JP2007032917A - Heat medium supply system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat medium supply system combining an absorption heat pump and heat source equipment such as a boiler, capable of minimizing the amount of fuel consumed by the heat source equipment by utilizing most effectively exhaust heat put into the absorption heat pump, and controlling the operating state of the absorption heat pump and heat source equipment such as the boiler installed in parallel, according to the load of a use destination. <P>SOLUTION: The absorption heat pump 32 driven by exhaust heat, an exhaust gas boiler 33 driven by exhaust heat, and a fuel burning boiler 34, are connected in parallel to a steam header to supply a heated heat medium (steam) to the steam header 36 from the absorption heat pump 32, the exhaust gas boiler 33 and the fuel burning boiler 34 and to supply the heated heat medium to the load of the use destination from the steam header. The start-stop or capacity control of the absorption heat pump 32, exhaust gas boiler 33 and fuel burning boiler 34 is performed according to the steam pressure (load amount) in the steam header 36 detected by a pressure sensor 38. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a heat medium supply system configured by combining a boiler with a second type absorption heat pump that is driven using exhaust heat such as warm water as a heat source.

  In cogeneration using an engine, steam produced by recovering heat from exhaust gas is used effectively, but jacket hot water has little effective use other than hot water supply, and often dissipates heat in a cooling tower or the like. Absorption heat pumps that generate high-temperature heat from such a low-quality heat source such as exhaust hot water or exhaust steam are already known from Patent Document 1 and Patent Document 2, for example.

The above known examples are all related to the internal cycle of the absorption heat pump, and are not a system that effectively combines an absorption heat pump and a device such as a normal boiler. Therefore, a heat medium supply system is configured by combining an absorption heat pump, a waste heat boiler, and a fuel-fired boiler.When operating the heat medium supply system, exhaust heat is used most effectively and the amount of fuel used is minimized. It is not a system that can minimize emissions.
Japanese Patent Publication No.58-18574 Japanese Patent Publication No. 58-18575

  The present invention has been made in view of the above-described points, and most effectively uses the exhaust heat input to the absorption heat pump, and according to the load of the user, the absorption heat pump and a heat source such as a boiler installed in parallel. Heat medium supply combining a heat source device such as an absorption heat pump and boiler that can minimize the amount of fuel consumed by the heat source device, that is, the amount of carbon dioxide emission when operating the device, by controlling the operation state with the device The purpose is to provide a system.

  In order to solve the above-mentioned problem, the invention described in claim 1 includes a header including one or more absorption heat pumps driven by exhaust heat and one or more heat source devices driven by exhaust heat or fuel. The heat medium supply, wherein the heat medium heated from the absorption heat pump and the heat source device is supplied to the header, and the heat medium heated from the header is supplied to the load. In the system.

  According to a second aspect of the present invention, in the heat medium supply system according to the first aspect of the present invention, load detection means for detecting the amount of the load is provided, and the absorption is performed according to the load amount detected by the load detection means. An operation control means for performing on / off or capacity control of the heat pump and the heat source device is provided.

  The invention according to claim 3 is the heat medium supply system according to claim 2, wherein the operation control means includes means for operating the absorption heat pump in preference to the heat source device. .

  According to a fourth aspect of the present invention, in the heat medium supply system according to the second or third aspect, the absorption heat pump and the heat source device start and stop according to the load amount are frequent in the absorption heat pump and the heat source device. Means is provided for setting so as not to start and stop.

  According to a fifth aspect of the present invention, in the heat medium supply system according to any one of the first to fourth aspects, the heat source device is an exhaust heat boiler and a fuel-fired boiler, and the operation control means is the absorption heat pump. And means for operating the exhaust heat boiler in preference to the fuel-fired boiler.

  The invention according to claim 6 is the heating medium supply system according to claim 5, wherein the heating medium is steam, and the load detecting means is a pressure sensor for detecting the steam pressure of the header. To do.

  According to a seventh aspect of the present invention, in the heat medium supply system according to any one of the first to sixth aspects, the exhaust heat source that supplies the exhaust heat includes an exhaust heat source that requires cooling of the exhaust heat medium. In the case where there is an exhaust heat source that does not require cooling of the exhaust heat medium, a means for preferentially using the exhaust heat from the exhaust heat source that requires cooling of the exhaust heat medium is provided.

  The invention according to claim 8 is the heating medium supply system according to any one of claims 1 to 7, further comprising means for determining an operation priority among the plurality of the absorption heat pumps based on an accumulated operation time. It is characterized by.

  The invention according to claim 9 is the heat medium supply system according to any one of claims 1 to 8, wherein the plurality of heat source devices are divided into a plurality of groups according to the type, and a plurality of heat source devices belonging to the same group are divided. Among heat source devices, the operation priority is provided with means for determining the accumulated operation time.

