 203E, the dotted line indicates the temperature of the sixth adsorbent 203F, and the thin solid line indicates the discharge temperature of the second heat medium.

[0254] According to the seventh embodiment, the number of adsorber 202 and the number of components of the adsorption regeneration valve system 209 are six, which is more than that of the sixth embodiment. Therefore, as shown in FIG. 15, the discharge temperature of the second heat medium is more uniform, and the possibility of damage to the turbine blades of the steam turbine 103A is further reduced.

[0255] (Embodiment 8) FIG. 16 is a diagram showing an example of an outline of hardware of a cold generating system 2000C according to the eighth embodiment of the present disclosure.

[0256] 16, the cold energy generation system 2000C of the embodiment mainly differs from the cold energy generation system 2000B of the embodiment 7 in that the adsorption refrigeration device 700 has a plurality of adsorption refrigerators 200, and the rest of the cold energy generation system 2000C is the same as the cold energy generation system 2000B of the embodiment 7. The following describes the difference.

[0257] In the cold generating system 2000C, an adsorption refrigeration apparatus 700 includes a plurality of (three in this example) adsorption refrigerators 200A-200C, one radiator 400, and one cold output device 500.

[0258] Each of the multiple adsorption refrigerators 200A-200C is configured by the adsorption refrigerator 200 of embodiment 7. Hereinafter, each of the multiple adsorption refrigerators may be referred to as the "j-th refrigerator," where j is an integer of 1 or greater.

[0259] The third heat medium circulation paths 212 of the multiple adsorption chillers 200A-200C each pass through one radiator 400. The third heat medium circulation paths 212 of the multiple adsorption chillers 200A-200C each may join together and pass through the radiator 400, or may pass through the radiator 400 separately.

[0260] Furthermore, the second heat medium circulation paths 211 of each of the multiple adsorption chillers 200A-200C pass through the first condenser 102. The second heat medium circulation paths 211 of each of the multiple adsorption chillers 200A-200C may join together and pass through the first condenser 102, or may pass through the first condenser 102 separately.

[0261] Furthermore, the fourth heat medium circulation path 214 of each of the multiple adsorption chillers 200A-200C passes through one cold load 501. The fourth heat medium circulation paths 214 of each of the multiple adsorption chillers 200A-200C may join together and pass through the cold load 501, or may pass through the cold load 501 separately.

[0262] The adsorption regeneration control circuit 324 (see Figure 11) of the control device 300 controls the operation of the adsorption regeneration valve systems 209 (see Figure 14) of all the adsorption refrigerators 200A to 200C so as to sequentially perform adsorption regeneration operations for the six adsorption devices 202A to 202F (see Figure 14) of all the adsorption refrigerators 200A to 200C.

[0263] In this embodiment 8, the time Ta required for the adsorption operation and the time Tr required for the regeneration operation for each of the adsorption devices 202A-202F of each of the adsorption refrigerators 200A-200C are the same for the n (n is an integer greater than or equal to 3: here 6) adsorption devices 202A-202F of the m (m is an integer greater than or equal to 1: here 3) adsorption refrigerators 200A-200C.

[0264] The adsorption regeneration control circuit 324 controls the operation of the adsorption regeneration valve system 209 (see FIG. 14) of the m adsorption refrigerators 200A-200C so that the adsorption regeneration operations for the n adsorber 202A-202F of each of the adsorption refrigerators 200A-200C are performed with a time shift of 1 / n (Tc / n) of the time Tc (Tc=Ta+Tr) required for the regeneration operation, and the adsorption regeneration operations are performed with a time shift of 1 / mn (Tc / mn: phase shift) of the cycle time Tc of the regeneration operation between the m adsorption refrigerators 200A-200C. In this case, for example, the phase shift of the cycle time Tc of the regeneration operation is Tc / mn=360 / (3×6)=20 (seconds).

[0265] FIG. 17 is a graph showing an example of a change in discharge temperature of the second heat medium and a change in return temperature of the second heat medium of each refrigerator in the cold generating system 2000C of FIG.

