JP2005274123A - Power generation system and control method thereof - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power generation system and a control method thereof capable of controlling output of power generation from a heat source side and capable of improving heat efficiency over the whole of the system. <P>SOLUTION: This power generation system is provided with a heating device 4, a Stirling engine 11, a generator 12, a flow control means 6 and a temperature control means 9. The flow control means controls flow of the heat gas to be supplied to the heating device by variably controlling exhaust flow of the heat gas flow (HG) downstream of the heating device. The temperature control means controls temperature of the heat gas flow to be supplied to the heating device by variably controlling quantity of the air for combustion to be supplied to the combustion device. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a power generation system and a control method therefor. More specifically, the present invention relates to a pyrolysis gas or a gasification gas (hereinafter simply referred to as “gasification gas”) obtained by gasification of solid fuel or liquid fuel such as waste and biomass fuel. The present invention relates to a power generation system configured to heat a working fluid of a Stirling engine using a “thermal decomposition gas”) as a heat source, and to drive a generator by the Stirling engine, and a control method thereof.

  The solid fuel or liquid fuel such as waste and biomass fuel is gasified, the tar content in the pyrolysis gas generated by gasification is reformed with high-temperature steam and air, and the reformed gas obtained in the reforming process is A power generation system configured to supply an internal combustion engine such as a diesel engine generator is known (Japanese Patent Laid-Open No. 2002-210444, etc.). In this type of power generation system, the tar content and moisture content of the reformed gas to be supplied to the internal combustion engine are severely limited. Moreover, since the temperature of the reformed gas supplied to the internal combustion engine is limited to a relatively low temperature, a gas cooling process is required, and a wastewater treatment facility for discharging steam condensate generated in the gas cooling process. Etc. are required.

  On the other hand, the Stirling engine is known as a regenerative external combustion engine that employs a Stirling cycle, which includes a process of isovolume heating, isothermal expansion, isovolume cooling, and isothermal compression, as a heat cycle. The Stirling engine, which is an external combustion engine, not only exhibits the same thermal efficiency as an internal combustion engine, but also has been put to practical use for many years because of its excellent environmental performance such as safety, low vibration, and low noise. Has been expected.

Research has been conducted on exhaust heat utilizing power generation devices using Stirling engines, household cogeneration systems, or power generation devices using biomass fuel. For example, Japanese Patent Application Laid-Open No. 64-88021 and Japanese Patent Application Laid-Open No. Hei 8 Japanese Patent Publication No. -94050 and Japanese Patent Application Laid-Open No. 2003-20993 disclose a power generator in which a heating unit of a Stirling engine is disposed in an exhaust gas flow path of high-temperature combustion gas generated in a waste incinerator or a dry distillation furnace. A Stirling engine uses a combustion gas of an incinerator as a heat source to drive a generator. Japanese Patent Application Laid-Open No. 11-159718 proposes a combustion apparatus in which a heating unit of a Stirling engine is arranged on a furnace wall portion and a generator is operated by a driving force of the Stirling engine. Further, Japanese Patent Laid-Open No. 7-19008 discloses a heating device for a Stirling engine provided with a damper device capable of selectively switching a combustion gas flow channel while disposing an exhaust gas reference fan in a high-temperature hot gas flow channel. It is disclosed.
JP 2002-210444 A JP-A 64-88021 JP-A-8-94050 Japanese Patent Laid-Open No. 2003-20993 Japanese Patent Laid-Open No. 11-159718 JP 7-19008 A

  In the above-described power generation system that operates an internal combustion engine such as a diesel engine using a pyrolysis gas of solid fuel or liquid fuel as a fuel, it is necessary to stably supply a reformed gas having a relatively high calorific value to the internal combustion engine. When a reformed gas with a relatively low calorific value that has not been reformed or a reformed gas with an unstable calorific value is supplied to the internal combustion engine, it is difficult to operate the power generation system effectively. In addition, when the reformed gas contains a relatively large amount of tar as a result of insufficient reforming, continuous operation of the diesel engine is likely to be hindered. For this reason, it is important to control the temperature and flow rate of steam and air to be supplied to the reforming process, and to manage the waste (solid fuel or liquid fuel) that is the source of pyrolysis gas. Will put a considerable burden on system managers and others in maintaining and managing the power generation system.

  In addition, since the reformed gas to be introduced into the internal combustion engine such as a diesel engine needs to be forcibly cooled to a temperature of about 40 to 50 ° C., water vapor in the reformed gas is condensed in the cooling process. As a result, a relatively large amount of condensed water is generated in the system. For this reason, in this kind of power generation system, it is necessary to provide a drainage channel and drainage treatment equipment for discharging such condensed water to the outside of the system.

  On the other hand, the Stirling engine typically includes a heating device that heats the working fluid for driving the piston by the sensible heat of the hot gas flow supplied to the Stirling engine, and the heating device includes the hot gas flow and the working fluid. A heat transfer section for performing heat exchange. In a power generation system equipped with such a Stirling engine, the output of the Stirling engine that drives the generator is regulated in accordance with the demand on the power receiving side or the power demand. For this reason, a large amount of heat possessed by the hot gas flow must be exhausted out of the system inefficiently, and surplus exhaust heat retained by the hot gas can be recovered by a heat medium for uses other than power generation. Only. However, if it becomes possible to control the power generation output of the generator from the hot gas flow side, not only the thermal efficiency of the entire power generation system can be improved, but also a plurality of pyrolysis gases of solid fuel or liquid fuel can be used as fuel. It is considered possible to construct a power generation system with a relatively large power generation output that drives the Stirling engine.

  In the Stirling engine heating device disclosed in the above-mentioned Japanese Patent Application Laid-Open No. 7-19008, the open / close type damper device is disposed in the high-temperature hot gas flow path and heat exchanged with the heat transfer section of the Stirling engine. A hot gas citation fan that attracts gas is placed in the flue section. However, this damper device is placed in the hot gas flow path and has a structure that requires high heat resistance, so the flow of hot gas supplied to the heat transfer section of the Stirling engine is selectively cut off. It is only a simple opening and closing structure. Japanese Patent Application Laid-Open No. 7-19008 discloses a fan for hot gas induction, but it is disposed in a hot gas passage at high temperature and indirectly flows the heat gas flowing into the heat transfer section of the Stirling engine. It can only be adjusted in an auxiliary manner, and is not intended to control the power output depending on the control of the hot gas flow.

  In addition, these conventional Stirling engines do not include means for variably controlling the temperature of the hot gas flow that is in heat transfer contact with the heat transfer section of the heating device. Therefore, heat having a temperature suitable for the operating state of the Stirling engine is not provided. The gas flow cannot be supplied to the heat transfer section of the Stirling engine, and the power generation output of the Stirling engine cannot be controlled by controlling the temperature of the hot gas flow.

  As another type of Stirling engine, a structure in which a heating device is configured as a combustor is known. This type of Stirling engine is configured to heat the heater tube in the combustor with the combustion heat of the combustible gas supplied into the apparatus. Since the working fluid of the Stirling engine is efficiently heated by the radiant heat transfer action and the convection heat transfer action of the flame and combustion gas generated in the combustor, relatively high thermal efficiency can be obtained. However, this type of Stirling engine is only premised on the use of a relatively high calorific fuel gas such as LPG. In contrast, pyrolysis gas of solid fuel or liquid fuel obtained in gasification furnace or pyrolysis furnace such as dry distillation furnace, pyrolysis furnace, waste gasification furnace, solid fuel gasification furnace has a low calorific value. In addition, as described above, since tar content is included, it has not been attempted to supply the pyrolysis gas directly to the heating device of the Stirling engine and operate the Stirling engine with the combustion heat.

Furthermore, in a gasification furnace or pyrolysis furnace that generates flammable gas by gasification or thermal decomposition of polymer waste (waste plastics, waste tires) or the like, the pyrolysis gas contains a relatively large amount of dust or Contains unburned components and contains a relatively large amount of corrosive components such as chloride, sulfide, NH ₃ and HCN. For this reason, the heater tube etc. which comprise the heat-transfer part of a heating apparatus need to manufacture with the comparatively expensive metal which has corrosion resistance.

  The present invention has been made in view of such circumstances, and an object thereof is to provide a Stirling engine using a pyrolysis gas of a solid fuel or a liquid fuel obtained in a gasification furnace or a pyrolysis furnace as a heat source. An object of the present invention is to provide a power generation system capable of operating and controlling the power generation output of a generator using a Stirling engine as a drive source from the heat source side to improve the thermal efficiency of the entire system, and a control method therefor.

