WO2020194919A1

WO2020194919A1 - Engine device

Info

Publication number: WO2020194919A1
Application number: PCT/JP2019/049415
Authority: WO
Inventors: 卓央岩橋; 知史小関; 晶福田
Original assignee: 株式会社豊田自動織機
Priority date: 2019-03-27
Filing date: 2019-12-17
Publication date: 2020-10-01
Also published as: JP2020157976A

Abstract

Combustion of an engine is stably continued. When a first piston member and a second piston member rotate with combustion of fuel, a control device decreases a regenerative torque generated in a first rotating electric machine if a control amount related to rotation of the first piston member falls below a target value, increases the regenerative torque generated in the first rotating electric machine if the control amount related to the rotation of the first piston member exceeds the target value, decreases a regenerative torque generated in a second rotating electric machine if a control amount related to rotation of the second piston member falls below a target value, and increases the regenerative torque generated in the second rotating electric machine if the control amount related to the rotation of the second piston member exceeds the target value.

Description

Engine equipment

This disclosure relates to an engine device.

Japanese Patent Application Laid-Open No. 6-2559 (Patent Document 1) describes a rotating shaft, a first rotor and a second rotor rotating on the rotating shaft, and a power for transmitting the power of the first rotor and the second rotor to the rotating shaft. It is described that in a rotary engine provided with a transmission means, rotational loss is eliminated by outputting rotational power generated by the perfect circular rotational motion of the first rotor and the second rotor.

Japanese Unexamined Patent Publication No. 6-2559

In a rotary piston type engine in which a plurality of piston members can rotate independently, it is desirable to stably continue combustion of the engine under more efficient conditions, but the above document describes from such a viewpoint. There is no.

In the present disclosure, an engine device that enables stable continuation of engine combustion is provided.

According to the present disclosure, an engine device including a rotating piston type engine is provided. The engine includes a housing, a first piston member rotatably supported within the housing, and a second piston member rotatably supported within the housing. The housing, the first piston member and the second piston member form a combustion chamber for burning fuel. The engine device further includes a first rotary electric machine, a second rotary electric machine, and a control device. The first rotary electric machine is connected to the first piston member. The first rotary electric machine can generate regenerative power by rotating the first piston member. The second rotary electric machine is connected to the second piston member. The second rotary electric machine can generate regenerative power by rotating the second piston member. The control device controls the first rotary electric machine and the second rotary electric machine. The control device reduces the regenerative torque generated in the first rotary electric machine when the first piston member and the second piston member rotate due to the combustion of fuel and the control amount related to the rotation of the first piston member falls below the target value. When the control amount related to the rotation of the first piston member exceeds the target value, the regenerative torque generated in the first rotary electric machine is increased. The control device reduces the regenerative torque generated in the second rotary electric machine when the control amount related to the rotation of the second piston member is less than the target value when the first piston member and the second piston member are rotated by the combustion of fuel. When the control amount related to the rotation of the second piston member exceeds the target value, the regenerative torque generated in the second rotary electric machine is increased.

The control device feedback-controls the control amount related to the rotation of the first piston member and the second piston member while the engine is operating, and adjusts the control amount so as to approach the target value. As a result, the combustion of the engine can be stably continued under a large amount of regenerative power generation and efficient conditions.

According to the engine device according to the present disclosure, the combustion of the engine can be stably continued.

It is a figure which shows an example of the schematic structure of the engine device in this embodiment. It is a perspective view which shows a part of the structure of an engine device. It is a figure which shows an example of the structure of the piston member provided in the engine. It is a figure for demonstrating an example of the operation of each component member in the case of burning fuel in a combustion chamber A. It is a figure for demonstrating an example of the operation of each component member at the time of burning fuel in a combustion chamber D. It is a figure for demonstrating an example of the change of the process in each combustion chamber. It is a graph which shows an example of the target value of the control amount with respect to the rotation of a piston member. It is a graph which shows an example of the target value of the regenerative torque generated in a rotary electric machine. It is a flowchart which shows an example of the process executed by a control device. It is a graph which shows an example of the feedback control with respect to the target value of the control amount about the rotation of a piston member. It is a flowchart which shows an example of the process executed by the control device in 2nd Embodiment. It is a graph which shows the 1st example of the target value of the rotational speed of a piston member. It is a graph which shows the 2nd example of the target value of the rotational speed of a piston member.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the same parts are designated by the same reference numerals. Their names and functions are the same. Therefore, detailed explanations about them will not be repeated.

[First Embodiment]
<About the schematic configuration of engine device 1>
FIG. 1 is a diagram showing an example of a schematic configuration of an engine device 1 according to the present embodiment. FIG. 2 is a perspective view showing a part of the configuration of the engine device 1. As shown in FIGS. 1 and 2, the engine device 1 includes an engine 2, a first MG (Motor Generator) 61, a second MG (Motor Generator) 62, a first inverter 71, a second inverter 72, and a battery. 80 and load 90 are included. The engine device 1 also includes a first resolver 101, a second resolver 102, and a control device 200.

<About the configuration of engine 2>
In the present embodiment, the engine 2 is a rotating piston type internal combustion engine. As the fuel for the engine 2, for example, hydrogen, gasoline, gas (liquefied natural gas, liquefied petroleum gas, etc.) or light oil is used. The engine 2 includes a housing 4, an intake pipe 6, an exhaust pipe 8, a fuel supply device 10, a throttle valve 12, a throttle motor 14, a first output shaft 16, and a second output shaft 18.

One end of the intake pipe 6 is connected to the intake port (not shown) of the housing 4. For example, an air cleaner (not shown) is connected to the other end of the intake pipe 6. The air cleaner removes foreign matter from the air sucked from the outside of the engine 2. While the engine 2 is operating, the air sucked from the air cleaner flows through the intake pipe 6. The air flowing through the intake pipe 6 circulates in the intake port of the housing 4.