[0266] 17, the vertical axis indicates the temperature (°C) of the adsorbent, and the horizontal axis indicates the elapsed time (seconds) of the adsorption regeneration operation. The longer dashed line indicates the discharge temperature of the second heat medium from the first refrigerator (adsorption refrigerator 200A), the shorter dashed line indicates the discharge temperature of the second heat medium from the second refrigerator (adsorption refrigerator 200B), the dashed dotted line indicates the discharge temperature of the second heat medium from the third refrigerator (adsorption refrigerator 200C), and the light solid line indicates the return temperature of the second heat medium. The return temperature of the second heat medium is the temperature of the second heat medium flowing from each of the adsorption refrigerators 200A-200C to the inlet of the first condenser 102.

[0267] According to the eighth embodiment, as shown in Fig. 17, the pressure shock of the back pressure of the steam turbine 103A (see Fig. 10) is more suitably suppressed, and the possibility of the turbine blade being damaged is further reduced. Also, it is possible to deal with a large-scale heat source 10 (see Fig. 10) and a cooling load 501.

[0268] (Embodiment 9) FIG. 18 is a diagram showing an example of an outline of hardware of a cold generating system 2000D according to the ninth embodiment of the present disclosure.

[0269] 18, in a cold energy generation system 2000D of the embodiment, a plurality (three in this case) of first condensers 102A-102C are provided in a plurality (three in this case) of branch paths 106A-106C of a first heat medium circulation path 106 in a Rankine cycle 110 (see FIG. 2) of a steam turbine unit 100, and a plurality (three in this case) of second heat medium circulation paths 211 (see FIG. 14) of adsorption chillers 200A-200C each pass through the plurality of branch paths 106A-106C of the first heat medium circulation path 106. Other points of the embodiment are the same as those of the eighth embodiment.

[0270] According to the embodiment 9, as in the embodiment 8, the pressure shock of the back pressure of the steam turbine 103A (see FIG. 10) is more suitably suppressed, and the possibility of the turbine blade being damaged is further reduced. Also, it is possible to deal with a large-scale heat source 10 (see FIG. 10) and a cooling load 501.

[0271] (Embodiment 10) The cold generating system according to the tenth embodiment of the present disclosure is obtained by modifying the cold generating system 2000A (FIG. 11) of the sixth embodiment or the cold generating system 2000B (FIG. 14) of the seventh embodiment as follows.

[0272] 11 or 14, the cold heat generation system of embodiment 10 includes a plurality of adsorption refrigeration devices 700, and the operating heat source of the adsorption refrigeration cycle used by all of the adsorption refrigeration devices 700 is one first condenser 102 of one steam turbine device 100, or a plurality of first condensers 102 provided in a plurality of branch paths of the first heat medium circulation path 106 in the Rankine cycle of one steam turbine device 100 corresponding to the plurality of adsorption refrigeration devices 700, respectively.

[0273] According to such an embodiment 10, it is possible to accommodate a larger heat source 10 (see FIG. 10) and a larger cooling load 501, and the possibility of damage to the turbine blades is reduced.

[0274] (Other embodiments) In any of the first to fourth and sixth to tenth embodiments, the backup heat source 216 of the fifth embodiment may be provided.

[0275] Numerous modifications and other embodiments will be apparent to those skilled in the art in light of the above description, and therefore the above description is to be construed as illustrative only. [Industrial Applicability]

[0276] INDUSTRIAL APPLICABILITY The present disclosure is useful as a cold energy generation system capable of effectively utilizing exhaust heat from a steam turbine. [Explanation of symbols]

