Power device

Abstract

To provide a power device that can improve the function of reforming means with predetermined turbo efficiency in an internal combustion engine for power generation.SOLUTION: A power device comprises an internal combustion engine for power generation, reforming means for generating reformed gas capable of being combusted in a combustion chamber of the internal combustion engine by an endothermic reaction using exhaust gas discharged from the combustion chamber, supply means for supplying reforming fuel causing the reformed gas, and a supercharger capable of supplying compressed air to the internal combustion engine by being driven by the exhaust gas. The reforming means is arranged between the internal combustion engine and the supercharger.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present disclosure relates to power plants. [Background technology]

[0002] It is known to generate a reformed gas combustible in an internal combustion engine by using a reforming means that utilizes exhaust gas.

[0003] For example, Patent Document 1 describes a system including: "a reforming fuel supply means for supplying reforming fuel, which is a fuel to be reformed, to exhaust gas discharged from a combustion chamber of an internal combustion engine; a reforming means located downstream of the reforming fuel supply means in the flow direction of the exhaust gas to which the reforming fuel is supplied by the reforming fuel supply means, and which generates a reformed gas combustible in the combustion chamber by endothermic reaction of the reforming fuel using the heat of the exhaust gas; a turbocharger that is actuated by exhaust gas and is capable of supplying air to the internal combustion engine at a pressure higher than atmospheric pressure; a first main exhaust passage provided between the internal combustion engine and the turbocharger, which is a passage through which exhaust gas flows from the internal combustion engine to the turbocharger; a second main exhaust passage which is a passage through which exhaust gas that has passed through the turbocharger flows; and a gas supply system branching off from the first main exhaust passage and supplying air from the first main exhaust passage to the reforming means. a first secondary exhaust passage through which exhaust gas flows that is headed toward the reforming means; a second secondary exhaust passage branching from the second main exhaust passage and through which exhaust gas flows that is headed toward the reforming means from the second main exhaust passage; a first secondary exhaust passage opening and closing means provided to be able to open and close the first secondary exhaust passage; a second secondary exhaust passage opening and closing means provided to be able to open and close the second secondary exhaust passage; and an exhaust passage opening and closing means control means that opens the first secondary exhaust passage opening and closing means and closes the second secondary exhaust passage opening and closing means when the temperature of the exhaust gas before flowing to the turbocharger is higher than a reformable temperature at which the reformed gas can be produced from the reforming fuel in the reforming means and the temperature of the exhaust gas after passing through the turbocharger is below the reformable temperature, and that closes the first secondary exhaust passage opening and closing means and opens the second secondary exhaust passage opening and closing means when the temperature of the exhaust gas before flowing to the turbocharger is equal to or lower than the reformable temperature. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Publication No. 8-135457 Summary of the Invention [Problem to be solved by the invention]

[0005] By positioning the reforming means in the fuel reformer disclosed in Patent Document 1 downstream of the turbocharger, the temperature of the exhaust gas that passes through the turbocharger drops, but the flow rate of the exhaust gas flowing into the turbocharger is ensured, and the flow rate of air sent to the internal combustion engine by the turbocharger is also ensured. This ensures high turbo efficiency and ensures responsiveness when load fluctuations occur in the internal combustion engine. However, when the above-mentioned fuel reformer is applied to an internal combustion engine for power generation, which is considered to have smaller load fluctuations than an internal combustion engine for a vehicle, there is a need to improve the function of the reforming means within a specified turbo efficiency.

[0006] An object of the present disclosure is to provide a power plant that solves the above-mentioned problems.