The throttle valve 12 is provided in the intake pipe 6 and limits the flow rate of air flowing through the intake pipe 6. The opening degree (throttle opening degree) of the throttle valve 12 is adjusted by the throttle motor 14 that operates in response to the control signal TH from the control device 200.

The fuel supply device 10 is provided on the upstream side of the throttle valve 12 of the intake pipe 6. The fuel supply device 10 supplies fuel into the intake pipe 6 in response to the control signal INJ from the control device 200. The fuel supplied into the intake pipe 6 is mixed with air in the intake pipe 6 and flows to the intake port of the housing 4.

The outer peripheral portion of the housing 4 is formed in a cylindrical shape, and the inner peripheral portion thereof is also formed in a cylindrical shape. The housing 4 houses a first piston member connected to the first output shaft 16 and a second piston member connected to the second output shaft 18 inside the housing 4.

One end of the exhaust pipe 8 is connected to the exhaust port (not shown) of the housing 4. An exhaust treatment device (not shown) is connected to the other end of the exhaust pipe 8, for example. During the operation of the engine 2, the exhaust generated by the combustion in the housing 4 flows from the exhaust port of the housing 4 to the exhaust pipe 8. The exhaust gas flowing through the exhaust pipe 8 is purified by the exhaust treatment device and discharged to the outside of the engine 2.

<About the internal structure of engine 2>
Hereinafter, an example of the internal structure of the engine 2 will be described with reference to FIG. FIG. 3 is a diagram showing an example of the configuration of a piston member provided inside the engine.

As shown in FIG. 3, the first piston member 24 and the second piston member 28 are housed in the housing 4 in combination. The first piston member 24 includes a first rotating body 24a and a first wall surface member 24b. The second piston member 28 includes a second rotating body 28a and a second wall surface member 28b.

The first rotating body 24a and the second rotating body 28a are rotatably supported by the housing 4 so that the centers of rotation coincide with each other, and one end surface of the first rotating body 24a and one of the second rotating body 28a. It is provided so as to face the end face.

The first rotating body 24a and the second rotating body 28a are formed so as to have a slope portion in the cross section including the center of rotation thereof. As a result, in a state where the first rotating body 24a and the second rotating body 28a are combined, a recess having a V-shaped cross section is formed in the circumferential direction between the first rotating body 24a and the second rotating body 28a. Is formed in.

The first rotating body 24a is provided with a first wall surface member 24b that extends from the center of rotation toward the inner peripheral surface of the housing 4 and whose end abuts on the inner peripheral surface of the housing 4. The first wall surface member 24b is composed of two triangular plate-shaped members. The two triangular plate-shaped members of the first wall surface member 24b are provided on the first rotating body 24a so as to have a positional relationship symmetrical with respect to the center of rotation.

The second rotating body 28a is provided with a second wall surface member 28b that extends from the center of rotation toward the inner peripheral surface of the housing 4 and whose end abuts on the inner peripheral surface of the housing 4. The second wall surface member 28b is composed of two triangular plate-shaped members having the same shape as the plate-shaped member constituting the first wall surface member 24b described above. The two triangular plate-shaped members of the second wall surface member 28b are provided on the second rotating body 28a so as to have a positional relationship symmetrical with respect to the center of rotation.

The triangular plate-shaped members of the first wall surface member 24b and the second wall surface member 28b are the first rotating body 24a and the first rotating body 24a in a state where the first piston member 24 and the second piston member 28 are housed in the housing 4. It is formed so as to match the cross-sectional shape of a triangle formed by the recess between the two rotating bodies 28a and the inner peripheral surface of the housing 4. Further, the outer peripheral portions of the triangular plate-shaped members of the first wall surface member 24b and the second wall surface member 28b are configured to be slidable with the inner peripheral surface of the housing 4.

Seals and the like are appropriately provided on the contact portion and the sliding portion between the members. The first output shaft 16 is connected to the first rotating body 24a so that the centers of rotation coincide with each other. The second output shaft 18 is connected to the second rotating body 28a so that the centers of rotation coincide with each other. Further, for example, one-

way clutches

22 and 26 are provided between each of the first rotating body 24a and the second rotating body 28a and the housing 4. The one-way clutch 22 allows rotation of the first rotating body 24a only in a predetermined rotation direction in the housing 4, and suppresses rotation in a direction opposite to the predetermined rotation direction. Similarly, the one-way clutch 26 allows rotation of the second rotating body 28a only in a predetermined rotation direction in the housing 4, and suppresses rotation in a direction opposite to the predetermined rotation direction.

<About configurations other than engine 2>
Returning to FIGS. 1 and 2, the configuration of the engine device 1 other than the engine 2 will be described below.

Both the first output shaft 16 and the second output shaft 18 rotate due to the combustion of fuel in the housing 4. The first output shaft 16 is connected to the rotation shaft of the first MG61. The second output shaft 18 is connected to the rotation shaft of the second MG 62.

The first MG61 and the second MG62 are, for example, both three-phase AC rotary electric machines. Both the first inverter 71 and the second inverter 72 are power conversion devices configured to enable power conversion between DC power and AC power.

The first MG 61 is electrically connected to the first inverter 71. The first inverter 71 is controlled by the control signal INV1 from the control device 200. That is, the electric power transmitted and received between the first MG 61 and the first inverter 71 is controlled by the control signal INV1 from the control device 200.

