WO2016175194A1

WO2016175194A1 - Supercharger surplus power recovery device for internal combustion engine

Info

Publication number: WO2016175194A1
Application number: PCT/JP2016/063013
Authority: WO
Inventors: 信之坂入; 和徳大田; 貴士谷口; 服部　泰典
Original assignee: 三井造船株式会社
Priority date: 2015-04-30
Filing date: 2016-04-26
Publication date: 2016-11-03
Also published as: CN107532502A; CN107532502B; JP6012810B1; JP2016211386A; KR101859893B1; KR20170124622A

Abstract

[Problem] To dramatically improve power transmission efficiency and avoid having to install redundant hydraulic devices. [Solution] The present invention is equipped with: an internal combustion engine (1) for which operation devices (51) for operating the engine are electronically controlled by means of hydraulic pressure; a supercharger (5); a first hydraulic pump (10) that is rotationally driven by the supercharger, thereby generating hydraulic pressure; a hydraulic mechanism (20); a second hydraulic pump (11) that is rotationally driven by the power source (1) and supplies hydraulic pressure to the operation devices; a controller (50) for controlling the operation of the first hydraulic pump, the second hydraulic pump, and the hydraulic mechanism; first oil passages (21, 22, 23) for supplying hydraulic pressure from the second hydraulic pump to the operation devices; and second oil passages (26, 27, 22, 23) for supplying hydraulic pressure from the first hydraulic pump to the operation devices. In addition, the present invention is equipped with third oil passages (26, 27, 22, 21) for supplying hydraulic pressure from the first hydraulic pump to the second hydraulic pump, and fourth oil passages (21, 22, 27, 26) for supplying hydraulic pressure from the second hydraulic pump to the first hydraulic pump.

Description

Supercharger surplus power recovery device for internal combustion engine

The present invention relates to a supercharger surplus power recovery device for an internal combustion engine equipped with a supercharger.

Conventionally, in an internal combustion engine such as a diesel engine or a gas engine, a turbocharger is used to rotationally drive the turbine by the exhaust gas of the engine, and the supply air density is increased by a compressor rotated by the turbine. The output is improved.

However, even if the turbocharger is attached in this way to effectively use the exhaust energy, the exhaust energy becomes surplus when the engine is under a high load (at the time of high output), and this surplus exhaust energy is used without waste. However, there is a strong demand not only for improving fuel efficiency but also for environmental protection.

As an example of effective use of the surplus exhaust energy of this engine, for example, a generator is connected to a supercharger and the generator is rotated by the supercharger to generate power (for example, Patent Document 1 and 2). In this case, surplus exhaust energy of the engine is directly converted into electric energy, which is used for inboard equipment of a ship equipped with this encin.

However, simply connecting the generator to the turbocharger and using it as electric energy does not mean that the exhaust energy of the engine is fully utilized when the power consumption on the ship is low, etc. It is an urgent task to effectively use all the excess exhaust energy from the viewpoint of environmental protection as well as improving fuel efficiency.

Therefore, the applicant of the present invention, as a unique technique, effectively uses almost all of the surplus exhaust energy of the engine, and connects the hydraulic pump to the supercharger of the internal combustion engine and rotates the hydraulic pump by the supercharger. Many supercharger surplus power recovery devices for internal combustion engines have been developed for generating hydraulic pressure and recovering surplus exhaust energy using the generated hydraulic pressure (see, for example, Patent Documents 3 and 4).

For example, in the inventions described in Patent Documents 3 and 4, a hydraulic pump is connected to a crankshaft of an internal combustion engine, and the hydraulic pump and a hydraulic pump connected to a supercharger are connected by an oil passage, so that excess exhaust energy is obtained. When the internal combustion engine has a high load, the hydraulic pump connected to the crankshaft of the internal combustion engine is driven to rotate as a hydraulic motor by the hydraulic pump on the supercharger side, and the surplus power of the supercharger is used to bias the internal combustion engine. It is used, and about 3-4% of the engine output can be recovered. As a result, it is possible to significantly utilize the surplus exhaust energy of the internal combustion engine.