  To achieve the above object, the present invention provides a power generation system including a Stirling engine (11) including a heating device (4) for heating a working fluid, and a generator (12) driven by the Stirling engine. ,

 (i) Combustion device for combusting pyrolysis gas (P) obtained by pyrolysis or gasification of solid fuel or liquid fuel and generating a hot gas flow (HG) to be supplied to the heating device (4) ( 3) and flow rate control means (6) for controlling the flow rate of the hot gas flow by variably controlling the exhaust gas flow rate on the downstream side of the heating device, and the heating device (4 The heating fluid is heated by heat exchange between the heat transfer section (13) and the hot gas flow (HG):

 (ii) Combustion device for combusting pyrolysis gas (P) obtained by pyrolysis or gasification of solid fuel or liquid fuel and generating a hot gas flow (HG) to be supplied to the heating device (4) ( 3) and temperature control means (9) for variably controlling the temperature of the hot gas flow, and the heat transfer section (13) of the heating device (4) and the heat gas flow (HG) The power generation system, wherein the working fluid is heated by replacement:

 (iii) A power generation system comprising both the flow rate control means (6) and the temperature control means (9):

 (iv) a reformer (50) for reforming the pyrolysis gas (P) obtained by pyrolysis or gasification of solid fuel or liquid fuel with steam, and a reformed gas obtained by the reformer ( Fuel gas supply means (6; 60; L8) for supplying R) to the combustion section (41) of the heating device (4), and heating the working fluid by the combustion heat of the reformed gas (R) Power generation system characterized by: or

 (v) The pyrolysis gas (P) obtained by pyrolysis or gasification of a solid fuel or a liquid fuel, or a reformed gas (R) obtained by reforming the pyrolysis gas with steam is used as the heating device (4). A fuel gas supply means (6; 60; L8) for supplying to the combustion section (41) of the fuel gas, and combustion of the pyrolysis gas (P) or reformed gas (R) of the fuel gas supply means in the heating device A gas branching means (80; L80) for supplying to the combustion air supply system (8; 9; 52; L61; L62) and mixing with the combustion air, the fuel gas supply means and the combustion air supply system The power generation system is characterized in that the working fluid is heated by the combustion heat of the pyrolysis gas or reformed gas supplied from both to the combustion section (4).

  According to the power generation system provided with the combustion apparatus (3), the combustion apparatus (3) for converting the pyrolysis gas (P) into a hot gas includes a gasification furnace or a pyrolysis furnace (1), and a heating apparatus (4 The hot gas flow (HG) obtained by combustion of the pyrolysis gas is heated by the Stirling engine under the control of the flow rate control means (6) and / or the temperature control means (9). Supplied to the device (4). The driving force of the Stirling engine is controlled by a hot gas flow that controls at least one of flow rate and temperature.

  According to the power generation system of the present invention provided with the reformer (50) and the fuel gas supply means (6; 60; L8), the tar content in the pyrolysis gas, which is an impediment to the operation of the apparatus, is reformed. Since it is removed in the process, the pressurizing means (60) such as a fan or a blower or the flow rate control valve (6) can be used as the fuel gas supply means. The fuel gas supply means can supply the flow-controlled fuel gas to the combustion section (41) of the heating device (4) to control the combustion heat in the combustion zone (40).

  According to the power generation system of the present invention including the gas branching means (80; L80), the pyrolysis gas (P) or the reformed gas (R) is supplied with the fuel gas supply means (6; 60; 90; L8) and It is supplied to the combustion part (41) of the heating device (4) from both of the combustion air supply systems (8; 9; 52; L61; L62). Therefore, it is possible to supply a large amount of pyrolysis gas (P) or reformed gas (R) with a low calorific value to the combustion section (41) of the heating device (4) to secure a heat source necessary for driving the Stirling engine. it can.

  In any configuration, pyrolysis gas (P) obtained by pyrolysis or gasification of solid fuel or liquid fuel is used as a heat source of the Stirling engine. A heating device (4) of the type provided with a heat transfer section (13) is supplied with a flow gas and / or temperature-controlled hot gas flow (HG), and is of a type provided with a combustion section (41) ( 4), the reformed gas whose flow rate is controlled by the pressurizing means (60) or the flow rate control valve (6), or the fuel gas supply means (6; 60; L8) and the combustion air supply system (8; 9; 52; L61; L62) is supplied with pyrolysis gas or reformed gas. Therefore, the pyrolysis gas (P) obtained by pyrolysis or gasification can be supplied to the heating device (4) of the Stirling engine as a controllable heat source. Can be controlled from the heat source side to improve the thermal efficiency of the entire system.

  Further, according to the present invention, the pyrolysis gas (P) obtained by pyrolysis or gasification can be supplied to the heating device (4) of the Stirling engine in a controllable manner. A high thermal efficiency power generation system using gas as a heat source, for example, a high thermal efficiency power generation system in which a plurality of Stirling engines are arranged in parallel can be constructed.

From another aspect, the present invention provides a control method for a power generation system including a Stirling engine (11) including a heating device (4) for heating a working fluid, and a generator (12) driven by the Stirling engine. In
The flow rate and / or temperature of the hot gas generated by burning the pyrolysis gas (P) obtained by pyrolysis or gasification of solid fuel or liquid fuel is controlled, and the flow rate and / or temperature of the hot gas is controlled. A method for controlling a power generation system is provided, characterized in that the method is supplied to a heat transfer section (13) of the heating device (4).

The present invention also provides a control method of a power generation system including a Stirling engine (11) including a heating device (4) for heating a working fluid, and a generator (12) driven by the Stirling engine.
The pyrolysis gas (P) obtained by pyrolysis or gasification of solid fuel or liquid fuel is reformed with steam, and the reformed gas (R) is controlled by the flow rate control means (6; 60). A control method for a power generation system is provided, wherein the working fluid is supplied to the combustion section (41) of (4) and the working fluid is heated by the combustion heat of the reformed gas.

The present invention further includes a Stirling engine (11) provided with a heating device (4) for heating a working fluid, and a power generation system control method comprising a generator (12) driven by the Stirling engine.
Part of the pyrolysis gas (P) obtained by pyrolysis or gasification of solid fuel or liquid fuel, or part of the reformed gas (R) obtained by reforming the pyrolysis gas with steam The pyrolysis gas supplied to both the fuel gas supply means and the combustion air supply system is supplied to the combustion air supply system (8; 9; 52; L61; L62) and mixed with the combustion air. Alternatively, the present invention provides a method for controlling a power generation system, wherein the working fluid is heated by combustion heat of reformed gas.

  According to the above-described configuration of the present invention, (i) the flow gas and / or temperature-controlled hot gas flow (HG) is supplied to the heating device (4) of the type including the heat transfer section (13), (ii) The heating device (4) of the type provided with the combustion section (41) is supplied with the reformed gas whose flow rate is controlled by the flow rate control means (6; 60), or (iii) the combustion section (41 ) With a heating device (4) of the type provided with a fuel gas supply means (6; 60; 90; L8) and a combustion air supply system (8; 9; 52; L61; L62). A cracked gas or a reformed gas is supplied. With such a configuration, the pyrolysis gas (P) obtained by pyrolysis or gasification is supplied to the heating device of the Stirling engine as a controllable heat source. Further, according to the present invention, the pyrolysis gas (P) obtained by pyrolysis or gasification can be supplied to the heating device (4) of the Stirling engine in a controllable manner. A power generation system having high thermal efficiency and high power generation output as a heat source can be constructed with a plurality of Stirling engine generators.

  In the present invention, solid fuel or liquid fuel is a concept including not only solid fuel or liquid fuel but also semi-solid fuel, slurry fuel, etc. that can be gasified.

  According to the power generation system and the power generation system control method of the present invention, the Stirling engine is operated using the pyrolysis gas of solid fuel or liquid fuel obtained in the gasification furnace or pyrolysis furnace as a heat source, and the Stirling engine is used as a drive source. The power generation output of the generator to be controlled can be controlled from the heat source side to improve the thermal efficiency of the entire system.

  Preferably, a heat exchanger (5) that cools the hot gas (HG) that has passed through the heating device (4) is disposed downstream of the heating device, and by exhaust gas flow rate control of the hot gas flow that has passed through the heat exchanger, The flow rate of the hot gas flow to be supplied to the heating device is controlled. The flow rate of the hot gas cooled by the heat exchanger can be directly controlled by the flow rate control valve (6) that can control the opening, and therefore the exhaust gas flow rate control can accurately control the hot gas flow rate of the heating device. Can be controlled.

  Preferably, the temperature control means (9) variably controls the flow rate of combustion air (CA; HA) to be supplied to the combustion device (3). As a result, the air-fuel ratio of the combustion device (3) is controlled, and the temperature of the hot gas flow changes according to the air-fuel ratio. That is, the temperature of the hot gas supplied to the heating device is controlled by controlling the flow rate of combustion air to be supplied to the combustion device (3).

  More preferably, the combustion air (CA; HA) exchanges heat with the hot gas stream that has passed through the heating device (4) and is preheated by the sensible heat that the hot gas has. A high temperature-efficiency heat exchanger (5) capable of heating the combustion air at a high temperature to a high temperature of 500 ° C. or higher and cooling a hot gas flow of 600 ° C. or higher to a temperature of 300 ° C. or lower It is desirable to arrange on the downstream side. Such preheating of the combustion air (CA; HA) by the heat exchanger is not only effective in maintaining and promoting the combustion reaction of the combustion device (3), but also reduces the hot gas exhaust temperature. This is advantageous in simplifying the structure of the flow rate control valve (6) described above.