[0007] An object of the present disclosure is to provide a power plant that can improve the function of a reforming means within a predetermined turbo efficiency in an internal combustion engine for power generation. [Means for solving the problem]

[0008] The power plant of the present disclosure comprises an internal combustion engine for generating electricity, a reforming means for generating a reformed gas combustible in the combustion chamber of the internal combustion engine through an endothermic reaction using exhaust gas discharged from the combustion chamber, a supplying means for supplying a reforming fuel that is the source of the reformed gas, and a supercharger that is driven by the exhaust gas to supply compressed air to the internal combustion engine, and the reforming means is arranged between the internal combustion engine and the supercharger. [Effects of the Invention]

[0009] According to the power plant of the present disclosure, in an internal combustion engine for power generation, it is possible to improve the function of the reforming means within a predetermined turbo efficiency. [Brief explanation of the drawings]

[0010] [Figure 1] 1 is a schematic diagram showing a configuration of a power plant according to a first embodiment of the present disclosure. [Figure 2] FIG. 4 is a schematic diagram showing the configuration of a power plant according to a second embodiment of the present disclosure. [Figure 3] FIG. 10 is a block diagram showing the configuration of a control means according to a second embodiment of the present disclosure. [Figure 4] 10 is a flowchart showing the processing of a control means according to a second embodiment of the present disclosure. DETAILED DESCRIPTION OF THE INVENTION

[0011] Hereinafter, each embodiment of the present disclosure will be described with reference to the drawings. Note that the drawings and specific configurations used in each embodiment should not be used to interpret the disclosure. The same or corresponding configurations in all drawings will be assigned the same reference numerals, and common descriptions will be omitted.

[0012] First Embodiment Hereinafter, a first embodiment according to the present disclosure will be described with reference to the drawings. The configuration of a power plant according to a first embodiment of the present disclosure will be described below with reference to FIG.

[0013] (Power unit configuration) The power plant 1 is used to separately generate a reformed gas that can be combusted in the combustion chamber by an endothermic reaction using exhaust gas discharged from the combustion chamber, and to mix and burn the gas mixed with the reformed gas. As shown in FIG. 1, the power plant 1 includes an internal combustion engine 11, a reforming means 12, a supplying means 13, a supercharger 14, and a cooler 15.

[0014] (Configuration of internal combustion engine) The internal combustion engine 11 burns a mixture (hereinafter also referred to as a "first mixture") obtained by mixing fuel supplied from the injection INJ with air taken in from the outside via the turbocharger 14 in the combustion chamber 111. For example, the fuel supplied from the injection INJ is a liquid fuel. For example, the liquid fuel is liquid ammonia. Note that the fuel may also be a gaseous fuel. The internal combustion engine 11 is an internal combustion engine for generating electricity. Compared to internal combustion engines for vehicles, internal combustion engines for generating electricity operate with smaller load fluctuations. Therefore, the internal combustion engine 11 operates at the stoichiometric air-fuel ratio or in a fuel-lean state compared to the stoichiometric air-fuel ratio. The amount of compressed air generated by the turbocharger 14 is appropriately controlled by the valve opening of the throttle valve TB. For example, when the internal combustion engine 11 burns a second air-fuel mixture in which a reformed gas containing hydrogen is added to the first air-fuel mixture, the valve opening of the throttle valve TB is controlled as follows. Combustion of the second air-fuel mixture in the internal combustion engine 11 produces greater engine torque than combustion of the first air-fuel mixture. Therefore, the valve opening of the throttle valve TB is controlled to be smaller than the valve opening during combustion of the first air-fuel mixture. The injection INJ is located upstream of the internal combustion engine 11 . The throttle valve TB is located upstream of the injection INJ.

[0015] (Modification means) The reforming means 12 generates a reformed gas that can be burned in the combustion chamber 111. The reformed gas is generated by an endothermic reaction that utilizes exhaust gas discharged from the combustion chamber 111 of the internal combustion engine 11. The reformed gas contains hydrogen. The reformed gas thus produced is supplied to the compressed air upstream of the cooler 15. In this way, the reformed gas is mixed with the compressed air to produce a second mixture. The reforming means 12 includes a catalyst for reforming, for example, a rhodium-based catalyst. The reforming means 12 is disposed between the combustion chamber 111 of the internal combustion engine 11 and the supercharger 14 on an exhaust line ExL, which will be described later. For example, the amount of reformed gas supplied may be appropriately controlled based on the engine torque of the internal combustion engine 11.

[0016] (supply means) The supply means 13 supplies the reforming fuel FR, which is the source of the reformed gas. For example, the reforming fuel FR is liquid ammonia. The supply means 13 is a pump, and an example thereof is a liquid ammonia pump. The reforming fuel FR is transferred to the reforming means 12 by the supply means 13. The amount of the reforming fuel FR supplied by the supply means 13 may be controlled as appropriate.