The control device 200 controls the first inverter 71 so that the regenerative torque is generated in the first MG 61, for example. At this time, the regenerative power generated in the first MG 61 is converted from AC power to DC power in the first inverter 71 and supplied to the battery 80. The battery 80 is charged by the DC power supplied from the first inverter 71. The first MG 61 is connected to the first piston member 24 via the first output shaft 16, and the first MG 61 is configured to be capable of regenerative power generation by the rotation of the first piston member 24.

Alternatively, the control device 200 controls the first inverter 71 so that the drive torque is generated in the first MG 61. At this time, the power of the battery 80 is converted from DC power to AC power in the first inverter 71 and supplied to the first MG 61. The first MG 61 is connected to the first piston member 24 via the first output shaft 16, and the first MG 61 is configured to be able to rotationally drive the first piston member 24.

The control device 200 controls the rotational operation of the first piston member 24 by transmitting the control signal INV1 to the first inverter 71.

The first resolver 101 detects the rotation angle (hereinafter, referred to as the rotation angle CA1) of the rotation axis (first output shaft 16) of the first MG61. The first resolver 101 transmits a signal indicating the detected rotation angle CA1 to the control device 200.

The second MG 62 is electrically connected to the second inverter 72. The second inverter 72 is controlled by the control signal INV2 from the control device 200. That is, the electric power exchanged between the second MG 62 and the second inverter 72 is controlled by the control signal INV2 from the control device 200.

The control device 200 controls the second inverter 72 so that the regenerative torque is generated in the second MG 62, for example. At this time, the regenerative power generated in the second MG 62 is converted from AC power to DC power in the second inverter 72 and supplied to the battery 80. The battery 80 is charged by the DC power supplied from the second inverter 72. The second MG 62 is connected to the second piston member 28 via the second output shaft 18, and the second MG 62 is configured to be capable of regenerative power generation by the rotation of the second piston member 28.

Alternatively, the control device 200 controls the second inverter 72 so that the drive torque is generated in the second MG 62. At this time, the power of the battery 80 is converted from DC power to AC power in the second inverter 72 and supplied to the second MG 62. The second MG 62 is connected to the second piston member 28 via the second output shaft 18, and the second MG 62 is configured to be able to rotationally drive the second piston member 28.

The control device 200 controls the rotational operation of the second piston member 28 by transmitting the control signal INV2 to the second inverter 72.

The second resolver 102 detects the rotation angle (hereinafter, referred to as the rotation angle CA2) of the rotation axis (second output shaft 18) of the second MG 62. The second resolver 102 transmits a signal indicating the detected rotation angle CA2 to the control device 200.

The battery 80 is a DC power source composed of a secondary battery such as a nickel hydrogen battery or a lithium ion battery, for example. The battery 80 may be a power storage device capable of storing DC power supplied from the first inverter 71 or the second inverter 72, and for example, a capacitor or the like may be used instead of the battery 80.

The operation of the engine device 1 is controlled by the control device 200. The control device 200 includes a CPU (Central Processing Unit) that performs various processes, a memory that includes a ROM (Read Only Memory) that stores programs and data, a RAM (Random Access Memory) that stores the processing results of the CPU, and the like. Includes input / output ports (neither shown) for exchanging information with the outside. The above-mentioned sensors (for example, the first resolver 101 and the second resolver 102) are connected to the input port. A device to be controlled (for example, engine 2, first inverter 71, second inverter 72, etc.) is connected to the output port.

The control device 200 controls various devices so that the engine device 1 is in a desired operating state based on signals from each sensor and device, as well as maps and programs stored in the memory. Note that various controls are not limited to software processing, but can also be processed by dedicated hardware (electronic circuits).

<Operation of combustion chambers A to D, first piston member 24, and second piston member 28>
In the engine device 1 having the above configuration, the operations of the combustion chamber and the piston member formed in the housing 4 will be described below. FIG. 4 is a diagram for explaining an example of the operation of each component member when fuel is burned in the combustion chamber A.

FIG. 4 shows a cross section orthogonal to the center of rotation in the central portion of the housing 4 (for example, the contact portion between the first rotating body 24a and the second rotating body 28a). As shown in FIG. 4, in the housing 4, four combustion chambers A to D for burning fuel by the inner peripheral surface of the housing 4, the first piston member 24, and the second piston member 28 are provided. It is formed. The first wall surface member 24b and the second wall surface member 28b form a wall surface in the circumferential direction of the combustion chambers A to D. The two combustion chambers adjacent to each other in the circumferential direction are separated by a first wall surface member 24b and a second wall surface member 28b.

In FIG. 4, the one-

way clutches

22 and 26 shown in FIG. 3 suppress the counterclockwise rotation of the first piston member 24 and the second piston member 28, and allow the clockwise rotation.

In the combustion chamber A shown in FIG. 4, the air-fuel mixture of the compressed air and the fuel becomes an expansion stroke in which the air-fuel mixture is ignited by self-ignition. That is, when the fuel burns in the combustion chamber A, the counterclockwise movement of the first piston member 24 is suppressed by the one-way clutch 22, so that the rotational position of the first piston member 24 is maintained and the second piston member 28 Only rotates in the direction of the dashed arrow, and the volume of the combustion chamber A increases with the expansion of the gas in the combustion chamber A.

In the combustion chamber B shown in FIG. 4, the expanded exhaust gas is discharged from the exhaust pipe 8. That is, when the second piston member 28 rotates in the direction of the broken arrow arrow due to the combustion of fuel in the combustion chamber A, the rotational position of the first piston member 24 is maintained, so that the volume of the combustion chamber B decreases. At this time, the combustion chamber B communicates with the exhaust pipe 8. Therefore, the exhaust gas in the combustion chamber B is discharged to the exhaust pipe 8 as the volume of the combustion chamber B decreases.