  According to the present invention, a highly efficient power generation system in which a plurality of Stirling engines are arranged in parallel can be constructed. Such a power generation system includes a plurality of Stirling engines (11), a plurality of hot gas flow paths (L3) for supplying a hot gas flow (HG) to a heating device (4) of each Stirling engine, and a hot gas flow. And a hot gas main channel (L30) connected to the upstream end of the channel. The flow control valves (6A; 6B; 6C; 6D) described above variably control the exhaust gas flow rate (HG) in each hot gas flow path, and thereby, the hot gas to be supplied to each heating device. Each flow rate is controlled. The combustion device (3) is arranged upstream of the hot gas main flow path, and the temperature control means (9A; 9B; 9C; 9D) is a combustion air (CA) to be supplied to the combustion device (3). ; Control the flow rate of HA) variably. The temperature of the hot gas flow (HG) is controlled by controlling the flow rate of combustion air (CA; HA), and the heat gas flow (HG) is controlled by the flow control valve (6A; 6B; 6C; 6D). It is distributed to the gas flow path (L3).

  When the hot gas contains a large amount of dust or the like, it is preferable that a dust removing means (2; 54) for removing the hot gas is disposed in the path between the heating device (4) and the pyrolysis gas generation source (1; 3). Be placed. For example, dust removing means (2) for removing dust from pyrolysis gas obtained by pyrolysis or gasification of solid fuel or liquid fuel is provided on the downstream side of the pyrolysis furnace or gasification furnace. When pyrolysis gas contains a large amount of corrosive components, a reformer (50) that reforms the pyrolysis gas with water vapor and air or with water vapor and oxygen, and cooling and refining to purify and cool the corrosive components in the gas It is desirable to provide a device (54; 55) and to reform, cool and purify the pyrolysis gas before supplying it to the combustion zone. Note that when the pyrolysis gas supplied to the reformer already contains a relatively large amount of water vapor, the pyrolysis gas can be reformed by supplying air or oxygen to the reformer.

  As described above, the present invention can be applied to a power generation system including a Stirling engine of a type in which pyrolysis gas (P) or reformed gas (R) is combusted in a combustion zone (40) of a heating device (4). it can. According to the present invention, the pyrolysis gas (P) has a temperature range in which the pressure can be pressurized by the pressure fan (60) and the flow rate control valve (6) and the flow rate can be controlled, and the water vapor does not condense. Alternatively, the reformed gas (R) can be supplied to the combustion zone (40). For example, the temperature of the pyrolysis gas (P) or the reformed gas (R) supplied to the heating device (4) can be set in the range of 100 to 300 ° C., for example, about 200 ° C. A Stirling engine generator equipped with this type of heating device has a high thermal efficiency or generator efficiency, so that a relatively low calorific value of pyrolysis gas (P) or reformed gas (R) is used as a heating device (4). Even when it is supplied to the combustion zone (40), it operates effectively.

  The use of this type of Stirling engine is also advantageous in reducing the heat required for the reforming process of the pyrolysis gas (P). For example, even when a reformed gas is obtained by a simple reforming process using relatively low temperature air and water vapor (for example, air at atmospheric temperature and water vapor of about 100 ° C.), such reforming is performed. Gas can be supplied to the combustion section (41) of the heating device (4).

  Further, by setting the temperature of the reformed gas (R) supplied to the heating device (4) within the above temperature range (100 to 300 ° C.), water vapor contained in the gas after the reforming process is condensed in the system. This can prevent the condensate drainage treatment. The water vapor contained in the reformed gas (R) is only exhausted out of the system together with the combustion exhaust gas.

  Preferably, the power generation system includes combustion means for burning excess pyrolysis gas (P) or reformed gas (R) in an exhaust device (71) such as an exhaust pipe. This combustion means includes a heat exchanger (83) for transferring the combustion heat of the pyrolysis gas (P) or the reformed gas (R) to the reforming air. The reforming air (WA) after the temperature rise is supplied to the reforming furnace (50).

  1 and 2 are a system flow diagram and a schematic cross-sectional view showing the overall configuration of the power generation system according to the first embodiment of the present invention.

  The power generation system includes a gasification furnace 1 that generates pyrolysis gas, and a power generation apparatus 10 that supplies power to a power receiving facility outside the system. The power generation device 10 includes a Stirling engine 11 and a generator 12. The gasification furnace 1 is supplied with solid fuel W, for example, combustible waste such as municipal waste and waste plastics, and gasification air LA is supplied by a gasification air blower 15. The gasification furnace 1 generates a pyrolysis gas P including a relatively large amount of combustible components by pyrolysis of the solid fuel W. The gasification furnace 1 is connected to the dust collector 2 via the pyrolysis gas feed pipe L1, and the dust collector 2 is connected to the combustion apparatus 3 via the purified gas feed pipe L2. As the gasification furnace 1, for example, a gasification furnace described in Japanese Patent Application No. 2001-10831 according to the invention of the present inventors can be exemplified.

  The dust collector 2 includes a heat-resistant metal filter, a cyclone dust collector, or a ceramic filter. The pyrolysis gas P of the gasification furnace 1 from which dust, dust and the like have been removed by the dust collector 2 is supplied to the combustion device 3 via the purified gas supply pipe L2. A cyclonic combustor having both dust collection and combustion functions can also be used as the dust collection device 2 and the combustion device 3.

  The high-temperature air supply pipe L7 is connected to the high-temperature air introduction port 31 of the combustion device 3, and the high-temperature combustion air HA preheated by the heat exchanger 5 is supplied to the combustion device 3. The pyrolysis gas P is mixed with the high-temperature combustion air HA in the combustion chamber 30 of the combustion apparatus 3, and the combustible components of the pyrolysis gas P are combusted. As a result, high-temperature hot gas is generated in the combustion chamber 30. .

  The upstream end of the hot gas supply pipe L3 is connected to the outlet side of the combustion device 3. The downstream end of the hot gas supply pipe L <b> 3 is connected to the heating device 4 of the Stirling engine 11. The hot gas generated in the combustion chamber 30 is supplied to the heating device 4 as a hot gas flow HG. In the heating device 4, a heater tube 13 that constitutes a heat transfer unit of the Stirling engine 11 is disposed. The working fluid such as helium and hydrogen sealed in the heater tube 13 exchanges heat with the hot gas through the tube wall of the heater tube 13 and receives the sensible heat of the hot gas. The working fluid changes its state according to a Stirling cycle consisting of processes of isovolume heating, isothermal expansion, isovolume cooling, and isothermal compression, and converts the heat received from the hot gas into motive power to convert the piston (not shown) in the Stirling engine 11. )). The driving force of the piston is output to the generator 12 to operate the generator 12, and the generator 12 supplies power to the power receiving equipment outside the system. If desired, the Stirling engine 11 includes exhaust heat recovery means (not shown) for supplying a heat medium fluid (hot water or the like) heated by exhaust heat recovery in a cooling unit of the engine itself to any facility outside the system.

  The hot gas flow HG exchanged with the working fluid in the heating device 4 is supplied to the heat exchanger 5 via the hot gas feed pipe L4. A combustion air supply pipe L 6 is connected to the heat receiving pipe 51 of the heat exchanger 5. The combustion air CA is supplied to the heat receiving pipe 51 of the heat exchanger 5 under the supply pressure of the supply fan 8, exchanges heat with the hot gas flow HG, and is heated. The heated combustion air HA is supplied to the combustion chamber 30 via the high-temperature air supply pipe L7 and causes the combustion reaction of the pyrolysis gas P to occur in the combustion chamber 30 as described above. A flow control valve 9 is interposed in the combustion air supply pipe L6. The flow control valve 9 is connected to the control device 20 via a control signal line (indicated by a broken line in FIG. 1). The flow rate of the combustion air HA supplied to the combustion chamber 30 is variably controlled by the flow rate control valve 9 under the control of the control device 20.

  An exhaust pipe L5 is connected to the outlet side of the heat exchanger 5, and the hot gas flow HG after the temperature reduction is sent from the heat exchanger 5 to the exhaust pipe L5 as exhaust gas EG. The suction port of the exhaust fan 7 is connected to the downstream end of the exhaust pipe L5. If desired, a heat exchanger 25 (shown in phantom) for recovering exhaust heat is interposed in the exhaust pipe L5, and the heat exchanger 25 recovers exhaust heat of the exhaust gas EG, and supplies hot water or water vapor outside the system. Supply to the equipment. The exhaust fan 7 sucks the exhaust gas EG from the exhaust pipe L5 and exhausts it outside the system through a stack or the like (not shown). Since the exhaust gas EG has already been cooled by heat exchange with the combustion air (and feed water), the exhaust fan 7 can directly suck the exhaust gas EG. Thus, the hot gas in the hot gas supply pipe L3 is supplied to the heating device 4 as a hot gas flow HG by the suction action of the exhaust fan 7, and passes through the heating device 4 and the heat exchanger 5 (and the heat exchanger 25). Exhausted outside the system.