[0017] (Turbocharger) The supercharger 14 is capable of supplying compressed air to the internal combustion engine 11 by being driven by exhaust gas. The supercharger 14 has a turbine 141 and a compressor 142. The supercharger 14 is rotationally driven by the exhaust gas discharged from the combustion chamber 111. The turbine 141 is connected to an exhaust line ExL that guides exhaust gas discharged from the combustion chamber 111. The compressor 142 is connected coaxially with the turbine 141. Therefore, the compressor 142 is rotated and driven in accordance with the rotation of the turbine 141, and compresses external air to generate compressed air. The generated compressed air is supplied to the combustion chamber 111 of the internal combustion engine 11 through the intake line InL.

[0018] In the present disclosure, the upstream side of the combustion chamber 111 is referred to as an intake line InL, and the downstream side of the combustion chamber 111 is referred to as an exhaust line ExL.

[0019] (cooler) The cooler 15 cools the compressed air supplied to the internal combustion engine 11. The cooler 15 is a heat exchanger that cools the compressed air by exchanging heat between a refrigerant supplied from the outside and the compressor air. For example, as shown in FIG. 1, the refrigerant is cooling water. For example, the cooler 15 may cool a mixture including compressed air (first mixture, second mixture). For example, the cooler 15 is located on the intake line InL between the injection INJ and the combustion chamber 111.

[0020] (Reformed gas generation flow) First, when fuel (liquid ammonia) is supplied into the intake line InL by the injection INJ, a first mixture of atomized fuel and compressed air is generated.

[0021] The first mixture is then cooled by passing through a cooler 15 .

[0022] Next, the cooled first mixture flows into the combustion chamber 111, and the first mixture is burned. The exhaust gas emitted by the combustion passes through the reforming means 12 via an exhaust line ExL.

[0023] Next, the reforming fuel FR (liquid ammonia) transferred to the reforming means 12 by the supply means 13 undergoes an endothermic reaction while passing through the reforming means 12. The catalyst contained in the reforming means 12 is heated and activated by the heat of the exhaust gas, and reforms the reforming fuel FR into reformed gas. The reformed gas produced is transferred upstream of the cooler 15 . The reformed gas produced by reforming liquid ammonia contains hydrogen.

[0024] Next, the exhaust gas that has passed through the reforming means 12 passes through the turbine 141 when it is discharged, thereby rotating the turbine 141 . The rotation of the turbine 141 drives the compressor 142 to rotate. The compressor 142 takes in external air into the intake line InL and compresses the taken-in air to generate compressed air. The compressed air is mixed with the fuel supplied by the injection INJ and the reformed gas transferred upstream of the cooler 15 to generate a second mixture.

[0025] Next, the second mixture passes through the cooler 15 and, after being cooled, flows into the combustion chamber 111. In this way, the second mixture is combusted.

[0026] The amount of the reforming fuel FR supplied by the supply means 13 may be controlled as appropriate.

[0027] (Action and effect) The power plant according to this embodiment is equipped with a reforming means 12 that generates combustible reformed gas in a combustion chamber 111 through an endothermic reaction using exhaust gas discharged from the combustion chamber 111 of an internal combustion engine 11 for power generation. The reforming means 12 is disposed between the internal combustion engine 11 and the turbocharger 14. This allows the reforming means 12 to easily utilize the exhaust gas discharged from the combustion chamber 111. This means that it is difficult for the reforming means 12 to utilize the exhaust gas whose temperature has been reduced by driving the turbocharger. Therefore, the exhaust gas discharged from the combustion chamber 111 can easily activate the reforming means 12 . As described above, the power plant of the present disclosure can improve the function of the reforming means within a predetermined turbo efficiency in an internal combustion engine for power generation.