  According to the invention described in each claim, the heat medium supply system includes one or more absorption heat pumps driven by exhaust heat, and one or more heat source devices driven by exhaust heat or fuel. Since the heat medium heated from the header is supplied to the load, the absorption heat pump and each heat source device are started and stopped by the load of the heat medium usage destination, and each device at that time In this operating state, exhaust heat can be used as effectively as possible, and the amount of fuel used, that is, the amount of carbon dioxide discharged from the heat medium supply system can be minimized.

  According to the second aspect of the present invention, since the operation control means for performing start / stop or capacity control of the absorption heat pump and the heat source device according to the load amount detected by the load detection means is provided, the absorption according to the load amount is provided. It is possible to utilize exhaust heat as effectively as possible in the operating state of the heat pump and the heat source device, and to minimize the amount of fuel used.

  According to the third aspect of the invention, since the absorption heat pump is provided with a means for operating with priority over the heat source device, it is possible to make the most effective use of exhaust heat and minimize the amount of fuel used. It becomes possible to do.

  According to the invention described in claim 4, since the absorption heat pump and the heat source device according to the load amount are set according to the load so that the absorption heat pump and the heat source device do not frequently start and stop, the frequent absorption heat pump and It is possible to reduce the deterioration of the equipment due to the start and stop of the heat source equipment and the energy loss at the start and stop.

  According to the invention described in claim 5, since the absorption heat pump and the exhaust heat boiler are operated with priority over the fuel-fired boiler, the exhaust heat can be utilized to the maximum extent and the amount of fuel used can be minimized. It becomes.

  According to the sixth aspect of the present invention, since the load detection means is a pressure sensor that detects the vapor pressure of the header, the load amount can be detected with a simple configuration.

  According to the seventh aspect of the present invention, the exhaust heat from the exhaust heat source that requires cooling of the exhaust heat medium is preferentially used, so that the power for driving the device for cooling the exhaust heat medium is reduced. It becomes possible.

  According to the eighth aspect of the invention, the operation priority among the plurality of absorption heat pumps is determined by the cumulative operation time, so that the operation time of the absorption heat pump becomes substantially equal.

  According to the invention of claim 9, the plurality of heat source devices are divided into a plurality of groups according to the type, and the operation priority is determined by the cumulative operation time among the plurality of heat source devices belonging to the same group. The operation time of the heat source devices belonging to the same group is substantially equal.

  First, a single-stage type 2 absorption heat pump will be described with reference to FIG. FIG. 1 is a diagram showing a configuration of a single-stage second type heat pump. As shown in the figure, a single-stage type 2 heat pump 1 includes an evaporator E, an absorber A, a regenerator G, a condenser C, a solution heat exchanger 10, a solution pump 11, a concentrated solution pipe 12, and a diluted solution pipe 13. The refrigerant pump 14, the refrigerant pipe 15, the heat source hot water pipe 16, the heat source hot water pipe 17, the cooling water pipe 18, the feed water pump 19, the feed water preheating heat transfer pipe 20, and the steam generating heat exchanger 21.

  In the single-stage type 2 heat pump 1 having the above configuration, the concentrated solution in the regenerator G is heated by the solution pump 11 through the concentrated solution pipe 12 and through the heated side of the solution heat exchanger 10, and then the absorber. A is sent to A and dispersed in the solution heat exchanger 10. The concentrated solution sprayed in the absorber A absorbs the refrigerant vapor flowing from the evaporator E to generate absorption heat, and the heated medium (water) flowing through the vapor generation heat exchanger 21 by the heat is absorbed. Heat. The dilute solution whose concentration has been reduced by absorbing the refrigerant vapor passes through the dilute solution pipe 13, passes through the heating side of the solution heat exchanger 10, heats the concentrated solution through the concentrated solution pipe 12, and returns to the regenerator G.

  The dilute solution that has returned to the regenerator G is heated by the heat source hot water 101 flowing in the heat source hot water pipe 17, generates refrigerant vapor, is concentrated to become a concentrated solution, and goes around the solution cycle. Refrigerant vapor generated in the regenerator G is guided to the condenser C, and is cooled and condensed by the cooling water 102 flowing in the cooling water pipe 18 to become a refrigerant liquid. This refrigerant liquid is sent to the evaporator E through the refrigerant pipe 15 by the refrigerant pump 14 and dispersed in the evaporator E, and is heated and evaporated by the heat source hot water 103 flowing in the heat source hot water pipe 16. Led to. The above is the cycle of the refrigerant and the solution.

  On the other hand, the heated medium (water) 104 is pressurized by the feed water pump 19 and guided to the feed water preheating heat transfer tube 20. The medium to be heated (water) 104 is heated in the feed water preheating heat transfer tube 20 as the refrigerant vapor generated in the evaporator E condenses, and then the absorption heat of the solution in the vapor generation heat exchanger 21 in the absorber A. Is heated to become water vapor.