  A flow rate control valve 6 for controlling the flow rate of the exhaust gas EG is interposed in the exhaust pipe L5. The flow control valve 6 is connected to the control device 20 via a control signal line (indicated by a dotted line). The flow rate control valve 6 variably controls the flow rate of the hot gas flow HG supplied from the combustion device 3 to the heating device 4 by controlling the flow rate of the exhaust gas EG. Since the flow rate control valve 6 in contact with the relatively low temperature exhaust gas EG has a control valve structure capable of controlling the flow rate smoothly and precisely, the flow rate of the exhaust gas EG can be accurately controlled.

The gas temperatures T1, T2, T3, T4, and T5 of the pyrolysis gas supply pipe L1, the purified gas supply pipe L2, the hot gas supply pipes L3 and L4, and the exhaust pipe L5 are set as follows, for example. .
T1: 200-800 ° C
T2: 200-800 ° C
T3: 800-1200 ° C
T4: 600-900 ° C
T5: 100-300 ° C

The air temperatures T6 and T7 of the combustion air supply pipe L6 and the high temperature air supply pipe L7 are set as follows, for example.
T6: Atmospheric temperature (for example, 20 ° C.)
T7: 500-800 ° C

  A flow rate detector and a temperature detector (not shown) are arranged at appropriate positions in each of the pipelines L1 to L7, and the flow rate and temperature of the pipelines L1 to L7 are input to the control device 20 from each detector. Factors or numerical values indicating the operating states of the Stirling engine 11 and the generator 12, for example, information such as engine speed and power generation output are also input to the control device 20. The control device 20 controls starting and stopping of the fans 7 and 8 and controls the opening degree of the flow control valves 6 and 9.

  For example, the control device 20 increases the opening degree of the flow control valve 9 when it is necessary to reduce the output of the Stirling engine 11 in a state where an air amount close to the theoretical air-fuel ratio is supplied to the combustion device 3. The amount of air supplied to the combustion device 3 is increased. Thereby, the mixing ratio of the combustion air HA and the pyrolysis gas P, that is, the air-fuel ratio of the combustion chamber (combustion zone) 30 is increased, and a large amount of air exceeding the theoretical air-fuel ratio is supplied to the combustion device 3. The hot gas temperature T3 decreases as the amount of air increases, and as a result, the output of the Stirling engine 11 decreases. Conversely, when the output of the Stirling engine 11 needs to be increased, the control device 20 reduces the air-fuel ratio of the combustion chamber 30 by reducing the opening of the flow control valve 9. As a result, air with an air quantity close to the stoichiometric air-fuel ratio is supplied to the combustion device 3, the hot gas temperature T3 rises, and the output of the Stirling engine 11 increases.

  Similarly, when the output of the Stirling engine 11 needs to be reduced, the control device 20 reduces the opening degree of the flow rate control valve 6 and reduces the flow rate of the hot gas flow HG supplied to the heating device 4. Due to the decrease in the hot gas flow rate, the amount of heat transferred from the hot gas flow HG to the working fluid of the heater tube 13 decreases, and the output of the Stirling engine 11 decreases. The decrease in the opening degree of the flow rate control valve 6 simultaneously decreases the flow rate of the hot gas flowing through the heat exchanger 5, so that the amount of heat transferred from the hot gas flow HG to the combustion air CA also decreases. As a result, the air temperature T7 of the combustion air HA supplied to the combustion chamber 30 decreases. This causes a drop in the hot gas temperature T3, which further reduces the output of the Stirling engine 11.

  Conversely, when the output of the Stirling engine 11 needs to be increased, the control device 20 increases the opening degree of the flow control valve 6 and increases the flow rate of the hot gas flow HG supplied to the heating device 4. The amount of heat transferred from the hot gas flow HG to the working fluid of the heater tube 13 increases as the hot gas flow rate increases, and the output of the Stirling engine 11 increases. The increase in the opening degree of the flow control valve 6 increases the flow rate of the hot gas flow HG supplied to the heat exchanger 5 at the same time, so that the amount of heat transferred from the hot gas flow HG to the combustion air CA increases. As a result, the air temperature T7 of the combustion air HA supplied to the combustion chamber 30 rises, and accordingly, the temperature T3 of the hot gas flow HG also rises. The output of 11 further increases.

  Thus, the temperature and flow rate of the combustion exhaust gas HG are controlled by the opening degree control of the flow rate control valves 6 and 9, whereby the output of the Stirling engine 11 is controlled. When the power demand or power load on the power receiving side fluctuates, the control device 20 controls the opening degree of the flow control valves 6 and 9, and controls the power generation output of the generator 12 to a target value suitable for the power demand or power load. can do. The hot gas supply pipe L3 is connected to an exhaust pipe L25 (shown by a virtual line) for transiently discharging excess hot gas that may be generated during the opening degree control of the flow control valve 6 to the outside of the system. .

  The power generation system shown in FIGS. 1 and 2 has a configuration in which a single heating device 4 and a power generation device 10 (a Stirling engine 11 and a generator 12) are provided to the gasification furnace 1, but the present invention is This is applicable to a power generation system having a configuration in which a plurality of power generation devices 10 are connected in parallel to the combustion device 3. In FIG.1 and FIG.2, the pipe line L21 which can supply the hot gas flow HG with respect to the electric power generating apparatus 10 of another system | strain is shown with the virtual line. The pipe L21 branches from the hot gas supply pipe L3 and supplies the hot gas flow HG to the heating device 4 and the heat exchanger 5 of the power generation device 10 of another system. A pipe line L22 (shown in phantom) that exhausts the hot gas flow HG flowing through the heating device 4 and the heat exchanger 5 of another system as the exhaust gas EG is connected to the exhaust pipe L5.

  FIG. 3 is a schematic cross-sectional view generally showing a power generation system having a configuration in which a plurality of power generation devices 10 and a heat exchanger 5 are connected to the combustion device 3 in parallel. 3, components that are substantially the same as those shown in FIGS. 1 and 2 are given the same reference numerals.

  The power generation system shown in FIG. 3 has a configuration in which four power generation devices 10A: 10B: 10C: 10D are connected to the combustion device 3 in parallel. The hot gas main pipe L30 is connected to the outlet of the combustion device 3, and the upstream ends of the four hot gas supply pipes L3 are connected to the main pipe L30. Heating devices 4A: 4B: 4C: 4D of the respective Stirling engines 11A: 11B: 11C: 11D are connected to the downstream ends of the feed pipes L3, respectively, and the heat exchangers 5A: 5B: 5C: 5D are hot gases. It connects with each heating apparatus 4A: 4B: 4C: 4D via the feed pipe L4. Each heat exchanger 5A: 5B: 5C: 5D is connected to the exhaust main pipe L50 via the exhaust pipe L5, and the downstream end of the exhaust main pipe L50 is connected to the exhaust fan 7. Each exhaust pipe L5 is provided with a flow control valve 6A: 6B: 6C: 6D. The flow rate control valves 6A: 6B: 6C: 6D control the exhaust gas flow rate, thereby variably controlling the flow rate of the hot gas flow HG supplied to each heating device 4A: 4B: 4C: 4D.

  The combustion air supply pipe L6 connected to the heat receiving pipe 51 of each heat exchanger 5A: 5B: 5C: 5D is connected to the low temperature air main pipe L60, and the upstream end of the low temperature air main pipe L60 is the discharge of the air supply fan 8 Connected to the exit. Each heat receiving pipe 51 is connected to a high temperature air supply pipe L7. The high temperature air supply pipe L7 is connected to the high temperature air main pipe L70. The downstream end of the hot air main pipe L70 is connected to the hot air inlet 31 of the combustion device 3. Each high temperature air supply pipe L6 is provided with a flow control valve 9A: 9B: 9C: 9D for controlling the amount of air to be supplied to each heat receiving pipe 51.

  The main pipe L30 functions as a collecting pipe (manifold) for the four high-temperature gas supply pipes L3, and the main pipe L50 functions as a collecting pipe (manifold) for the four exhaust pipes L5. The power generation outputs of the power generators 10A: 10B: 10C: 10D of each system are controlled according to the opening control of the flow control valves 6A to 6D and 9A to 9D.

  The flow control valves 6A to 6D and 9A to 9D are connected to the control device 20 via control signal lines (indicated by dotted lines), and control the flow rates of the hot gas flow HG and the combustion air CA under the control of the control device 20. . Detected values of flow rate detectors and temperature detectors (not shown) of the respective pipelines L1 to L7, factors or numerical values indicating the operating states of the Stirling engines 11A to 11D and the generators 12A to 12D (engine speed and power generation output, etc.) ) Is input to the control device 20. The control device 20 controls the starting and stopping of the fans 7 and 8 and also controls the opening degree of the flow rate control valves 6A to 6D and 9A to 9D, thereby controlling the flow rates of the hot gas flow HG and the combustion air CA. Control.

  If desired, as in the embodiment shown in FIG. 1, a heat exchanger 25 (shown by phantom lines) for exhaust heat recovery is interposed in the exhaust main pipe L50. The heat exchanger 25 collects excess exhaust heat of the combustion exhaust gas and supplies hot water, steam, or the like to any facility outside the system.

  Further, an exhaust pipe L25 (shown by phantom lines) that discharges excess hot gas that may be generated during the opening degree control of the flow control valve 6 or its heat to the outside of the system is connected to the hot gas main pipe L30 as necessary. .

