WO2010092684A1

WO2010092684A1 - Operating gas circulation type engine

Info

Publication number: WO2010092684A1
Application number: PCT/JP2009/052431
Authority: WO
Inventors: 享加藤; 澤田　大作; 黒木　錬太郎
Original assignee: トヨタ自動車株式会社
Priority date: 2009-02-13
Filing date: 2009-02-13
Publication date: 2010-08-19
Also published as: JPWO2010092684A1

Abstract

An operating gas circulation type engine has a combustion chamber (CC) into which an oxidizing agent, fuel which generates water vapor when combusted together with the oxidizing agent, and operating gas which has a higher specific heat ratio than air are supplied, in which the operating gas can expand as the fuel combusts, and which can discharge the water vapor and operating gas as exhaust gas after the combustion of the fuel, a circulating route (20) capable of circulating the operating gas, contained in the exhaust gas, from the exhaust side to the intake side of the combustion chamber (CC) and supplying the operating gas again to the combustion chamber, a condensing means (60) provided in the circulating route (20) and condensing water vapor contained in the exhaust gas to turn the water vapor into condensed water, a condensed water containing means (70) capable of containing the condensed water, a pumping means (80) for pumping the condensed water, contained in the condensed water containing means (70), by higher pressure than the atmospheric pressure, and evaporating means (90) for evaporating the condensed water, pumped by the pumping means (80), by exhaust heat of the exhaust gas. Thus, the condensed water can be appropriately processed.

Description

Working gas circulation engine

The present invention relates to a working gas circulation engine, and more particularly to a working gas circulation engine in which working gas contained in exhaust gas is circulated from the exhaust side to the intake side of the combustion chamber and can be supplied to the combustion chamber again.

As a conventional engine, a working gas circulation engine that is a so-called closed-cycle engine that can circulate the working gas contained in the exhaust gas from the exhaust side of the combustion chamber to the intake side and supply it again to the combustion chamber is known. . Such a working gas circulation engine has a combustion chamber to which oxygen as an oxidant, hydrogen as a fuel, and a working gas having a higher specific heat ratio than air are supplied, and the working gas is sucked from the exhaust side of the combustion chamber. A circulation path that can be circulated to the combustion chamber and re-supplied to the combustion chamber. The working gas is thermally expanded in the combustion chamber as the hydrogen burns, generating power and releasing the working gas to the atmosphere. Without being supplied again to the combustion chamber via the circulation path.

As a conventional working gas circulation engine, for example, a hydrogen engine disclosed in Patent Document 1 below is known. In the hydrogen engine described in Patent Document 1, oxygen and hydrogen are supplied to a combustion chamber, and argon is circulated as a working gas to increase thermal efficiency, for example, composed of a monoatomic gas and having a higher specific heat ratio than air. Has been. In this working gas circulation engine, argon is thermally expanded by combustion of hydrogen in a combustion chamber, and thereby a piston is pushed down to generate power.

Here, since hydrogen and oxygen react (combine) with the combustion of hydrogen in the combustion chamber to generate water vapor, the steam is discharged into the circulation path together with argon as exhaust gas from the combustion chamber. For this reason, the hydrogen engine described in Patent Document 1 as a conventional working gas circulation engine is a molecule composed of three atoms (triatomic molecules), which liquefies water vapor having a smaller specific heat ratio than argon and removes it as condensed water. By disposing the condenser on the circulation path so that argon as the working gas circulates and is supplied to the combustion chamber again, a decrease in thermal efficiency is suppressed.

JP-A-11-93681

By the way, in the hydrogen engine described in Patent Document 1 as described above, for example, simply storing the condensed water condensed from the exhaust gas by the condenser in the tank is limited because the size of the tank is limited. Since various problems such as deterioration of properties may occur, it is necessary to appropriately treat this condensed water.

Therefore, an object of the present invention is to provide a working gas circulation engine capable of appropriately treating condensed water.

In order to achieve the above object, a working gas circulation engine according to the present invention is supplied with an oxidizing agent, a fuel that generates water vapor by combustion with the oxidizing agent, and a working gas having a higher specific heat ratio than air, A combustion chamber in which the working gas can expand as the fuel burns and exhausts the water vapor and the working gas as exhaust gas after the combustion of the fuel, and the working gas contained in the exhaust gas. A circulation path that can be circulated from the exhaust side to the intake side of the combustion chamber and re-supplied to the combustion chamber, and a condensing means that is provided in the circulation path and condenses the water vapor contained in the exhaust gas into condensed water. The condensed water storage means capable of storing the condensed water, the pressure feeding means for pumping the condensed water stored in the condensed water storage means at a pressure higher than the atmospheric pressure, and the condensation pumped by the pressure feeding means The characterized in that it comprises an evaporation means for evaporating the exhaust heat of the exhaust gas.

In the working gas circulation engine, the oxidant may be oxygen, and the fuel may be hydrogen.

In the working gas circulation engine, the evaporation means evaporates the condensed water by exhaust heat of the exhaust gas upstream of the condensing means with respect to the circulation direction of the working gas circulating in the circulation path. You may comprise as follows.

Further, in the working gas circulation engine, the pressure feeding means is provided in a condensed water path connecting the condensed water storage means and the evaporation means so that the condensed water can flow, and the condensed water path is provided in the condensed water path. You may comprise so that it may have the pump which pressurizes the said condensed water of a path | route and pumps it from the said condensed water storage means side to the said evaporation means side.

In the working gas circulation engine, the pressure feeding unit connects the condensed water storage unit and the evaporation unit so that the condensed water can flow, and a space portion for storing the condensed water is sealed. A condensed water path that communicates with the circulation path via the condensed water storage means, and pressurizes the condensed water in the condensed water path with a pressure of gas in the circulation path higher than atmospheric pressure to store the condensed water. You may comprise so that it pumps from the means side to the said evaporation means side.

Further, in the working gas circulation engine, the pressure feeding means is branched from the circulation path, is provided with working gas storage means for storing the relatively high pressure working gas, the working gas storage means, and the circulation path. Adjusting means for adjusting the inflow and outflow of the working gas between them.

Further, the working gas circulation engine may be configured to include a pumping amount control unit that controls a pumping amount of the condensed water by the pumping unit based on a generation amount of the condensed water.

In the working gas circulation engine, the pumping amount control means may control the pumping amount so that the pumping amount becomes equal to the generated amount.

The working gas circulation engine may further include a flow rate detection unit that detects a flow rate of the condensed water to the condensed water storage unit, and the pumping amount control unit may detect a flow rate of the condensed water detected by the flow rate detection unit. The pumping amount may be controlled based on the above.

The working gas circulation engine may further include a water level detection unit that detects a level of the condensed water stored in the condensed water storage unit, and the pumping amount control unit may detect the condensation detected by the water level detection unit. The pumping amount may be controlled based on the water level.

Further, in the working gas circulation engine, the pumping amount control means may be configured to control the pumping amount based on a supply amount of the oxidant or the fuel supplied to the combustion chamber.

Further, in the working gas circulation engine, the pumping amount control means may be configured to control the pumping amount of the condensed water based on the engine load and the engine speed.

Further, the working gas circulation engine may be configured to include waste heat recovery means for recovering the energy of water vapor generated by evaporating the condensed water by the evaporation means as kinetic energy.

In the working gas circulation engine, the temperature detection means for detecting the temperature of the condensed water stored in the condensed water storage means, and the temperature detected by the temperature detection means is less than or equal to a preset predetermined temperature. In some cases, it may be configured to include heat transfer means for moving the heat of water vapor through the waste heat recovery means to the condensed water stored in the condensed water storage means.

The working gas circulation engine further includes a water level detection unit that detects a level of the condensed water stored in the condensed water storage unit, and the heat transfer unit has a water level detected by the water level detection unit in advance. When the water level is equal to or lower than a predetermined water level, water vapor that has passed through the waste heat recovery means may be introduced into the condensed water stored in the condensed water storage means.

According to the working gas circulation engine according to the present invention, the condensed water can be appropriately processed.

FIG. 1 is a schematic configuration diagram of a working gas circulation engine according to Embodiment 1 of the present invention. FIG. 2 is a schematic configuration diagram of a working gas circulation engine according to Modification 1 of the present invention. FIG. 3 is a schematic configuration diagram of a working gas circulation engine according to the second embodiment of the present invention. FIG. 4 is a schematic configuration diagram of a working gas circulation engine according to Modification 2 of the present invention. FIG. 5 is a schematic configuration diagram of a working gas circulation engine according to the third embodiment of the present invention. FIG. 6 is a flowchart for explaining the control of the pumping amount of the working gas circulation engine according to the third embodiment of the present invention. FIG. 7 is a schematic schematic configuration diagram of a working gas circulation engine according to Embodiment 4 of the present invention. FIG. 8 is a diagram showing a pressure feed amount map of the working gas circulation engine according to the fourth embodiment of the present invention. FIG. 9 is a flowchart for explaining the control of the pumping amount of the working gas circulation engine according to the fourth embodiment of the present invention. FIG. 10 is a schematic schematic configuration diagram of a working gas circulation engine according to the fifth embodiment of the present invention. FIG. 11 is a diagram showing a pressure feed amount map of the working gas circulation engine according to the fifth embodiment of the present invention. FIG. 12 is a diagram showing a response delay time map of the working gas circulation engine according to the fifth embodiment of the present invention. FIG. 13 is a flowchart for explaining the pressure feed amount control of the working gas circulation engine according to the fifth embodiment of the present invention. FIG. 14 is a schematic configuration diagram of a working gas circulation engine according to Modification 3 of the present invention. FIG. 15 is a schematic configuration diagram of a working gas circulation engine according to Embodiment 6 of the present invention. FIG. 16 is a schematic schematic configuration diagram of a working gas circulation engine according to a seventh embodiment of the present invention. FIG. 17 is a flowchart for explaining condensate temperature control of the working gas circulation engine according to the seventh embodiment of the present invention. FIG. 18 is a schematic schematic configuration diagram of a working gas circulation engine according to an eighth embodiment of the present invention. FIG. 19 is a flowchart illustrating condensate temperature / water level control of the working gas circulation engine according to the eighth embodiment of the present invention. FIG. 20 is a schematic schematic configuration diagram of a working gas circulation engine according to Modification 4 of the present invention.

Explanation of symbols

1, 1A, 201, 201A, 301, 401, 501, 501A, 601, 701, 801, 801A Working gas circulation engine 10 Engine body 11 Cylinder head

11b Intake port

11c Exhaust port 12 Cylinder block 13 Piston 14 Connecting rod 15 Intake Valve 16 Exhaust valve 17 Intake pipe 18 Exhaust pipe 19 Crankshaft 20 Circulation path 21 Circulation path 21a First circulation path 21b Second circulation path 21c Third circulation path 30 Oxidant supply device 40 Fuel supply device 50 Electronic control device 51 Crank angle Sensor 52 Hydrogen concentration sensor 53 Oxygen concentration sensor 54 Flow rate sensor (flow rate detection means)
55 Water level sensor (water level detection means)
56A Pressure sensor 57 Temperature sensor (temperature detection means)
60 Condenser (condensing means)
61 Cooling water circulation path 62 Cooling water pump 63 Radiator 64 Condensed

water discharge passages

70, 70A, 270, 870 Condensed water storage tank (condensed water storage means)
80, 80A, 280, 280A pumping section (pumping means)
81

Condensate path

82, 82A Condensate pump (pump)
83 Open air passage 90 Heat exchanger (evaporation means)
284A High-pressure tank (working gas storage means)
285A Pressure regulating valve (regulating means)

286A Branch passages

351, 451, 551 Pressure feed control unit (pressure feed control means)
610 Expander (waste heat recovery means)
611

Output rotating member

720, 820 Heat transfer part (heat transfer means)
721 Branch passage 722 Heat exchanger 723 Flow rate adjustment valve 724 Heat medium circulation path 725 Heat medium pump 726 Circulation path heat radiation part 752,852 Heat transfer part control part 821 Branch passage 822 Flow rate adjustment valve CC Combustion chamber

Hereinafter, an embodiment of a working gas circulation engine according to the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily replaced by those skilled in the art or those that are substantially the same.

(Embodiment 1)
1 is a schematic schematic configuration diagram of a working gas circulation engine according to Embodiment 1 of the present invention, and FIG. 2 is a schematic schematic configuration diagram of a working gas circulation engine according to Modification 1 of the present invention. is there.

As shown in FIG. 1, the working gas circulation engine 1 of the present embodiment includes a combustion chamber CC to which an oxidant, fuel, and a working gas that generates power accompanying combustion of the fuel are supplied, and the combustion chamber CC. A so-called closed cycle engine configured to supply the working gas to the combustion chamber CC again through the circulation path 20 without being released to the atmosphere. It is. The working gas circulation engine 1 burns fuel in a combustion chamber CC and generates power by thermally expanding the working gas as the fuel burns.

The working gas circulation engine 1 includes an engine body 10 in which a combustion chamber CC is formed, a circulation path 20 that connects the intake side and the exhaust side of the combustion chamber CC, and an oxidant supply that supplies an oxidant to the combustion chamber CC. A device 30, a fuel supply device 40 that supplies fuel to the combustion chamber CC, and an electronic control unit (ECU) 50 that controls each part of the working gas circulation engine 1 are provided. The combustion chamber CC and the circulation path 20 of the engine body 10 are both filled with working gas, and the working gas circulates between the combustion chamber CC and the circulation path 20. 1 shows only one cylinder, the working gas circulation engine 1 of the present invention is not limited to this, and a multi-cylinder engine body 10 can also be applied.

The combustion chamber CC of the present embodiment is formed in the engine body 10. The combustion chamber CC of the engine body 10 is supplied with an oxidant, a fuel that generates water vapor by combustion with the oxidant, and a working gas. As the exhaust gas after combustion, water vapor and working gas can be exhausted.

Specifically, the engine body 10 includes a cylinder head 11, a cylinder block 12, and a piston 13 that form a combustion chamber CC. The piston 13 is connected to the crankshaft 19 via the connecting rod 14 and is disposed so as to be able to reciprocate in a space defined between the recess 11 a on the lower surface of the cylinder head 11 and the cylinder bore 12 a of the cylinder block 12. The combustion chamber CC is configured by a space surrounded by the wall surface of the recess 11 a of the cylinder head 11, the wall surface of the cylinder bore 12 a, and the top surface 13 a of the piston 13.

The engine body 10 has a cylinder head 11 formed with an intake port 11b and an exhaust port 11c. Both the intake port 11b and the exhaust port 11c form part of the circulation path 20. One end of each of the intake port 11b and the exhaust port 11c opens into the combustion chamber CC. The engine main body 10 is provided with an intake valve 15 at an opening portion of the intake port 11b on the combustion chamber CC side. The intake valve 15 opens the opening on the combustion chamber CC side of the intake port 11b when the valve is opened, and closes the opening on the combustion chamber CC side of the intake port 11b when the valve is closed. The engine body 10 is provided with an exhaust valve 16 at an opening portion of the exhaust port 11c on the combustion chamber CC side. The exhaust valve 16 opens the opening on the combustion chamber CC side of the exhaust port 11c when the valve is opened, and closes the opening on the combustion chamber CC side of the exhaust port 11c when the valve is closed.

As the intake valve 15 and the exhaust valve 16, for example, there are those that are opened and closed in accordance with the rotation of a camshaft (not shown) and the elastic force of an elastic member (string spring). In this type of intake valve 15 and exhaust valve 16, a camshaft is interlocked with the rotation of the crankshaft 19 by interposing a power transmission mechanism composed of a chain, a sprocket, etc. between the camshaft and the crankshaft 19, Open / close drive is performed at a preset opening / closing timing. The engine body 10 may include a variable valve mechanism such as a so-called variable valve timing & lift mechanism that can change the opening / closing timing and lift amount of the intake valve 15 and the exhaust valve 16, thereby The opening / closing timing and lift amount of the valve 15 and the exhaust valve 16 can be changed to suitable ones according to the operating conditions. Furthermore, the engine body 10 is applied with a so-called electromagnetically driven valve that opens and closes the intake valve 15 and the exhaust valve 16 using electromagnetic force in order to obtain the same effect as the variable valve mechanism. Also good.

The engine body 10 has an intake pipe 17 connected to an opening of the intake port 11b opposite to the combustion chamber CC side, and an exhaust pipe 18 connected to an opening of the exhaust port 11c opposite to the combustion chamber CC side. It is connected. The intake pipe 17 and the exhaust pipe 18 together form part of the circulation path 20. The intake pipe 17 is formed in a cylindrical shape and allows fluid to pass therethrough. As will be described later, the combustion chamber CC contains argon (Ar) as a working gas and oxygen (O ₂ ) as an oxidant. It is an intake passage for supplying. In other words, when the intake valve 15 is opened, the oxidant and the working gas are supplied (intake) from the intake pipe 17 to the combustion chamber CC via the intake port 11b. On the other hand, the exhaust pipe 18 is formed in a cylindrical shape so that a fluid can pass therethrough. As will be described later, as an exhaust gas after combustion of hydrogen (H ₂ ) as a fuel, the exhaust pipe 18 serves as a working gas from the combustion chamber CC. This is an exhaust passage for discharging argon (Ar) and water vapor (H ₂ O). That is, when the exhaust valve 16 is opened, the combustion chamber CC exhausts water vapor and working gas to the exhaust pipe 18 through the exhaust port 11c as exhaust gas after combustion of fuel.