  Thus, by supplying the heat source medium (heat source hot water 101, 103) and the cooling medium (cooling water 102) to the absorption heat pump 1, the absorber A can generate high-temperature heat. Note that the feed water preheating heat transfer tube 20 is not limited to being installed inside the evaporator as in the present embodiment, but heat recovery from the solution circulation system (heat exchange with the pipe 13) or direct heating with hot water (hot water 101). , 103), the heat of condensation of the condenser C (a heat transfer tube is installed in the can body of the condenser C), and the like can be considered. Moreover, you may combine these. Further, a heat exchanger may be installed in the refrigerant pipe 15 to preheat the refrigerant supplied to the evaporator E. By preheating, steam production efficiency can be improved.

  FIG. 2 is a diagram showing an example in which a heat medium supply system combining an absorption heat pump and a boiler according to the present invention is applied to cogeneration using an engine. Fuel 105 is supplied to the engine 30 to drive the generator 31 to generate electricity. At the same time, the jacket hot water 106 generated from the engine 30 is supplied to the absorption heat pump 32, and the absorption heat pump 32 is driven by the heat of the jacket hot water 106. The steam 107 is generated. Further, the exhaust gas 108 generated from the engine 30 is supplied to the exhaust gas boiler 33, and steam 109 is generated by the heat of the exhaust gas 108. A boiler 34-1 and a boiler 34-2 connected in parallel to the steam header 36 are ordinary fuel-fired boilers that generate steam 111 and steam 111 supplied with fuel 110.

  The steam 107, 109, 111, 111 generated in the absorption heat pump 32, the exhaust gas boiler 33, the boiler 34-1, and the boiler 34-2 is once collected in the steam header 36 and then supplied to the user 37. A pressure sensor 38 is attached to the steam header 36, and the excess or deficiency of the steam is detected by the steam pressure value detected by the pressure sensor 38. By detecting the excess or deficiency of the steam with the pressure sensor 38 of the steam header 36, it is possible to detect the load easily and inexpensively. Also, check valves V1, V2, V3-1, and V3-2 are attached to the absorption heat pump 32, the exhaust gas boiler 33, the boiler 34-1 and the piping connecting the boiler 34-2 and the steam header 36, which are heat source devices. This prevents the steam from flowing back from the steam header 36 to each heat source device.

  In the above system, the number of heat source devices of the absorption heat pump 32, the exhaust gas boiler 33, the boiler 34-1 and the boiler 34-2 is controlled. This number control will be described with reference to FIG. In the unit control, a plurality of pressure categories are set for the steam pressure value of the steam header 36, the operating state of each heat source device is determined in advance for each pressure category, and the steam pressure value of the steam header 36 detected by the pressure sensor 38 is determined. Depending on the pressure category, each heat source device is started and stopped.

  FIG. 3 shows the operation when a total of four heat source devices of an absorption heat pump 32, an exhaust gas boiler 33, a boiler 34-1 and a boiler 34-2 controlled at two positions of ON-OFF are installed as shown in FIG. An example of pressure setting values and operating states for each priority is shown. The vertical axis represents the operational (operation) priority, and the horizontal axis represents the steam header pressure. As for the operation priority, the absorption heat pump 32 is first, the exhaust gas boiler 33 is second, the boiler 34-2 is third, and the boiler 34-1 is fourth. In order to effectively use the exhaust heat, the absorption heat pump 32 and the exhaust gas boiler 33 are operated with priority. Among them, the absorption heat pump 32 uses hot water exhaust heat as a heat source, so the ranking is first and the exhaust gas boiler is second.

  The absorption heat pump 32 having the first operating priority is operated when the detected steam pressure value of the steam header 36 detected by the pressure sensor 38 is 0.80 MPa or less, and is stopped when it exceeds 0.82 MPa. The reason why the width of 0.02 MPa is provided for each operation / stop pressure setting value is to prevent frequent start / stop. Similarly, the exhaust gas boiler 33 with the second highest operating priority is operated when the detected steam pressure value of the steam header 36 detected by the pressure sensor 38 is 0.78 MPa or less, and is stopped when it exceeds 0.80 MPa.

  In this number control, the operation priority order of the boiler 34-1 and the boiler 34-2 is determined by comparing the accumulated operation times. Here, the case where the accumulated operation time of the boiler 34-1 is shorter is shown. In this case, the operation priority is the third place for the boiler 34-2 and the fourth place for the boiler 34-1 and the pressure is set to the pressure. The operation is started when the detected steam pressure value of the steam header 36 detected by the sensor 38 is 0.76 / 0.74 MPa or less, and the operation is stopped when the detected value exceeds 0.78 / 0.76 MPa. In a state where the pressure of the steam header 36 exceeds 0.82 MPa, all the heat source devices are stopped, and the jacket hot water 106 of the engine 30 is supplied to a cooling tower, a radiator (not shown) or the like and radiated to the atmosphere.