On the other hand, in recent internal combustion engines, electronic control engines that electronically control the opening and closing operations of exhaust valves and fuel injection valves via hydraulic pressure are becoming mainstream mainly for the purpose of improving fuel consumption and reducing NOx soot emissions. There is a possibility that almost all internal combustion engines mounted on ships to be built in the future become electronic control engines (see, for example, Patent Document 5).

In other words, this electronically controlled internal combustion engine appropriately adjusts the in-cylinder pressure of the engine by appropriately changing the opening and closing timing of the exhaust valve and the fuel injection valve by an electronic controller, and the internal combustion engine according to the operating conditions and environment. The engine performance can be improved. In addition, for example, the hydraulic pressure supplied for operating the exhaust valve and the fuel injection valve varies depending on the engine load, and the amount of hydraulic oil consumed also varies depending on the engine load. Therefore, the hydraulic pressure is controlled by the variable mechanism of the variable displacement hydraulic pump. I have control.

Further, as shown in FIG. 7, this variable displacement hydraulic pump is a system in which the hydraulic pump 103 is driven by shaft power transmitted from the crankshaft of the internal combustion engine 100 via a transmission, or a motor-driven hydraulic pressure (not shown). Driven by a pump. After all, the latter electric motor uses electric power generated by the generator rotated by the power of the auxiliary internal combustion engine described above or different from the above, and accordingly, the fuel consumption of the entire internal combustion engine is correspondingly increased. To raise. The hydraulic power necessary for operating the exhaust valve and the fuel injection valve corresponds to approximately 2% of the engine output.

Japanese Utility Model Publication No. 61-200423 JP 2004-346803 A JP 2006-242051 A JP 2011-214458 A JP 2010-209747 A

As described above, the turbocharger surplus power recovery device of the conventional internal combustion engine recovers surplus power of exhaust gas as hydraulic power by rotating the hydraulic pump with the power of the supercharger, and the crankshaft of the engine The hydraulic motor attached to the engine is driven to rotate by this hydraulic power, and the crankshaft is energized to reduce the fuel consumption of the engine.

However, first, when the exhaust energy is converted into hydraulic pressure by the hydraulic pump via the supercharger, power loss of the hydraulic pump occurs. Next, when this hydraulic pressure is converted into rotational power by a hydraulic pump (hydraulic motor) connected to the crankshaft of the internal combustion engine, a power loss of the hydraulic motor occurs.

In addition, in a conventional electronic control engine, when hydraulic pressure is generated from an internal combustion engine or an electric motor by a hydraulic pump, power loss also occurs in this hydraulic pump. For this reason, the conventional turbocharger surplus power recovery device in an electronically controlled internal combustion engine has a problem that the power transmission efficiency of the entire system is low.

In addition, in the conventional supercharger surplus power recovery device for an internal combustion engine of electronic control, as shown in FIG. 7, the surplus power recovery device 101 of the supercharger, the exhaust valve, the fuel injection valve, and the like are hydraulically controlled. Therefore, it is necessary to equip both the hydraulic device (hereinafter also referred to as an engine operating device) 102 for the system configuration with a hydraulic pump, valves, safety devices, piping, and the like for the system configuration, resulting in an increase in cost. .

Further, around the internal combustion engine in which a large number of auxiliary machines are arranged in a complicated manner, the redundant arrangement of the equipment necessary for the surplus power recovery device 101 and the engine operating device 102 of the supercharger is a major obstacle to the design. There is also a problem that.

The present invention has been made to solve such problems, and in an internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, a system for a supercharger surplus power recovery device for the internal combustion engine The overall power transmission efficiency can be drastically improved, and the redundant arrangement of hydraulic equipment can be eliminated, which can greatly reduce the cost and facilitate the design. It is an object to provide a surplus machine power recovery device.