The circulation path 20 can circulate the working gas contained in the exhaust gas exhausted to the exhaust pipe 18 from the exhaust side to the intake side of the combustion chamber CC and supply it to the combustion chamber CC again. The circulation path 20 includes the intake port 11b and the exhaust port 11c described above, and a circulation passage 21 that connects the other end of the intake port 11b and the other end of the exhaust port 11c. As a result, the circulation path 20 and the combustion chamber CC basically form a closed space. The circulation passage 21 is formed in a cylindrical shape and allows fluid to pass therethrough. The intake pipe 17 and the exhaust pipe 18 described above form part of the circulation passage 21.

This working gas circulation engine 1 is filled with working gas in a closed space composed of the circulation path 20 and the combustion chamber CC. The working gas circulation engine 1 circulates the working gas through the intake pipe 17 of the circulation path 20, the intake port 11b into the combustion chamber CC, the exhaust port 11c of the circulation path 20 from the combustion chamber CC, the exhaust pipe 18, and the exhaust gas. The air is circulated from the port 11c and the exhaust pipe 18 to the intake pipe 17 and the intake port 11b through the circulation passage 21 again. That is, the circulation path 20 connects the intake side (intake port 11b side) and the exhaust side (exhaust port 11c side) of the combustion chamber CC outside the combustion chamber CC, and again without releasing the working gas to the atmosphere. Supply to combustion chamber CC. Furthermore, the circulator 20 has both ends communicating with the combustion chamber CC, an exhaust gas containing water vapor and working gas flows from one end into the combustion chamber CC, and an oxidant that the combustion chamber CC takes in from the other end. And the working gas can flow out to the combustion chamber CC. Here, in the working gas circulation engine 1, when the intake valve 15 is opened, the oxidant and working gas in the circulation passage 21 are supplied to the combustion chamber CC via the intake pipe 17 and the intake port 11b. Further, in the working gas circulation engine 1, when the exhaust valve 16 is opened, the exhaust gas in the combustion chamber CC is discharged to the circulation passage 21 through the exhaust port 11c and the exhaust pipe 18.

More specifically, the circulation path 21 of the circulation path 20 includes, for example, a first circulation path 21a, a second circulation path 21b, and a third circulation path 21c. The first circulation passage 21 a connects the other end of the intake port 11 b and a discharge port 32 a of an oxidant supply means 32 described later in the oxidant supply device 30. The second circulation passage 21b connects the other end of the exhaust port 11c and an exhaust gas inlet 60a of a condenser 60 as a condensing means of the present invention described later. In addition, the heat exchanger 90 as an evaporation means of the present invention described later is provided in the second circulation passage 21b. Further, the third circulation passage 21 c connects the working gas discharge port 60 b of the condenser 60 and the working gas introduction port 32 b of the oxidant supply means 32. The intake pipe 17 described above forms part of the first circulation passage 21a, while the exhaust pipe 18 forms part of the second circulation passage 21b.

Here, a gas having a higher specific heat ratio than air is used as the working gas filled in the closed space formed by the circulation path 20 and the combustion chamber CC. As the working gas, for example, a monoatomic gas is used. Here, the working gas of the present embodiment has a higher specific heat ratio than air, and for example, a rare gas such as argon (Ar) or helium (He) that is a monoatomic gas is used. In the present embodiment, the working gas is described as using argon (Ar) as described above.

The oxidant supply device 30 supplies oxidant to the combustion chamber CC via the intake pipe 17 and the intake port 11b of the circulation path 20, and includes an oxidant storage tank 31, an oxidant supply means 32, an oxidant. A supply passage 33, a regulator 34, and an oxidant flow meter 35 are included.

The oxidant storage tank 31 stores the oxidant in a high pressure state. The oxidant supply means 32 supplies the oxidant stored in the oxidant storage tank 31 to the circulation passage 21. The oxidant supply passage 33 connects the oxidant storage tank 31 and the oxidant supply means 32. The regulator 34 and the oxidant flow meter 35 are provided on the oxidant supply passage 33.

Here, as the oxidant supply means 32 of the present embodiment, the oxidant flowing from the oxidant supply passage 33 and the working gas flowing from the circulation passage 21 through the working gas introduction port 32b are mixed, An oxidant mixing means is used for flowing the mixed oxidant and working gas from the discharge port 32a to the downstream side of the circulation passage 21 (the intake port 11b side). Therefore, the oxidant supply device 30 of the present embodiment can not only supply the oxidant to the circulation passage 21 but also mix it with the working gas passing through the circulation passage 21 and send it to the circulation passage 21. As a result, the oxidant is supplied to the combustion chamber CC together with the working gas via the intake port 11b when the intake valve 15 is opened. The oxidant supply means 32 is not limited to the above-described configuration, and is controlled by the electronic control unit 50 so that the oxidant is injected and supplied to the circulation path 20, for example, the circulation path 21 or the intake port 11b. An agent injection valve may be used.

The regulator 34 adjusts the pressure downstream of the regulator 34 in the oxidant supply passage 33 (on the engine body 10 side) to a target pressure in accordance with a command from the electronic control unit 50. In other words, the regulator 34 controls the flow rate of the oxidant in the oxidant supply passage 33. The oxidant flow meter 35 is a means for measuring the flow rate of the oxidant in the oxidant supply passage 33 and measures the flow rate of the oxidant adjusted by the regulator 34. The measurement signal of the oxidant flow meter 35 is transmitted to the electronic control unit 50.

Here, oxygen (O ₂ ) is used as the oxidant supplied by the oxidant supply device 30 as described above. That is, the oxidant storage tank 31 of the present embodiment stores oxygen as an oxidant at a high pressure of about 70 MPa, for example, and the oxidant supply means 32 supplies this high-pressure oxygen (O ₂ ) to the circulation passage 21. .

The fuel supply device 40 supplies fuel to the combustion chamber CC, and includes a fuel storage tank 41, a fuel injection means 42, a fuel supply passage 43, a regulator 44, a fuel flow meter 45, a surge tank 46, and the like. It is comprised including.

The fuel storage tank 41 stores fuel in a high pressure state. The fuel injection means 42 injects the fuel stored in the fuel storage tank 41 into the combustion chamber CC. The fuel supply passage 43 connects the fuel storage tank 41 and the fuel injection means 42. The regulator 44, the fuel flow meter 45, and the surge tank 46 are provided on the fuel supply passage 43. The regulator 44, the fuel flow meter 45, and the surge tank 46 are directed from the upstream side (the fuel storage tank 41 side) to the downstream side (the fuel injection means 42 side) with respect to the fuel supply direction in the fuel supply passage 43. The regulator 44, the fuel flow meter 45, and the surge tank 46 are provided in this order.

Here, the fuel injection means 42 of the present embodiment is provided in the cylinder head 11 so that the fuel can be directly injected into the combustion chamber CC. The fuel injection means 42 is a so-called fuel injection valve controlled by the electronic control unit 50. The electronic control unit 50, for example, the fuel injection timing or the injection amount, in other words, the supply according to the driving state (requested engine load) required by the driver for the working gas circulation engine 1 and the operating state such as the engine speed. Control the amount.

Note that the driving force (requested engine load) required by the driver for the working gas circulation engine 1 is set based on, for example, the accelerator opening degree of the vehicle on which the working gas circulation engine 1 is mounted. For example, the electronic control unit 50 can obtain the driving force required for the working gas circulation engine 1 at the current engine speed based on the engine speed of the working gas circulation engine 1 and the requested driving force. Determine how much hydrogen can be supplied. The engine speed of the working gas circulation engine 1 can be detected based on, for example, a crank angle sensor 51. The crank angle sensor 51 detects, for example, a crank angle that is a rotation angle of the crankshaft 19 of the working gas circulation engine 1. The crank angle sensor 51 transmits a detection signal to the electronic control unit 50. For example, the electronic control unit 50 determines an intake stroke, a compression stroke, an expansion stroke, and an exhaust stroke in each cylinder based on the detected crank angle, and the engine speed (rpm) as the rotational speed of the working gas circulation engine 1. ) Is calculated. Here, the engine speed corresponds to the rotational speed of the crankshaft 19 in other words, and if the rotational speed of the crankshaft 19 increases, the engine rotational speed that is the rotational speed of the crankshaft 19 also increases.

The regulator 44 adjusts the pressure downstream of the regulator 44 in the fuel supply passage 43 (on the fuel flow meter 45 and surge tank 46 side) to the set pressure. The fuel flow meter 45 is a means for measuring the fuel flow rate in the fuel supply passage 43 and measures the fuel flow rate adjusted by the regulator 44. The measurement signal of the fuel flow meter 45 is transmitted to the electronic control device 50. The surge tank 46 is intended to reduce pulsation generated in the fuel supply passage 43 when fuel is injected by the fuel injection means 42.

Here, as the fuel supplied by the fuel supply device 40, one that generates water vapor by combustion is used, and in the present embodiment, hydrogen (H ₂ ) is used as described above. That is, the fuel storage tank 41 of the present embodiment stores hydrogen as fuel at a high pressure of, for example, about 70 MPa, and the fuel injection means 42 injects this high pressure hydrogen into the combustion chamber CC.

The working gas circulation engine 1 of this embodiment is exemplified as one in which hydrogen as a fuel and oxygen as an oxidant are supplied into the combustion chamber CC to diffuse and burn hydrogen. That is, the working gas circulation engine 1 configured as described above includes high-pressure hydrogen (H ₂ ) in high-temperature compressed gas (oxygen (O ₂ ) and argon (Ar)) formed in the combustion chamber CC. ) Is self-ignited, and hydrogen and compressed gas (oxygen) are combusted while being diffusely mixed. By combustion of hydrogen in the combustion chamber CC, hydrogen and oxygen (O ₂ ) react in the combustion chamber CC to generate water vapor (H ₂ O), and argon (Ar) having a large specific heat ratio. Causes thermal expansion. As a result, in the working gas circulation engine 1, the piston 13 is pushed down by the diffusion combustion of hydrogen and the thermal expansion of argon, thereby generating power.

The working gas circulation engine 1 opens the exhaust valve 16 when the combustion of hydrogen and the thermal expansion of argon are completed (for example, when the piston 13 is located near the bottom dead center). Accordingly, exhaust gas containing water vapor and argon is discharged from the combustion chamber CC to the exhaust pipe 18 through the exhaust port 11c. Here, the argon in the exhaust gas discharged is circulated from the exhaust side to the intake side of the combustion chamber CC via the circulation path 20 and supplied to the combustion chamber CC from the intake side again in order to increase the thermal efficiency of the engine body 10. There is a need to. However, since the water vapor in the exhaust gas discharged at the same time is a molecule composed of three atoms (triatomic molecule) and has a specific heat ratio smaller than that of argon composed of a single atom, if it is circulated to the combustion chamber CC together with argon. There is a risk that the thermal efficiency of the engine body 10 may be reduced. For this reason, this working gas circulation engine 1 is provided with a means on the circulation path 20 for removing water vapor contained in the exhaust gas.

Specifically, the working gas circulation engine 1 includes a condenser 60 as a condensing means as means for removing water vapor contained in the exhaust gas flowing through the circulation path 20. The working gas circulation engine 1 further includes a cooling water circulation path 61, a cooling water pump 62, and a radiator 63.

The condenser 60 is provided in the circulation path 20 to condense the water vapor contained in the exhaust gas into condensed water (H ₂ O). The condenser 60 is provided between the second circulation passage 21b and the third circulation passage 21c on the circulation passage 21. That is, the condenser 60 is provided on the exhaust side of the oxidant supply means 32 on the circulation passage 21. The condenser 60 is connected so that the cooling water circulation path 61 passes through the inside.

The cooling water circulation path 61 circulates cooling water as a heat exchange medium through the condenser 60, and the cooling water can flow. The cooling water circulation path 61 is a closed annular path and is filled with cooling water.

The cooling water pump 62 is provided on the cooling water circulation path 61, and the cooling water in the cooling water circulation path 61 can be circulated through the cooling water circulation path 61 by driving the cooling water pump 62.

The radiator 63 is provided on the cooling water circulation path 61 and can cool the cooling water circulating in the cooling water circulation path 61. The radiator 63 of the present embodiment acts as a heat radiating means, and can cool the cooling water circulating through the cooling water circulation path 61 by the traveling wind of the vehicle on which the working gas circulation engine 1 is mounted.

Therefore, the condenser 60 circulates through the cooling water circulation path 61 and is circulated and supplied with the cooling water cooled by the radiator 63, thereby heat-exchanging the cooling water and the exhaust gas flowing through the circulation path 20. By cooling the exhaust gas, water vapor (H ₂ O) contained in the exhaust gas is liquefied and condensed to be condensed water and separated from the exhaust gas. That is, the condenser 60 can separate the exhaust gas into argon and condensed water. At this time, the cooling water whose temperature has risen due to heat exchange by exchanging heat with the exhaust gas in the circulation path 20 in the condenser 60 is radiated when circulating through the cooling water circulation path 61 and again passing through the radiator 63. As a result, the temperature is lowered, that is, cooled. That is, the cooling water circulating in the cooling water circulation path 61 radiates the heat absorbed by the condenser 60 by the radiator 63.

Then, the argon separated by the condenser 60 is discharged to the third circulation passage 21c through the working gas discharge port 60b of the condenser 60. On the other hand, the condensed water separated by the condenser 60 is discharged to the condensed water discharge passage 64 through the condensed water discharge port 60c of the condenser 60, and is outside the system of the circulation path 20, here as condensed water storage means described later. The condensed water storage tank 70 is discharged.

The condenser 60 and the radiator 63 are configured to reach a temperature at which the water vapor in the exhaust gas is liquefied and condensed when the hottest exhaust gas that can be assumed during engine operation is discharged from the combustion chamber CC. The capacity capable of lowering the exhaust gas temperature (in other words, the exhaust gas cooling performance) is set.

Here, the exhaust gas discharged from the combustion chamber CC may contain not only water vapor and argon but also hydrogen or oxygen. For example, when the supply amount of hydrogen to the combustion chamber CC is larger than a predetermined amount relative to oxygen, unburned hydrogen remains and is discharged to the circulation path 20 as it is. Further, when the supply amount of oxygen to the combustion chamber CC is larger than a predetermined amount with respect to hydrogen, oxygen remains and is discharged to the circulation path 20 as it is. For this reason, hydrogen and oxygen in the exhaust gas are discharged from the working gas discharge port 60b of the condenser 60 to the third circulation passage 21c together with argon after the water vapor in the exhaust gas is separated by the condenser 60. Accordingly, hydrogen and oxygen in the exhaust gas circulate through the circulation path 20 similarly to argon and are supplied again to the combustion chamber CC.

Therefore, the working gas circulation engine 1 detects the amount of hydrogen or oxygen in the gas (circulation gas) circulating in the circulation path 20 from the exhaust side to the intake side, and determines when the hydrogen or oxygen reaches the combustion chamber CC. As a matter of course, the injection amount of hydrogen from the fuel supply device 40 or the supply amount of oxygen from the oxidant supply device 30 is adjusted. Thereby, the working gas circulation engine 1 can prevent excessive hydrogen or oxygen in the combustion chamber CC.

Specifically, the working gas circulation engine 1 is a fuel concentration detection means for detecting the concentration of fuel in the circulation gas circulating through the circulation path 20, here, a hydrogen concentration detection means for detecting the hydrogen concentration in the circulation gas. Specifically, a hydrogen concentration sensor 52 and an oxidant concentration detection means for detecting the concentration of the oxidant in the circulation gas, here an oxygen concentration detection means for detecting the oxygen concentration in the circulation gas, Specifically, an oxygen concentration sensor 53 is provided. The hydrogen concentration sensor 52 and the oxygen concentration sensor 53 each transmit a detection signal to the electronic control unit 50. Therefore, the electronic control unit 50 grasps the remaining amount of hydrogen or oxygen in the circulating gas from the respective detection signals, estimates the time when the hydrogen or oxygen reaches the combustion chamber CC, and determines the amount of hydrogen in the fuel injection means 42. The injection amount or the target pressure of the regulator 34 (that is, the supply amount of oxygen) is controlled.