[0277] 10 Heat source 11 Heat generation control section 100 Steam turbine equipment 101 First evaporator 102 Condenser 103 Steam Turbine Unit 103A Steam Turbine 104 First heat transfer pump 105 First heat transfer tank 106 First heat transfer medium circulation path 110 Rankine Cycle 200 Adsorption refrigerator 201 Second evaporator 202 Adsorption device 203 Adsorbent 204 Second Condenser 205A to 205F First to sixth inlet side refrigerant on-off valves 206A to 206F 1st to 6th outlet side refrigerant on-off valves 207A to 207F 1st to 6th inlet side heat medium switching valves 208A to 208F 1st to 6th outlet side heat medium switching valves 209 Adsorption Regeneration Valve System 210 Adsorption Refrigeration Cycle 211 Second heat transfer medium circulation path 212 Third heat transfer medium circulation path 213 Refrigerant Circulation Path 214 4th heat transfer medium circulation route 216 Backup Heat Source 221 Second heat transfer pump 222 3rd heat transfer pump 223 Refrigerant Pump 224 4th heat transfer pump 300 Control device 310 System Control Circuit 320 Heat receiving control circuit 321 Thermal COP control circuit 323 Heat balance control circuit 324 Adsorption regeneration control circuit 325-327 Second to fourth heat medium flow control circuits 330 Operation control circuit 340 Received heat amount acquisition part 350 Cooling energy acquisition section 400 Heatsink 401 Cooling Body 500 Cold output device 601, 601a to 601c First heat medium temperature sensor 602, 602a, 602b Second heat medium temperature sensor 603a, 603b Third heat medium temperature sensor 604a, 604b Fourth heat medium temperature sensor 610 Turbine back pressure sensor 611 to 614 First to fourth heat medium flow rate sensors 700 Adsorption refrigerator 1000A~1000F,2000A~2000D Cold generation system Me Memory Pr Processor

Claims

1. A cold energy generation system comprising: a steam turbine device that generates power using a Rankine cycle that receives heat from a heat source; an adsorption refrigeration device that outputs cold energy to a cold energy load and emits refrigeration exhaust heat using an adsorption refrigeration cycle that uses exhaust heat emitted by a first condenser that constitutes the Rankine cycle as a working heat source; and a heat balance control mechanism that controls the heat balance between the steam turbine device and the adsorption refrigeration device so that the condensation temperature of a first heat medium in the Rankine cycle is maintained within a first predetermined temperature range.

2. 2. The cold heat generation system of claim 1, wherein the heat balance control mechanism includes a heat reception quantity acquisition device that acquires heat reception from the heat source, a cold heat quantity acquisition device that acquires the cold heat quantity to be output to the cold heat load, a condensation temperature correlation physical quantity sensor that detects a condensation temperature correlation physical quantity that correlates with the condensation temperature of the first heat medium, and a heat reception quantity control circuit that controls the heat balance based on the heat reception quantity, the cold heat quantity, and the condensation temperature correlation physical quantity to control the heat balance in accordance with the output of the cold heat to the cold heat load so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range.

3. 2. The cold energy generation system of claim 1, wherein the heat balance control mechanism includes a cold energy quantity acquisition device that acquires the amount of cold energy to be output to the cold energy load, a condensation temperature correlated physical quantity sensor that detects a condensation temperature correlated physical quantity that correlates with the condensation temperature of the first heat medium, and a thermal COP control circuit that controls the thermal balance based on the amount of cold energy and the condensation temperature correlated physical quantity to control the heat balance so that the condensation temperature of the first heat medium is maintained within the first predetermined temperature range and the cold energy corresponding to the cold energy load amount of the cold energy load is output.

4. the first condenser is a working heat source that releases heat as a result of a second heat medium being heated by heat exchange with the first heat medium, the adsorption refrigeration device includes a second heat medium circulation path that circulates the heated second heat medium through the first condenser and the adsorber so as to heat an adsorbent that is accommodated in the adsorber constituting the adsorption refrigeration cycle and that has adsorbed a refrigerant, The cold energy generation system of claim 3, wherein the thermal COP control circuit includes a second heat medium flow control circuit that controls the flow rate of the second heat medium flowing from the first condenser to the adsorber so that the temperature of the second heat medium is maintained within a second predetermined temperature range as part of the control of the thermal COP.