  Hereinafter, the operation of the power generation system shown in FIG. 3 will be described.

  The solid fuel W supplied to the gasification furnace 1 is pyrolyzed in the gasification furnace 1 to generate a pyrolysis gas P. The pyrolysis gas P is supplied to the dust collector 2 via the pyrolysis gas feed pipe L1, and the dust collector 2 removes dust, dust and the like in the pyrolysis gas. The purified pyrolysis gas is mixed and contacted in the combustion chamber 30 with the high temperature air injected from the high temperature air inlet 31 and burns. Hot hot gas generated in the combustion device 3 flows out to the main pipe L30. Since the hot gas flow rate of each hot gas supply pipe L3 is controlled by opening control of the flow control valves 6A to 6D, the hot gas flow HG of the main pipe L30 follows the opening control of the flow control valves 6A to 6D. It flows into each feed pipe L3. Therefore, by controlling the opening degree of the flow control valves 6A to 6D, the hot gas flow rate or the hot gas distribution ratio of each feed pipe L3 is controlled, and the outputs of the respective power generators 10A: 10B: 10C: 10D can be individually controlled. it can.

  4 to 6 exemplify operation modes of the power generation system.

  For example, as shown in FIG. 4, the control device 20 sets the flow control valves 6 </ b> A to 6 </ b> D and 9 </ b> A to 9 </ b> D to predetermined opening degrees, and the power generation system performs steady operation with a predetermined power generation output. In this state, an appropriate amount of hot gas flow HG corresponding to the opening degree of the flow control valves 6A to 6D is supplied from the main pipe L30 to the heating devices 4A to 4D and the heat exchangers 5A to 5D of the Stirling engines 11A to 11D. . In such an operating state, the control device 20 sets the opening degree of the flow rate control valves 9 </ b> A to 9 </ b> D so that, for example, combustion air corresponding to the theoretical combustion air-fuel ratio of the combustion device 3 is supplied to the combustion device 3.

  When lowering the power generation output of the power generation system, the control device 20 decreases the flow rate of the hot gas flow HG supplied to the heating devices 4A to 4D by reducing the opening degree of the flow control valves 6A to 6D. At the same time, the control device 20 increases the opening degree of the flow rate control valves 9A to 9D and increases the amount of combustion air supplied to the combustion device 3. Such a state is shown in FIG. The flow rate of the hot gas flow HG supplied to each of the heating devices 4A to 4D is decreased and the temperature is decreased. As a result, the output of each Stirling engine 11A to 11D is decreased, and the power generation output of the power generation system is decreased.

  FIG. 6 shows an operation mode in which the flow rate control valves 6A: 6B and 9A: 9B are switched to the fully closed positions. In this operation mode, the system of the power generation devices 10A: 10B completely stops operation, and the power generation system operates as a power generation system in which two power generation devices 10C: 10D are arranged in parallel.

  Controls that can be executed by opening control or switching control of the flow control valves 6A to 6D and 9A to 9D are not limited to the control forms shown in FIGS. Control of the power generation output of the system can be executed in various control modes.

  For example, the control device 20 includes a control unit that stores a preset control map, a control program, and the like, and the control unit controls the opening of the flow control valves 6A to 6D and 9A to 9D to generate power of the power generation system. Variable control of output. A wide variety of patterns can be adopted as the opening settings of the flow control valves 6A to 6D and 9A to 9D, and the control unit can operate the power generation system in a highly efficient manner in accordance with fluctuations in power demand or power load. Is controlled by controlling the opening degree of the flow control valves 6A to 6D, 9A to 9D.

  Such start / stop control and opening degree control of the power generation devices 10A to 10D and the flow rate control valves 6A to 6D and 9A to 9D can be used only as power generation output control means for controlling the power generation output during steady operation of the power generation system. However, it can be applied as an operation control means during warm-up operation, maintenance operation or emergency operation of the power generation system. The control unit of the control device 20 stores a control map and a control program for controlling the operation in the transition period, and performs a smooth warm-up operation of the power generation system, a maintenance operation, a quick emergency operation, or the like. to enable.

  FIG. 7 is a system flow diagram showing the overall configuration of the power generation system according to the second embodiment of the present invention. In FIG. 7, constituent elements that are substantially the same as those shown in FIGS. 1 to 6 are given the same reference numerals.

The power generation system shown in FIG. 7 is further provided with a reforming furnace 50, an air preheater 52, an exhaust heat boiler 53, a cooling / refining device 55, and a high-temperature air / high-temperature steam generator 56, as described in the first embodiment. Is different. This configuration can be suitably employed when the pyrolysis gas P contains a relatively large amount of corrosive gas (H ₂ S; HCl; NH ₃ ; HCN, etc.). According to such a power generation system, for example, any fuel such as general waste, waste plastics, and rubber can be gasified in the gasification furnace 1 and supplied to the power generation apparatus 10. That is, the power generation system of the present embodiment including the reforming process and the cooling / refining process enables diversification of fuels (raw materials) that can be supplied to the power generation system.

  The gasification furnace 1 is supplied with combustible waste as solid fuel W, and the pyrolysis gas P generated by thermal decomposition of the solid fuel W is supplied to the reforming furnace 50. The pyrolysis gas P is reformed by high-temperature steam and air supplied to the reforming furnace 50, and the tar content contained in the pyrolysis gas P is decomposed. The reformed gas R flows through the flow paths L11: L12: L13: L14, the air preheater 52, the exhaust heat boiler 53, the dust collector 54, and the cooling / purifying device 55, and is combusted from the reformed gas supply pipe L2. 3 is supplied. Dust and dust contained in the pyrolysis gas P are removed by the dust collector 54. The corrosive gas contained in the pyrolysis gas P is removed by the cooling / purification device 55. The air preheater 52 heats air at ambient temperature with the sensible heat of the reformed gas R, and supplies the preheated air from the flow path L15 to the gasifier 1. Further, the exhaust heat boiler 53 generates water vapor by the sensible heat of the reformed gas R, and the water vapor S is sent to the flow path L16 and together with the air supplied to the flow path L16, a high temperature air / high temperature steam generator. 56. A part of the reformed gas R is supplied from the flow path L18 to the high temperature air / high temperature steam generator 56 as fuel for heating the steam and air. Steam and air are heated by combustion heat. The heated steam and air are supplied from the flow path L17 to the reforming furnace 50, mixed and contacted with the pyrolysis gas P, and reform the pyrolysis gas P as described above.

The gas temperatures T1, T2, T11, T12, T13, T14, T16, and T17 in the pyrolysis gas supply pipe L1, the purified gas supply pipe L2, and the flow paths L11: L12: L13: L14: L16: L17 are, for example, Are set as follows.
T1: 200-300 ° C
T2: 30 to 150 ° C
T11: 600-1000 ° C
T12, T13, T14: 200-500 ° C
T16: about 100 to 200 ° C.
T17: 500-1000 ° C

  The gas temperatures T3, T4, T5 of the hot gas supply pipes L3, L4 and the exhaust pipe L5 are as described above. As the reforming furnace 50, a reforming furnace described in Japanese Patent Application No. 2001-10831 according to the invention of the present inventors can be suitably used.

  Since the configuration of the power generation system on the downstream side of the combustion device 3 is substantially the same as the configuration shown in FIGS. 1 and 2, the description relating to the configuration in FIGS. To do.

  8 and 9 are a system flow diagram and a schematic cross-sectional view showing the overall configuration of the power generation system according to the third embodiment of the present invention. 8 and 9, the same reference numerals are assigned to substantially the same components as those shown in FIGS. 1 to 7.

  The power generation system of the present embodiment has a configuration in which the reformed gas R is directly introduced into the heating device 4 of the Stirling engine 11 and burned in the heating device 4, and the heating device 4 constitutes a combustor.

  The gasification furnace 1 is supplied with combustible waste as solid fuel W, and the pyrolysis gas P generated by thermal decomposition of the solid fuel W is supplied to the reforming furnace 50. Steam and air are supplied to the reforming furnace 50, and the steam and air decompose the tar content in the pyrolysis gas and reform the pyrolysis gas P. The reformed gas R flows through the flow path L11, the exhaust heat boiler 53, the flow path L13, the dust collector 54, and the flow path L14, and is sucked into the pressurized fan 60. The exhaust heat boiler 53 heats the feed water by the sensible heat of the reformed gas R to generate steam S, and the steam S is supplied to the reforming furnace 50 via the flow path L16. A flow rate control valve 91 is interposed in the flow path L16. In addition, surplus water vapor is supplied to any equipment inside or outside the system via the pressure control valve 92 or is released to the atmosphere.

  The upstream end of the reformed gas supply pipe L8 is connected to the discharge port of the pressurizing fan 60. The downstream end of the reformed gas supply pipe L8 is connected to the combustion unit 41 of the heating device 4. The reformed gas R is supplied to the combustion unit 41 as a relatively low temperature fuel gas under the pressure of the pressurized fan 50. The combustion air HA preheated to a high temperature by the air preheating unit 51 of the heating device 4 is supplied to the combustion unit 41. The reformed gas R is mixed with combustion air and combusted to generate a flame in the combustion zone 40 in the heating device 4.