In the working gas circulation engine 1 configured as described above, the piston 13 is pushed down by the thermal expansion of argon having a large specific heat ratio accompanying the combustion of hydrogen in the combustion chamber CC. By repeating the reciprocating motion within 12a, this cycle is repeated with the intake stroke, compression stroke, combustion stroke, and exhaust stroke as one cycle. The reciprocating motion of the piston 13 is transmitted to the crankshaft 19 by the connecting rod 14, and the reciprocating motion is converted into rotational motion by the action of the connecting rod 14 and the crankshaft 19, and the crankshaft 19 rotates. During this time, the electronic control unit 50 determines the rotational position of the crankshaft 19, the accelerator opening that is the operation amount of an accelerator pedal (not shown) provided in the driver's seat of the vehicle, the remaining amount of hydrogen or oxygen in the circulating gas, and the like. The hydrogen injection amount of the fuel injection means 42 or the target pressure of the regulator 34 (that is, the oxygen supply amount) is controlled according to the operating state.

In addition, the working gas circulation engine 1 reciprocates the intake valve 15 and the exhaust valve 16 as the crankshaft 19 rotates, and repeats communication and disconnection between the circulation path 20 and the combustion chamber CC. And repeat the above four steps.

That is, in the working gas circulation engine 1, in the intake stroke, the intake valve 15 is opened, the exhaust valve 16 is closed, and the piston 13 is moved from the top dead center side to the bottom dead center side. Oxygen and argon are sucked into the combustion chamber CC via the intake pipe 17 and the intake port 11b of the circulation path 20.

Next, in the working gas circulation engine 1, in the compression stroke, the intake valve 15 is closed, both the intake valve 15 and the exhaust valve 16 are closed, and the piston 13 is moved from the bottom dead center to the top dead center. By moving to the side, oxygen and argon in the combustion chamber CC are compressed and the temperature rises.

Next, the working gas circulation engine 1 injects high-pressure hydrogen into high-temperature compressed gas (oxygen and argon) formed in the combustion chamber CC in the combustion stroke, so that a part of the hydrogen is injected. It self-ignites and burns while diffusing and mixing hydrogen and compressed gas (oxygen). When hydrogen burns, argon having a large specific heat ratio causes thermal expansion, and the piston 13 is pushed down by the diffusion combustion of hydrogen and the thermal expansion of argon, whereby the working gas circulation engine 1 Generate power.

Next, in the working gas circulation engine 1, in the exhaust stroke, the intake valve 15 is kept closed, the exhaust valve 16 is opened, and the piston 13 is moved from the bottom dead center side to the top dead center side. As a result, the exhaust gas containing water vapor and argon is discharged from the combustion chamber CC to the exhaust pipe 18 via the exhaust port 11c of the circulation path 20.

In the working gas circulation engine 1, exhaust gas containing water vapor and argon is discharged from the combustion chamber CC to the circulation path 20, and when this exhaust gas circulates in the circulation path 20 toward the combustion chamber CC. In the condenser 60, the water vapor in the exhaust gas is liquefied, condensed and separated. As a result, the working gas circulation engine 1 does not supply steam with a small specific heat ratio to the combustion chamber CC, and again supplies argon as a working gas with a large specific heat ratio to the combustion chamber CC. High driving can be performed.

Incidentally, as described above, the working gas circulation engine 1 removes water vapor in the exhaust gas in the condenser 60 when the exhaust gas is circulated toward the combustion chamber CC as a circulation gas. The working gas circulation engine 1 does not supply water vapor with a small specific heat ratio to the combustion chamber CC, but again supplies argon as a working gas with a large specific heat ratio to the combustion chamber CC, thereby performing an operation with high thermal efficiency. ing. At this time, the working gas circulation engine 1 discharges the condensed water separated by the condenser 60 from the condensed water discharge port 60c to the condensed water discharge passage 64, drains it outside the system of the circulation path 20, and simply condensate water. Since the size of the condensed water storage tank 70 is limited only by being stored in the storage tank 70, various problems such as deterioration of the mountability may occur. Therefore, it is necessary to appropriately process this condensed water. .

For example, the working gas circulation engine 1 is provided with a condensate water storage tank for storing condensate water so as to cover the exhaust pipe 18 through which high-temperature exhaust gas after combustion flows. Although the condensed water can be appropriately treated by treating after evaporating the water, there is room for further improvement in terms of mountability. That is, the working gas circulation engine 1 is stored in the condensed water storage tank when the condensed water storage tank is provided so as to cover the exhaust pipe 18 as described above and the condensed water is evaporated using the exhaust heat. In order to bring the condensed water into contact with the outer surface of the exhaust pipe 18, the condensed water storage tank must be disposed in a limited mounting space near the exhaust pipe 18. For this reason, the working gas circulation engine 1 has less freedom in mounting the condensed water storage tank. For example, to ensure a sufficient capacity of the condensed water storage tank, the working gas circulation engine 1 is made larger. On the other hand, there is a risk that sufficient condensate storage tank capacity cannot be secured.

Therefore, the working gas circulation engine 1 of the present embodiment, as shown in FIG. 1, causes the condensed water stored in the condensed water storage tank 70 as the condensed water storage means to be discharged from the atmospheric pressure by the pressure feeding unit 80 as the pressure feeding means. The condensed water is pumped to the heat exchanger 90 as the evaporation means at a high pressure, and the condensed water pumped by the heat exchanger 90 is evaporated using the exhaust heat of the exhaust gas, so that the condensed water is appropriately processed. Yes.

The condensed water storage tank 70 can store condensed water. In other words, the condensed water storage tank 70 can store the condensed water separated by the condenser 60 and is connected to the condensed water discharge passage 64. Therefore, the condensed water separated by the condenser 60 is discharged to the condensed water discharge passage 64 via the condensed water discharge port 60 c of the condenser 60 and discharged to the condensed water storage tank 70.

The pressure feeding unit 80 pumps the condensed water stored in the condensed water storage tank 70 at a pressure higher than the atmospheric pressure. The pumping unit 80 of this embodiment includes a condensed water path 81 and a condensed water pump 82.

Condensed water path 81 allows condensed water to flow inside. The condensed water path 81 connects the condensed water storage tank 70 and a heat exchanger 90 described later so that condensed water can flow. Here, the condensed water path 81 is configured to include the above-described condensed water discharge path 64 and the atmosphere opening path 83.

As described above, the condensed water discharge passage 64 connects the condensed water discharge port 60c of the condenser 60 and the condensed water storage tank 70, and one end is connected to the condensed water discharge port 60c of the condenser 60. The end opens to a space for storing condensed water inside the condensed water storage tank 70. Thereby, the condensed water separated by the condenser 60 is discharged to the condensed water storage tank 70 via the condensed water discharge port 60 c and the condensed water discharge passage 64, and stored in the condensed water storage tank 70.

The atmosphere opening passage 83 opens the inside of the condensed water storage tank 70 to the atmosphere via a heat exchanger 90 to be described later, and one end opens to a space for storing condensed water inside the condensed water storage tank 70. The other end opens to the atmosphere. A heat exchanger 90 described later is provided in the atmosphere opening passage 83. As a result, as will be described later, the condensed water pumped from the condensed water storage tank 70 to the heat exchanger 90 via the atmosphere release passage 83 evaporates in the heat exchanger 90 to become water vapor, and this water vapor is released to the atmosphere. The other end of the passage 83 is opened to the atmosphere.

That is, the condensed water path 81 as a whole is a path in which one end on the condensed water discharge passage 64 side is connected to the condensed water discharge port 60c of the condenser 60 and the other end on the atmosphere opening passage 83 side is opened to the atmosphere. The condensed water storage tank 70 is provided between the condensed water discharge passage 64 and the atmosphere release passage 83, and the heat exchanger 90 is provided on the atmosphere release passage 83.

The condensate pump 82 is provided in the condensate path 81 and pressurizes the condensate and pumps it from the condensate storage tank 70 side to the heat exchanger 90 side. The condensed water pump 82 of the present embodiment is provided on the atmosphere opening passage 83 in the condensed water path 81. The condensed water pump 82 is provided in the atmosphere opening passage 83 between the opening of the atmosphere opening passage 83 located inside the condensed water storage tank 70 and a heat exchanger 90 described later.

The condensed water pump 82 sucks condensed water stored in the condensed water storage tank 70 into the atmosphere opening passage 83 through an opening of the atmosphere opening passage 83 located inside the condensed water storage tank 70, and this condensed water is atmospheric pressure. Pressurize to a higher pressure. The condensed water pump 82 pressurizes the pressure of the condensed water in the atmosphere open passage 83 of the condensed water path 81 to a pressure higher than the atmospheric pressure, and then pumps the condensed water from the condensed water storage tank 70 side to the heat exchanger 90 side. Therefore, the condensed water pumped by the condensed water pump 82 at a pressure higher than the atmospheric pressure (water vapor after being evaporated by the heat exchanger 90 described later) from the condensed water storage tank 70 side to the atmosphere side. It flows in one direction and is prevented from flowing back. In addition, this condensed water pump 82 can adjust the pumping amount of condensed water by the drive being controlled by the electronic control apparatus 50, for example.

The heat exchanger 90 evaporates the condensed water pumped by the pumping unit 80 by the exhaust heat of the exhaust gas. The heat exchanger 90 evaporates the condensed water by the exhaust heat of the exhaust gas by exchanging heat between the exhaust gas and the condensed water. The heat exchanger 90 is provided in the circulation path 20. The heat exchanger 90 of the present embodiment is provided on the second circulation passage 21 b in the circulation passage 21. That is, the heat exchanger 90 is provided between the exhaust port 11c and the condenser 60 in the second circulation passage 21b, and the exhaust gas introduction port 90a for introducing the exhaust gas therein is provided in the exhaust port of the second circulation passage 21b. An exhaust gas discharge port 90b that is connected to the 11c side and discharges exhaust gas from the inside is connected to the condenser 60 side of the second circulation passage 21b. The heat exchanger 90 is connected so that the atmosphere opening passage 83 of the condensed water passage 81 passes through the inside. In other words, the condensed water path 81 is provided so as to pass through the inside of the heat exchanger 90.

Therefore, the heat exchanger 90 exchanges heat between the exhaust gas flowing through the second circulation passage 21b and the condensed water that is pumped through the atmosphere opening passage 83 by the condensed water pump 82, and this heat is generated by the exhaust heat of the exhaust gas. The condensed water can be evaporated. Here, the heat exchanger 90 evaporates the condensed water by the exhaust gas upstream of the condenser 60 with respect to the circulation direction of the working gas circulating in the circulation path 20, that is, the exhaust heat of the high-temperature exhaust gas after combustion. Can be made.

In the working gas circulation engine 1 configured as described above, the condensed water separated by the condenser 60 is discharged to the condensed water storage tank 70 via the condensed water discharge port 60c and the condensed water discharge passage 64. It is stored in the water storage tank 70. The condensed water stored in the condensed water storage tank 70 is sucked into the atmospheric open passage 83 through the opening of the atmospheric open passage 83 located inside the condensed water storage tank 70 when the condensed water pump 82 is driven. Is pressurized to a high pressure and fed toward the heat exchanger 90. Then, the condensed water pressure-fed toward the heat exchanger 90 through the atmosphere opening passage 83 reaches the heat exchanger 90.

Then, the condensed water that is pumped by the condensed water pump 82 through the atmosphere opening passage 83 and reaches the heat exchanger 90 flows through the second circulation passage 21b and is introduced into the heat exchanger 90 by the heat exchanger 90. By exchanging heat with the exhaust gas, the heat of the exhaust gas is absorbed and the temperature rises. As a result, it evaporates and becomes water vapor. The water vapor generated by the evaporation of the condensed water in the heat exchanger 90 flows in one direction from the heat exchanger 90 side to the atmosphere side through the atmosphere opening passage 83 and is released from the opening of the atmosphere opening passage 83 to the atmosphere. .

As a result, the working gas circulation engine 1 is separated by the condenser 60 by evaporating the condensed water in the condensed water storage tank 70 by using the exhaust heat of the exhaust gas in the heat exchanger 90 and releasing it into the atmosphere as water vapor. Since the condensed water thus treated can be appropriately processed, the capacity of the condensed water storage tank 70 can be relatively reduced, and the mounting property of the working gas circulation engine 1 on the vehicle can be improved.

Further, the working gas circulation engine 1 pumps the condensed water stored in the condensed water storage tank 70 to the heat exchanger 90 by the pumping unit 80 and evaporates the condensed water. Therefore, it is not necessary to directly contact the condensed water stored in the exhaust pipe 18 and the outer surface of the exhaust pipe 18 forming the second circulation passage 21b, and it is not necessary to arrange the condensed water storage tank 70 in a limited mounting space near the exhaust pipe 18. . As a result, this working gas circulation engine 1 can improve the degree of freedom of the place where the condensed water storage tank 70 is mounted. Therefore, this working gas circulation engine 1 may, for example, increase the size of the working gas circulation engine 1 in order to ensure a sufficient capacity of the condensed water storage tank 70, or conversely, a sufficient capacity of the condensed water storage tank 70. Can not be secured. Further, in this working gas circulation engine 1, since the condensed water is not in direct contact with the exhaust pipe 18 forming the second circulation passage 21b, it is possible to prevent the exhaust pipe 18 from locally lowering the temperature. As a result, it is possible to suppress the occurrence of thermal distortion in the exhaust pipe 18, thereby improving the durability of the exhaust pipe 18.

At this time, the working gas circulation engine 1 pumps the condensed water stored in the condensed water storage tank 70 to the heat exchanger 90 at a pressure higher than the atmospheric pressure by the pumping unit 80 and generates water vapor generated in the heat exchanger 90. From the condensed water storage tank 70 side through the heat exchanger 90 to the atmosphere side in one direction after the condensed water and the heat exchanger 90 evaporate. It is possible to prevent the condensed water and water vapor from flowing back through the atmosphere opening passage 83. As a result, the working gas circulation engine 1 can pump the condensed water stored in the condensed water storage tank 70 to the heat exchanger 90 by the pumping unit 80, evaporate the condensed water, and reliably release it to the atmosphere. .

Furthermore, this working gas circulation engine 1 is provided in the second circulation passage 21b upstream of the condenser 60 with respect to the circulation direction of the working gas in which the heat exchanger 90 circulates in the circulation path 20, so that heat exchange is performed. Since the exhaust heat of the exhaust gas before the condenser 90 reaches the condenser 60 can be absorbed by the condensed water, the temperature of the exhaust gas before being introduced into the condenser 60 can be lowered. As a result, since the working gas circulation engine 1 can lower the temperature of the exhaust gas introduced into the condenser 60, the exhaust gas temperature is lowered to a temperature at which the water vapor in the exhaust gas is liquefied and condensed. Since the capacities of the condenser 60 and the radiator 63 that can be reduced can be reduced, the condenser 60 and the radiator 63 can be reduced in size. In other words, since the working gas circulation engine 1 can reduce the temperature of the exhaust gas introduced into the condenser 60, the amount of heat that the cooling water takes from the exhaust gas in the condenser 60 can be reduced. The capacity of the device 60 and the radiator 63 can be reduced. In other words, the working gas circulation engine 1 can separate the water vapor from the exhaust gas by the condenser 60 and the radiator 63 having a relatively small capacity, and can prevent a decrease in the average specific heat ratio of the working gas. The highly efficient operation can be maintained while the working gas circulation engine 1 is downsized and mountability is improved.

In other words, this working gas circulation engine 1 is exhausted by exchanging heat between the exhaust gas and the condensed water in the heat exchanger 90 without providing a condenser, a radiator, etc. separately from the radiator 63 for the condenser 60, for example. Since the temperature of the gas can be lowered, the working gas circulation engine 1 can be downsized also in this respect, and as a result, the mounting property of the working gas circulation engine 1 on the vehicle can be improved. . In the working gas circulation engine 1, the condensate resulting from the heat exchange between the exhaust gas and the condensed water in the heat exchanger 90 is, for example, the second circulation passage 21 b and the exhaust gas inlet 60 a. , It may be discharged to the condensed water storage tank 70 via the condenser 60, the condensed water discharge port 60c and the condensed water discharge passage 64, or condensed via a condensed water discharge passage (not shown) of a separate system. You may make it discharge to the water storage tank 70. FIG.

According to the working gas circulation engine 1 according to the embodiment of the present invention described above, oxygen as an oxidant, hydrogen as a fuel that generates water vapor by combustion with this oxygen, and a specific heat ratio higher than that of air. Argon is supplied and can expand as the hydrogen burns, and the combustion chamber CC is capable of exhausting water vapor and argon as the exhaust gas after the hydrogen combustion, and the argon contained in the exhaust gas is the combustion chamber. A circulation path 20 that can be circulated from the exhaust side of the CC to the intake side and supplied to the combustion chamber CC again, a condenser 60 that is provided in the circulation path 20 and that condenses water vapor contained in the exhaust gas into condensed water, The condensed water storage tank 70 capable of storing water, the pumping unit 80 for pumping the condensed water stored in the condensed water storage tank 70 at a pressure higher than the atmospheric pressure, and the condensed water pumped by the pumping unit 80 The exhaust heat of the exhaust gas and a heat exchanger 90 to evaporate.