[0028] As a comparative example, a power plant in which the reforming means 12 is installed downstream of the turbocharger 14 will be taken as an example. When a reforming means 12 that reforms the reforming fuel FR by utilizing the heat of the exhaust gas discharged from the combustion chamber is installed in an internal combustion engine equipped with a turbocharger 14, the reforming means 12 is installed downstream of the turbocharger 14. This is because there is little change required in the specifications of an existing internal combustion engine and it is easy to add a reforming means. In this case, part of the energy of the exhaust gas that has passed through the turbocharger 14 is used to rotate the turbine 141. Therefore, the temperature of the exhaust gas drops after passing through, and the reforming means 12 is less likely to be heated to the temperature range required for reforming the reforming fuel FR. For this reason, it was necessary to heat the reforming means 12 to a temperature range required for reforming by externally oxidizing the fuel and supplying the oxidized fuel as heat.

[0029] In contrast to the comparative example, in the power plant of the present disclosure, the reforming means 12 is located upstream of the turbocharger 14. This makes it easier for the reforming means 12 to utilize the exhaust gas discharged from the combustion chamber 111. This means that it is difficult for the reforming means 12 to utilize the exhaust gas whose temperature has been lowered by driving the turbocharger. Therefore, the reforming means 12 is more likely to be activated by the exhaust gas discharged from the combustion chamber 111 . Therefore, the exhaust gas can easily heat the reforming means 12 to a temperature range required for reforming, and it is no longer necessary to supply heat to the reforming means 12 from outside.

[0030] Second Embodiment In the first embodiment, the reforming means 12 is located upstream of the turbocharger 14, so that the temperature of the exhaust gas supplied to the reforming means 12 can be increased compared to when the reforming means 12 is located downstream. This makes it possible to ensure a temperature range required for reforming the reforming fuel FR in the reforming means 12. In contrast to this, in the power plant according to this embodiment, when the work that the exhaust gas does on the turbine 141 decreases, it becomes difficult for the temperature to reach the range required for reforming by the reforming means 12. In this case, attention is also focused on the fact that by supplying heat to the reforming means 12 from the outside, it is easy to secure the energy of the exhaust gas used to heat the reforming means 12. An embodiment of the present disclosure will be described below with reference to FIG. An example of the configuration of the power plant according to the present disclosure will be described below with reference to FIGS. The same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted.

[0031] As shown in FIG. 2, the power plant 1B includes, in addition to the components of the power plant 1, a heating promotion means 16 and a control means 17. Additionally, the power plant 1B may further include a tachometer TA that communicates with the control means 17. The tachometer TA measures the rotation speed of the internal combustion engine 11. The power plant 1B may also include a load detector or a dynamometer. The load detector or dynamometer measures the torque or output of the internal combustion engine 11. In the following disclosure, the rotation speed of the internal combustion engine 11 is measured by the tachometer TA, and the output value of the power plant 1B, which is a generator, is used as the output value of the internal combustion engine 11.

[0032] For example, the power plant 1B may further include an intake pressure gauge PR and an intake temperature gauge TH that communicate with the control means 17. The intake pressure gauge PR and the intake temperature gauge TH are located on the intake line InL between the injection INJ and the combustion chamber 111. More specifically, the intake pressure gauge PR and the intake temperature gauge TH are located on the intake line InL between the cooler 15 and the combustion chamber 111. This allows the state of the mixture (first mixture, second mixture) flowing into the combustion chamber 111 to be measured.

[0033] For example, the power plant 1B may further include measuring instruments that measure the reformed gas and the fuel supplied from the injection INJ, thereby obtaining the amount of fuel supplied in the mixture (first mixture, second mixture).

[0034] (heating acceleration means) The heating promotion means 16 heats the exhaust gas discharged from the combustion chamber 111 . There are many types of heating promotion means 16, which may be used in combination as appropriate within power plant 1B. In the present disclosure, there are two heating promotion means 16, which are used in combination within power plant 1B.

[0035] For example, the heating promotion means 16 is an additional fuel supply valve 16A. The additional fuel supply valve 16A supplies additional fuel AF to the exhaust gas. When the additional fuel AF is supplied into the exhaust gas, combustion occurs with the additional fuel AF heated by the temperature of the exhaust gas. The combustion of the additional fuel AF heats the reforming means 12, and the catalyst contained in the reforming means 12 is activated. The additional fuel AF is supplied into the exhaust line ExL between the combustion chamber 111 and the reforming means 12. That is, the additional fuel AF is supplied upstream of the reforming means 12, and combustion of the additional fuel AF occurs upstream of the reforming means 12. The additional fuel AF may be liquid ammonia or reformed gas. In the case of liquid ammonia, a part of the reformed fuel FR (liquid ammonia) may be used by branching the supply line of the reformed fuel FR. Also, a part of the reformed gas generated by the reforming means 12 may be used.