  A flow control valve 6 is interposed in the reformed gas supply pipe L8. The flow control valve 6 controls the flow rate of the reformed gas R supplied to the combustion unit 41. Since the reformed gas R has a relatively low temperature, the pressurizing fan 50 can suck and pressurize the reformed gas R, and the flow rate control valve 6 accurately adjusts the flow rate of the reformed gas R. A controllable structure can be provided.

  The air preheating part 51 is arrange | positioned in the heating apparatus 4, and the downstream end (outflow end) of the heat exchanger 51 directs the combustion air after a preheating to the combustion part 41. FIG. The upstream end (inflow end) of the heat exchanger 51 is connected to the combustion air supply pipe L6. An air supply fan 8 is connected to the upstream end of the combustion air supply pipe L6. The combustion air CA is pumped to the combustion air supply pipe L <b> 6 under the supply pressure of the supply fan 8 and supplied to the air preheating unit 51. The combustion air CA flowing through the air preheating unit 51 exchanges heat with the combustion exhaust gas generated in the combustion zone 40 and is heated to a high temperature. Thereafter, the combustion air CA is supplied to the combustion unit 41 as the high-temperature combustion air HA. Thus, it is mixed with the reformed gas R and undergoes a combustion reaction.

  A heater tube 13 constituting a heat receiving portion of the heating device 4 is disposed in the combustion zone 40 of the heating device 4, and working fluid such as helium and hydrogen sealed in the heater tube 13 is generated in the combustion zone 40. It is heated to a high temperature by the radiant heat transfer action and convection heat transfer action of the flame and combustion gas. The working fluid changes its state according to a Stirling cycle consisting of processes of isovolume heating, isothermal expansion, isovolume cooling, and isothermal compression, and converts the heat received from the hot gas into motive power to convert the piston (not shown) in the Stirling engine 11. )). The driving force of the piston is output to the generator 12 to operate the generator 12, and the generator 12 supplies power to the power receiving equipment outside the system. If desired, the Stirling engine 11 includes exhaust heat recovery means (not shown) for supplying a heat medium fluid (hot water or the like) heated by exhaust heat recovery of the cooling unit to any facility outside the system.

  The exhaust pipe L5 is connected to the heating device 4. The exhaust gas EG in the combustion zone 40 is sent to the stack 71 via the exhaust pipe L5, and is released from the stack 71 to the atmosphere. If desired, an exhaust fan (not shown) is interposed in the exhaust pipe L5. Connected to the stack 71 is an exhaust pipe L25 (indicated by a dotted line) for transiently discharging excess reformed gas from the reformed gas supply pipe L8 to the outside of the system. A flow control valve 93 is interposed in the exhaust pipe L5. The stack 71 includes combustion means (not shown) for burning such reformed gas in the exhaust stack. A heat exchanger 83 is disposed in the stack 71, and an upstream end (inflow end) of the heat exchanger 83 is connected to the reforming air supply pipe L18, and a downstream end (outflow end) of the heat exchanger 83. ) Is connected to the reforming air supply pipe L19. The feed pipe L19 is connected to the reforming furnace 50. The reforming air supply fan 81 is connected to the supply pipe L <b> 18, and the reforming air OA is supplied to the heat exchanger 83 under the supply pressure of the fan 81. The reforming air OA receives the exhaust heat in the stack 71 and then is supplied to the reforming furnace 50 from the feed pipe L19 as the reforming air WA after the temperature rise. A flow rate control valve 82 is interposed in the supply pipe L18.

  A flow rate detector and a temperature detector (not shown) are arranged at appropriate positions in each pipeline or flow path constituting the power generation system, and the flow rate and temperature of each pipeline or flow path are controlled from each detector. 20 is input. Factors or numerical values indicating the operating states of the Stirling engine 11 and the generator 12, for example, information such as engine speed and power generation output are also input to the control device 20. Each of the control valves 6, 9, 82, 91, 92, 93 is connected to the control device 20 through a control signal line indicated by a broken line in FIG. 8 and is controlled by the control device 20.

The gas temperatures T1, T5, T6, T8, T11, T13, T14, T16, T18, and T19 at each pipe line or flow path L1: L5: L6: L8: L11: L13: L14: L16: L18: L19 are: For example, it is set as follows.
T1: 200-300 ° C
T8, T13, T14: about 200 ° C
T5: 200-400 ° C
T6, T18: Atmospheric temperature (for example, 20 ° C.)
T11: 800-1000 ° C
T16, T19: about 100 to 200 ° C.

  The power generation system of this embodiment supplies a relatively low temperature (about 200 ° C.) reformed gas R as a combustible gas to the combustion zone 40 in the heating device 4, and combustion heat generated by the combustion reaction of the reformed gas R. Is different from the first and second embodiments (FIGS. 1 to 7) described above in that the heater tube 13 is heated, and the temperatures T16 and T19 of the steam and air supplied to the reforming furnace 50 are compared. 7 is different from the second embodiment shown in FIG. 7 (relatively high temperature steam and air (500 to 1000 ° C.) are supplied to the reforming furnace 50) in that the temperature is set to a low temperature (about 100 to 200 ° C.). .

  In contrast to the configurations of the first and second embodiments (FIGS. 1 to 7) described above, in the present embodiment, the reformed gas R is supplied to the heating device 4 and the combustion reaction of the reformed gas R is heated. 4, the heater tube 13 is efficiently heated by the radiation heat transfer effect and the convection heat transfer effect using the combustion heat of the reformed gas R. The generator efficiency of the power generator 10 can be greatly improved.

  Further, when compared with a power generation system of a type that supplies such reformed gas to an internal combustion type mixed fuel diesel engine, in the power generation system of the present embodiment, steam and air temperatures T16 to be supplied to the reforming furnace 50, T19 is set to a considerably low temperature (about 100 to 200 ° C.). Therefore, according to the power generation system of this embodiment, the thermal efficiency of the entire power generation system can be improved.

  The latter characteristic will be described below by comparing the power generation system that supplies the reformed gas to the internal combustion type mixed fuel diesel engine and the power generation system of the present embodiment.

  In a power generation system using an internal combustion type mixed fuel diesel engine, the fuel gas to be supplied to the diesel engine needs to be reformed into a high-quality fuel gas having a relatively high calorific value, and is supplied to the reforming process. It is necessary to preheat the air and water vapor to a high temperature. For this reason, not only can the temperature management and flow rate control of air and steam be difficult, but if reformed gas containing undecomposed tar content continues to be supplied to the diesel engine as a result of insufficient reforming There is also concern that the maintenance of diesel engines will be difficult. Moreover, since the fuel gas (reformed gas) to be introduced into the internal combustion engine of the diesel engine needs to be cooled to about room temperature (about 40 ° C.), a relatively large amount of condensed water is brought into the system by condensation of water vapor. It is necessary to provide a drainage route for generating and discharging this to the outside, a wastewater treatment facility, and the like.

  On the other hand, in the present embodiment (FIGS. 8 and 9), even if the fuel gas (reformed gas R) has a relatively low calorific value, it can be effectively used as the fuel for the Stirling engine 11. For this reason, even if it is 100 degreeC water vapor | steam and normal temperature (atmospheric temperature) air, this can be used as a modification | reformation adjuvant, Therefore, heating load, such as water vapor | steam and air which should be supplied to a modification | reformation process, is carried out. Reduce. Thereby, the thermal efficiency of the entire system is improved, and the temperature management and flow rate control of water vapor and air required for the reforming process are simplified. For example, in this embodiment, the high temperature air / high temperature steam generator shown in FIG. 7 is omitted. Moreover, according to the power generation system of the present embodiment, a gas generation source (waste etc.) that only generates a pyrolysis gas having a relatively low calorific value can be used, so that the management of solid fuel or liquid fuel is possible. Can be simplified. Further, the reformed gas R to be supplied to the heating device 4 of the Stirling engine 11 does not need to be cooled to about 40 to 50 ° C. as in the case of supplying to the internal combustion engine of a diesel engine, and is relatively high (100 to 100 ° C.). 200 ° C.) is introduced into the heating device 4. For this reason, the water vapor in the reformed gas R does not condense in the system, but is only released into the atmosphere as exhaust gas EG together with the combustion exhaust gas. Accordingly, it is possible to omit a drainage facility or drainage path, a drainage treatment facility, and the like for discharging the condensed water of steam out of the system.

  Thus, according to the power generation system of this embodiment, the system configuration can be simplified as a whole, and the amount of heat held by the pyrolysis gas can be efficiently used to improve the thermal efficiency of the entire power generation system. Can do.

  8 and 9 show a pipe L21 (indicated by a virtual line) that can supply the reformed gas R to the power generation apparatus 10 of another system. The pipe L21 branches from the hot gas feed pipe L8 and supplies the hot gas flow HG to the heating device 4 of the power generation device 10 of another system. A pipe line L22 (shown in phantom) for exhausting the combustion exhaust gas of the heating device 4 of another system as the exhaust gas EG is shown in FIGS. 8 and 9, and the pipe line L22 is connected to the exhaust pipe L5.