Therefore, the working gas circulation engine 1 pumps the condensed water stored in the condensed water storage tank 70 to the heat exchanger 90 at a pressure higher than the atmospheric pressure by the pressure feeding unit 80, and the pressure is fed by the heat exchanger 90. Since the condensed water is evaporated using the exhaust heat of the exhaust gas, the condensed water stored in the condensed water storage tank 70 can be discharged to the atmosphere as water vapor. As a result, for example, a working gas circulation engine 1 can be mounted on the vehicle, and the condensed water separated by the condenser 60 can be appropriately treated.

Furthermore, according to the working gas circulation engine 1 according to the embodiment of the present invention described above, the oxidant is oxygen and the fuel is hydrogen. Therefore, the working gas circulation engine 1 separates the water vapor generated by the combustion of oxygen and hydrogen as condensed water by the condenser 60, temporarily stores the condensed water in the condensed water storage tank 70, and then presses the pressure feeding unit 80. And the heat exchanger 90 can be discharged into the atmosphere as water vapor and processed appropriately.

Further, according to the working gas circulation engine 1 according to the embodiment of the present invention described above, the heat exchanger 90 is located upstream of the condenser 60 with respect to the circulation direction of the working gas circulating in the circulation path 20. The condensed water is evaporated by the exhaust heat of the exhaust gas. Accordingly, the working gas circulation engine 1 evaporates the condensed water by the exhaust heat of the exhaust gas upstream of the condenser 60 with respect to the circulation direction of the working gas through which the heat exchanger 90 circulates in the circulation path 20. The condensed water can be efficiently evaporated by the exhaust heat of the relatively high temperature exhaust gas. Furthermore, since the working gas circulation engine 1 can absorb the exhaust heat of the exhaust gas before reaching the condenser 60 into the condensed water, the temperature of the exhaust gas introduced into the condenser 60 can be reduced. The capacity of the condenser 60 and the radiator 63 can be reduced. As a result, the working gas circulation engine 1 can reduce the size of the condenser 60 and the radiator 63, and can further improve the mountability after properly treating the condensed water separated by the condenser 60. .

Furthermore, according to the working gas circulation engine 1 according to the embodiment of the present invention described above, the pressure feeding unit 80 connects the condensed water storage tank 70 and the heat exchanger 90 so that the condensed water can flow. A condensate water pump 82 is provided in the condensate water path 81 and pressurizes the condensate water in the condensate water path 81 and pumps it from the condensate water storage tank 70 side to the heat exchanger 90 side. Therefore, the working gas circulation engine 1 pumps the condensed water stored in the condensed water storage tank 70 to the heat exchanger 90 via the condensed water path 81 at a pressure higher than the atmospheric pressure by the condensed water pump 82 to exchange heat. Since the water vapor generated in the vessel 90 is released to the atmosphere, it is possible to reliably prevent the condensed water flowing through the condensed water path 81 (water vapor after being evaporated in the heat exchanger 90) from flowing backward. As a result, the working gas circulation engine 1 can pump the condensed water stored in the condensed water storage tank 70 to the heat exchanger 90 by the pumping unit 80, evaporate the condensed water, and reliably release it to the atmosphere. .

In the above description, the heat exchanger 90 is condensed water by the exhaust heat of the exhaust gas upstream of the condenser 60 with respect to the circulation direction of the working gas provided in the second circulation passage 21b and circulating in the circulation path 20. However, the present invention is not limited to this. The heat exchanger 90 is provided, for example, on the downstream side of the condenser 60 in the circulation passage 21 as long as it can obtain a heat quantity sufficient to evaporate the condensed water from the exhaust heat of the exhaust gas. It may be. However, since the exhaust heat of the exhaust gas after combustion becomes relatively high as it becomes closer to the exhaust port 11c side of the combustion chamber CC, the heat exchanger 90 is relatively in the combustion chamber CC in the circulation passage 21. It is preferable to be provided at a position close to the exhaust port 11c side. For example, the heat exchanger 90 is preferably provided on the upstream side of the working gas discharge port 60b of the condenser 60, and more specifically, on the upstream side of the exhaust gas introduction port 60a of the condenser 60 as described above. More preferably, it is provided.

Further, the atmosphere opening passage 83 that forms the condensed water path 81 may be configured such that a part of the condensed water storage tank 70 side from the heat exchanger 90 passes inside the condenser 60. In this case, the cooling water circulation path 61 and the air release path 83 need only be separate from each other inside the condenser 60. In this case, the working gas circulation engine 1 reaches the heat exchanger 90 because the condensed water moving toward the heat exchanger 90 in the atmosphere opening passage 83 absorbs the exhaust heat of the exhaust gas in the condenser 60. Therefore, the heat exchanger 90 can efficiently evaporate the condensed water preheated in the condenser 60.

Further, the condensed water pump 82 of the pressure feeding unit 80 may be provided other than the atmosphere opening passage 83.

FIG. 2 is a schematic configuration diagram of a working gas circulation engine according to Modification 1 of the present invention.

As shown in FIG. 2, the working gas circulation engine 1A according to the present modification includes a pumping unit 80A as a pumping unit, and the pumping unit 80A includes a condensed water path 81 and a condensed water pump 82A. The condensed water path 81 includes a condensed water discharge path 64 and an atmosphere opening path 83. The condensed water pump 82A is provided in the condensed water path 81, pressurizes condensed water, and pumps the condensed water from the condensed water storage tank 70A side to the heat exchanger 90 side. The condensed water pump 82 </ b> A of this modification is provided on the condensed water discharge passage 64 in the condensed water path 81.

And the condensate water storage tank 70A as the condensate storage means of this modification has a sealed space for storing condensate. Therefore, the condensed water pump 82A pumps the condensed water in the condensed water discharge passage 64 so as to push it toward the condensed water storage tank 70A side in which the internal space is sealed, so that the inside of the condensed water storage tank 70A. Can be pressurized to a pressure higher than atmospheric pressure, and the condensed water stored in the condensed water storage tank 70 </ b> A can be pumped toward the heat exchanger 90 side through the atmosphere opening passage 83.

Even in this case, the working gas circulation engine 1A pumps the condensed water stored in the condensed water storage tank 70A to the heat exchanger 90 at a pressure higher than the atmospheric pressure by the pumping unit 80A. The condensed water thus pumped is evaporated using the exhaust heat of the exhaust gas, so that the condensed water stored in the condensed water storage tank 70A can be discharged to the atmosphere as water vapor. The mounting property of the working gas circulation engine 1A on the vehicle can be improved, and the condensed water separated by the condenser 60 can be appropriately treated.

Even in this case, the working gas circulation engine 1A exchanges heat of the condensed water stored in the condensed water storage tank 70A through the condensed water path 81 at a pressure higher than the atmospheric pressure by the condensed water pump 82A. Since the water vapor generated by the heat exchanger 90 is pumped to the vessel 90 and released to the atmosphere, it is possible to prevent the condensed water and water vapor flowing through the condensed water passage 81 from flowing backward. As a result, the working gas circulation engine 1 can pump the condensed water stored in the condensed water storage tank 70A to the heat exchanger 90 by the pumping section 80A, evaporate the condensed water, and reliably release it to the atmosphere. .

(Embodiment 2)
FIG. 3 is a schematic schematic configuration diagram of a working gas circulation engine according to Embodiment 2 of the present invention, and FIG. 4 is a schematic schematic configuration diagram of a working gas circulation engine according to Modification 2 of the present invention. is there. The working gas circulation engine according to the second embodiment has substantially the same configuration as the working gas circulation engine according to the first embodiment, but the structure of the pressure feeding means is different from that of the working gas circulation engine according to the first embodiment. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

The working gas circulation engine 201 according to the present embodiment includes a pressure feeding unit 280 as pressure feeding means, as shown in FIG. The pumping unit 280 pumps the condensed water stored in the condensed water storage tank 270 at a pressure higher than the atmospheric pressure. The pumping unit 280 includes a condensed water passage 81, and the condensed water passage 81 includes a condensed water discharge passage 64 and an air release passage 83.

As a whole, the condensed water path 81 has a path in which one end on the condensed water discharge passage 64 side is connected to the condensed water discharge port 60c of the condenser 60 and the other end on the atmosphere opening path 83 side is opened to the atmosphere. A condensed water storage tank 270 as condensed water storage means is provided between the water discharge passage 64 and the atmosphere release passage 83, and a heat exchanger 90 is provided on the atmosphere release passage 83.

Here, the pumping unit 280 of the present embodiment does not include the condensed water pump 82 (see FIG. 1) and the condensed water pump 82A (see FIG. 2) described above, and the pumping unit 80 (see FIG. 1) This is different from the pressure feeding unit 80A (see FIG. 2).

And the condensed water storage tank 270 of this embodiment has the space part which stores condensed water sealed like the condensed water storage tank 70A (refer FIG. 2) demonstrated above.

Therefore, the condensed water path 81 of the pumping unit 280 of this embodiment connects the condensed water storage tank 270 and the heat exchanger 90 so that the condensed water can flow, and the space for storing the condensed water is sealed. The condensed water storage tank 270 communicates with the circulation path 20. That is, the condensed water path 81 is configured to communicate with the circulation path 21 of the circulation path 20 through the condenser 60 via the condensed water storage tank 270 in which the space for storing condensed water is sealed. .

The pressure feeding unit 280 uses the pressure of the circulation passage 21 of the circulation path 20, that is, the pressure of the gas in the circulation path 21, after the condensed water storage tank 270 is sealed, The condensed water is pressurized and fed from the condensed water storage tank 270 side to the heat exchanger 90 side. The pressure feeding unit 280 pressurizes the condensed water in the condensed water path 81 and pumps it from the condensed water storage tank 270 side to the heat exchanger 90 side when the pressure in the circulation path 21 of the circulation path 20 becomes higher than the atmospheric pressure. Can do. In other words, the pressure feeding unit 280 pushes the condensed water in the condensed water discharge passage 64 toward the condensed water storage tank 270 that is in a sealed state by the pressure of the circulation passage 21 of the circulation path 20 higher than the atmospheric pressure. By pressure-feeding, the pressure inside the condensed water storage tank 270 is increased to a pressure higher than the atmospheric pressure, and the condensed water stored in the condensed water storage tank 270 is transferred to the heat exchanger 90 side via the atmosphere opening passage 83. Can be pumped toward.

Here, the pressure in the circulation path 21 of the circulation path 20 does not need to be higher than the atmospheric pressure in the entire circulation path 20, for example, in the vicinity of a portion where condensed water is discharged from the condenser 60, that is, a condensed water discharge port. What is necessary is just to make the vicinity of 60c higher than atmospheric pressure.

According to the working gas circulation engine 201 according to the embodiment of the present invention described above, the working gas circulation engine 201 causes the condensed water stored in the condensed water storage tank 270 to be higher than the atmospheric pressure by the pumping unit 280. The condensate stored in the condensate storage tank 270 is steamed because the condensed water pumped by the heat exchanger 90 is evaporated using the exhaust heat of the exhaust gas. As a result, for example, the mounting property of the working gas circulation engine 201 on the vehicle can be improved, and the condensed water separated by the condenser 60 can be appropriately treated.

Furthermore, according to the working gas circulation engine 201 according to the embodiment of the present invention described above, the pressure feeding unit 280 connects the condensed water storage tank 270 and the heat exchanger 90 so that the condensed water can flow, A condensed water path 81 communicates with the circulation path 20 via a condensed water storage tank 270 in which the space for storing the condensed water is hermetically sealed, and the condensed water is caused by the gas pressure in the circulation path 20 higher than the atmospheric pressure. The condensed water in the path 81 is pressurized and fed from the condensed water storage tank 270 side to the heat exchanger 90 side. Therefore, the working gas circulation engine 201 pumps the condensed water stored in the condensed water storage tank 270 to the heat exchanger 90 via the condensed water path 81 by the pressure of the gas in the circulation path 20 higher than the atmospheric pressure. Since the water vapor generated in the exchanger 90 is released to the atmosphere, it is possible to reliably prevent the condensed water flowing through the condensed water path 81 (water vapor after being evaporated in the heat exchanger 90) from flowing backward. As a result, the working gas circulation engine 1 can pump the condensed water stored in the condensed water storage tank 270 to the heat exchanger 90 by the pumping unit 280, evaporate the condensed water, and reliably release it to the atmosphere. . The working gas circulation engine 201 pressurizes the condensed water in the condensed water path 81 using the pressure of the gas in the circulation path 20 after the pressure feeding unit 280 has sealed the condensed water storage tank 270 in a sealed state. Since it is pumped from the condensed water storage tank 270 side to the heat exchanger 90 side, for example, there is no need to provide the condensed water pump 82 (see FIG. 1) and the condensed water pump 82A (see FIG. 2) as described above. The working gas circulation engine 201 can be reduced in size, and the mounting property of the working gas circulation engine 201 on the vehicle can be further improved.

In addition, the pumping unit 280 of the working gas circulation engine 201 described above may further include working gas storage means and adjustment means.

FIG. 4 is a schematic configuration diagram of a working gas circulation engine according to the second modification of the present invention.

As shown in FIG. 4, the working gas circulation engine 201A according to this modification includes a pressure feeding unit 280A as pressure feeding means. As described above, the condensed water storage tank 270 has a sealed space for storing condensed water. The pumping unit 280A of the present modification has substantially the same configuration as the above-described pumping unit 280, but further includes a high-pressure tank 284A as a working gas storage unit and a pressure regulating valve 285A as a regulating unit. It differs from the above-mentioned pumping part 280 by the point comprised.

The high-pressure tank 284A is provided to be branched from the circulation path 20, and stores, for example, a working gas having a relatively high pressure compared to the gas pressure in the circulation path 20. The high-pressure tank 284A is provided on the circulation passage 21 of the circulation passage 20, here, the branch passage 286A branched from the third circulation passage 21c. The inside of the high-pressure tank 284A communicates with the inside of the third circulation passage 21c via the branch passage 286A.

The pressure regulating valve 285A regulates the inflow / outflow of the working gas between the high pressure tank 284A and the circulation passage 21 of the circulation path 20, in this case, the third circulation path 21c. The pressure regulating valve 285A is provided in the branch passage 286A, and the opening and closing operation of the valve body is executed, the opening degree of the branch passage 286A is adjusted, and the passage area of the branch passage 286A is adjusted, so that the high pressure tank 284A and the third circulation are provided. The inflow and outflow of the working gas to and from the passage 21c can be adjusted.

As a result, in the working gas circulation engine 201A, the opening degree of the pressure regulating valve 285A is adjusted by the electronic control unit 50, and the flow of working gas between the high pressure tank 284A and the third circulation passage 21c is adjusted. The pressure of the gas in the circulation passage 21 of the circulation path 20 can be made higher than the atmospheric pressure, so that the pressure feeding unit 280A condenses using the pressure of the gas in the circulation path 21 of the circulation path 20. The condensed water in the water path 81 can be pressurized and fed from the condensed water storage tank 270 side to the heat exchanger 90 side. Further, in the pressure feeding unit 280A, the opening degree of the pressure regulating valve 285A is adjusted by the electronic control unit 50, and the inflow / outflow of the working gas between the high pressure tank 284A and the third circulation passage 21c is regulated, so By controlling the pressure of the gas inside, the pumping amount of the condensed water can be adjusted.

According to the working gas circulation engine 201A according to the modification of the present invention described above, the pressure feeding unit 280A is branched from the circulation path 20 and stores a relatively high pressure working gas 284A. You may comprise so that it may have the pressure control valve 285A which adjusts the inflow / outflow of the working gas between the high pressure tank 284A and the circulation path 20. In this case, the pressure of the gas in the circulation path 20 can be made higher than the atmospheric pressure by adjusting the opening degree of the pressure control valve 285A by the electronic control unit 50, whereby the pressure feeding unit 280A By using the pressure of the gas in the circulation path 20, the condensed water in the condensed water path 81 can be pressurized and fed from the condensed water storage tank 270 side to the heat exchanger 90 side. In this case, for example, the pressure feeding unit 280A regulates the opening degree of the pressure regulating valve 285A without controlling the combustion state of oxygen and hydrogen in the combustion chamber CC, in other words, without controlling the supply amount of oxygen and hydrogen. The pressure of the gas in the circulation path 20 can be adjusted by adjusting the flow of the working gas between the high-pressure tank 284A and the third circulation passage 21c, for example, the condensed water pump 82 (FIG. 1). And the condensate pump 82A (see FIG. 2) can be adjusted without changing the combustion state of oxygen and hydrogen in the combustion chamber CC.

(Embodiment 3)
FIG. 5 is a schematic schematic configuration diagram of a working gas circulation engine according to the third embodiment of the present invention, and FIG. 6 is a flowchart for explaining pressure feed amount control of the working gas circulation engine according to the third embodiment of the present invention. It is. The working gas circulation engine according to the third embodiment has substantially the same configuration as the working gas circulation engine according to the first embodiment, but is different from the working gas circulation engine according to the first embodiment in that it includes a pressure feed amount control unit. Different. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

As shown in FIG. 5, the working gas circulation engine 301 according to the present embodiment is functionally conceptually provided with a pumping amount control unit 351 as a pumping amount control unit in an electronic control unit (ECU) 50.