[0036] For example, the heating promotion means 16 is a heater 16B. The heater 16B heats the reforming means 12. When the reforming means 12 is heated, the catalyst contained in the reforming means 12 is activated. For example, the heater 16B is an electric heater.

[0037] The heating promotion means 16 (additional fuel supply valve 16A, heater 16B) is controlled by control means 17.

[0038] (Functional configuration of control means) When the temperature of the reforming means 12 is lower than the reformable temperature at which reformed gas can be generated from the reforming fuel FR, the control means 17 heats the exhaust gas via the heating promotion means 16. The control means 17 that controls the heating promotion means 16 will be described in detail below. FIG. 3 is a block diagram showing the functional configuration of the control means of the present disclosure. As shown in FIG. 3, the control means 17 includes a processor 171, a memory 172, a storage 173, and a communication interface 174.

[0039] The processor 171 operates according to a predetermined program to function as an acquisition unit 1711 and a command unit 1712. The processor 171 may further function as a storage unit 1713. For example, the processor 171 may be an ECU (Electronic Control Unit) that controls devices provided around the internal combustion engine. The operations of the various parts of the control means 17 described below correspond to part of the information processing method of the present disclosure.

[0040] The acquisition unit 1711 acquires measurement data from the tachometer TA, thereby acquiring the rotation speed of the internal combustion engine 11 while the internal combustion engine 11 is operating. In addition to the rotation speed, the acquisition unit 1711 acquires the output value of the power plant 1B, which is a generator. The acquisition unit 1711 acquires the output value of the power plant 1B, which is a generator, instead of the output value of the internal combustion engine 11.

[0041] For example, the acquiring unit 1711 may further acquire measurement data from an intake pressure gauge PR and an intake temperature gauge TH. In this case, information on the state of the mixture (first mixture, second mixture) flowing into the combustion chamber 111 of the internal combustion engine 11 while the internal combustion engine 11 is operating is acquired.

[0042] For example, the acquisition unit 1711 may further acquire the fuel supply amount. The acquisition unit 1711 acquires the fuel supply amount in the mixture (first mixture, second mixture). The fuel supply amount is acquired by measuring the reformed gas and the fuel supplied from the injection INJ.

[0043] The command unit 1712 issues a control command to the heating promotion means 16 (additional fuel supply valve 16A, heater 16B) to superheat the exhaust gas according to the temperature of the exhaust gas. If the exhaust gas temperature is low and it is difficult for the included catalyst to reach the temperature range required for reforming the reforming fuel FR when the reforming means 12 is heated, the command unit 1712 issues a control command to supply heat from outside to the reforming means 12. For example, the command unit 1712 issues a control command as to whether or not to supply heat from outside to the reforming means 12 by determining whether or not the temperature of the exhaust gas is equal to or lower than a predetermined threshold.

[0044] The temperature of the exhaust gas can be measured either directly or estimated.

[0045] In the case of direct measurement, the temperature of the exhaust gas is measured by a thermocouple etc. The thermocouple is installed in the exhaust line ExL between the combustion chamber 111 and the reforming means 12. Instead of measuring the temperature of the exhaust gas, the temperature of the catalyst included in the reforming means 12 may be measured. In this case, the command unit 1712 determines whether the temperature of the catalyst is equal to or lower than a predetermined threshold value, and issues a command as to whether or not to supply heat from outside to the reforming means 12.

[0046] The following methods can be used to estimate. For example, the temperature of the exhaust gas may be estimated by calculation using the rotation speed, output value, state quantity of the mixture, and amount of fuel supplied of the internal combustion engine 11. In this case, measurement data may be further acquired from an intake pressure gauge PR, an intake temperature gauge TH, and measuring instruments that measure the reformed gas and the fuel supplied from the injection INJ. By acquiring information about the mixture (first mixture, second mixture) flowing into the combustion chamber 111 of the internal combustion engine 11 while the internal combustion engine 11 is operating, the temperature of the exhaust gas can be estimated with higher accuracy. The amount of the mixture (first mixture, second mixture) flowing into the combustion chamber 111 is calculated from the measured values ​​of the tachometer TA, the intake pressure gauge PR, and the intake temperature gauge TH.