  By controlling the number of units as described above, the jacket hot water 106 generated from the engine 30 can be used with the highest priority, and the exhaust gas 108 can be used with the next highest priority. By increasing the heat utilization efficiency of the system, fossil fuel consumption for steam generation can be reduced and carbon dioxide emissions can be suppressed. Further, in the number control of the present embodiment example, the absorption heat pump and the heat source device are started and stopped according to the load amount so that the absorption heat pump and the heat source device do not frequently start and stop, so the frequent absorption heat pump and the heat source It is possible to reduce the deterioration of the device due to the start / stop of the device and the energy loss at the start / stop. Here, the reason why the jacket hot water 106 is used in preference to the exhaust gas 108 is that, as described above, when the jacket hot water 106 is not used, it is necessary to radiate heat by a cooling tower or the like. However, when the exhaust gas 108 is not used, it is only necessary to bypass the exhaust gas boiler 33 and exhaust the exhaust gas.

  In the present embodiment, the case where the absorption heat pump 32 and the exhaust gas boiler 33 are provided one by one has been described, but a plurality of these may be provided, and the priority of starting and stopping is the same as that of the boilers 34-1 and 34-2 described above. It is better to determine the cumulative operating time. Of course, when the engine is stopped, neither the jacket hot water 106 nor the exhaust gas 108 is generated. Therefore, the absorption heat pump 32 and the exhaust gas boiler 33 are stopped, and steam is generated only by the boiler 34-1 and the boiler 34-2. Corresponding to the load.

  In the number control of the present embodiment, when the state where the steam pressure value of the steam header 36 is higher than a predetermined value continues for a certain period of time, one operating heat source device is stopped and, conversely, the state is lower than the predetermined value. Is continued for a certain period of time, one of the stopped heat source devices is operated.

  4 shows the same equipment configuration as FIG. 2, that is, an absorption heat pump 32 (referred to as “absorption heat pump” in FIG. 4), an exhaust gas boiler 33 (referred to as “exhaust gas boiler” in FIG. 4), and a boiler 34-1 (referred to as “boiler” in FIG. 4). 1 ”) and a boiler 34-2 (referred to as“ boiler 2 ”in FIG. 4). FIG. 6 is a diagram showing an operation flow when the number control of this embodiment is applied to a system having a configuration. When the detected steam pressure of the steam header 36 detected by the pressure sensor 38 is P, the set pressure is Pd, and the differential is Δ, the number of operating heat source devices is decreased when the state of P> Pd + Δ continues for a set time. (Steps ST1 and ST2).

  As for the priority of the stop, the first is the longer cumulative operation time of the boiler 34-1 and the boiler 34-2, the second is the shorter cumulative operation time of the boiler 34-1 and the boiler 34-2, The third is the exhaust gas boiler, and the fourth is the absorption heat pump. Therefore, the operation times of the boiler 34-1 and the boiler 34-2 are compared (step ST3), and if the operation time of the boiler 34-1> the operation time of the boiler 34-2, it is determined whether the boiler 34-1 is in operation. (Step ST4) If it is in operation, the boiler 34-1 is stopped (Step ST5), and the process returns to START. In step ST3, if the operation time of the boiler 34-2 is greater than the operation time of the boiler 34-1 and if the boiler 34-1 is not in operation in step ST4, it is determined whether the boiler 34-2 is in operation (step ST6). If it is in operation, the boiler 34-2 is stopped (step ST7), and the process returns to START.

  If the boiler 34-2 is not in operation in step ST6, it is determined whether the boiler 34-1 is in operation (step ST8). If it is in operation, the process proceeds to step ST5. It is determined whether or not 33 is in operation. If it is in operation, the exhaust gas boiler 33 is stopped (step ST10), and the process returns to START. If the exhaust gas boiler 33 is not in operation in step ST9, it is determined whether the absorption heat pump 32 is in operation (step ST11). If it is in operation, the absorption heat pump 32 is stopped (step ST12) and the process returns to START. If the absorption heat pump 32 is not in operation, an alarm is issued (step ST13).

  The increase in the number of operating heat source devices is executed when the condition of P <Pd−Δ continues for a set time, and the priority order is the absorption heat pump in the first place, the exhaust gas boiler in the second place, and the boiler in the third place Among the boilers 34-1 and 34-2, the one with the shorter operation time, and the fourth place is the one with the longer operation time among the boilers 34-1 and 34-2. Therefore, in step ST1, it is determined whether P> Pd + Δ and P <Pd−Δ have elapsed for the set time (steps ST14 and ST15), and whether the absorption heat pump 32 is stopped (step ST16). If there is, the absorption heat pump 32 is operated (step ST17), and the process returns to START.