Here, the electronic control unit 50 is mainly configured of a microcomputer, and includes a processing unit 50a, a storage unit 50b, and an input / output unit 50c, which are connected to each other and can exchange signals with each other. A drive circuit (not shown) for driving each part of the vehicle including the working gas circulation engine 301 and the various sensors described above are connected to the input / output unit 50c. The input / output unit 50c is connected to these sensors and the like. To input and output signals. The storage unit 50b stores a computer program for controlling each unit of the working gas circulation engine 301. The storage unit 50b is a hard disk device, a magneto-optical disk device, a non-volatile memory such as a flash memory (a storage medium that can only be read such as a CD-ROM), or a RAM (Random Access Memory). A volatile memory or a combination thereof can be used. The processing unit 50a is configured by a memory (not shown) and a CPU (Central Processing Unit), and includes at least the above-described pumping amount control unit 351. Various controls by the electronic control unit 50 are performed by the processing unit 50a reading the computer program into a memory incorporated in the processing unit 50a based on the detection results of the sensors provided in the respective units, and depending on the calculation results. This is executed by sending a control signal. At that time, the processing unit 50a appropriately stores a numerical value in the middle of the calculation in the storage unit 50b, and extracts the stored numerical value to execute the calculation. In addition, when controlling each part of this working gas circulation engine 301, you may control by the dedicated hardware different from the electronic controller 50 instead of the said computer program.

And the pumping amount control part 351 adjusts the pumping quantity of the condensed water in the pumping part 80 by controlling the drive of the condensate pump 82. The pumping amount control unit 351 of the present embodiment controls the driving of the condensed water pump 82 based on the amount of condensed water generated separated by the condenser 60 to control the pumping amount of condensed water.

Here, the working gas circulation engine 301 of this embodiment includes a flow rate sensor 54 as a flow rate detection means. The flow rate sensor 54 detects the flow rate of the condensed water to the condensed water storage means. The flow rate sensor 54 of the present embodiment is provided in the condensed water discharge passage 64 that forms the condensed water passage 81. In the condensed water discharge passage 64, the condensed water discharge port 60 c and the condensed water discharge passage 64 are connected from the condenser 60. The flow rate of the condensed water discharged to the condensed water storage tank 70 is detected. The flow sensor 54 transmits a detection signal to the electronic control device 50. The pumping amount control unit 351 detects and acquires the generation amount of the condensed water separated by the condenser 60 based on the flow rate of the condensed water detected by the flow sensor 54.

And the pumping amount control part 351 controls the drive of the condensed water pump 82 based on the acquired amount of condensed water, and controls the pumping amount of condensed water. More specifically, the pumping amount control unit 351 controls the pumping amount so that the condensate pumping amount by the condensate pump 82 is substantially equal to the acquired condensed water generation amount. The pumping amount control unit 351 may use the flow rate of the condensed water detected by the flow sensor 54 as it is as a value corresponding to the amount of condensed water generated. That is, the pumping amount control unit 351 controls the pumping amount of the condensed water by the pumping unit 80 based on the flow rate of the condensed water detected by the flow sensor 54, and as a result, the pumping unit based on the amount of condensed water generated. The amount of condensed water pumped by 80 can be controlled.

As a result, in the working gas circulation engine 301, the pumping amount controller 351 controls the driving of the condensate pump 82 based on the amount of condensed water generated, and the amount of condensed water pumped is almost equal to the amount of condensed water generated. Therefore, the condensed water in the condensed water storage tank 70 is pumped toward the heat exchanger 90 and evaporated with a pumping amount corresponding to the amount of condensed water generated. Therefore, the amount of condensed water stored in the condensed water storage tank 70 can be reduced. Therefore, since the working gas circulation engine 301 can reduce the amount of condensed water stored in the condensed water storage tank 70, the condensed water is appropriately treated after the condensed water separated by the condenser 60 is processed. The capacity of the water storage tank 70 can be reduced, so that the mounting property of the working gas circulation engine 301 on the vehicle can be further improved.

Next, the control of the pumping amount of the working gas circulation engine 301 according to this embodiment will be described with reference to the flowchart of FIG. This control routine is repeatedly executed at a control cycle of several ms to several tens of ms.

First, the pumping amount control unit 351 of the electronic control device 50 detects and acquires the generation amount of the condensed water separated by the condenser 60 based on the flow rate of the condensed water detected by the flow sensor 54 (S100).

Next, the pumping amount control unit 351 compares the amount of condensed water generated acquired in S100 with the current amount of condensed water pumped by the condensed water pump 82, and the amount of condensed water generated is the current amount of condensed water. It is determined whether the amount is greater than the pumping amount (S101).

When it is determined that the amount of condensed water generated is greater than the current amount of condensed water pumped (S101: Yes), the pumping amount controller 351 controls the driving of the condensed water pump 82 to set the pumping amount of the condensed water in advance. The predetermined amount is increased (S102), the current control cycle is terminated, and the process proceeds to the next control cycle.

When it is determined that the amount of condensed water generated is less than or equal to the current amount of condensed water pumped (S101: No), the pumping amount control unit 351 controls the driving of the condensed water pump 82 to preset the pumping amount of condensed water. The predetermined amount is decreased (S103), the current control cycle is terminated, and the process proceeds to the next control cycle.

According to the working gas circulation engine 301 according to the embodiment of the present invention described above, the working gas circulation engine 301 causes the condensed water stored in the condensed water storage tank 70 to be higher than the atmospheric pressure by the pumping unit 80. The condensate stored in the condensate storage tank 70 is steamed because the condensed water pumped by the heat exchanger 90 is evaporated using the exhaust heat of the exhaust gas. As a result, for example, the mounting property of the working gas circulation engine 301 on the vehicle can be improved, and the condensed water separated by the condenser 60 can be appropriately treated.

Furthermore, the working gas circulation engine 301 according to the embodiment of the present invention described above includes the pumping amount control unit 351 that controls the pumping amount of the condensed water by the pumping unit 80 based on the generation amount of the condensed water. . Therefore, in the working gas circulation engine 301, the pumping amount control unit 351 controls the driving of the condensate pump 82 of the pumping unit 80 based on the amount of condensed water generated, and the condensate pumping of the condensed water by the condensate pump 82 of the pumping unit 80 is performed. Since the amount is controlled, the condensed water in the condensed water storage tank 70 can be pressure-fed and evaporated toward the heat exchanger 90 with a pumping amount corresponding to the amount of condensed water generated. The amount of condensate stored in can be reduced. As a result, the working gas circulation engine 301 can appropriately reduce the capacity of the condensed water storage tank 70 after properly treating the condensed water separated by the condenser 60. Can be further improved. Further, since the working gas circulation engine 301 controls the pumping amount by the pumping unit 80 based on the amount of condensed water generated, the amount of heat absorbed by the condensed water from the exhaust gas in the heat exchanger 90 is also the amount of condensed water generated. Therefore, the amount of condensed water generated in the condenser 60 itself can be optimized.

Furthermore, according to the working gas circulation engine 301 according to the embodiment of the present invention described above, the pumping amount control unit 351 includes the pumping unit such that the pumping amount by the pumping unit 80 is equal to the amount of condensed water generated. The pumping amount by 80 is controlled. Therefore, the working gas circulation engine 301 controls the pumping amount by the pumping unit 80 so that the pumping amount control unit 351 controls the pumping amount of the condensed water to be substantially equal to the amount of condensed water generated. The amount of condensed water stored in 70 can be minimized.

Furthermore, according to the working gas circulation engine 301 according to the embodiment of the present invention described above, the flow rate sensor 54 that detects the flow rate of the condensed water to the condensed water storage tank 70 is provided, and the pumping amount control unit 351 includes: The pumping amount by the pumping unit 80 is controlled based on the flow rate of the condensed water detected by the flow sensor 54. Therefore, the working gas circulation engine 301 detects the amount of condensed water or a value corresponding to the amount of condensed water based on the actual flow rate of condensed water to the condensed water storage tank 70 detected by the flow sensor 54. Therefore, the accurate amount of condensed water generated can be acquired, and the amount of pumping by the pumping unit 80 can be accurately determined based on this exact amount of condensed water generated or a value corresponding to the amount of condensed water generated. Can be controlled.

In the above description, the pumping amount control unit 351 has been described as adjusting the pumping amount of the condensed water in the pumping unit 80 by controlling the driving of the condensed water pump 82 of the pumping unit 80. When adjusting the amount of condensed water pumped in the pumping unit 280 (see FIG. 3) included in the working gas circulation engine 201 (see FIG. 3) of the second embodiment, the amount control unit 351 The oxygen and hydrogen combustion state, in other words, the supply amount of oxygen and hydrogen is controlled, and the pressure of the gas in the circulation passage 21 of the circulation path 20 is controlled, thereby controlling the pumping amount of the condensed water by the pumping unit 280. be able to. In addition, the pressure feed amount control unit 351 is configured to adjust the pressure feed amount of the condensed water in the pressure feed unit 280A (see FIG. 4) included in the working gas circulation engine 201A (see FIG. 4) of the second modification. By controlling the opening of 285A (see FIG. 4), controlling the flow of working gas between the high-pressure tank 284A and the third circulation passage 21c, and controlling the pressure of the gas in the circulation passage 21 of the circulation passage 20. The amount of condensed water pumped by the pumping unit 280A can be controlled.

(Embodiment 4)
FIG. 7 is a schematic schematic configuration diagram of a working gas circulation engine according to Embodiment 4 of the present invention, and FIG. 8 is a diagram illustrating a pressure feed amount map of the working gas circulation engine according to Embodiment 4 of the present invention. FIG. 9 is a flowchart for explaining the control of the pumping amount of the working gas circulation engine according to the fourth embodiment of the present invention. The working gas circulation engine according to the fourth embodiment has substantially the same configuration as the working gas circulation engine according to the third embodiment, but the working gas according to the third embodiment is provided with a water level detection means instead of the flow rate detection means. It is different from the circulation type engine. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

As shown in FIG. 7, the working gas circulation engine 401 according to the present embodiment is functionally conceptually provided with a pumping amount control unit 451 as a pumping amount control unit in an electronic control unit (ECU) 50.

And the pumping amount control part 451 controls the pumping amount of the condensed water in the pumping part 80 by controlling the drive of the condensed water pump 82. The pumping amount control unit 451 of this embodiment controls the driving of the condensed water pump 82 based on the amount of condensed water generated separated by the condenser 60 and controls the pumping amount of condensed water.

Here, the working gas circulation engine 401 of this embodiment includes a water level sensor 55 as water level detection means. The water level sensor 55 detects the water level of the condensed water stored in the condensed water storage tank 70. The water level sensor 55 is provided inside the condensed water storage tank 70 and detects the height from the bottom of the condensed water storage tank 70 to the water level of the condensed water, that is, the water level of the condensed water storage tank 70. The water level sensor 55 transmits a detection signal to the electronic control unit 50. The pumping amount control unit 451 detects and acquires the generation amount of condensed water separated by the condenser 60 based on the water level of the condensed water storage tank 70 detected by the water level sensor 55. That is, the pumping amount control unit 451 compares the water level of the condensed water storage tank 70 detected by the water level sensor 55 in the current control cycle with the water level of the condensed water storage tank 70 detected by the water level sensor 55 in the previous control cycle. Then, by calculating these differences, the amount of condensed water separated by the condenser 60 is calculated and acquired.

And the pumping amount control part 451 controls the drive of the condensed water pump 82 based on the acquired amount of condensed water, and controls the pumping amount of condensed water. The pumping amount control unit 451 is the same as the pumping amount control unit 351 (see FIG. 5) of the third embodiment described above, and the amount of condensed water generated by acquiring the condensate pumping amount by the condensed water pump 82 of the pumping unit 80. However, here, the amount of condensed water generated by the pumping amount control unit 451 and the condensed water detected by the water level sensor 55 in the current control cycle are controlled. Based on the level of the condensed water in the storage tank 70, the drive of the condensed water pump 82 of the pressure feeding unit 80 may be controlled to control the amount of condensed water pumped.

The pumping amount control unit 451 of the present embodiment obtains the pumping amount of the condensed water by the pumping unit 80 based on, for example, the pumping amount map m01 illustrated in FIG. In this pumping amount map m01, the horizontal axis indicates the water level of the condensed water storage tank 70, and the vertical axis indicates the amount of condensed water generated. The pumping amount map m01 describes the relationship between the water level of the condensed water storage tank 70, the amount of condensed water generated, and the amount of condensed water pumped by the pumping unit 80. In this pumping amount map m01, the amount of condensed water pumped by the pumping unit 80 increases as the water level of the condensed water storage tank 70 increases, and increases as the amount of condensed water generated increases. The pumping amount map m01 is stored in the storage unit 50b. Based on this pumping amount map m01, the pumping amount control unit 451 determines the condensed water generated by the pumping unit 80 from the acquired amount of condensed water and the level of condensed water in the condensed water storage tank 70 detected by the water level sensor 55. Find the pumping amount.

In addition, in this embodiment, although the pumping amount control part 451 calculated | required the pumping amount of the condensed water by the pumping part 80 using the pumping amount map m01, this embodiment is not limited to this. For example, the pumping amount control unit 451 may determine the pumping amount of the condensed water by the pumping unit 80 based on a mathematical expression corresponding to the pumping amount map m01. The same applies to various maps described below.

As a result, in the working gas circulation engine 401, the pumping amount control unit 451 controls the driving of the condensate pump 82 based on the acquired amount of condensed water, and controls the pumping amount by the condensate pump 82. Since the condensed water in the condensed water storage tank 70 can be pumped toward the heat exchanger 90 and evaporated with a pumping amount corresponding to the amount of condensed water generated, the condensation stored in the condensed water storage tank 70 The amount of water can be reduced. Therefore, since the working gas circulation engine 401 can reduce the amount of condensed water stored in the condensed water storage tank 70, the condensed water is properly treated after the condensed water separated by the condenser 60 is processed. The capacity of the water storage tank 70 can be reduced, so that the mounting property of the working gas circulation engine 401 on the vehicle can be further improved.

Further, the working gas circulation engine 401 detects the amount of condensed water generated and detected by the pumping amount control unit 451 based on the level of condensed water in the condensed water storage tank 70 detected by the water level sensor 55. The condensed water in the condensed water storage tank 70 can be pumped with a pumping amount corresponding to the amount of condensed water generated while maintaining the water level of the condensed water in the storage tank 70 at an appropriate water level. It is possible to prevent the condensed water from being depleted, and to prevent the condensed water pump 82 from sucking gas. For example, the working gas circulation engine 401 has a relatively high level of condensed water in the condensed water storage tank 70 detected by the water level sensor 55, assuming that the amount of condensed water generated is constant. Accordingly, the pumping amount control unit 451 relatively increases the pumping amount of the condensed water by the pumping unit 80, and the water level of the condensed water in the condensed water storage tank 70 detected by the water level sensor 55 has relatively decreased. In response to this, the pumping amount control unit 451 relatively decreases the pumping amount of the condensed water by the pumping unit 80, thereby reliably maintaining the water level of the condensed water in the condensate water storage tank 70 at an appropriate level. can do.

Note that the pumping amount control unit 451 may use the level of the condensed water in the condensed water storage tank 70 detected by the water level sensor 55 as a value corresponding to the amount of condensed water generated. That is, the pumping amount control unit 451 controls the amount of condensed water pumped by the pumping unit 80 based on the level of condensed water in the condensed water storage tank 70 detected by the water level sensor 55, resulting in generation of condensed water. Based on the amount, the pumping amount of the condensed water by the pumping unit 80 can be controlled.

Next, with reference to the flowchart of FIG. 9, the control of the pumping amount of the working gas circulation engine 401 according to this embodiment will be described. This control routine is repeatedly executed at a control cycle of several ms to several tens of ms.

First, the pumping amount control unit 451 of the electronic control device 50 acquires the water level of the condensed water in the condensed water storage tank 70 detected by the water level sensor 55 (S200).

Next, the pumping amount control unit 451 determines the water level of the condensed water storage tank 70 detected by the water level sensor 55 in the previous control cycle and the water level of the condensed water storage tank 70 detected by the water level sensor 55 in the current control cycle. By comparing and calculating these differences, the amount of condensed water separated by the condenser 60 is calculated and acquired (S201).

Next, the pumping amount control unit 451, for example, based on the pumping amount map m01, the current condensate water level in the condensate storage tank 70 detected by the water level sensor 55 in S200 and the amount of condensate generation acquired in S201. From this, the pumping amount of the condensed water by the pumping unit 80 is obtained (S202).

Then, the pumping amount control unit 451 controls the driving of the condensed water pump 82 of the pumping unit 80 based on the pumping amount of the condensed water by the pumping unit 80 calculated in S202, and changes the pumping amount by the condensed water pump 82. (S203), the current control cycle is terminated, and the process proceeds to the next control cycle.