In the combustion chamber C shown in FIG. 4, the intake stroke is such that the air-fuel mixture is sucked from the intake pipe 6. That is, when the second piston member 28 rotates in the direction of the broken arrow arrow due to the combustion of fuel in the combustion chamber A, the rotational position of the first piston member 24 is maintained, so that the volume of the combustion chamber C increases. At this time, the combustion chamber C communicates with the intake pipe 6 while the second piston member 28 is rotating in the direction of the broken line arrow. Therefore, as the volume of the combustion chamber C increases, the air-fuel mixture is sucked into the combustion chamber C from the intake pipe 6.

In the combustion chamber D shown in FIG. 4, the air-fuel mixture sucked from the intake pipe 6 is compressed. That is, when the second piston member 28 rotates in the direction of the broken arrow arrow due to the combustion of fuel in the combustion chamber A, the rotational position of the first piston member 24 is maintained, so that the volume of the combustion chamber D decreases. At this time, since the combustion chamber D does not communicate with either the intake pipe 6 or the exhaust pipe 8, the air-fuel mixture in the combustion chamber D is compressed by the decrease in the volume of the combustion chamber D.

Then, when a clockwise force acts on the first piston member 24 due to the increase in the pressure in the combustion chamber D, the first piston member 24 rotates, and the positions of the first piston member 24 and the second piston member 28 are located. The relationship is the positional relationship shown in FIG.

FIG. 5 is a diagram for explaining an example of the operation of each component member when fuel is burned in the combustion chamber D. FIG. 5 shows a cross section orthogonal to the center of rotation in the central portion of the housing 4, as in FIG. The configuration of the engine 2 shown in FIG. 5 is different from the configuration of the engine 2 shown in FIG. 4 in the positional relationship between the first piston member 24 and the second piston member 28, and the positions and volumes of the combustion chambers A to D. The same is true except that

In the combustion chamber D shown in FIG. 5, the expansion stroke is performed after the compression stroke. That is, in the combustion chamber D, the air-fuel mixture of the compressed air and the fuel is ignited by self-ignition. When the fuel burns in the combustion chamber D, the counterclockwise movement of the second piston member 28 is suppressed by the one-way clutch 26, so that only the first piston member 24 can maintain the rotational position of the second piston member 28. It rotates clockwise and the volume of the combustion chamber D increases with the expansion of the gas in the combustion chamber D.

In the combustion chamber A shown in FIG. 5, the exhaust stroke is performed after the expansion stroke. That is, when the first piston member 24 rotates clockwise due to the combustion of fuel in the combustion chamber D, the rotational position of the second piston member 28 is maintained, so that the volume of the combustion chamber A decreases. At this time, the combustion chamber A communicates with the exhaust pipe 8. Therefore, the exhaust gas in the combustion chamber A is discharged to the exhaust pipe 8 as the volume of the combustion chamber A decreases.

In the combustion chamber B shown in FIG. 5, the intake stroke is performed after the exhaust stroke. That is, when the first piston member 24 rotates clockwise due to the combustion of fuel in the combustion chamber D, the rotational position of the second piston member 28 is maintained, so that the volume of the combustion chamber B increases. At this time, the combustion chamber B communicates with the intake pipe 6 while the first piston member 24 is rotating. Therefore, as the volume of the combustion chamber B increases, the air-fuel mixture is sucked into the combustion chamber B from the intake pipe 6.

In the combustion chamber C shown in FIG. 5, the compression stroke is performed after the intake stroke. That is, when the first piston member 24 rotates clockwise due to the combustion of fuel in the combustion chamber D, the rotational position of the second piston member 28 is maintained, so that the volume of the combustion chamber C decreases. At this time, since the combustion chamber C does not communicate with either the intake pipe 6 or the exhaust pipe 8, the air-fuel mixture in the combustion chamber C is compressed by the decrease in the volume of the combustion chamber C.

Then, when a clockwise force acts on the second piston member 28 due to the increase in the pressure in the combustion chamber C, the second piston member 28 rotates, and the positions of the first piston member 24 and the second piston member 28 are located. The relationship is the positional relationship shown in FIG.

In this way, each time combustion is performed in any of the combustion chambers A to D, the first piston member 24 and the second piston member 28 rotate alternately, so that the engine 2 operates. In this case, as shown in FIG. 4, when the fuel burns in the combustion chamber A or the combustion chamber C, the rotation of the second piston member 28 while the second piston member 28 rotates to a predetermined rotation position. Is generated by generating a regenerative torque for braking in the second MG 62. Similarly, as shown in FIG. 5, when the fuel burns in the combustion chamber B or the combustion chamber D, the rotation of the first piston member 24 is performed while the first piston member 24 rotates to a predetermined rotation position. Power is generated by generating a regenerative torque for braking in the first MG61.

That is, the first piston member 24 and the second piston member 28 rotate alternately to generate electricity in the first MG 61 and the second MG 62, and the generated AC power becomes DC power in the first inverter 71 and the second inverter 72. It is converted and supplied to the battery 80.

FIG. 6 is a diagram for explaining an example of a change in the process in each combustion chamber. As shown in FIG. 6, for example, in the stroke (1), the combustion chamber A becomes an expansion stroke, the combustion chamber B becomes an exhaust stroke, the combustion chamber C becomes an intake stroke, and the combustion chamber D becomes a compression stroke. The positional relationship between the first piston member 24 and the second piston member 28 is the positional relationship shown in FIG. Therefore, in the process (1), the second piston member 28 is rotated by the combustion in the combustion chamber A, and the regenerative torque is generated in the second MG 62.