  If the absorption heat pump is not stopped in step ST16, it is subsequently determined whether the exhaust gas boiler 33 is stopped (step ST18). If it is stopped, the exhaust gas boiler 33 is operated (step ST19), and the process returns to START. In step ST18, if the exhaust gas boiler 33 is not stopped, it is subsequently determined whether the operation time of the boiler 34-1 <the operation time of the boiler 34-2 (step ST20), and the operation time of the boiler 34-1 <boiler. If it is the operation time of 34-2, it is determined whether the boiler 34-1 is stopped (step ST21). If it is stopped, the boiler 34-1 is operated (step ST22), and the process returns to START.

  When the operation time of the boiler 34-2 is less than the operation time of the boiler 34-1 at the step ST20 and when the boiler 34-1 is not stopped at the step ST21, it is determined whether the boiler 34-2 is stopped. If it is stopped (step ST23), the boiler 34-2 is operated (step ST24), and the process returns to START. If the boiler 34-2 is not stopped in step ST23, it is determined whether the boiler 34-1 is stopped (step ST25). If it is stopped, the process proceeds to step ST22, and if it is not stopped, an alarm is issued. Is issued (step ST13).

  By controlling the number of units as described above, the jacket hot water 106 generated from the engine 30 can be used with the highest priority and the exhaust gas 108 can be used with the highest priority, as in the example of FIG. By promoting the effective use of exhaust heat and increasing the heat utilization efficiency of the system, the consumption of fossil fuel for generating steam can be reduced and the amount of carbon dioxide emission can be suppressed. Moreover, since the pressure of the steam header 36 can be controlled to be substantially constant, the pressure fluctuation of the steam header accompanying the load fluctuation can be reduced as compared with the embodiment of FIG. Furthermore, since the start / stop is performed according to the load amount so that the frequent start / stop of each heat source device does not occur, the deterioration of the device due to the frequent start / stop of the device and the energy loss at the start / stop can be reduced. .

  As another configuration example of the system for controlling the number of units according to the present invention, a plurality of absorption heat pumps 32-1 to 32-3, a plurality of exhaust gas boilers 33-1 to 33-3, and a plurality of boilers 34-1 to 3-1. The case where 34-3 is installed is demonstrated using FIG.

  FIG. 5 is an expansion of the apparatus configuration of FIG. 2 and includes absorption heat pumps 32-1 to 32-3 driven by hot water exhaust heat to generate steam, and an exhaust gas boiler 33-driven by exhaust gas to generate steam. 1 to 3-3 and normal fuel-fired boilers 34-1 to 34-3 that generate steam by burning fuel, check valves V1-1 to V1-3, V2-1 to V2 -3, connected in parallel to the steam header 36 via V3-1 to V3-3. The steam generated from each of these heat source devices is once gathered in the steam header 36 and then supplied to the user 37, and the load status of the user 37 is determined by the detected pressure value detected by the pressure sensor 38 attached to the steam header 36. The points to be detected are the same as in the example of FIG.

  An example of the number control of the system shown in FIG. 5 will be described with reference to FIG. As in the case of FIG. 3, in this number control, the pressure value of the steam header 36 is divided every 0.01 MPa, and the operation state of each heat source device is preset for each division, and the pressure sensor 38 Each heat source device is started and stopped according to the detected steam pressure value of the steam header 36. Each heat source device is divided into three groups of absorption heat pumps 32-1 to 32-3, exhaust gas boilers 33-1 to 33-3, and boilers 34-1 to 34-3, and is operated with priority in this order. Shall be. For each heat source device in the same heat source device group, the order is determined in advance so that the heat source devices are operated with priority from the shortest accumulated operation time of each heat source device.

  In FIG. 6, a total of nine heat source devices of absorption heat pumps 32-1 to 32-3, exhaust gas boilers 33-1 to 33-3, and boilers 34-1 to 34-3 controlled at two positions of ON-OFF are installed. In this case, an example of a table of steam pressure set values and operation states is shown. First, in each heat source equipment group (a group of absorption heat pumps 32-1 to 32-3, a group of exhaust gas boilers 33-1 to 33-3, a group of boilers 34-1 to 34-3), Among them, the order of “A”, “B”, “C” is assigned in order from the shortest accumulated operation time, and the operation is started from the equipment with the highest priority in the group of the absorption heat pumps 32-1 to 32-3. Start. When all the devices in the group of the absorption heat pumps 32-1 to 32-3 are operated, the operation is similarly performed according to the priority order in the group of the exhaust gas boilers 33-1 to 33-3, and the exhaust gas boilers 33-1 to 33-1 are operated. When all the devices in the group 33-3 are operated, the same operation is performed in accordance with the priority order of the fuel-fired boilers 34-1 to 34-3, and finally all the heat source devices are operated. .