In order to solve the above-described problems, a supercharger surplus power recovery device for an internal combustion engine according to the present invention includes an internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, and an exhaust gas path of the internal combustion engine. And a turbocharger that is rotationally driven by the exhaust gas of the internal combustion engine and supplies supercharged air to the internal combustion engine, and is connected to the supercharger and is rotationally driven by the supercharger to generate hydraulic pressure. A first hydraulic pump that is operated, a hydraulic mechanism that supplies hydraulic pressure to an operating device of the internal combustion engine to operate the internal combustion engine, and a power source that is connected to a power source that generates rotational power and is driven to rotate by the power source. A second hydraulic pump that supplies hydraulic pressure to the operating device, a controller that controls the operation of the hydraulic mechanism, the first hydraulic pump, and the second hydraulic pump, and a hydraulic mechanism that is disposed from the second hydraulic pump to the operating device. First oil to supply hydraulic pressure In the supercharger excess power recovery apparatus for an internal combustion engine having bets, in that a second oil passage for supplying hydraulic pressure from the first hydraulic pump is disposed in the hydraulic mechanism to the operating device.

Further, the supercharger surplus power recovery device for an internal combustion engine according to another aspect of the present invention is provided in an internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, and an exhaust gas passage of the internal combustion engine. A turbocharger that is rotationally driven by the exhaust gas of the internal combustion engine and supplies the supercharged air to the internal combustion engine; a turbine that is disposed in parallel with the supercharger in the exhaust gas path and is rotationally driven by the exhaust gas; A first hydraulic pump connected to a turbine and driven to rotate by the turbine to generate hydraulic pressure, a hydraulic mechanism for supplying hydraulic pressure to an operating device of the internal combustion engine to operate the internal combustion engine, and a power source for generating rotational power A second hydraulic pump that is rotationally driven by the power source and supplies hydraulic pressure to the operating device via the hydraulic mechanism, a controller that controls operations of the hydraulic mechanism, the first hydraulic pump, and the second hydraulic pump, and hydraulic pressure Machine In the supercharger surplus power recovery device for an internal combustion engine provided with a first oil passage for supplying hydraulic pressure from the second hydraulic pump to the operating device, the hydraulic mechanism is arranged to operate from the first hydraulic pump. A second oil passage for supplying hydraulic pressure to the equipment is provided.

Here, the operating device for operating the above-mentioned engine means devices such as an exhaust valve and a fuel injection valve necessary for operating the internal combustion engine, and a power source that generates rotational power is, for example, An internal combustion engine, an electric motor, etc. are said. However, the operating device for operating the above-described engine and the power source for generating rotational power are merely examples, and the present invention is not limited to these.

As described above, the supercharger surplus power recovery device for an internal combustion engine of the present invention is connected to a supercharger or a turbine and is driven to rotate by the supercharger or the turbine to generate hydraulic pressure. The hydraulic pressure can be directly supplied to the operating device of the internal combustion engine via the second oil passage without using a power source.

On the other hand, in a conventional supercharger surplus power recovery device for an internal combustion engine in which an operating device for operating an engine is electronically controlled, it is connected to the supercharger and is rotationally driven by this supercharger or turbine to be hydraulically operated. First, the hydraulic pump connected to the crankshaft of the internal combustion engine is rotationally driven, and then the internal combustion engine and a power source such as an electric motor that is rotationally driven by the electric power generated by the internal combustion engine are operated. The hydraulic pump necessary to supply hydraulic pressure to the equipment is driven to rotate.

Here, the second hydraulic pump that is rotationally driven by the power source and supplies hydraulic pressure to the operating device via the hydraulic mechanism must supply a large amount of hydraulic pressure required for operation to the operating device depending on the load of the internal combustion engine. . For this reason, the required capacity or number of second hydraulic pumps must be determined according to the maximum discharge amount.

However, in the supercharger surplus power recovery device for an internal combustion engine according to the present invention, since there is still surplus even if the supercharger is rotationally driven by exhaust energy at the time when the maximum discharge amount is required, the first hydraulic pump Can supply hydraulic pressure to the operating device via the second oil passage.

Therefore, the required capacity or number of second hydraulic pumps can be reduced by the amount of hydraulic pressure supplied from the first hydraulic pump, and cost reduction can be achieved. Further, the power loss that increases in accordance with the discharge amount can be reduced as the required capacity or the number of second hydraulic pumps decreases.

What is most notable here is that in the conventional turbocharger surplus power recovery device, the hydraulic pump connected to the crankshaft of the internal combustion engine by the hydraulic pressure generated by the hydraulic pump driven to rotate by the supercharger. When power is converted into rotational power of the internal combustion engine, power loss has occurred.