[0047] For example, a map may be created in advance that shows the relationship between the rotation speed of the internal combustion engine 11, the output value (in this case, the output value as a generator is used; the engine torque value may be used instead of the output value), and the temperature of the exhaust gas discharged from the combustion chamber 111. The created map is stored in the memory unit 1713, and the measured rotation speed and output value of the internal combustion engine 11 are compared with this map to estimate the temperature of the exhaust gas.

[0048] For example, the above-described map is stored when the function of the storage unit 1713 is further exerted by the function of the processor 171. For example, the storage unit 1713 may store various measurement data previously acquired by the acquisition unit 1711.

[0049] The predetermined program executed by processor 171 is stored in a computer-readable recording medium. Computer-readable recording media include magnetic disks, optical magnetic disks, CD-ROMs, DVD-ROMs, and semiconductor memories. This computer program may be distributed to a computer via a communication line, and the computer that receives the program may execute it. This program may also be a program for implementing some of the above-described functions. Furthermore, this program may be a so-called differential file (differential program) that can realize the above-described functions in combination with a program already stored in the computer system.

[0050] The memory 172 has a memory area necessary for the operation of the processor 171 .

[0051] The storage 173 is a so-called auxiliary storage device, such as a hard disk drive (HDD) or a solid state drive (SSD).

[0052] The communication interface 174 is an interface for transmitting and receiving various signals to and from external devices (e.g., devices provided around the internal combustion engine such as an injection INJ, a throttle valve TB, an intake pressure gauge PR, and an intake temperature gauge TH).

[0053] (Control Flow) The control method of the control means in this embodiment will be described. The control method of the control means in this embodiment is carried out according to the flow shown in FIG.

[0054] First, the acquisition unit 1711 of the control means 17 acquires each measurement value (step ST10). For example, the number of revolutions of the internal combustion engine 11 obtained by the tachometer TA and the output value of the internal combustion engine 11 (this time, the output value as a generator is used. The engine torque value may be used instead of the output value) are acquired. In addition, the measurement values ​​of the intake pressure gauge PR and the intake temperature gauge TH, and the state quantity of the air-fuel mixture obtained from the amount of fuel supplied may also be acquired.

[0055] Next, the command unit 1712 of the control means 17 issues a control command to the heating promotion means 16 to superheat the exhaust gas in accordance with the directly measured or estimated exhaust gas temperature (step ST20). For example, the command unit 1712 issues a control command as to whether or not to supply heat from outside to the reforming means 12 by determining whether or not the exhaust gas temperature is equal to or lower than a predetermined threshold. Here, the reforming means 12 is heated, and the catalyst contained in the reforming means 12 is activated. (Complete)

[0056] (Action and effect) The power plant 1B of this embodiment is provided with a reforming means 12 that generates combustible reformed gas in the combustion chamber 111 by an endothermic reaction using exhaust gas discharged from the combustion chamber 111 of the power-generating internal combustion engine 11. The reforming means 12 is disposed between the internal combustion engine 11 and the turbocharger 14. This allows the reforming means 12 to easily utilize the exhaust gas discharged from the combustion chamber 111. This means that it is difficult for the reforming means 12 to utilize the exhaust gas whose temperature has been reduced by driving the turbocharger. Therefore, the exhaust gas discharged from the combustion chamber 111 can easily activate the reforming means 12 . Furthermore, if the work that the exhaust gas does on the turbocharger turbine decreases, it becomes difficult to reach the temperature range required for reforming by the reforming means 12. In this case, by supplying heat from the outside to the reforming means 12 by the heating promotion means 16, it becomes easier to secure the energy of the exhaust gas used to heat the reforming means 12. As described above, the power plant of the present disclosure can improve the function of the reforming means within a predetermined turbo efficiency in an internal combustion engine for power generation.