According to the working gas circulation engine 401 according to the embodiment of the present invention described above, the working gas circulation engine 401 is configured to cause the condensed water stored in the condensed water storage tank 70 to be higher than the atmospheric pressure by the pumping unit 80. The condensate stored in the condensate storage tank 70 is steamed because the condensed water pumped by the heat exchanger 90 is evaporated using the exhaust heat of the exhaust gas. As a result, for example, the mounting property of the working gas circulation engine 401 on the vehicle can be improved, and the condensed water separated by the condenser 60 can be appropriately treated.

Further, according to the working gas circulation engine 401 according to the embodiment of the present invention described above, the working gas circulation engine 401 is configured so that the pumping amount control unit 451 is based on the acquired amount of condensed water. Since the condensate pump 82 is controlled to control the pumping amount of the condensate water by the condensate pump 82 of the pumping unit 80, the condensate of the condensate storage tank 70 can be condensed with a pumping amount corresponding to the amount of condensed water generated. Since water can be pumped toward the heat exchanger 90 and evaporated, the amount of condensed water stored in the condensed water storage tank 70 can be reduced. As a result, the working gas circulation engine 401 can appropriately reduce the capacity of the condensed water storage tank 70 after properly treating the condensed water separated by the condenser 60. Can be further improved.

Furthermore, according to the working gas circulation engine 401 according to the embodiment of the present invention described above, the pressure level control unit includes the water level sensor 55 that detects the water level of the condensed water stored in the condensed water storage tank 70. 451 controls the amount of condensed water pumped by the condensed water pump 82 of the pumping unit 80 based on the water level of the condensed water detected by the water level sensor 55. Therefore, the working gas circulation engine 401 detects and acquires the amount of condensed water or a value corresponding to the amount of condensed water based on the level of condensed water in the condensed water storage tank 70 detected by the water level sensor 55. Therefore, the condensed water in the condensed water storage tank 70 can be pumped with a pumping amount corresponding to the amount of condensed water generated while maintaining the water level of the condensed water in the condensed water storage tank 70 at an appropriate level.

(Embodiment 5)
FIG. 10 is a schematic schematic configuration diagram of a working gas circulation engine according to Embodiment 5 of the present invention, and FIG. 11 is a diagram illustrating a pressure feed amount map of the working gas circulation engine according to Embodiment 5 of the present invention. FIG. 12 is a view showing a response delay time map of the working gas circulation engine according to the fifth embodiment of the present invention, and FIG. 13 explains the pressure feed amount control of the working gas circulation engine according to the fifth embodiment of the present invention. FIG. 14 is a schematic schematic configuration diagram of a working gas circulation engine according to the third modification of the present invention. The working gas circulation engine according to the fifth embodiment has substantially the same configuration as the working gas circulation engine according to the third and fourth embodiments, but is implemented in that the pumping amount is controlled based on the supply amount of oxidant or fuel. This is different from the working gas circulation engine according to the third and fourth embodiments. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

As shown in FIG. 10, the working gas circulation engine 501 according to the present embodiment is functionally conceptually provided with a pumping amount control unit 551 as a pumping amount control unit in an electronic control unit (ECU) 50.

The pressure feed amount control unit 551 adjusts the pressure feed amount of the condensed water in the pressure feed unit 80 by controlling the driving of the condensed water pump 82. The pumping amount control unit 551 of the present embodiment controls the driving of the condensed water pump 82 based on the amount of condensed water generated separated by the condenser 60 to control the pumping amount of condensed water.

Here, the amount of condensed water separated by the condenser 60 is an amount corresponding to the amount of water vapor generated by the combustion of hydrogen and oxygen in the combustion chamber CC. Further, the amount of water vapor generated by the combustion of hydrogen and oxygen in the combustion chamber CC is the engine load, in other words, the amount of hydrogen combusted in the combustion chamber CC, in other words, hydrogen supplied to the combustion chamber CC or The amount corresponds to the amount of oxygen supplied. Normally, such a working gas circulation engine 501 can realize an engine load according to the driving force requested by the driver for the working gas circulation engine 501 as described above. A hydrogen supply amount is set, and an oxygen supply amount is set.

Therefore, the pumping amount control unit 551 of the present embodiment is configured to pump the condensed water by the pumping unit 80 based on the engine load, for example, the supply amount of oxygen as the oxidant or hydrogen as the fuel supplied to the combustion chamber CC. To control. Here, such a working gas circulation engine 501 may be operated, for example, by supplying a little excess of oxygen with respect to the supply amount of hydrogen and burning all the hydrogen supplied to the combustion chamber CC. Therefore, here, the pumping amount control unit 551 controls the pumping amount of the condensed water by the pumping unit 80 based on the supply amount of hydrogen supplied to the combustion chamber CC. Even in such a case, the pumping amount control unit 551 may control the pumping amount of condensed water by the pumping unit 80 based on the supply amount of oxygen supplied to the combustion chamber CC. The pumping amount of the condensed water by the pumping unit 80 may be controlled based on both the supply amount of oxygen and the supply amount of oxygen.

The pumping amount control unit 551 acquires the supply amount of hydrogen actually injected from the fuel injection means 42 into the combustion chamber CC, and controls the driving of the condensate pump 82 based on the supply amount of hydrogen to pump condensate water. Control the amount. The pumping amount control unit 551 is actually injected from the fuel injection unit 42 into the combustion chamber CC based on, for example, the opening period of the fuel injection unit (fuel injection valve) 42 or the flow rate of hydrogen detected by the fuel flow meter 45. What is necessary is just to acquire the supply amount of hydrogen. The pumping amount control unit 551 controls the pumping amount of condensed water by the pumping unit 80 based on the supply amount of hydrogen actually injected from the fuel injection means 42 into the combustion chamber CC as a value corresponding to the amount of condensed water generated. As a result, the pumping amount of the condensed water by the pumping unit 80 can be controlled based on the amount of the condensed water generated. The pumping amount control unit 551 estimates and obtains the amount of condensed water generated based on the amount of hydrogen actually injected from the fuel injection means 42 into the combustion chamber CC, and based on the amount of condensed water generated. You may make it control the pumping amount of the condensed water by the pumping part 80. FIG.

The pumping amount control unit 551 obtains the pumping amount of the condensed water by the pumping unit 80 based on, for example, the pumping amount map m02 shown in FIG. In this pumping amount map m02, the horizontal axis indicates the hydrogen supply amount, and the vertical axis indicates the condensate pumping amount. The pumping amount map m02 describes the relationship between the amount of hydrogen actually injected from the fuel injection means 42 into the combustion chamber CC and the pumping amount of condensed water by the pumping unit 80. In this pumping amount map m02, the pumping amount of the condensed water by the pumping unit 80 increases as the hydrogen supply amount increases. The pumping amount map m02 is stored in the storage unit 50b. The pumping amount control unit 551 obtains the pumping amount of condensed water by the pumping unit 80 from the supply amount of hydrogen actually injected into the combustion chamber CC based on the pumping amount map m02.

The relationship between the amount of hydrogen actually injected from the fuel injection means 42 into the combustion chamber CC and the amount of condensed water generated is that the amount of condensed water generated is relatively increased when the amount of hydrogen supplied is relatively increased. As the amount of hydrogen increases and the amount of hydrogen supplied decreases relatively, the amount of condensed water generated also decreases. For this reason, the pumping amount control unit 551 estimates and acquires the amount of condensed water generated based on the amount of hydrogen actually injected from the fuel injection means 42 into the combustion chamber CC, and based on the amount of condensed water generated. Even when the pumping amount of the condensed water by the pumping unit 80 is controlled, a map that is substantially the same as the pumping amount map m02 (a pumping amount map in which the horizontal axis indicates the amount of condensed water generated) may be used.

Here, in this working gas circulation engine 501, hydrogen supplied to the combustion chamber CC at a certain time burns in the combustion chamber CC, and water vapor generated by this combustion is separated by the condenser 60 and stored as condensed water. There is a certain time delay before the tank 70 is reached. That is, in the working gas circulation engine 501, the supply time when hydrogen is supplied to the combustion chamber CC, and the condensed water corresponding to the supply amount of hydrogen supplied at this supply time actually reaches the condensed water storage tank 70. A predetermined response delay time occurs between the time when the condensed water is reached. The response delay time at the time when the condensed water reaches the supply time varies depending on the flow velocity of the gas flowing through the circulation path 20. The flow rate of the gas flowing through the circulation path 20 varies according to the engine speed of the working gas circulation engine 501. That is, the flow rate of the gas flowing through the circulation path 20 increases as the engine speed increases, and decreases as the engine speed decreases. As a result, the response delay time of the condensed water arrival time with respect to the supply time becomes shorter as the engine speed increases and the flow velocity of the gas flowing through the circulation path 20 increases, and the engine speed decreases and the circulation path 20 decreases. As the flow rate of the gas flowing through decreases, it becomes longer.

Therefore, the pumping amount control unit 551 of the present embodiment further acquires the engine speed of the working gas circulation engine 501 and controls the driving of the condensate pump 82 based on the engine speed, thereby controlling the pumping amount of the condensed water. By controlling, the pumping amount of the condensed water is controlled based on the response delay time at the time when the condensed water reaches the condensed water.

The pumping amount control unit 551 calculates and acquires the engine speed, which is the speed of the crankshaft 19, based on the crank angle detected by the crank angle sensor 51 as described above. And the pumping amount control part 551 calculates | requires the response delay time of the condensed water arrival time of the condensed water with respect to a supply time, for example based on the response delay time map m03 shown in FIG. In this response delay time map m03, the horizontal axis indicates the engine speed, and the vertical axis indicates the response delay time. The response delay time map m03 describes the relationship between the engine speed acquired by the pumping amount control unit 551 and the response delay time when the condensed water reaches the condensate relative to the supply time. In this response delay time map m03, the response delay time decreases as the engine speed increases. The response delay time map m03 is stored in the storage unit 50b. The pumping amount control unit 551 obtains a response delay time from the engine speed based on the response delay time map m03.

Then, the pumping amount control unit 551 pumps the condensate so that it becomes the pumping amount of the condensed water based on the supply amount of hydrogen actually injected into the combustion chamber CC after the response delay time obtained based on the engine speed has elapsed. The drive of the condensed water pump 82 of the part 80 is controlled. As a result, the working gas circulation engine 501 of the present embodiment is configured so that the condensed water corresponding to the supply time when hydrogen is supplied to the combustion chamber CC and the supply amount of hydrogen supplied at this supply time is stored in the condensed water storage tank 70. The condensate pumping amount can be controlled based on the response delay time between the condensate arrival time and the condensate water arrival point at which the condensate water is supplied by the pumping unit 80 according to the actual hydrogen supply amount to the combustion chamber CC. The predictive control of the pumping amount can be executed accurately. That is, the working gas circulation engine 501 of the present embodiment is configured to reduce the amount of condensed water pumped by the pumping unit 80 with respect to the amount of condensed water generated according to the amount of hydrogen actually injected into the combustion chamber CC. Since the responsiveness can be followed accurately, the condensed water storage tank 70 can be downsized as a result.

Next, the control of the pumping amount of the working gas circulation engine 501 according to this embodiment will be described with reference to the flowchart of FIG. This control routine is repeatedly executed at a control cycle of several ms to several tens of ms.

First, the pumping amount control unit 551 of the electronic control unit 50 actually starts from the fuel injection unit 42 based on the valve opening period of the fuel injection unit (fuel injection valve) 42 or the flow rate of hydrogen detected by the fuel flow meter 45, for example. A supply amount of hydrogen injected into the combustion chamber CC is acquired (S300).

Next, for example, based on the pumping amount map m02, the pumping amount control unit 551 calculates the pumping amount of condensed water by the pumping unit 80 from the hydrogen supply amount acquired in S300 (S301).

Next, the pumping amount control unit 551 calculates and acquires the engine speed based on the crank angle detected by the crank angle sensor 51, and calculates the response delay time from the engine speed based on the response delay time map m03, for example. Calculate (S302).

Next, the pumping amount control unit 551 stores the pumping amount calculated in S301 in the storage unit 50b as the pumping amount after the response delay time calculated in S302 (S303).

Next, the pumping amount control unit 551 calls the current pumping amount from the storage unit 50b (S304).

Next, the pumping amount control unit 551 controls the driving of the condensed water pump 82 of the pumping unit 80 based on the current pumping amount called in S304, and changes the pumping amount by the condensed water pump 82 (S305). End the current control cycle and move to the next control cycle.

According to the working gas circulation engine 501 according to the embodiment of the present invention described above, the working gas circulation engine 501 has the condensed water stored in the condensed water storage tank 70 higher than the atmospheric pressure by the pumping unit 80. The condensate stored in the condensate storage tank 70 is steamed because the condensed water pumped by the heat exchanger 90 is evaporated using the exhaust heat of the exhaust gas. As a result, for example, the mounting property of the working gas circulation engine 501 on the vehicle can be improved, and the condensed water separated by the condenser 60 can be appropriately processed.

Furthermore, according to the working gas circulation engine 501 according to the embodiment of the present invention described above, the working gas circulation engine 501 is configured such that the pumping amount control unit 551 condenses the pumping unit 80 based on the amount of condensed water generated. Since the driving of the water pump 82 is controlled and the amount of condensed water pumped by the condensed water pump 82 of the pressure feeding unit 80 is controlled, the condensed water in the condensed water storage tank 70 is heated with the amount of pumping according to the amount of condensed water generated. Since it can be pumped toward the exchanger 90 and evaporated, the amount of condensed water stored in the condensed water storage tank 70 can be reduced. As a result, the working gas circulation engine 501 can reduce the capacity of the condensed water storage tank 70 after properly treating the condensed water separated by the condenser 60, and thus the working gas circulation engine 501. Can be further improved.

Furthermore, according to the working gas circulation engine 501 according to the embodiment of the present invention described above, the pumping amount control unit 551 is based on oxygen or hydrogen supplied to the combustion chamber CC, here, the supply amount of hydrogen. The pumping amount of the condensed water by the pumping unit 80 is controlled. Therefore, the working gas circulation engine 501 is a sensor that directly detects the amount of condensed water actually generated, such as the flow rate sensor 54 (see FIG. 5) and the water level sensor 55 (see FIG. 7) described above. Even if it is not provided, the condensate water by the pressure feed unit 80 is based on the supply amount of hydrogen actually injected from the fuel injection means 42 into the combustion chamber CC as a value corresponding to the amount of condensed water generated by the pressure feed amount control unit 551. By controlling the pumping amount, as a result, the pumping amount of the condensed water by the pumping unit 80 can be controlled based on the amount of condensed water generated. As a result, the working gas circulation engine 501 can suppress the number of parts constituting the working gas circulation engine 501 and can reduce the manufacturing cost of the working gas circulation engine 501.

Furthermore, according to the working gas circulation engine 501 according to the embodiment of the present invention described above, the pumping amount control unit 551 controls the pumping amount of the condensed water by the pumping unit 80 based on the engine load and the engine speed. To do. Therefore, the working gas circulation engine 501 has a response delay time corresponding to the engine speed by the pumping amount control unit 551 controlling the pumping amount of the condensed water by the pumping unit 80 based on the engine load and the engine speed. After the elapse of time, the driving of the condensate pump 82 of the pumping unit 80 can be controlled so that the engine load, for example, the condensate pumping amount based on the hydrogen supply amount, can be controlled. As a result, the amount of condensed water pumped by the pumping section 80 can be accurately followed with high response to the amount of condensed water generated according to the amount of hydrogen injected into the combustion chamber CC. Moreover, the condensed water storage tank 70 can be reduced in size.

In the above description, the pumping amount control unit 551 is actually connected to the fuel injection means 42 based on the valve opening period of the fuel injection means (fuel injection valve) 42 or the hydrogen flow rate detected by the fuel flow meter 45. Although it demonstrated as what acquires the supply amount of the hydrogen injected into the combustion chamber CC, it is not restricted to this.

FIG. 14 is a schematic configuration diagram of a working gas circulation engine according to the third modification of the present invention.

The working gas circulation engine 501A according to this modification includes a pressure sensor 56A as pressure detecting means, as shown in FIG. The pressure sensor 56 </ b> A is provided in the fuel storage tank 41 and detects the pressure in the fuel storage tank 41. The pressure sensor 56 </ b> A transmits a detection signal to the electronic control device 50.

Then, the pumping amount control unit 551 calculates and acquires the supply amount of hydrogen actually injected from the fuel injection means 42 into the combustion chamber CC based on the pressure in the fuel storage tank 41 detected by the pressure sensor 56A. It may be. That is, the pumping amount control unit 551 is actually injected from the fuel injection means 42 into the combustion chamber CC based on the fluctuation amount of the pressure in the fuel storage tank 41 detected by the pressure sensor 56A, that is, the reduction amount. The supply amount of hydrogen can be calculated. Even in this case, the working gas circulation engine 501A directly determines the amount of condensed water actually generated, such as the flow rate sensor 54 (see FIG. 5) and the water level sensor 55 (see FIG. 7) described above. Even if a sensor for detecting the pressure is not provided, the pressure feed control unit 551 determines the value corresponding to the amount of condensed water generated based on the supply amount of hydrogen actually injected from the fuel injection means 42 into the combustion chamber CC. As a result, the amount of condensed water pumped by the pumping unit 80 can be controlled based on the amount of condensed water generated.