However, in the supercharger surplus power recovery device for an internal combustion engine according to the present invention, as described above, surplus exhaust energy is directly supplied to the operating device as hydraulic pressure through the second oil passage so as to be used effectively. Therefore, the conventional supercharger surplus power recovery device for the internal combustion engine can be eliminated. That is, the hydraulic pump connected to the crankshaft of the internal combustion engine can be eliminated, and the power loss generated by this hydraulic pump can be completely eliminated.

In addition to this, it is possible to eliminate all the hydraulic mechanisms necessary for urging the hydraulic pump connected to the crankshaft of the internal combustion engine by the first hydraulic pump, which was necessary in the past. Therefore, it is not necessary to equip the hydraulic pumps, valves, safety devices, pipes, etc. that constitute the hydraulic mechanism of the turbocharger surplus power recovery device of the conventional internal combustion engine, so that significant cost reduction can be achieved. . Further, around the internal combustion engine in which a large number of auxiliary machines are arranged in a complicated manner, it is not necessary to overlap the surplus power recovery device of the supercharger and the hydraulic mechanism of the engine operating device, thereby facilitating the design. it can.

In the supercharger surplus power recovery device of the internal combustion engine, it is desirable that the controller supplies the hydraulic pressure generated by the first hydraulic pump to the operating device via the second oil passage when the internal combustion engine is at a high load.

In this way, the controller supplies the hydraulic pressure generated by the first hydraulic pump when the internal combustion engine is at a high load directly to the operating device via the second oil passage, so that the excess exhaust energy of the internal combustion engine at the time of the high load is increased. Without power loss, it can be used effectively as the hydraulic pressure required for operating equipment.

In the above-described supercharger surplus power recovery device for an internal combustion engine, it is desirable to further include a third oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the first hydraulic pump to the second hydraulic pump.

As described above, by further including the third oil passage that is disposed in the hydraulic mechanism and supplies the hydraulic pressure from the first hydraulic pump to the second hydraulic pump, the hydraulic pressure can still be supplied from the first hydraulic pump to the operating device. When there is a sufficient surplus in the exhaust gas energy, the second hydraulic pump can be driven to rotate by the hydraulic pressure generated by the first hydraulic pump via the third oil passage, thereby energizing the rotation of the power source.

For example, when the power source is an internal combustion engine, fuel efficiency can be improved directly, and when the power source is an electric motor, it is operated as a generator to generate electric power. Significant improvement in fuel consumption can be achieved.

In the supercharger surplus power recovery apparatus for an internal combustion engine, the controller supplies a part of the hydraulic pressure generated by the first hydraulic pump to the operating device via the second oil passage at the time of high load, and the first hydraulic pump It is desirable to supply the remainder of the hydraulic pressure generated by the second hydraulic pump via the third oil passage.

When the internal combustion engine is under a high load, for example, the first hydraulic pump can generate a hydraulic pressure that is approximately twice that required for the operating equipment. Accordingly, the controller supplies a part of the hydraulic pressure generated by the first hydraulic pump at the time of high load to the operating device via the second oil passage, and the third hydraulic oil generates the remaining hydraulic pressure generated by the first hydraulic pump. By supplying the second hydraulic pump via the passage, the surplus exhaust energy of the internal combustion engine at the time of high load can be effectively utilized as the hydraulic pressure required for the operating equipment without power loss, and the first hydraulic pressure The rotation of the power source connected to the second hydraulic pump can be energized by the hydraulic pressure generated by the pump.

In the supercharger surplus power recovery device for the internal combustion engine, the second hydraulic pump is a variable displacement hydraulic pump, and the hydraulic mechanism allows the supply of hydraulic pressure from the second hydraulic pump to the operating device and the first hydraulic pump. A non-return function that prevents backflow of hydraulic pressure from the downstream side of the oil passage to the second hydraulic pump and a control of the controller forcibly allow backflow of hydraulic pressure from the downstream side of the first oil passage to the second hydraulic pump. The first oil passage is provided with a first check valve mechanism having a check release function, and the second oil passage is formed by connecting the operating device side to the downstream side of the first check valve mechanism of the first oil passage. The third oil passage is preferably formed by connecting the second hydraulic pump side to the downstream side of the first check valve mechanism of the first oil passage.