  Further, the order of stopping is the reverse of the order of operation priority. First, the boilers having the lowest operation priority of the fuel-fired boilers 34-1 to 34-3 are stopped in order. When all of the boilers in the fuel-fired boilers 34-1 to 34-3 are stopped, the boilers in the order of lower operation priority of the exhaust gas boilers 33-1 to 33-3 are stopped in turn, and the exhaust gas boiler 33- When all of the boilers in the 1-33-3 groups are stopped, the next stop is in order from the equipment with the lowest operating priority in the absorption heat pumps 32-1 to 32-3 group, and finally all the heat source equipments are stopped. become.

  By doing so, it is possible to reduce the deviation of the total operation time of each device in each heat source device group. For example, assuming that the cumulative operation time of the absorption heat pumps 32-1, 32-2, and 32-3 is 150 hours, 100 hours, and 180 hours, respectively, the operation priority order is the first rank A = absorption heat pump 32-2 and second The position B = absorption heat pump 32-1 and the third position C = absorption heat pump 32-3 are assigned. Similarly, the exhaust gas boilers 33-1, 33-2, 33-3 are assigned first rank A, second rank B, and third rank C within the group according to their accumulated operation time, and the fuel-fired boiler 34-1 , 34-2, and 34-3 are also assigned first rank A, second rank B, and third rank C within the group according to their accumulated operation time.

  The absorption heat pump 32-2 whose operation priority is first rank A is operated when the detected vapor pressure of the vapor header 36 of the pressure sensor 38 is 0.81 MPa or less, and is stopped when it exceeds 0.82 MPa. The reason why a range of 0.01 MPa is provided for each operation / stop pressure setting value is to prevent frequent start / stop. Similarly, the absorption heat pump 32-1 with the operation priority of the second rank B operates when the detected vapor pressure of the vapor header 36 of the pressure sensor 38 becomes 0.80 MPa or less, and stops when it exceeds 0.81 MPa. The absorption heat pump 32-3 whose operation priority is the third rank C operates when the detected vapor pressure of the vapor header 36 of the pressure sensor 38 is 0.79 MPa or less, and stops when it exceeds 0.80 MPa.

  Similarly, the exhaust gas boiler of No. 1 in the group of exhaust gas boilers 33-1 to 33-3 is the fourth highest priority for operation, and the second exhaust gas boiler is the fifth highest priority for operation. Exhaust boiler of C is 6th in operation priority, fuel-fired boilers 34-1 to 34-3, 1st A fuel-fired boiler is 7th in operation priority, 2nd B is fuel-fired The boiler with the No. 8 priority in operation and the No. 3 fuel-capped boiler with No. 9 in the priority order of operation, start and stop based on the detected steam pressure value of the steam header 36 detected by the pressure sensor 38. It is like that.

  All the heat source devices are operated when the steam header 36 is 0.73 MPa or less, and all the heat source devices are stopped when the pressure of the steam header 36 exceeds 0.82 MPa.

  By controlling the number of units as described above, hot water exhaust heat that needs to be cooled by a cooling tower or the like must be given top priority when not using heat source equipment, and exhaust gas can be used with priority next to it. The heat from the cogeneration system can be utilized most efficiently and economically. Moreover, since the operation priority order of each heat source device is determined based on the accumulated operation time of each heat source device, the operation time of each heat source device becomes substantially uniform, and the maintenance cycle can be lengthened. Furthermore, since the start and stop is performed according to the load amount so that frequent start and stop of each heat source device does not occur, deterioration of the device due to frequent start and stop of the device and energy loss at the time of start and stop can be reduced.

  In the present embodiment, the number control is performed by a group of absorption heat pumps 32-1 to 32-3, a group of exhaust gas boilers 33-1 to 33-3, a group of fuel-fired boilers 34-1 to 34-3, Although the priorities “A”, “B”, and “C” are assigned according to the cumulative operation time, the operation of each heat source device can be performed more easily, for example, by rotating the operation priority every week. The purpose of time equalization can be sufficiently achieved.

  Further, in the number control of the present embodiment, each heat source device is started and stopped according to the operation table based on the steam pressure of the steam header 36, but as in FIG. 4, while comparing with the pressure set value of the steam header 36, You may employ | adopt the method of controlling the start / stop of each heat-source apparatus according to a simple sequence.

  Although the above embodiment described the case where a single stage absorption heat pump was combined, you may comprise with a multistage heat pump. The two-stage absorption heat pump will be described with reference to FIG.