In the process (2), the combustion chamber A becomes the exhaust stroke, the combustion chamber B becomes the intake stroke, the combustion chamber C becomes the compression stroke, and the combustion chamber D becomes the expansion stroke. The positional relationship between the first piston member 24 and the second piston member 28 is the positional relationship shown in FIG. Therefore, in the process (2), the first piston member 24 is rotated by the combustion in the combustion chamber D, and the regenerative torque is generated in the first MG 61.

In the process (3), the combustion chamber A becomes the intake stroke, the combustion chamber B becomes the compression stroke, the combustion chamber C becomes the expansion stroke, and the combustion chamber D becomes the exhaust stroke. The positional relationship between the first piston member 24 and the second piston member 28 is the positional relationship shown in FIG. Therefore, in the process (3), the second piston member 28 is rotated by the combustion in the combustion chamber C, and the regenerative torque is generated in the second MG 62.

In the process (4), the combustion chamber A becomes the compression process, the combustion chamber B becomes the expansion process, the combustion chamber C becomes the exhaust process, and the combustion chamber D becomes the intake process. The positional relationship between the first piston member 24 and the second piston member 28 is the positional relationship shown in FIG. Therefore, in the process (4), the first piston member 24 is rotated by the combustion in the combustion chamber B, and the regenerative torque is generated in the first MG 61.

After that, as long as the operation of the engine 2 continues, the operations of the steps (1) to (4) will be repeated.

<Control of engine device 1>
In the engine device 1 having such a configuration, in order to appropriately continue the operation of the engine 2 (that is, in the strokes (1) to (4), the expansion stroke, the exhaust stroke, the intake stroke and the compression stroke are appropriately performed. Therefore, it is required to control the rotation of the first piston member 24 and the second piston member 28 that rotate and slide in the housing 4 with high accuracy.

In the engine 2 having the above configuration, the control device 200 controls the first MG61 and the second MG62. The control device 200 executes rotation control of the first piston member 24 by increasing or decreasing the regenerative torque generated in the first MG 61, and executes rotation control of the second piston member 28 by increasing or decreasing the regenerative torque generated in the second MG 62.

More specifically, the control device 200 controls the rotation of the first piston member 24 when the first piston member 24 and the second piston member 28 rotate due to the combustion of fuel in the combustion chambers A to D. When the amount is less than the target value, the regenerative torque generated in the first MG61 is reduced, and when the control amount related to the rotation of the first piston member 24 exceeds the target value, the regenerative torque generated in the first MG61 is increased.

Further, in the control device 200, when the first piston member 24 and the second piston member 28 rotate due to the combustion of fuel in the combustion chambers A to D, the control amount regarding the rotation of the second piston member 28 sets a target value. When it falls below the target value, the regenerative torque generated in the second MG 62 is reduced, and when the control amount related to the rotation of the second piston member 28 exceeds the target value, the regenerative torque generated in the second MG 62 is increased.

In the present embodiment, the control amount related to the rotation of the first piston member 24 is determined based on the control map showing the relationship between the time and the phase of the first piston member 24, and the control amount related to the rotation of the second piston member 28. Is determined based on a control map showing the relationship between time and the phase of the second piston member 28. The target value of the control amount regarding the rotation of the first piston member 24 shall be determined so that the regenerative power generation amount by the first MG 61 is maximized. The target value of the control amount regarding the rotation of the second piston member 28 shall be determined so that the regenerative power generation amount by the second MG 62 is maximized.

The control device 200 feedback-controls the phases of the first piston member 24 and the second piston member 28 while the engine 2 is operating so that the phases of the first piston member 24 and the second piston member 28 approach the target value. Adjust to. By controlling the rotational positions of the first piston member 24 and the second piston member 28 with high accuracy and controlling the first piston member 24 and the second piston member 28 so as to follow the target line indicating the transition of the target value, the first piston member 24 and the second piston member 28 are controlled. It is possible to stably continue the combustion of the engine 2 under a large amount of regenerative power generation and efficient conditions. In addition, the collision between the first piston member 24 and the second piston member 28 can be reliably avoided, and the reliability of the engine 2 can be ensured.

Since it is not necessary to separately add a new mechanism, parts, etc. in order to perform such control, the configuration of the engine 2 can be simplified. Therefore, it is possible to suppress an increase in manufacturing cost and the number of parts and a decrease in durability.

Hereinafter, the details of the control process executed by the control device 200 in the present embodiment will be described with reference to FIGS. 7 to 10. FIG. 7 is a graph showing an example of a target value of a controlled amount related to rotation of the piston member.

The horizontal axis in FIG. 7 indicates the rotation cycle of the piston member. One scale on the horizontal axis indicates one cycle. The time when the coordinates on the horizontal axis take a value of zero indicates the moment of ignition of the air-fuel mixture in any one of the combustion chambers A to D. Ignition is performed every time the coordinates on the horizontal axis increase by 0.5. That is, the next ignition is performed at the time when the coordinates on the horizontal axis take a value of 0.5, and the next ignition is performed at the time when the coordinates on the horizontal axis take a value of 1.0.

The vertical axis of FIG. 7 indicates the angle of rotation of the piston member, that is, the phase. Since the engine 2 of the present embodiment has two piston members, a first piston member 24 and a second piston member 28, the rotation angle of the piston member in one cycle is 180 °. FIG. 7 shows the rotational operation of the piston member that partitions the combustion chamber that is the expansion stroke and the combustion chamber that is the exhaust stroke. The position where the coordinates of the vertical axis take a value of zero indicates the center of the combustion chamber in the rotation direction, which is the expansion stroke. Therefore, at the moment of ignition in the combustion chamber, that is, when the coordinates on the horizontal axis are zero, the angle shown on the vertical axis has a positive value.