  FIG. 10 is a system flow diagram schematically showing a power generation system having a configuration in which a plurality of power generation devices 10 are connected in parallel. In addition, in FIG. 10, illustration of the electric power generating apparatus 10 is abbreviate | omitted.

  For example, as shown in FIG. 10, the control device 20 sets the flow control valves 6A to 6D and 9A to 9D to predetermined opening degrees, and the power generation system performs steady operation with a predetermined power generation output. In this state, an appropriate amount of the reformed gas R corresponding to the opening degree of the flow control valves 6A to 6D is supplied from the main pipe L30 to the heating devices 4A to 4D of the Stirling engines.

  FIG. 11 shows an operation mode in which the flow control valves 6C: 6D and 9C: 9D are switched to the fully closed position. In this operation mode, the system of the power generation devices 10C: 10D completely stops operation, and the power generation system operates as a power generation system in which two power generation devices 10A: 10B are arranged in parallel.

  Controls that can be executed by opening control or switching control of the flow control valves 6A to 6D and 9A to 9D are not limited to the control modes shown in FIGS. 10 and 11, but output control of the Stirling engine group, and therefore power generation Control of the power generation output of the system can be executed in various control modes.

  12 and 13 are a system flow diagram and a schematic cross-sectional view showing the overall configuration of the power generation system according to the fourth embodiment of the present invention. 12 and 13, components that are substantially the same as those shown in FIGS. 1 to 11 are given the same reference numerals.

In the above-described third embodiment (FIGS. 8 to 11), the reformed gas R is supplied to the heating device 4 of the Stirling engine 11, and this is mixed with the combustion air after preheating in the combustion section 41, and the combustion reaction is performed. Let On the other hand, in order to sufficiently secure the operating heat source of the Stirling engine 11 with the reformed gas R having a low calorific value, it may be necessary to supply a large amount of the reformed gas R to the combustion unit 41. For example, from comparison with the case of supplying the reformed gas R about calorific 1000 kcal / Nm ³ in the combustion section 41, and a case of supplying a high-calorie gas such as LPG calorific value 20000kcal / Nm ³ in the combustion section 41 As is obvious, in order to secure the same amount of heat as the high calorie gas using the reformed gas R, it is necessary to set the supply amount of the reformed gas R to about 20 to 30 times. However, in consideration of the structural restrictions of the combustion section 41 and the structural restrictions of the fuel supply system around the combustion section 41, the fuel gas supply flow rate naturally has a limit. Is difficult to supply to the combustion unit 41.

  On the other hand, when the theoretical air amount of the reformed gas R required for the combustion reaction is compared with the theoretical air amount of the fuel gas (LPG etc.) having a high calorific value, the theoretical air amount of the fuel gas having a high calorific value is almost reformed. It reaches 20-30 times the gas R. Therefore, when the reformed gas R is used as the fuel gas, a much smaller amount of combustion air may be supplied to the combustion section 41 than when the high-calorie gas is used as the fuel gas. The system has surplus air supply capacity.

  In consideration of such circumstances, the power generation system of the present embodiment includes a configuration in which a part of the reformed gas R is supplied from the combustion air supply system to the combustion unit 41. Hereinafter, this point will be described in detail.

  As shown in FIGS. 12 and 13, the bypass flow path L80 branches from the reformed gas supply pipe L8 and is connected to the suction pipe L61 of the air supply fan 8. A flow rate control valve 80 is interposed in the bypass flow path L80. The flow control valve 80 is connected to the control device 20 via a control signal line (indicated by a dotted line). The control device 20 controls the opening degree of the flow rate control valve 80 and adjusts the reformed gas flow rate of the bypass flow path 80.

  FIG. 14 is a block diagram schematically showing the configuration of the heating device 4.

  In the heating device 4, a fuel injection device 45 and an air-fuel mixture supply device 46 that constitute the combustion unit 41 are arranged. The reformed gas R pressurized by the pressure fan 60 is further pressurized by the booster fan (or blower) 90 and supplied to the fuel injection device 45 under the control of the flow rate control valve 6. The fuel injection device 45 injects the reformed gas R into the combustion zone 40.

  The mixture supply device 46 communicates with the mixture supply path L62 via the mixture heating section 52, and the upstream end of the mixture supply path L62 is connected to the discharge port of the supply air fan 8. The suction port of the air supply fan 8 is connected to the suction pipe L61. As described above, one end of the bypass flow path L80 is connected to the suction pipe L61. The other end of the bypass flow path L80 is connected to the reformed gas supply pipe L8.

  A part of the reformed gas R supplied from the reformed gas supply pipe L8 to the fuel injection device 45 is supplied to the suction pipe L61 via the bypass flow path L80 and mixed with the combustion air CA. In the present embodiment, the opening degree of the flow control valve 80 is initially set so as to optimize the reformed gas flow rate (bypass flow rate) of the bypass flow path L80, and during normal operation, a predetermined opening degree (initial setting opening degree). Fixed to. The ratio (volume ratio) between the flow rate of the bypass flow path L80 and the flow rate of the reformed gas R supplied to the fuel injection device 45 is set to 2: 1 (bypass flow rate: injection gas flow rate), for example. The flow rate ratio is appropriately changed based on the calorific value of the reformed gas R.

  The air-fuel mixture MG of the reformed gas R and the combustion air CA is supplied to the air-fuel mixture heating section 52 under the air supply pushing pressure of the air supply fan 8, and is preheated by exchanging heat with the combustion exhaust gas in the combustion zone 41. The preheated air-fuel mixture MG flows out from the supply port 46a of the air-fuel mixture supply device 46 to the combustion zone 41, mixes with the reformed gas jet of the fuel injection device 45, and undergoes a combustion reaction.

  Thus, the air-fuel mixture supply device 46 supplies means for supplying the air-fuel mixture MG of the reformed gas R and the combustion air CA to the combustion zone 40 (not only the combustion air CA but also the reformed gas R is supplied to the combustion zone 40. Function as a means to In the present embodiment, the structure of the air-fuel mixture supply device 46 is a structure that can be used as combustion air supply means when a high-calorie gas such as LPG is supplied from the fuel injection device 45.

  As in the previous embodiments, the working fluid in the heater tube 13 is heated to a high temperature by the radiant heat transfer action and convection heat transfer action of the flame and combustion gas generated in the combustion zone 40, and the heat received from the hot gas. Is converted into power to operate a piston (not shown) in the Stirling engine 11, and the driving force of the piston is output to the generator 12. Since the overall configuration and operation of the power generation system are the same as those in the above-described embodiments, the description thereof will be omitted by citing the description of the above-described embodiments. Note that a pipe line L21 (shown in phantom lines in FIGS. 12 and 13) for connecting the reformed gas supply pipe L8 to the system of the power generator of another system is provided between the booster fan 90 and the flow rate control valve 6. It may be connected to the reformed gas feed pipe L8.

  As described above, according to the power generation system of the present embodiment, since the reformed gas R is partially supplied from the combustion air supply system to the combustion unit 41, structural limitations of the combustion unit 41 and A large amount of the low-calorie reformed gas R can be supplied to the heating device 11 of the Stirling engine 11 without being subjected to structural restrictions on the fuel supply system around the combustion section. Further, since the flow rate of the reformed gas R supplied from the fuel supply system to the combustion unit 41 is reduced, the load on the booster fan 90 is reduced. This eliminates the need to provide an excessive booster fan 90 in the fuel supply system in order to secure the fuel injection pressure. Therefore, in this sense as well, the power generation system configured as described above has the structure of the fuel supply system of the Stirling engine 11. Fit.

  The preferred embodiments of the present invention have been described in detail above. However, the present invention is not limited to the above-described embodiments, and various modifications or changes can be made within the scope of the invention described in the claims. Needless to say, such modifications and changes are also included in the scope of the present invention.

  For example, various control valves and exhaust fans (or exhaust blowers) of any kind and structure having heat resistance against the hot gas flow after cooling (exhaust gas of the exhaust pipe L5) are adopted as the flow control valve 6 and the exhaust fan 7. Can do.

  Further, in the above embodiment, the flow rate of the hot gas flow HG and the combustion air HA is variably controlled by the opening degree control of the flow rate control valves 6, 9. It may be adopted.

  The present invention relates to a power generation system configured to heat a working fluid of a Stirling engine using a pyrolysis gas obtained by pyrolysis or gasification of a solid fuel or a liquid fuel, and to drive a generator by the Stirling engine. Preferably applied. In particular, it has been generally considered difficult to control, such as pyrolysis gas generated in a pyrolysis furnace or gasification furnace of solid fuel or liquid fuel, for example, waste gasification furnace, waste oil gasification furnace, etc. When the present invention is applied to a power generation system that operates a Stirling engine using a flammable gas, the benefits are particularly significant.