  As shown in FIG. 7, the two-stage type 2 absorption heat pump includes a low pressure evaporator EL, a high pressure evaporator EH, a low pressure absorber AL, a high pressure absorber AH, a regenerator G, a condenser C, a solution heat exchanger 40L, Solution heat exchanger 40H, solution pump 41, concentrated solution piping 42, diluted solution piping 43, diluted solution piping 44, refrigerant pump 45, refrigerant piping 46, heat source hot water piping 47, heat source hot water piping 48, cooling water piping 49, heat medium The pipe 50, the feed water pump 51, the feed water preheat heat transfer pipe 52, the feed water preheat heat transfer pipe 53, and the steam generation heat transfer pipe 54 are configured.

  In the second type two-stage absorption heat pump 3 having the above-described configuration, the concentrated solution of the regenerator G is passed through the concentrated solution pipe 42, the solution heat exchanger 40L, and the heated side of the solution heat exchanger 40L by the solution pump 41. After being heated through, the one branch is sent to the low pressure absorber AL and sprayed into the low pressure absorber AL, and the other is heated through the heated side of the solution heat exchanger 40H and then the high pressure absorption. Sent to the vessel AH and sprayed into the high-pressure absorber AH. The concentrated solution sprayed in the low-pressure absorber AL absorbs the refrigerant vapor flowing from the low-pressure evaporator EL, generates absorption heat, and heats the heat medium flowing into the heat medium pipe 46 with the heat.

  The diluted solution that has absorbed the refrigerant vapor and has a reduced concentration returns to the regenerator G via the heating side of the solution heat exchanger 40L. On the other hand, the concentrated solution dispersed in the high-pressure absorber AH absorbs refrigerant vapor flowing from the high-pressure evaporator EH to generate absorption heat, and heats the heated medium flowing in the vapor generation heat transfer tube 54 with the heat. To do. The dilute solution having a reduced concentration due to absorption of the refrigerant vapor passes through the dilute solution pipe 43, passes through the heating side of the solution heat exchanger 40H, and the dilute solution flowing from the low pressure absorber AL through the dilute solution pipe 44. It joins, returns to the regenerator G, and is dispersed in the regenerator G. The dilute solution sprayed in the regenerator G is heated by the heat source hot water 101 flowing in the heat source hot water pipe 48, generates refrigerant vapor and becomes a concentrated solution, and completes the solution cycle.

  Refrigerant vapor generated in the regenerator G is guided to the condenser C, and is cooled and condensed by the cooling water 102 flowing in the cooling water pipe 49 to become a refrigerant liquid. This refrigerant liquid is sent to the low-pressure evaporator EL and the high-pressure evaporator EH through the refrigerant pipe 46 by the refrigerant pump 45 and dispersed in the low-pressure evaporator EL and the high-pressure evaporator EH, respectively. The sprayed refrigerant liquid is heated and evaporated by the heat source hot water 103 flowing in the heat source hot water pipe 47 in the low pressure evaporator EL, and is led to the low pressure absorber AL. Similarly, in the high-pressure evaporator EH, it is heated and evaporated by the heat medium flowing through the heat medium pipe 50 and led to the high-pressure absorber AH. This is the solution cycle.

  On the other hand, the heated medium (water) 104 is pressurized by the feed water pump 51 and guided to the feed water preheating heat transfer tube 52. In the feed water preheating heat transfer tube 52, the refrigerant vapor generated in the regenerator G condenses to heat the heated medium (water) 104, and in the feed water preheating heat transfer tube 53, the refrigerant vapor generated in the high pressure evaporator EH. As a result of condensation, the heated medium (water) 104 is further heated. Finally, the medium to be heated (water) 104 is heated by the absorption heat of the solution in the steam generation heat transfer tube 54 in the high-pressure absorber AH to become water vapor. Thus, higher temperature heat can be produced from the same temperature heat source by making the cycle of the absorption heat pump multistage.

  In addition, as a place for installing the feed water preheating heat transfer tube 53, heat recovery from the solution circulation system, direct heating with heat source hot water, or the like can be used, and a combination thereof may be used. Moreover, efficiency can also be improved by preheating the refrigerant liquid supplied to the high-pressure evaporator EH with warm water or the like.

  In the above embodiment, the exhaust heat form is the jacket warm water 106 and the exhaust gas 108 of the engine 30, but factory exhaust heat and the like can be similarly applied. Further, the heating medium is not limited to hot water and exhaust gas, and other heating media may be used.

  The medium to be heated does not change phase and may be taken out as high temperature water. In that case, a flow meter is used in addition to the temperature sensor instead of the pressure sensor. Further, the medium to be heated is not limited to water, and may be another heat medium.

  There are no restrictions on the number of heat source devices such as absorption heat pumps, exhaust gas boilers, and fuel-fired boilers. One or more units may be used. Further, it can be established without an exhaust heat boiler or a fuel-fired boiler. The fuel-fired boiler may be an electric boiler that generates steam by converting electric energy into heat. If the exhaust heat boiler has a reheating function, it can be regarded as “exhaust heat boiler + fuel-fired boiler”.