(Embodiment 6)
FIG. 15 is a schematic configuration diagram of a working gas circulation engine according to Embodiment 6 of the present invention. The working gas circulation engine according to the sixth embodiment has substantially the same configuration as the working gas circulation engine according to the first embodiment, but is different from the working gas circulation engine according to the first embodiment in that it includes waste heat recovery means. Different. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

The working gas circulation engine 601 according to the present embodiment includes an expander 610 as waste heat recovery means, as shown in FIG.

The expander 610 collects the energy of water vapor generated by evaporating condensed water by the heat exchanger 90 as kinetic energy.

The expander 610 is provided in the atmosphere opening passage 83 that forms the condensed water passage 81. The expander 610 is provided between the heat exchanger 90 in the atmosphere opening passage 83 and the opening on the atmosphere side. As a result, the expander 610 is introduced with water vapor generated in the heat exchanger 90 through the atmosphere opening passage 83.

The expander 610 expands the water vapor to work, that is, rotates the output rotation member 611 by the expansion of the water vapor, thereby converting the energy of the water vapor into the rotational kinetic energy of the output rotation member 611. . That is, the expander 610 recovers the energy of water vapor generated in the heat exchanger 90, converts it into mechanical energy, and outputs the mechanical energy as the rotational output of the output rotating member 611. The output rotation member 611 is connected to, for example, a rotation shaft of a crankshaft 19 or a generator (not shown), and the rotation output of the output rotation member 611 is transmitted to the rotation shaft of the crankshaft 19 or a generator (not shown). Is done.

The working gas circulation engine 601 configured as described above collects the energy of water vapor generated by the expander 610 in the heat exchanger 90 as kinetic energy, and uses the recovered rotational output of the output rotating member 611 as the crankshaft 19 or the like. By transmitting to the rotating shaft of the generator (not shown), for example, the engine output by the engine body 10 for obtaining the output required for the working gas circulation engine 601 as a whole can be relatively reduced. The fuel consumption rate can be suppressed, and the cruising range can be extended. The working gas circulation engine 601 can relatively reduce the engine output by the engine body 10 to obtain the output required for the working gas circulation engine 601 as a whole. For example, the working gas circulation engine 601 Since the engine output by the engine body 10 for obtaining the output required for the entire 601 can be made relatively small, the amount of water vapor generated by the combustion of hydrogen and oxygen can be suppressed. The amount of condensed water generated can be suppressed. As a result, the working gas circulation engine 601 can relatively reduce the capacities of the condenser 60, the radiator 63, and the condensed water storage tank 70, thereby improving the mountability of the working gas circulation engine 601 on the vehicle. be able to.

According to the working gas circulation engine 601 according to the embodiment of the present invention described above, the working gas circulation engine 601 is configured so that the condensed water stored in the condensed water storage tank 70 is higher than the atmospheric pressure by the pumping unit 80. The condensate stored in the condensate storage tank 70 is steamed because the condensed water pumped by the heat exchanger 90 is evaporated using the exhaust heat of the exhaust gas. As a result, for example, the mounting property of the working gas circulation engine 601 on the vehicle can be improved, and the condensed water separated by the condenser 60 can be appropriately treated.

Furthermore, according to the working gas circulation engine 601 according to the embodiment of the present invention described above, the expander 610 that recovers the energy of water vapor generated by evaporating condensed water by the heat exchanger 90 as kinetic energy. Prepare. Therefore, the working gas circulation engine 601 collects the energy of water vapor generated by the expander 610 in the heat exchanger 90 as kinetic energy, and uses the collected rotational output of the output rotating member 611 as a crankshaft 19 or a generator (not shown). ) To the rotating shaft, for example, the engine output by the engine body 10 for obtaining the output required for the working gas circulation engine 601 as a whole can be made relatively small, so the fuel consumption rate is suppressed. The cruising distance can be increased, the amount of water vapor and condensed water generated can be suppressed, and the capacities of the condenser 60, radiator 63, and condensed water storage tank 70 can be made relatively small. Therefore, the mounting property of the working gas circulation engine 601 on the vehicle can be improved.

(Embodiment 7)
FIG. 16 is a schematic schematic configuration diagram of a working gas circulation engine according to Embodiment 7 of the present invention, and FIG. 17 illustrates condensate temperature control of the working gas circulation engine according to Embodiment 7 of the present invention. It is a flowchart. The working gas circulation engine according to the seventh embodiment has substantially the same configuration as the working gas circulation engine according to the sixth embodiment, but is different from the working gas circulation engine according to the sixth embodiment in that it includes a heat transfer means. . In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

The working gas circulation engine 701 according to the present embodiment includes a heat transfer unit 720 as heat transfer means, as shown in FIG.

The heat transfer unit 720 moves the heat of water vapor via the expander 610 to the condensed water stored in the condensed water storage tank 70 under a predetermined condition.

The heat transfer unit 720 according to the present embodiment includes a branch passage 721, a heat exchanger 722, a flow rate adjustment valve 723, a heat medium circulation path 724, a heat medium pump 725, and a circulation path heat dissipation section 726. Is done.

The branch passage 721 is a water vapor passage that branches off from the atmosphere opening passage 83 forming the condensed water passage 81. One end of the branch passage 721 is connected between the expander 610 of the atmosphere release passage 83 and the opening on the atmosphere side, and the other end opens to the atmosphere.

The heat exchanger 722 exchanges heat between water vapor flowing through the branch passage 721 and a heat exchange medium (hereinafter referred to as a heat medium) flowing through the heat medium circulation path 724. The heat exchanger 722 is provided in the branch passage 721. The heat exchanger 722 is connected so that the heat medium circulation path 724 passes through the inside.

The flow rate adjusting valve 723 adjusts the flow rate of water vapor flowing through the branch passage 721. The flow rate adjustment valve 723 is provided between one end of the branch passage 721 connected to the atmosphere opening passage 83 and the heat exchanger 722. The flow rate adjustment valve 723 is controlled by the electronic control unit 50 so that the opening thereof is controlled, so that the flow rate of water vapor introduced into the heat exchanger 722 through the branch passage 721 can be adjusted.

The heat medium circulation path 724 circulates the heat medium in the heat exchanger 722, and the heat medium can flow. The heat medium circulation path 724 is a closed annular path, and the inside is filled with the heat medium. The heat medium circulation path 724 is provided so as to pass through the inside of the heat exchanger 722.

The heat medium pump 725 is provided on the path of the heat medium circulation path 724, and the heat medium of the heat medium circulation path 724 is driven in the heat medium circulation path 724 in a predetermined circulation direction by driving the heat medium pump 725. Can be circulated in. The driving of the heat medium pump 725 is controlled by the electronic control device 50, and thus the circulation amount of the heat medium that is circulated through the heat medium circulation path 724 and introduced into the heat exchanger 722 can be adjusted.

The circulation path heat radiation part 726 is provided on the route of the heat medium circulation path 724. The circulation path heat radiating unit 726 is configured to come into contact with the condensed water stored in the condensed water storage tank 70. The circulation path heat radiation part 726 is formed so as to meander a part of the heat medium circulation path 724 in the condensed water storage tank 70. Thereby, the circulation path heat radiation part 726 can secure a sufficient contact area with the condensed water stored in the condensed water storage tank 70, that is, a heat radiation area, and can efficiently radiate heat to the condensed water. it can.

Therefore, in the heat transfer unit 720, the flow rate adjustment valve 723 adjusts the flow rate of water vapor flowing through the branch passage 721 so that the water vapor is introduced into the heat exchanger 722, and the heat medium pump 725 is driven to heat the heat medium circulation path 724. As the medium circulates between the heat exchanger 722 and the circulation path heat radiating unit 726, the heat of the steam via the expander 610 is transferred to the condensed water storage tank 70 via the heating medium circulating in the heating medium circulation path 724. It can be moved to the stored condensed water. That is, the heat transfer unit 720 exchanges heat with the water vapor via the expander 610 in the heat exchanger 722 by the heat medium circulating in the heat medium circulation path 724 and absorbs heat from the water vapor, so that the temperature of the heat medium Rises. The heat transfer unit 720 absorbs the heat of the water vapor and the heat medium whose temperature has risen circulates in the heat medium circulation path 724, and the condensed water and heat stored in the condensed water storage tank 70 in the circulation path heat radiation part 726. By exchanging heat and radiating heat to the condensed water, in other words, the condensed water absorbs the heat of the heat medium, so that the temperature of the condensed water rises. That is, the heat transfer unit 720 recovers the heat from the water vapor via the expander 610 and raises the temperature of the condensed water stored in the condensed water storage tank 70 by the recovered heat. Note that the water vapor exchanged with the heat medium circulating in the heat medium circulation path 724 by the heat exchanger 722 is released to the atmosphere from the opening at the other end of the branch path 721.

Here, the working gas circulation engine 701 of the present embodiment includes a temperature sensor 57 as temperature detecting means, and a functionally conceptual electronic control unit (ECU) 50 is provided with a heat transfer unit control unit 752. Yes.

The temperature sensor 57 is provided inside the condensed water storage tank 70 and detects the temperature of the condensed water stored in the condensed water storage tank 70. The temperature sensor 57 transmits a detection signal to the electronic control device 50.

The heat transfer unit controller 752 controls the drive of the heat transfer unit 720, and here controls the drive of the flow rate adjustment valve 723 and the heat medium pump 725 of the heat transfer unit 720. And the heat transfer part control part 752 of this embodiment condenses the heat | fever of the water vapor | steam via the expander 610 by driving the flow control valve 723 and the heat medium pump 725 of the heat transfer part 720 on predetermined conditions. The condensed water stored in the water storage tank 70 is moved.

Specifically, when the temperature of the condensed water stored in the condensed water storage tank 70 detected by the temperature sensor 57 is equal to or lower than a predetermined temperature set in advance, the heat transfer unit control unit 752 performs heat transfer unit 720. The flow rate adjustment valve 723 and the heat medium pump 725 are driven to move the heat of the water vapor via the expander 610 to the condensed water stored in the condensed water storage tank 70. As a result, the condensed water stored in the condensed water storage tank 70 is heated by heat recovered from the water vapor via the expander 610 by the heat transfer unit 720 when the temperature is lower than a predetermined temperature set in advance. The temperature rises and is preheated.

As a result, when the condensed water stored in the condensed water storage tank 70 is at a low temperature that is equal to or lower than a preset predetermined temperature, the working gas circulation engine 701 is not allowed to reach the heat exchanger 90 before the condensed water reaches the heat exchanger 90. By preheating, the preheated condensed water can be efficiently evaporated in the heat exchanger 90. Further, since the temperature of the water vapor introduced into the expander 610 relatively increases, the working gas circulation engine 701 can improve the efficiency of waste heat recovery in the expander 610, that is, the expansion The output of the machine 610 can be increased. Accordingly, the working gas circulation engine 701 can further reduce the engine output by the engine body 10 for obtaining the output required for the working gas circulation engine 701 as a whole, for example. Further, the cruising distance can be further increased and the generation amount of water vapor and the generation amount of condensed water can be further suppressed, and the capacities of the condenser 60, the radiator 63, and the condensed water storage tank 70 can be further increased. Since it can be made small, the mountability of the working gas circulation engine 701 on the vehicle can be further improved.

In the working gas circulation engine 701, the heat transfer unit controller 752 controls driving of the flow rate adjusting valve 723 and the heat medium pump 725 of the heat transfer unit 720, and the condensed water stored in the condensed water storage tank 70 is controlled. The heat transfer unit 720 adjusts the output of the expander 610 by adjusting the temperature and, in turn, the temperature of the water vapor introduced into the expander 610, and the working gas circulation engine 701 as a whole. It can also function as an adjusting device that adjusts the output of the.

Next, the condensate temperature control of the working gas circulation engine 701 according to this embodiment will be described with reference to the flowchart of FIG. This control routine is repeatedly executed at a control cycle of several ms to several tens of ms.

First, the heat transfer unit controller 752 of the electronic control unit 50 acquires the temperature of the condensed water stored in the condensed water storage tank 70 detected by the temperature sensor 57 (S400).

Next, the heat transfer unit control unit 752 determines whether or not the temperature of the condensed water acquired in S400 is higher than a predetermined temperature set in advance (S401).

When it is determined that the temperature of the condensed water acquired in S400 is higher than the predetermined temperature set in advance (S401: Yes), the heat transfer unit control unit 752 ends the current control cycle and proceeds to the next control cycle. To do.

When it is determined that the temperature of the condensed water acquired in S400 is equal to or lower than a predetermined temperature set in advance (S401: No), the heat transfer unit control unit 752 drives the heat medium pump 725 to control it to ON and adjust the flow rate. The valve 723 is driven and opened to a predetermined opening degree corresponding to the temperature of the condensed water (S402), the current control cycle is terminated, and the next control cycle is started.

According to the working gas circulation engine 701 according to the embodiment of the present invention described above, the working gas circulation engine 701 has the condensed water stored in the condensed water storage tank 70 higher than the atmospheric pressure by the pumping unit 80. The condensate stored in the condensate storage tank 70 is steamed because the condensed water pumped by the heat exchanger 90 is evaporated using the exhaust heat of the exhaust gas. As a result, for example, the mounting property of the working gas circulation engine 701 on the vehicle can be improved, and the condensed water separated by the condenser 60 can be appropriately treated.

Furthermore, according to the working gas circulation engine 701 according to the embodiment of the present invention described above, the working gas circulation engine 701 collects energy of water vapor generated by the expander 610 in the heat exchanger 90 as kinetic energy. Then, the rotation output of the collected output rotation member 611 is transmitted to the rotation shaft of the crankshaft 19 or a generator (not shown), for example, an engine for obtaining the output required for the entire working gas circulation engine 701 Since the engine output by the main body 10 can be made relatively small, the fuel consumption rate can be suppressed and the cruising distance can be increased, and the amount of water vapor and condensed water can be suppressed. 60, the capacity of the radiator 63, and the condensed water storage tank 70 can be relatively reduced. It is possible to improve the mountability to the vehicle.

Furthermore, according to the working gas circulation engine 701 according to the embodiment of the present invention described above, the temperature sensor 57 that detects the temperature of the condensed water stored in the condensed water storage tank 70, and the temperature sensor 57 detects the temperature. And a heat transfer unit 720 that moves the heat of water vapor via the expander 610 to the condensed water stored in the condensed water storage tank 70 when the temperature is equal to or lower than a predetermined temperature set in advance. Therefore, when the condensed water stored in the condensed water storage tank 70 is at a low temperature that is equal to or lower than a predetermined temperature set in advance, the working gas circulation engine 701 uses the condensed water stored in the condensed water storage tank 70. Since the temperature is increased and preheated by the heat recovered from the water vapor via the expander 610 by the heat transfer unit 720, the temperature of the water vapor introduced into the expander 610 is relatively increased to increase the output of the expander 610. Can be increased. As a result, the working gas circulation engine 701 can further suppress the fuel consumption rate and further extend the cruising distance, and can further suppress the generation amount of water vapor and the generation amount of condensed water. Since the capacity | capacitance of the radiator 63 and the condensed water storage tank 70 can be made further relatively small, the mounting property to the vehicle of the working gas circulation type engine 701 can further be improved. In addition, the working gas circulation engine 701 adjusts the heat amount of water vapor transferred to the condensed water stored in the condensed water storage tank 70 by the heat transfer unit 720, so that the output of the expander 610 and the working gas circulation engine are adjusted. The output of the entire 701 can be adjusted.

(Embodiment 8)
FIG. 18 is a schematic schematic configuration diagram of a working gas circulation engine according to an eighth embodiment of the present invention, and FIG. 19 illustrates condensate temperature and water level control of the working gas circulation engine according to the eighth embodiment of the present invention. It is a flowchart to explain. The working gas circulation engine according to the eighth embodiment has substantially the same configuration as the working gas circulation engine according to the seventh embodiment, but the structure of the heat transfer means is different from that of the working gas circulation engine according to the seventh embodiment. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

The working gas circulation engine 801 according to the present embodiment includes a heat transfer unit 820 as heat transfer means, as shown in FIG.

The heat transfer unit 820 moves the heat of water vapor via the expander 610 to the condensed water stored in the condensed water storage tank 870 under predetermined conditions. The heat transfer unit 820 of the present embodiment directly introduces the water vapor via the expander 610 into the condensed water storage tank 870, so that the heat of the water vapor together with the water vapor via the expander 610 is transferred to the condensed water storage tank 870. Move to stored condensate.

The heat transfer unit 820 of this embodiment includes a branch passage 821 and a flow rate adjustment valve 822.

The branch passage 821 is a water vapor passage that branches off from the open air passage 83 forming the condensed water passage 81. One end of the branch passage 821 is connected between the expander 610 of the atmosphere opening passage 83 and the opening on the atmosphere side, and the other end opens inside a condensed water storage tank 870 as condensed water storage means.