FIG. 7 shows an ideal control map (target line) showing the relationship between time and the phase of the piston member. As shown in FIG. 7, the ideal rotational operation of the piston member is roughly as follows. As the piston member rotates due to the combustion of fuel in the combustion chamber, the phase increases substantially linearly with time between 0 and 0.5 cycles, and the piston member rotates to nearly 180 °. After that, the rotational position of the piston member is maintained by the action of the one-way clutch. When the cycle is close to one cycle, pressure is applied by the rotation of another piston member, so that the piston member rotates, and at this time, the phase of the piston member gradually increases with time.

FIG. 8 is a graph showing an example of a target value of regenerative torque generated in a rotary electric machine. The horizontal axis of FIG. 8 shows the rotation cycle of the piston member as in FIG. 7. The vertical axis of FIG. 8 shows the regenerative torque generated in the rotary electric machine connected to the target piston member.

As shown in FIG. 8, the regenerative torque increases and decreases along the parabolic graph in the range of the period 0 to 0.5. In cycle 0, the value of the regenerative torque is zero, the regenerative torque gradually increases to reach the maximum value in cycle 0.25, and then the regenerative torque gradually decreases and becomes zero again in cycle 0.5. In the range of the period 0.5 to 1, the value of the regenerative torque remains zero.

The piston member connected to the rotating electric machine that increases or decreases the regenerative torque in a parabolic shape in this way can perform the ideal rotational operation shown in FIG. 7.

As shown in FIG. 8, the regenerative torque generated in the rotary electric machine differs in magnitude according to the rotation speed of the piston member. Specifically, the higher the rotational speed of the piston member, the larger the regenerative torque generated in the rotary electric machine connected to the piston member. FIG. 8 shows three types of regenerative torque when the rotation speed of the piston member (that is, the rotation speed of the rotary electric machine) is 1000 rpm, 1500 rpm, and 2500 rpm. The control device 200 selects the optimum target value of the regenerative torque according to the rotation speed of the piston member (rotary electric machine), and generates the regenerative torque according to the rotation cycle. Can be controlled.

FIG. 9 is a flowchart showing an example of processing executed by the control device 200. The process shown in the flowchart of FIG. 9 is called and executed from the main routine (not shown) at predetermined control cycles. Hereinafter, the process of controlling the first MG 61 connected to the first piston member 24 will be described, but the same process is performed for the second MG 62 connected to the second piston member 28. The control device 200 continuously operates the engine 2 by alternately executing the process of controlling the first MG 61 and the process of controlling the second MG 62.

As shown in FIG. 9, first, in step S1, the rotation position of the first MG61 is acquired. The control device 200 uses the first resolver 101 (FIG. 1) to acquire a rotation angle CA1 (FIG. 1) indicating the rotation position of the first MG 61.

Next, in step S2, the rotation speed of the first MG61 is calculated. The control device 200 calculates the rotation speed of the first MG 61 by dividing the amount of change in the rotation angle CA1 of the first MG 61 in the immediately preceding predetermined period by the time elapsed in the period.

Next, in step S3, the target value of the regenerative torque of the first MG61 is set. The control device 200 sets an optimum target value of the regenerative torque based on the rotation speed of the first MG61 calculated in step S2 with reference to the map of the regenerative torque shown in FIG. As a result, the first piston member 24 connected to the first MG 61 is controlled with the ideal rotational motion shown in FIG. 7 as a target value.

Next, in step S4, the control device 200 determines whether or not the actual phase of the first piston member 24 detected by the rotation angle CA1 is equal to the target value of the phase with respect to the rotation cycle shown in FIG. .. When it is determined that the actual phase of the first piston member 24 is equal to the target value (YES in step S4), the process proceeds to step S5, and the regenerative torque generated in the first MG 61 is maintained as it is. Then, the process ends (end).

If it is determined in step S4 that the actual phase of the first piston member 24 is different from the target value (NO in step S4), the process proceeds to step S6, and the control device 200 controls the actual phase of the first piston member 24. Is larger than the target value.

If it is determined that the actual phase of the first piston member 24 is larger than the target value (YES in step S6), the first piston member 24 is excessively rotated with respect to the ideal position. The process of suppressing the rotation of the first piston member 24 to bring it closer to the ideal position is performed. Specifically, in step S7, the control device 200 increases the regenerative torque generated in the first MG 61. As a result, the load on the rotation of the first piston member 24 increases, so that the rotation of the first piston member 24 is suppressed. Therefore, the phase of the first piston member 24 can be brought close to the ideal position. Then, the process ends (end).

In the determination in step S6, when it is determined that the actual phase of the first piston member 24 is not larger than the target value, that is, the actual phase of the first piston member 24 is smaller than the target value (NO in step S6). , The first piston member 24 is insufficiently rotated with respect to the ideal position. In this case, the process of promoting the rotation of the first piston member 24 to bring it closer to the ideal position is performed.

Specifically, first, in step S8, the control device 200 determines whether or not the regenerative torque generated in the first MG 61 is zero. If it is determined that the regenerative torque is not zero (NO in step S8), in step S9, the control device 200 reduces the regenerative torque generated in the first MG 61. As a result, the load on the rotation of the first piston member 24 is reduced, so that the rotation of the first piston member 24 is promoted. Therefore, the phase of the first piston member 24 can be brought close to the ideal position.

Subsequently, in step S10, the control device 200 determines whether or not the regenerative torque generated in the first MG 61 is zero. When it is determined that the regenerative torque is not zero (NO in step S10), the process ends as it is (end).

When it is determined in the determination in step S8 and the determination in step S10 that the regenerative torque generated in the first MG 61 is zero (YES in step S8, YES in step S10), the regenerative torque is already set to zero. Therefore, it is not possible to perform a process of reducing the regenerative torque and promoting the rotation of the first piston member 24. For example, when the engine 2 misfires, the expansion of the gas in the combustion chamber does not exert a force to rotate the piston member, so that even if the regenerative torque is reduced to zero, the first piston member 24 is in the ideal position. On the other hand, the rotation tends to be insufficient.