[0057] (Other embodiments) The above describes in detail the embodiments of the present disclosure with reference to the drawings, but the specific configuration is not limited to this embodiment, and design changes and the like are also included within the scope that does not deviate from the gist of the present disclosure. For example, in the above disclosure, the inflow amount of the mixture (first mixture, second mixture) flowing into the combustion chamber 111 was calculated based on the measurement values ​​of each instrument (tachometer TA, intake pressure gauge PR, intake temperature gauge TH), but it may also be measured directly by an air flow meter.

[0058] A part or all of the above-described embodiments can be described as, but not limited to, the following supplementary notes.

[0059] (Appendix 1) (1) The power plant 1 according to the first aspect comprises an internal combustion engine 11 for generating electricity, a reforming means 12 for generating combustible reformed gas in the combustion chamber 111 by an endothermic reaction using exhaust gas discharged from the combustion chamber 111 of the internal combustion engine 11, a supplying means 13 for supplying reforming fuel FR which is the source of the reformed gas, and a supercharger 14 which is driven by the exhaust gas and can supply compressed air to the internal combustion engine 11, and the reforming means 12 is a power plant arranged between the internal combustion engine 11 and the supercharger 14.

[0060] In this configuration, a reforming means 12 is provided that generates a reformed gas that can be burned in the combustion chamber 111 by an endothermic reaction using exhaust gas discharged from the combustion chamber 111 of the internal combustion engine 11 for power generation. The reforming means 12 is disposed between the internal combustion engine 11 and the turbocharger 14. This allows the reforming means 12 to easily utilize the exhaust gas discharged from the combustion chamber 111. This means that it is difficult for the reforming means 12 to utilize the exhaust gas whose temperature has been reduced by driving the turbocharger. Therefore, the exhaust gas discharged from the combustion chamber 111 can easily activate the reforming means 12 . As described above, the power plant of the present disclosure can improve the function of the reforming means within a predetermined turbo efficiency in an internal combustion engine for power generation.

[0061] (Appendix 2) (2) The power plant 1 according to a second aspect is the power plant described in (1), further comprising a cooler 15 that cools the compressed air supplied to the internal combustion engine.

[0062] According to this configuration, the temperature of the compressed air is lowered before it flows into the combustion chamber 111, and the density of the compressed air supplied to the combustion chamber 111 can be improved.

[0063] (Appendix 3) (3) The power plant 1 according to a third aspect is the power plant described in (2), in which the generated reformed gas is supplied to compressed air upstream of the cooler 15.

[0064] With this configuration, the fuel temperature of the reformed gas can be lowered, and the fuel density of the reformed gas supplied to the combustion chamber 111 can be improved.

[0065] (Appendix 4) (4) A power plant 1B according to a fourth aspect is the power plant according to any one of (1) to (3), and further includes a heating promotion means 16 that heats the exhaust gas.

[0066] With this configuration, the following situations can be taken into consideration: If the work that the exhaust gas does on the turbine of the turbocharger 14 decreases, it becomes difficult to reach the temperature range required for reforming by the reforming means 12. In this case, by supplying heat from the outside to the reforming means 12 using the heating promotion means 16, it becomes easier to secure the energy of the exhaust gas used to heat the reforming means 12. As described above, the power plant of the present disclosure can improve the function of the reforming means within a predetermined turbo efficiency in an internal combustion engine for power generation.

[0067] (Appendix 5) (5) The power plant 1 according to a fifth aspect is the power plant described in (4), in which the heating promotion means 16 is an additional fuel supply valve 16A, and the additional fuel supply valve 16A supplies additional fuel to the exhaust gas.

[0068] According to this configuration, when additional fuel AF is supplied into the exhaust gas, combustion occurs with the additional fuel AF heated by the temperature of the exhaust gas. The combustion of the additional fuel AF heats the reforming means 12, and the catalyst contained in the reforming means 12 can be activated. As described above, the power plant of the present disclosure can improve the function of the reforming means within a predetermined turbo efficiency in an internal combustion engine for power generation.

[0069] (Appendix 6) (6) The power plant 1 according to a sixth aspect is the power plant according to (4), in which the heating promotion means 16 is a heater 16B, and the heater heats the reforming means.