  The absorption heat pump is not particularly specified as single stage or multistage. In the above-described embodiment, each heat source device has two-position control of ON / OFF, but can be extended to multi-position control (HI, LO, OFF, etc.) and proportional control. Various control methods known in the multi-can boiler system can be adopted as the control method at that time.

  Moreover, the same number control (load prediction, schedule operation, etc.) as other known multi-can boiler systems can be applied. In particular, since an absorption heat pump takes longer to start than a normal boiler, it is very effective to prevent frequent start / stop by load prediction. For example, even when the load at the use destination decreases, by keeping the absorption heat pump in a standby state without stopping, it is possible to follow the load without delay when the load increases again.

It is a figure which shows the structural example of a single stage 2nd type | mold absorption heat pump. It is a figure which shows the example which applied the heat-medium supply system which concerns on this invention to the cogeneration using an engine. It is a figure for demonstrating the number control of the heat-medium supply system which concerns on this invention. It is a figure which shows the flow of the number control of the heat-medium supply system which concerns on this invention. It is a figure which shows the structural example of the heat-medium supply system which concerns on this invention. It is a figure which shows the operating state of the steam pressure setting value and each heat-source apparatus of the heat-medium supply system which concerns on this invention. It is a figure which shows the structure of a two-stage type 2 absorption heat pump.

Explanation of symbols

1 Single stage type 2 absorption heat pump 3 2nd stage type 2 absorption heat pump E Evaporator A Absorber G Regenerator C Condenser EH High pressure evaporator EL Low pressure evaporator AH High pressure absorber AL Low pressure absorber V1 Check valve V2 Reverse Stop valve V3 Check valve 11 Solution pump 12 Concentrated solution piping 13 Dilute solution piping 14 Refrigerant pump 15 Refrigerant piping 16 Heat source hot water piping 17 Heat source hot water piping 18 Cooling water piping 19 Water supply pump 20 Water supply preheating heat transfer tube 21 Steam generating heat exchanger 30 Engine 31 Generator 32 Absorption heat pump 33 Exhaust gas boiler 34 Boiler 36 Steam header 37 Usage 40L Solution heat exchanger 40H Solution heat exchanger 41 Solution pump 42 Concentrated solution piping 43 Diluted solution piping 44 Dilute solution piping 45 Refrigerant pump 46 Refrigerant piping 47 Heat source hot water piping 48 Heat source hot water piping 49 Cooling water piping 50 Heat medium piping 1 feed water pump 52 water preheating heat exchanger tube 53 the water supply preheating heat exchanger tube 54 steam generator heat transfer tube

Claims (9)

  One or more absorption heat pumps driven by exhaust heat and one or more heat source devices driven by exhaust heat or fuel are connected in parallel to the header and heated from the absorption heat pump and heat source devices. The heat medium supply system is configured to supply the heated heat medium to the header and to supply the heat medium heated from the header to the load. In the heating medium supply system according to claim 1,
Load detecting means for detecting the amount of the load is provided, and operation control means for performing start / stop or capacity control of the absorption heat pump and the heat source device according to the load amount detected by the load detecting means is provided. Heating medium supply system. In the heating medium supply system according to claim 2,
The operation control means includes means for operating the absorption heat pump in preference to the heat source device. In the heating medium supply system according to claim 2 or 3,
The heat medium supply system characterized in that means for setting the absorption heat pump and the heat source device according to the load amount so as not to frequently start and stop the absorption heat pump and the heat source device is provided. . The heating medium supply system according to any one of claims 1 to 4,
The heat source equipment is a waste heat boiler and a fuel-fired boiler,
The operation control means includes means for operating the absorption heat pump and the exhaust heat boiler in preference to the fuel-fired boiler. In the heating medium supply system according to claim 5,
The heating medium supply system, wherein the heating medium is steam, and the load detection means is a pressure sensor that detects a vapor pressure of the header. The heating medium supply system according to any one of claims 1 to 6,
When the exhaust heat source that supplies the exhaust heat includes an exhaust heat source that requires cooling of the exhaust heat medium and an exhaust heat source that does not require cooling of the exhaust heat medium, the exhaust heat source that requires cooling of the exhaust heat medium A heating medium supply system comprising means for giving priority to waste heat. The heating medium supply system according to any one of claims 1 to 7,
A heating medium supply system comprising means for determining the operation priority among a plurality of the absorption heat pumps based on an accumulated operation time. In the heating medium supply system according to any one of claims 1 to 8,
Heat medium supply, characterized in that a plurality of heat source devices are divided into a plurality of groups according to the type, and the operation priority among the plurality of heat source devices belonging to the same group is determined by the cumulative operation time. system.

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