5. The steam turbine device includes: a first evaporator that evaporates the first heat medium in a liquid state by heat from the heat source to generate the first heat medium in a vapor state; a steam turbine that generates rotational power by the vapor-phase first heat medium; a first condenser that condenses the vapor-phase first heat medium obtained after rotating the steam turbine by heat exchange with a second heat medium to generate the liquid first heat medium; a first heat medium circulation path that circulates the first heat medium to pass through the evaporator, the steam turbine, and the first condenser in this order, The adsorption refrigeration device has the following adsorption refrigeration cycle: an adsorber containing an adsorbent that adsorbs a vapor-phase refrigerant in a state cooled by a third heat medium whose temperature has been decreased, and that releases the adsorbed refrigerant as vapor in a state heated by the second heat medium whose temperature has been increased by heat exchange with the vapor-phase first heat medium; a second condenser that condenses the vapor refrigerant released from the adsorbent accommodated in the adsorber through heat exchange with the third heat medium to generate a liquid refrigerant; a second evaporator that evaporates the liquid refrigerant through heat exchange with a fourth heat medium to generate the vapor refrigerant; a radiator that radiates heat to lower the temperature of the third heat medium, the temperature of which has been increased by heat exchange with the vapor-state refrigerant; a cold energy output device that outputs the cold energy of the fourth heat medium, the temperature of which has been lowered by heat exchange with the liquid refrigerant, to the cold energy load; a second heat medium circulation path that circulates the second heat medium through the first condenser and the adsorber; a third heat medium circulation path that circulates the third heat medium so that the third heat medium passes through the adsorber, the second condenser, and the radiator in this order; a fourth heat medium circulation path that circulates the fourth heat medium through the second evaporator and the cold heat output device; a refrigerant circulation path that circulates the refrigerant so that the refrigerant passes through the second evaporator, the adsorber, and the second condenser in this order; an adsorption regeneration mechanism that connects the adsorber to the second evaporator and to the third heat medium circulation path during a process in which the adsorber adsorbs the refrigerant, and that connects the adsorber to the second condenser and to the second heat medium circulation path during a process in which the adsorber releases the refrigerant and is regenerated.

6. The cold energy generation system according to claim 5, wherein the heat balance control mechanism includes a third heat medium flow control circuit that controls the flow rate of the third heat medium so that the temperature of the third heat medium flowing from the radiator to the adsorber is maintained within a third predetermined temperature range.

7. The cold generation system according to claim 5 or 6, wherein the heat balance control mechanism includes a fourth heat medium flow control circuit that controls the flow rate of the fourth heat medium flowing from the cold output device to the second evaporator so that the temperature of the fourth heat medium is maintained within a fourth predetermined temperature range.

8. The cold generation system according to claim 5 or 6, wherein the cold generation system is provided with any one of the temperature sensors or flow rate sensors i) to ix) below, and the heat balance control mechanism includes a heat balance control circuit that controls the heat balance based on the temperature or flow rate detected by any one of the temperature sensors or flow rate sensors i) to ix) below. i) a temperature sensor that detects the temperature of the first heat medium flowing from the first condenser to the first evaporator; ii) a temperature sensor that detects the temperature of the first heat medium flowing from the first evaporator to the steam turbine; iii) a flow rate sensor that detects a flow rate of the first heat medium flowing from the first condenser to the first evaporator; iv) a temperature sensor that detects the temperature of the second heat medium flowing from the adsorber to the second condenser; v) a flow rate sensor that detects the flow rate of the second heat medium; vi) a temperature sensor that detects the temperature of the third heat medium flowing from the second condenser to the radiator; vii) a flow rate sensor that detects the flow rate of the third heat medium; viii) a temperature sensor that detects the temperature of the fourth heat medium flowing from the second evaporator to the cold heat output device; ix) a flow rate sensor for detecting the flow rate of the fourth heat medium;

9. The adsorption refrigeration device comprises three or more adsorbers, each containing an adsorbent; a refrigerant circulation path that constitutes the adsorption refrigeration cycle and circulates a refrigerant through a second evaporator and a second condenser; a second heat medium circulation path that circulates a second heat medium through the first condenser; and a third heat medium circulation path that circulates a third heat medium through the second condenser and a radiator so that the hot heat obtained in the second condenser is radiated by the radiator.

2. The cold energy generation system according to claim 1, further comprising an adsorption regeneration control mechanism that controls the operation of the adsorption refrigeration device to sequentially perform an adsorption regeneration operation for the three or more adsorbers, in which, in an adsorption operation, each of the adsorbers is connected to the second evaporator and is interposed between the radiator and the second condenser in the third heat medium circulation path so that the adsorbent adsorbs the refrigerant, and in a regeneration operation, each of the adsorbers is connected to the second condenser and is interposed in the second heat medium circulation path so that the adsorbent releases the refrigerant for regeneration.