Therefore, in such a case, the first MG61 is used as an electric motor instead of a generator, and the first piston member 24 is driven by the first MG61 to bring the phase of the first piston member 24 closer to the ideal position. Is done. Specifically, in step S11, the control device 200 increases the rotational driving force generated by the first MG 61. By transmitting a larger rotational driving force to the first piston member 24, the rotation of the first piston member 24 is promoted. Therefore, the phase of the first piston member 24 can be brought close to the ideal position. Then, the process ends (end).

FIG. 10 is a graph showing an example of feedback control of the control amount related to the rotation of the piston member with respect to the target value. As described with reference to the flowchart of FIG. 9, if the phase of the first piston member 24 is larger than the target value, the rotation of the first piston member 24 is suppressed, and the phase of the first piston member 24 is smaller than the target value. For example, feedback control that promotes the rotation of the first piston member 24 is executed. As a result, as shown in the graph of FIG. 10, the phase of the first piston member 24 can be converged to the target value, and the first piston member 24 can be controlled so as to follow the target line.

As described above, in the engine device 1 of the present embodiment, the control device 200 reduces the regenerative torque generated in the rotary electric machine when the phase of the piston member with respect to time falls below the target value, and the phase of the piston member with respect to time. When exceeds the target value, the regenerative torque generated in the rotary electric machine is increased. By executing the feedback control with respect to the target value of the phase of the piston member in this way, the phase of the piston member can be converged to the target value. Therefore, the operation of the engine 2 can be stably continued under the conditions closer to the ideal rotational operation in which the amount of regenerative power generation is maximized.

By setting the target value of the phase of the first piston member 24 and the second piston member 28 with respect to time and performing control so that the piston member exists at that position at each moment, the first piston member 24 and the second piston member 24 and the second piston member 28 are controlled. Since unnecessary braking and reacceleration of the piston member 28 are not required, vibration of the engine device 1 can be reduced. Further, the collision between the first piston member 24 and the second piston member 28 can be reliably avoided. Therefore, the reliability of the engine device 1 can be ensured.

Even if the engine 2 misfires, the piston member is controlled to exist at the ideal position at each moment by driving the rotary electric machine. The operation in a state where ignition is possible in the combustion chamber is continued, and even if a misfire occurs, combustion can be restored at the next ignition timing, so that the combustion of the engine 2 can be stably continued.

[Second Embodiment]
FIG. 11 is a flowchart showing an example of the processing executed by the control device 200 in the second embodiment. In the second embodiment, the control amount related to the rotation of the first piston member 24 is the rotation speed of the first piston member 24, and the control amount related to the rotation of the second piston member 28 is the rotation speed of the second piston member 28. It is assumed that. More specifically, the control amount for the rotation of the first piston member 24 is the rotation speed of the first piston member 24 with respect to time or the rotation speed of the first piston member 24 with respect to the phase. The control amount related to the rotation of the second piston member 28 is the rotation speed of the second piston member 28 with respect to time or the rotation speed of the second piston member 28 with respect to the phase.

Hereinafter, details of the control process executed by the control device 200 in the second embodiment will be described with reference to FIGS. 11 to 13. In the following description, the process of controlling the first MG 61 connected to the first piston member 24 will be described, but the same process will be performed on the second MG 62 connected to the second piston member 28.

As shown in FIG. 11, first, in step S101, the rotation position of the first MG61 is acquired. Next, in step S102, the rotation speed of the first MG61 is calculated. Since the processing in steps S101 and S102 is the same as in steps S1 and S2 shown in FIG. 9, the description thereof will be omitted. Next, in step S103, a target value of the rotational speed of the first piston member 24 is set.

FIG. 12 is a graph showing the first example of the target value of the rotational speed of the piston member. The horizontal axis of FIG. 12 shows the rotation cycle of the piston member as in FIG. 7. The vertical axis of FIG. 12 shows the rotation speed of the piston member.

As shown in FIG. 12, the rotational speed of the piston member increases or decreases along the parabolic graph in the range of the period 0 to 0.5. In cycle 0, the value of the rotational speed is zero, the rotational speed gradually increases to reach the maximum value in period 0.25, and then the rotational speed gradually decreases and becomes zero again in period 0.5. In the range of period 0.5 to 1, the value of rotational speed remains zero. The piston member that increases or decreases the rotation speed in a parabolic manner in this way can perform the ideal rotation operation shown in FIG. 7.

FIG. 12 shows three rotation speeds when the rotation speed of the piston member (that is, the rotation speed of the rotary electric machine) is 1000 rpm, 1500 rpm, and 2500 rpm. The control device 200 selects a target value of the optimum rotation speed according to the rotation speed of the piston member (rotary electric machine), and rotates the piston member so as to have the selected rotation speed according to the rotation cycle. The regenerative torque generated by the electric machine can be controlled.

FIG. 13 is a graph showing a second example of the target value of the rotational speed of the piston member. The horizontal axis of FIG. 13 indicates the angle of rotation of the piston member, that is, the phase. The vertical axis of FIG. 13 shows the rotation speed of the piston member.

As shown in FIG. 13, the rotational speed of the piston member increases or decreases along a parabolic graph in the phase range of 0 ° to 180 °. At phase 0 °, the value of rotational speed is zero, the rotational speed gradually increases to reach the maximum value at phase 90 °, then the rotational speed gradually decreases and becomes zero again at phase 180 °. The piston member that increases or decreases the rotation speed in a parabolic manner in this way can perform the ideal rotation operation shown in FIG. 7.