[0070] According to this configuration, the catalyst contained in the reforming means 12 can be activated by heating the reforming means 12. As described above, the power plant of the present disclosure can improve the function of the reforming means within a predetermined turbo efficiency in an internal combustion engine for power generation.

[0071] (Appendix 7) (7) The power plant 1 according to the seventh aspect is a power plant according to any one of (4) to (6), further comprising a control means for controlling the heating promotion means, and the control means heats the exhaust gas via the heating promotion means when the temperature of the reforming means is lower than the reformable temperature, which is the temperature at which reformed gas can be produced from the reforming fuel.

[0072] According to this configuration, when the exhaust gas temperature is low and the catalyst contained in the reforming means 12 is unlikely to reach the temperature range required for reforming the reforming fuel FR when the reforming means 12 is heated, the command unit 1712 can issue a control command to supply heat from outside to the reforming means 12. As described above, the power plant of the present disclosure can improve the function of the reforming means within a predetermined turbo efficiency in an internal combustion engine for power generation.

[0073] (Appendix 8) (8) The power plant 1 according to an eighth aspect is the power plant described in any one of (1) to (7), in which the internal combustion engine is operating at the stoichiometric air-fuel ratio or in a fuel-lean state compared to the stoichiometric air-fuel ratio.

[0074] With this configuration, the internal combustion engine 11 operates at an engine efficiency that takes economy into consideration, which means that the temperature of the exhaust gas tends to be lower than in a fuel-rich state. However, the reforming means 12 is disposed between the internal combustion engine 11 and the turbocharger 14. This makes it easier for the reforming means 12 to utilize the exhaust gas discharged from the combustion chamber 111. This means that it is difficult for the reforming means 12 to utilize the exhaust gas whose temperature has been reduced by driving the turbocharger. Therefore, even if the engine is operated at the stoichiometric air-fuel ratio or in a fuel-lean state compared to the stoichiometric air-fuel ratio, the exhaust gas discharged from the combustion chamber 111 is most likely to activate the reforming means 12 . As described above, the power plant of the present disclosure can improve the function of the reforming means within a predetermined turbo efficiency in an internal combustion engine for power generation. [Explanation of symbols]

[0075] 1 Power plant 1B Power plant 11 Internal combustion engine 12 Modification means 13 Supply means 14 Supercharger 15 Cooler 16 Heating acceleration means 16A Additional fuel supply valve 16B Heater 17 Control Means 111 Combustion chamber 141 Turbine 142 Compressor 171 processors 1711 Acquisition Department 1712 Command Department 1713 Storage section AF additional fuel FR reforming fuel ExL exhaust line InL Intake line INJ Injection TB throttle valve TA tachometer PR intake pressure gauge TH intake temperature gauge

Claims

1. an internal combustion engine for generating electricity; a reforming means for generating a reformed gas combustible in a combustion chamber of the internal combustion engine by an endothermic reaction using exhaust gas discharged from the combustion chamber; a supply means for supplying a reforming fuel that is the source of the reformed gas; a supercharger that is driven by the exhaust gas to supply compressed air to the internal combustion engine; Equipped with The reforming means is disposed between the internal combustion engine and the supercharger. Power plant.

2. a cooler that cools the compressed air supplied to the internal combustion engine; Further equipped The power plant of claim 1 .

3. The reformed gas thus produced is supplied to the compressed air upstream of the cooler. The power plant of claim 2.

4. and a heating promotion means for heating the exhaust gas. A power plant according to any one of claims 1 to 3.

5. the heating promoting means is an additional fuel supply valve; The additional fuel supply valve supplies additional fuel to the exhaust gas.

5. The power plant of claim 4.

6. the heating promotion means is a heater, The heater heats the reforming means.

5. The power plant of claim 4.

7. and a control means for controlling the heating promotion means. The control means heats the exhaust gas via the heating promotion means when the temperature of the reforming means is lower than a reformable temperature at which the reformed gas can be generated from the reforming fuel.

5. The power plant of claim 4.

8. The internal combustion engine is operated at a stoichiometric air-fuel ratio or at a fuel-lean ratio. The power plant according to any one of claims 1 to 3.

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