10. a time Ta required for the adsorption operation and a time Tr required for the regeneration operation for each of the n adsorbers (n is an integer of 3 or more) are the same for each of the n adsorbers, The cold energy generation system of claim 9, wherein the adsorption regeneration control mechanism is capable of controlling the operation of the adsorption refrigeration device so that the adsorption regeneration operation for the n adsorbers is performed at intervals of 1 / n of the time Tc (Tc = Ta + Tr) required for the adsorption regeneration operation (Tc / n).

11. the adsorption regeneration control mechanism includes an adsorption regeneration valve system that connects each of the adsorbents to the second evaporator and interposes it between the radiator and the second condenser in the third heat medium circulation path so that the adsorbents adsorb the refrigerant in the adsorption operation, and that connects each of the adsorbents to the second condenser and interposes it in the second heat medium circulation path so that the adsorbents release the refrigerant for regeneration in the regeneration operation; and an adsorption regeneration control circuit that controls the operation of the adsorption regeneration valve system so that the adsorption regeneration operation is performed sequentially for the three or more adsorbents, the adsorption refrigeration device includes a plurality of adsorption refrigerators, one radiator, and one cold energy output device that outputs the cold energy obtained in the second evaporator to the cold energy load; each of the adsorption chillers comprises the second evaporator, the three or more adsorbers, the second condenser, the refrigerant circulation path, the second heat medium circulation path, the third heat medium circulation path, and the adsorption regeneration valve system; the third heat medium circulation path of each of the plurality of adsorption refrigerators passes through one of the radiators, the second heat medium circulation path of each of the plurality of adsorption refrigerators passes through one of the first condensers or a plurality of the first condensers, and the plurality of first condensers are provided on a plurality of branch paths of the first heat medium circulation path in the Rankine cycle of the steam turbine device; and The cold energy generation system according to claim 9, wherein the adsorption regeneration control circuit is a control circuit that controls the operation of the adsorption regeneration valve systems of all of the adsorption refrigerators so as to sequentially perform the adsorption regeneration operation for the three or more adsorbers of all of the adsorption refrigerators.

12. a time Ta required for the adsorption operation and a time Tr required for the regeneration operation for each of the adsorbers of each of the adsorption refrigerators are the same for n (n is an integer of 3 or more) adsorbers of m (m is an integer of 1 or more) of the adsorption refrigerators, 12. The cold energy generation system according to claim 11, wherein the adsorption regeneration control circuit is capable of controlling the operation of the adsorption regeneration valve systems of the m adsorption refrigerators so that the adsorption regeneration operations for the n adsorbers of each of the adsorption refrigerators are performed with a time lag of 1 / n (Tc / n) of the time Tc (Tc = Ta + Tr) required for the regeneration operation, and the adsorption regeneration operations are performed among m (m is an integer of 1 or more) of the adsorption refrigerators with a time lag of 1 / mn (Tc / mn) of the time Tc required for the regeneration operation.

13. a plurality of said adsorption refrigeration units; A cold energy generation system according to any one of claims 1 to 6 and 9 to 12, wherein the operating heat source of the adsorption refrigeration cycle used by all of the adsorption refrigeration devices is one of the first condensers of one of the steam turbine devices, or a plurality of the first condensers provided in a plurality of branch paths of the circulation path of the first heat medium in the Rankine cycle of one of the steam turbine devices, each corresponding to the plurality of adsorption refrigeration devices.

14. A backup heat source for backing up the exhaust heat is provided in a heat medium path that carries the exhaust heat from the first condenser to the adsorption refrigeration cycle of the adsorption refrigeration device. A cold heat generation system according to any one of claims 1 to 6 and 9 to 12.

15. The cold energy generating system according to any one of claims 1 to 6 and 9 to 12, wherein the adsorption refrigeration device includes a radiator for discharging the refrigeration waste heat, and the radiator includes a cooling tower and an electric heat pump.

16. The cold energy generating system according to any one of claims 1 to 6 and 9 to 12, including information and communication equipment as the cold energy load.

17. The cold energy generation system of claim 16, wherein the steam turbine device includes a generator that generates electricity using power generated using the Rankine cycle, and the generator and the information and communication equipment are connected so that at least a portion of the electricity generated by the generator can be supplied to the information and communication equipment.

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