FIG. 13 shows three rotation speeds when the rotation speed of the piston member (that is, the rotation speed of the rotary electric machine) is 1000 rpm, 1500 rpm, and 2500 rpm. The control device 200 selects a target value of the optimum rotation speed according to the rotation speed of the piston member (rotary electric machine), and rotates the piston member so as to have the selected rotation speed according to the rotation cycle. The regenerative torque generated by the electric machine can be controlled.

Returning to FIG. 11, next, in step S103, the target value of the rotation speed of the first piston member 24 is set. The control device 200 refers to the map of the rotation speed with respect to the rotation cycle (time) of the first piston member 24 shown in FIG. 12, and has an optimum rotation speed based on the rotation speed of the first MG 61 calculated in step S102. Set the target value. Alternatively, the control device 200 sets a target value of the optimum rotation speed with reference to the map of the rotation speed with respect to the rotation phase of the first piston member 24 shown in FIG.

In the determination in step S104, the control device 200 determines whether or not the actual rotational speed of the first piston member 24 is equal to the target value of the rotational speed shown in FIG. 12 or 13. In the determination in step S106, the control device 200 determines whether or not the actual rotational speed of the first piston member 24 is larger than the target value of the rotational speed shown in FIG. 12 or 13. In this way, if the rotation speed of the first piston member 24 is larger than the target value, the rotation of the first piston member 24 is suppressed, and if the rotation speed of the first piston member 24 is smaller than the target value, the first piston member Execute feedback control that promotes the rotation of 24. Since the processing of each subsequent step is the same as that of the first embodiment described with reference to FIG. 9, the description thereof will be omitted.

As described above, in the engine device 1 of the second embodiment, the control device 200 reduces the regenerative torque generated in the rotary electric machine when the rotation speed of the piston member is lower than the target value, and the rotation speed of the piston member becomes the target value. When it exceeds, the regenerative torque generated in the rotary electric machine is increased. In this way, by executing the feedback control with respect to the target value of the rotation speed of the piston member, the rotation speed of the piston member can be converged to the target value. Therefore, the operation of the engine 2 can be stably continued under the conditions closer to the ideal rotational operation in which the amount of regenerative power generation is maximized.

Although the embodiments have been described as described above, it should be considered that the embodiments disclosed this time are examples in all respects and are not restrictive. The scope of the present invention is shown by the claims rather than the above description, and it is intended to include all modifications within the meaning and scope of the claims.

1 engine device, 2 engine, 4 housing, 6 intake pipe, 8 exhaust pipe, 10 fuel supply device, 12 throttle valve, 14 throttle motor, 16 1st output shaft, 18 2nd output shaft, 22, 26 one-way clutch, 24 1st piston member, 24a 1st rotating body, 24b 1st wall surface member, 28 2nd piston member, 28a 2nd rotating body, 28b 2nd wall surface member, 61 1st MG, 62 2nd MG, 71 1st inverter, 72nd 2 inverter, 80 battery, 90 load, 101 1st resolver, 102 2nd resolver, 200 control device, A, B, C, D combustion chamber, CA1, CA2 rotation angle, INJ, INV1, INV2, TH control signal.

Claims

The housing, the first piston member rotatably supported in the housing, and the second piston member rotatably supported in the housing include the housing, the first piston member, and the second. The piston member is a rotating piston type engine that forms a combustion chamber for burning fuel,
A first rotating electric machine connected to the first piston member and capable of regenerative power generation by rotation of the first piston member.
A second rotating electric machine connected to the second piston member and capable of regenerative power generation by rotation of the second piston member.
A control device for controlling the first rotary electric machine and the second rotary electric machine is provided.
The control device is used when the first piston member and the second piston member are rotated by the combustion of the fuel.
When the control amount related to the rotation of the first piston member is less than the target value, the regenerative torque generated in the first rotary electric machine is reduced, and when the control amount related to the rotation of the first piston member exceeds the target value, the first Increase the regenerative torque generated in the one-turn electric machine,
When the control amount related to the rotation of the second piston member is less than the target value, the regenerative torque generated in the second rotary electric machine is reduced, and when the control amount related to the rotation of the second piston member exceeds the target value, the first Increases the regenerative torque generated in a two-turn electric machine,
Engine device.
The engine device according to claim 1, wherein the first piston member and the second piston member are controlled so as to follow a target line indicating a transition of the target value.
The control amount related to the rotation of the first piston member is determined based on a control map showing the relationship between time and the phase of the first piston member.
The engine device according to claim 1 or 2, wherein the control amount related to the rotation of the second piston member is determined based on a control map showing the relationship between time and the phase of the second piston member.
The target value of the control amount regarding the rotation of the first piston member is set so that the regenerative power generation amount by the first rotary electric machine is maximized.
The engine device according to any one of claims 1 to 3, wherein the target value of the control amount regarding the rotation of the second piston member is determined so that the regenerative power generation amount by the second rotary electric machine is maximized.
The first rotary electric machine is configured to be able to rotationally drive the first piston member.
The second rotary electric machine is configured to be able to rotationally drive the second piston member.
When the control amount related to the rotation of the first piston member falls below the target value and the target value cannot be reached even if the regenerative torque generated in the first rotary electric machine is reduced to zero, the first rotary electric machine causes the first. 1 Drive the piston member,
When the control amount related to the rotation of the second piston member falls below the target value and the target value cannot be reached even if the regenerative torque generated in the second rotary electric machine is reduced to zero, the second rotary electric machine causes the first. 2. The engine device according to any one of claims 1 to 4, which drives a piston member.
The engine device according to claim 5, wherein when the engine misfires, the first rotating electric machine drives the first piston member, and the second rotating electric machine drives the second piston member.