The flow rate adjustment valve 822 adjusts the flow rate of water vapor flowing through the branch passage 821. The flow rate adjustment valve 822 is controlled by the electronic control unit 50 so that the opening thereof is controlled, and thereby the flow rate of the water vapor introduced into the condensed water storage tank 870 through the branch passage 821 can be adjusted. it can.

Accordingly, the heat transfer unit 820 adjusts the flow rate of the water vapor flowing through the branch passage 821 by the flow rate adjustment valve 822 and introduces the water vapor into the condensed water storage tank 870 so that the water vapor via the expander 610 is stored in the condensed water. It is directly introduced into the tank 870, and the heat of the water vapor can be transferred to the condensed water stored in the condensed water storage tank 870 together with the water vapor itself. That is, the heat transfer unit 820 directly introduces the water vapor that has passed through the expander 610 through the branch passage 821 into the condensate water storage tank 870, so that the condensate water and water vapor stored in the condensate water storage tank 870 Heat exchange and the condensed water absorbs the heat of the water vapor, so that the temperature of the condensed water rises. That is, the heat transfer unit 820 directly introduces the water vapor via the expander 610 into the condensed water storage tank 870, so that the heat from the water vapor via the expander 610 is obtained by the condensed water in the condensed water storage tank 870. Waste heat is recovered, and the temperature of the condensed water is increased by the recovered heat. Further, the heat transfer unit 820 directly introduces the water vapor that has passed through the expander 610 via the branch passage 821 into the condensed water storage tank 870, and the condensed water and the water vapor stored in the condensed water storage tank 870 are heated. When the water vapor is exchanged and heat is absorbed by the condensed water, the temperature of the water vapor is lowered, and a part of the water vapor is liquefied and condensed. Thereby, the water level of the condensed water stored in the condensed water storage tank 870 rises as a part of the water vapor is liquefied and condensed.

In addition, the condensed water storage tank 870 of this embodiment has the discharge port 871 which discharge | releases the water vapor | steam introduced via the branch passage 821 to air | atmosphere. The water vapor introduced into the condensed water storage tank 870 through the branch passage 821 and not liquefied in the condensed water storage tank 870 is discharged to the atmosphere through the discharge port 871.

Here, the working gas circulation engine 801 of the present embodiment includes a water level sensor 55 as a water level detection unit and a temperature sensor 57 as a temperature detection unit, and is functionally conceptually an electronic control unit (ECU) 50. The heat transfer unit control unit 852 is provided.

The heat transfer unit controller 852 controls the drive of the heat transfer unit 820, and here controls the drive of the flow rate adjustment valve 822 of the heat transfer unit 820. Then, the heat transfer unit control unit 852 of this embodiment drives the flow rate adjustment valve 822 of the heat transfer unit 820 under a predetermined condition, so that the water vapor via the expander 610 is stored in the condensed water storage tank 870. Move to condensed water.

Specifically, the heat transfer unit control unit 852, when the temperature of the condensed water stored in the condensed water storage tank 870 detected by the temperature sensor 57 is equal to or lower than a predetermined temperature set in advance, The flow rate regulating valve 822 is driven, and the water vapor that has passed through the expander 610 is directly introduced into the condensed water storage tank 870 via the branch passage 821. As a result, when the condensed water stored in the condensed water storage tank 870 is at a low temperature equal to or lower than a predetermined temperature set in advance, the heat transfer unit 820 directly introduces water vapor via the expander 610. The temperature rises and is preheated by the heat of water vapor.

As a result, when the condensed water stored in the condensed water storage tank 870 is at a low temperature that is equal to or lower than a predetermined temperature set in advance, the working gas circulation engine 801 does not reach the heat exchanger 90 before the condensed water reaches the heat exchanger 90. By preheating, the preheated condensed water can be efficiently evaporated in the heat exchanger 90. Further, the working gas circulation engine 801 can improve the efficiency of waste heat recovery in the expander 610 since the temperature of the water vapor introduced into the expander 610 is relatively increased. The output of the machine 610 can be increased. Accordingly, the working gas circulation engine 801 can further reduce the engine output by the engine main body 10 for obtaining the output required for the working gas circulation engine 801 as a whole, for example, so that the fuel consumption rate can be reduced. Further, the cruising distance can be further increased and the generation amount of water vapor and the generation amount of condensed water can be further suppressed, and the capacities of the condenser 60, the radiator 63, and the condensed water storage tank 870 can be further relatively increased. Since it can be made small, the mountability of the working gas circulation engine 801 on the vehicle can be further improved.

Further, in the working gas circulation engine 801, the heat transfer unit control unit 852 controls the driving of the flow rate adjustment valve 822 of the heat transfer unit 820 to adjust the temperature of the condensed water stored in the condensed water storage tank 870, As a result, the heat transfer unit 820 adjusts the output of the expander 610 by adjusting the temperature of water vapor introduced into the expander 610, and further adjusts the output of the working gas circulation engine 801 as a whole. It can also function as an adjusting device.

Further, the heat transfer unit controller 852 of the present embodiment performs heat transfer when the water level of the condensed water stored in the condensed water storage tank 870 detected by the water level sensor 55 is equal to or lower than a predetermined water level set in advance. The flow control valve 822 of the unit 820 is driven, and the water vapor that has passed through the expander 610 is directly introduced into the condensed water storage tank 870 via the branch passage 821. Thereby, when the condensed water stored in the condensed water storage tank 870 is at a low water level not higher than a predetermined water level set in advance, water vapor is directly introduced by the heat transfer unit 820 via the expander 610. As a result, part of the water vapor liquefies and condenses and the water level rises.

As a result, when the condensed water stored in the condensed water storage tank 870 has a low water level that is equal to or lower than a predetermined water level set in advance, the working gas circulation engine 801 passes the expander 610 through the expander 610. Steam is directly introduced and a part of the steam is liquefied and condensed, and its water level rises. For example, it is possible to prevent depletion of condensed water in the condensed water storage tank 870, and the condensed water pump 82 sucks gas. This can be prevented.

Next, the condensate temperature / water level control of the working gas circulation engine 801 according to this embodiment will be described with reference to the flowchart of FIG. This control routine is repeatedly executed at a control cycle of several ms to several tens of ms.

First, the heat transfer unit controller 852 of the electronic control unit 50 is stored in the condensed water storage tank 870 detected by the temperature sensor 55 and the temperature of the condensed water stored in the condensed water storage tank 870 detected by the temperature sensor 57. The level of the condensed water is acquired (S500).

Next, the heat transfer unit control unit 852 determines whether or not the temperature of the condensed water acquired in S500 is higher than a predetermined temperature set in advance (S501).

When it is determined that the temperature of the condensed water acquired in S500 is higher than the predetermined temperature set in advance (S501: Yes), the heat transfer unit control unit 852 sets the predetermined water level of the condensed water acquired in S500. It is determined whether it is higher than the water level (S502).

When it is determined that the water level of the condensed water acquired in S500 is higher than the predetermined water level set in advance (S502: Yes), the heat transfer unit control unit 852 ends the current control cycle and proceeds to the next control cycle. To do.

When it is determined that the temperature of the condensed water acquired in S500 is equal to or lower than the predetermined temperature set in advance (S501: No), the heat transfer unit control unit 852 drives the flow rate adjustment valve 822 to respond to the temperature of the condensed water. The valve is opened to a predetermined opening degree (S503), the current control cycle is terminated, and the next control cycle is started.

When it is determined that the water level of the condensed water acquired in S500 is equal to or lower than the predetermined water level set in advance (S502: No), the heat transfer unit control unit 852 drives the flow control valve 822 to respond to the water level of the condensed water. The valve is opened to a predetermined opening degree (S503), the current control cycle is terminated, and the next control cycle is started.

According to the working gas circulation engine 801 according to the embodiment of the present invention described above, the working gas circulation engine 801 has the condensed water stored in the condensed water storage tank 870 higher than the atmospheric pressure by the pumping unit 80. The condensate stored in the condensate storage tank 870 is steamed because the condensed water pumped by the heat exchanger 90 is evaporated using the exhaust heat of the exhaust gas. As a result, for example, the mounting property of the working gas circulation engine 801 on the vehicle can be improved, and the condensed water separated by the condenser 60 can be appropriately treated.

Furthermore, according to the working gas circulation engine 801 according to the embodiment of the present invention described above, the working gas circulation engine 801 collects the energy of water vapor generated by the expander 610 in the heat exchanger 90 as kinetic energy. Then, by transmitting the rotation output of the collected output rotation member 611 to the rotation shaft of the crankshaft 19 or a generator (not shown), for example, an engine for obtaining an output required for the entire working gas circulation engine 801 Since the engine output by the main body 10 can be made relatively small, the fuel consumption rate can be suppressed and the cruising distance can be increased, and the amount of water vapor and condensed water can be suppressed. 60, the capacity of the radiator 63, and the condensed water storage tank 870 can be relatively reduced, so that the working gas circulation engine 8 It is possible to improve the mountability to the first vehicle.

Furthermore, according to the working gas circulation engine 801 according to the embodiment of the present invention described above, the temperature sensor 57 that detects the temperature of the condensed water stored in the condensed water storage tank 870, and the temperature sensor 57 detects the temperature. And a heat transfer unit 820 that moves the heat of the water vapor via the expander 610 to the condensed water stored in the condensed water storage tank 870 when the temperature is equal to or lower than a predetermined temperature set in advance. Therefore, when the condensed water stored in the condensed water storage tank 870 has a low temperature equal to or lower than a predetermined temperature set in advance, the working gas circulation engine 801 uses the condensed water stored in the condensed water storage tank 870 to Since the temperature rises and is preheated by the heat recovered from the water vapor via the expander 610 by the heat transfer unit 820, the temperature of the water vapor introduced into the expander 610 is relatively increased to increase the output of the expander 610. Can be increased. As a result, the working gas circulation engine 801 can further suppress the fuel consumption rate and further extend the cruising distance, and can further suppress the generation amount of water vapor and the generation amount of condensed water. Since the capacity | capacitance of the radiator 63 and the condensed water storage tank 870 can further be made relatively small, the mounting property to the vehicle of the working gas circulation type engine 801 can further be improved. In addition, the working gas circulation engine 801 adjusts the amount of water vapor transferred to the condensed water stored in the condensed water storage tank 870 by the heat transfer unit 820, so that the output of the expander 610 and the working gas circulation engine can be adjusted. The output of the whole 801 can be adjusted.

Furthermore, the working gas circulation engine 801 according to the embodiment of the present invention described above includes the water level sensor 55 that detects the water level of the condensed water stored in the condensed water storage tank 870, and includes the heat transfer unit 820. When the water level detected by the water level sensor 55 is equal to or lower than a predetermined water level set in advance, the water vapor through the expander 610 is introduced into the condensed water stored in the condensed water storage tank 870. Therefore, the working gas circulation engine 801 passes the expander 610 by the heat transfer unit 820 when the water level of the condensed water stored in the condensed water storage tank 870 is a low water level equal to or lower than a predetermined water level set in advance. By directly introducing the water vapor into the condensed water storage tank 870 and liquefying and condensing a part of the water vapor, the water level of the condensed water stored in the condensed water storage tank 870 can be raised. As a result, the working gas circulation engine 801 can prevent depletion of the condensed water in the condensed water storage tank 870, for example, by increasing the water level of the condensed water stored in the condensed water storage tank 870. It is possible to prevent the water pump 82 from sucking gas.

The working gas circulation engine according to the above-described embodiment of the present invention is not limited to the above-described embodiment, and various modifications can be made within the scope described in the claims. The working gas circulation engine according to the embodiment of the present invention may be configured by combining a plurality of the embodiments described above. For example, the working gas circulation engine according to the embodiment of the present invention includes the working gas circulation engine 501 according to the fifth embodiment (see FIG. 10) and the working gas circulation engine 801 according to the eighth embodiment (see FIG. 18). You may comprise by combining. That is, the working gas circulation engine 801A according to the fourth modification of the present invention shown in FIG. A pumping amount control unit 551 as a pumping amount control unit and a heat transfer unit control unit 852 may be provided.

In the above description, the working gas circulation engine has been described as providing the fuel injection means 42 so that the fuel is directly injected into the combustion chamber CC. However, the fuel injection means 42 injects the fuel into the intake port 11b. It may be attached to the cylinder head 11 as much as possible. That is, the working gas circulation engine of the present invention described above may be applied to a so-called port injection working gas circulation engine, and even in this case, the condensed water can be appropriately processed. .

In the above description, the working gas circulation engine has been exemplified as a fuel that diffuses and burns hydrogen (H ₂ ) as a fuel. However, a so-called spark ignition combustion is performed by igniting a fuel with a spark plug (not shown). Alternatively, the fuel may be ignited with a spark plug to assist ignition and diffuse combustion may be used. That is, the working gas circulation engine of the present invention described above may be applied to working gas circulation engines having different combustion forms, and even in this case, the condensed water can be appropriately processed.

As described above, the working gas circulation engine according to the present invention can appropriately process condensed water, and circulates the working gas contained in the exhaust gas from the exhaust side to the intake side of the combustion chamber. The present invention is suitable for various working gas circulation engines that can be supplied to the combustion chamber again.

Claims

An oxidant, a fuel that generates water vapor by combustion with the oxidant, and a working gas having a specific heat ratio higher than that of air are supplied, and the working gas can expand as the fuel burns, and the fuel A combustion chamber capable of exhausting the water vapor and the working gas as exhaust gas after combustion;
A circulation path through which the working gas contained in the exhaust gas can be circulated from the exhaust side to the intake side of the combustion chamber and supplied again to the combustion chamber;
Condensation means provided in the circulation path to condense the water vapor contained in the exhaust gas into condensed water;
Condensed water storage means capable of storing the condensed water;
A pumping means for pumping the condensed water stored in the condensed water storage means at a pressure higher than atmospheric pressure;
Evaporating means for evaporating the condensed water pumped by the pumping means by exhaust heat of the exhaust gas,
Working gas circulation engine.
The oxidant is oxygen and the fuel is hydrogen;
The working gas circulation engine according to claim 1.
The evaporating means evaporates the condensed water by exhaust heat of the exhaust gas upstream from the condensing means with respect to a circulation direction of the working gas circulating in the circulation path;
The working gas circulation engine according to claim 1.
The pressure feeding means includes a condensed water path connecting the condensed water storage means and the evaporation means so that the condensed water can flow, and pressurizes the condensed water of the condensed water path provided in the condensed water path to condense the condensed water. A pump for pumping from the water storage means side to the evaporation means side,
The working gas circulation engine according to claim 1.
The pumping means connects the condensed water storage means and the evaporating means so that the condensed water can flow, and the space for storing the condensed water is sealed via the condensed water storage means. A condensed water path communicating with the circulating path, pressurizing the condensed water in the condensed water path by the pressure of the gas in the circulating path higher than atmospheric pressure, and pumping the condensed water from the condensed water storage means side to the evaporation means side ,
The working gas circulation engine according to claim 1.
The pressure feeding means is provided by branching from the circulation path and storing the relatively high pressure working gas, and the working gas inflow and outflow between the working gas storage means and the circulation path. Adjusting means for adjusting
The working gas circulation engine according to claim 5.
Comprising a pumping amount control means for controlling the pumping amount of the condensed water by the pumping means based on the generation amount of the condensed water;
The working gas circulation engine according to claim 1.
The pumping amount control means controls the pumping amount so that the pumping amount becomes equal to the generated amount.
The working gas circulation engine according to claim 7.
Comprising flow rate detection means for detecting the flow rate of the condensed water to the condensed water storage means,
The pumping amount control unit controls the pumping amount based on the flow rate of the condensed water detected by the flow rate detection unit.
The working gas circulation engine according to claim 7.
Comprising water level detection means for detecting the level of the condensed water stored in the condensed water storage means,
The pumping amount control unit controls the pumping amount based on the water level of the condensed water detected by the water level detection unit.
The working gas circulation engine according to claim 7.
The pumping amount control means controls the pumping amount based on a supply amount of the oxidant or the fuel supplied to the combustion chamber.
The working gas circulation engine according to claim 7.
The pumping amount control means controls the pumping amount of the condensed water based on the engine load and the engine speed.
The working gas circulation engine according to claim 7.
A waste heat recovery means for recovering the energy of water vapor generated by evaporating the condensed water by the evaporation means as kinetic energy;
The working gas circulation engine according to claim 1.
Temperature detecting means for detecting the temperature of the condensed water stored in the condensed water storing means;
Heat that moves the heat of water vapor through the waste heat recovery means to the condensed water stored in the condensed water storage means when the temperature detected by the temperature detection means is equal to or lower than a predetermined temperature set in advance. A moving means,
The working gas circulation engine according to claim 13.
Comprising water level detection means for detecting the level of the condensed water stored in the condensed water storage means,
When the water level detected by the water level detection unit is equal to or lower than a predetermined water level set in advance, the heat transfer unit is configured to store the condensed water stored in the condensed water storage unit through the waste heat recovery unit. To introduce,
The working gas circulation engine according to claim 14.