It is a system flow figure showing the whole power generation system composition concerning a 1st embodiment of the present invention. It is a schematic sectional drawing which shows the whole structure of the electric power generation system shown in FIG. It is a schematic sectional drawing which shows the whole electric power generation system which has the structure which connected the some heating apparatus, the heat exchanger, and the electric power generating apparatus in parallel with the combustion apparatus. FIG. 4 is a system flow diagram illustrating an operation mode of the power generation system illustrated in FIG. 3. FIG. 4 is a system flow diagram illustrating another operation mode of the power generation system illustrated in FIG. 3. FIG. 6 is a system flow diagram illustrating still another operation mode of the power generation system illustrated in FIG. 3. FIG. 7 is a system flow diagram showing the overall configuration of the power generation system according to the second embodiment of the present invention. It is a system flow figure showing the whole power generation system composition concerning a 3rd embodiment of the present invention. It is a schematic sectional drawing which shows the whole structure of the electric power generation system shown in FIG. It is a system flow figure showing roughly a power generation system which has the composition which connected a plurality of heating devices and power generation devices in parallel, and the mode of operation of a power generation system is illustrated. FIG. 11 is a system flow diagram illustrating another operation mode of the power generation system illustrated in FIG. 10. It is a system flow figure showing the whole power generation system composition concerning a 4th embodiment of the present invention. It is a schematic sectional drawing which shows the whole structure of the electric power generation system shown in FIG. It is a block diagram which shows the structure of a heating apparatus roughly.

Explanation of symbols

1 Gasifier 2, 54 Dust collector 3 Combustion device
4 Heating device 5 Heat exchanger 6 Flow control valve (flow control means, fuel gas supply means)
7 Exhaust fan 8 Air supply fan (combustion air supply system)
9 Flow control valve (temperature control means)
DESCRIPTION OF SYMBOLS 10 Power generator 11 Stirling engine 12 Generator 13 Heater tube (heat-transfer part, heat-receiving part)
20 Control device 30 Combustion chamber 40 Combustion zone 41 Combustion section 50 Reforming furnace (reforming device)
60 Pressurizing fan (fuel gas supply means, flow rate control means)
80 Flow control valve (gas branching means)
P pyrolysis gas HG hot gas flow R reformed gas

Claims (21)

In a power generation system including a Stirling engine provided with a heating device for heating a working fluid, and a generator driven by the Stirling engine,
A combustion apparatus for combusting a pyrolysis gas obtained by pyrolysis or gasification of a solid fuel or a liquid fuel, and generating a hot gas flow to be supplied to the heating apparatus;
Flow rate control means for controlling the flow rate of the hot gas flow by variably controlling the exhaust gas flow rate of the hot gas flow on the downstream side of the heating device;
The power generation system, wherein the working fluid is heated by heat exchange between the heat transfer section of the heating device and the hot gas flow. In a power generation system including a Stirling engine provided with a heating device for heating a working fluid, and a generator driven by the Stirling engine,
A combustion apparatus for combusting a pyrolysis gas obtained by pyrolysis or gasification of a solid fuel or a liquid fuel, and generating a hot gas flow to be supplied to the heating apparatus;
Temperature control means for variably controlling the temperature of the hot gas flow,
The power generation system, wherein the working fluid is heated by heat exchange between the heat transfer section of the heating device and the hot gas flow. In a power generation system including a Stirling engine provided with a heating device for heating a working fluid, and a generator driven by the Stirling engine,
A combustion apparatus for combusting a pyrolysis gas obtained by pyrolysis or gasification of a solid fuel or a liquid fuel, and generating a hot gas flow to be supplied to the heating apparatus;
Flow rate control means for controlling the flow rate of the hot gas flow by variably controlling the exhaust gas flow rate of the hot gas flow on the downstream side of the heating device;
Temperature control means for variably controlling the temperature of the hot gas flow,
The power generation system, wherein the working fluid is heated by heat exchange between the heat transfer section of the heating device and the hot gas flow. In a power generation system including a Stirling engine provided with a heating device for heating a working fluid, and a generator driven by the Stirling engine,
A reformer for reforming pyrolysis gas obtained by pyrolysis or gasification of solid fuel or liquid fuel with steam;
Fuel gas supply means for supplying the reformed gas obtained by the reformer to the combustion section of the heating device;
The power generation system, wherein the working fluid is heated by combustion heat of the reformed gas. In a power generation system including a Stirling engine provided with a heating device for heating a working fluid, and a generator driven by the Stirling engine,
A fuel gas supply means for supplying a pyrolysis gas obtained by pyrolysis or gasification of a solid fuel or a liquid fuel, or a reformed gas obtained by reforming the pyrolysis gas with water vapor to a combustion section of the heating device;
Gas branching means for supplying a part of the pyrolysis gas or reformed gas of the fuel gas supply means to the combustion air supply system of the heating device and mixing with the combustion air;
The power generation system is characterized in that the working fluid is heated by combustion heat of the pyrolysis gas or reformed gas supplied to the combustion section from both the fuel gas supply means and the combustion air supply system. .   A heat exchanger that cools the hot gas that has passed through the heating device is interposed in a hot gas flow path on the downstream side of the heating device, and the flow rate control means is configured to flow the hot gas flow cooled by the heat exchanger. It controls, The electric power generation system of Claim 1 or 3 characterized by the above-mentioned.   The power generation system according to claim 2 or 3, wherein the temperature control means variably controls the flow rate of combustion air to be supplied to the combustion device.   The heat exchanger which preheats the said combustion air with the heat | fever of the said hot gas flow which passed through the said heating apparatus was interposed by the hot gas flow path in the downstream of the said heating apparatus. The power generation system described.   A plurality of the Stirling engines, a plurality of hot gas passages for supplying the hot gas flow to the heating device of each Stirling engine, and a hot gas main passage connecting the upstream ends of the hot gas passages, The power generation system according to claim 1, wherein the flow rate control unit variably controls an exhaust flow rate of the hot gas flow in each of the hot gas flow paths.   A reformer for reforming a pyrolysis gas obtained by pyrolysis or gasification of a solid fuel or a liquid fuel with steam and air, steam and oxygen, air or oxygen, and a corrosive component in the pyrolysis gas. The power generation system according to any one of claims 1 to 5, further comprising a cooling / purification device to be removed.   The power generation system according to claim 4, wherein the fuel gas supply unit includes a pressurizing unit that pressurizes the reformed gas and a flow rate control valve that controls a flow rate of the reformed gas. In a control method of a power generation system including a Stirling engine provided with a heating device for heating a working fluid and a generator driven by the Stirling engine,
The heating device controls the flow rate and / or temperature of the hot gas produced by burning the pyrolysis gas obtained by pyrolysis or gasification of solid fuel or liquid fuel, and controls the flow rate and / or temperature. A control method for a power generation system, characterized in that the method is supplied to a heat transfer section. In a control method of a power generation system including a Stirling engine provided with a heating device for heating a working fluid and a generator driven by the Stirling engine,
The pyrolysis gas obtained by pyrolysis or gasification of solid fuel or liquid fuel is reformed with steam, and the reformed gas is supplied to the combustion section of the heating device under the control of the flow rate control means, and the reformed gas A control method for a power generation system, wherein the working fluid is heated by combustion heat of In a control method of a power generation system including a Stirling engine provided with a heating device for heating a working fluid and a generator driven by the Stirling engine,
A part of the pyrolysis gas obtained by pyrolysis or gasification of solid fuel or liquid fuel, or a part of the reformed gas obtained by reforming the pyrolysis gas with steam, is a combustion air supply system for the heating device. And is mixed with combustion air, and the working fluid is heated by combustion heat of the pyrolysis gas or reformed gas supplied from both the fuel gas supply means and the combustion air supply system. A method for controlling the power generation system.   The method of controlling a power generation system according to claim 12, wherein the exhaust gas flow rate of the hot gas flow that has passed through the heating device is controlled to control the flow rate of the hot gas supplied to the heating device.   The power generation system control method according to claim 12 or 15, wherein a flow rate of combustion air for burning the pyrolysis gas is controlled to control a temperature of the hot gas.   The heat of the hot gas stream that has passed through the heating device is transferred to the combustion air of the pyrolysis gas, the combustion air is preheated with the heat of the hot gas stream, and the hot gas stream is cooled, after cooling The method of controlling a power generation system according to claim 16, wherein the flow rate of the hot gas flow is controlled. The power generation system has a configuration in which a plurality of heating devices are connected in parallel to a hot gas main flow path by a plurality of hot gas flow paths,
16. The flow rate of the hot gas flow to be supplied to each heating device is controlled by controlling the exhaust gas flow rate of the hot gas flow that has passed through each heating device, respectively. Control method for power generation system.   19. The method of controlling a power generation system according to claim 18, wherein the temperature of the hot gas is controlled by controlling a flow rate of combustion air for burning the pyrolysis gas.   15. The reformed gas or pyrolysis gas to be supplied to the combustion section of the heating device is pressurized, and the flow rate of the reformed gas or pyrolysis gas after pressurization is controlled. Method of power generation system. Before supplying the pyrolysis gas to the combustion zone, the pyrolysis gas is reformed with water vapor and air, water vapor and oxygen, air, or oxygen to remove a corrosive component in the pyrolysis gas. The method for controlling the power generation system according to any one of claims 12 to 20.

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