With the hydraulic mechanism having such a configuration, the controller turns off the check release function of the first check valve mechanism, so that the second hydraulic pump can supply hydraulic pressure to the operating device of the internal combustion engine, and the first The hydraulic pressure generated by one pump can be supplied to the operating device of the internal combustion engine. In addition, since the second hydraulic pump is a variable displacement hydraulic pump, the controller turns on the check release function of the first check valve mechanism, so that the hydraulic pressure generated by the first hydraulic pump is supplied to the second pump. Thus, the rotation of the second hydraulic pump including the variable displacement hydraulic pump, that is, the rotation of the power source to which the second hydraulic pump is connected can be energized.

That is, the hydraulic mechanism can be simplified by the above-described configuration. In the variable displacement hydraulic pump, the hydraulic pump can be rotated forward by the backflow of the hydraulic pressure from the normal discharge port by the variable mechanism.

In the supercharger surplus power recovery device for the internal combustion engine, it is desirable to further include a fourth oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the second hydraulic pump to the first hydraulic pump.

In this way, by further including a fourth oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the second hydraulic pump to the first hydraulic pump, the hydraulic pressure generated by the second hydraulic pump is transferred to the fourth oil passage. If it is possible to supply the first hydraulic pump via the first hydraulic pump and thereby increase the supercharging capability of the supercharger by energizing the rotation of the first hydraulic pump, the exhaust gas energy is insufficient and the supercharging is insufficient. Even in this case, the internal combustion engine can be sufficiently supercharged.

In the supercharger surplus power recovery device for the internal combustion engine, the controller supplies the hydraulic pressure generated by the second hydraulic pump to the first hydraulic pump via the fourth oil passage when the internal combustion engine is under a low load, thereby supplying the first hydraulic pressure. It is desirable to increase the supercharging capability of the supercharger by energizing the rotation of the pump.

In this way, the controller supplies the hydraulic pressure generated by the second hydraulic pump to the first hydraulic pump via the fourth oil passage when the internal combustion engine is under a low load, thereby energizing the rotation of the first hydraulic pump and the supercharger By increasing the supercharging capability of the engine, sufficient supercharging can be performed on the internal combustion engine, especially at low loads where exhaust gas energy is insufficient and the supercharging tends to be insufficient.

The supercharger surplus power recovery apparatus for an internal combustion engine further includes a third oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the first hydraulic pump to the second hydraulic pump, and the first hydraulic pump has a variable capacity. The hydraulic mechanism includes a non-return function that allows the supply of hydraulic pressure from the first hydraulic pump to the second hydraulic pump and prevents backflow of hydraulic pressure from the second hydraulic pump to the first hydraulic pump; The third oil passage is provided with a second check valve mechanism having a check release function forcibly allowing a backflow of hydraulic pressure from the second hydraulic pump to the first hydraulic pump under the control of the controller. The oil passage is preferably composed of the third oil passage.

As described above, the hydraulic mechanism further includes a third oil passage that supplies hydraulic pressure from the first hydraulic pump to the second hydraulic pump, and the first hydraulic pump is a variable displacement hydraulic pump, The second hydraulic pump is forcibly controlled by a non-return function that allows the hydraulic pressure to be supplied from the first hydraulic pump to the second hydraulic pump and prevents the backflow of hydraulic pressure from the second hydraulic pump to the first hydraulic pump and the controller. A third check valve mechanism having a check release function for allowing a backflow of hydraulic pressure from the first hydraulic pump to the first hydraulic pump is provided in the third oil passage, and the fourth oil passage is constituted by the third oil passage. As a result, the hydraulic pressure generated by the second hydraulic pump by the control of the controller can be supplied to the first hydraulic pump via the third oil passage, and thereby the first hydraulic pump is connected. Boost turbocharger rotation It is possible.

That is, the hydraulic mechanism can be simplified by the above-described configuration. As described above, in a variable displacement hydraulic pump, the hydraulic pump can be rotated forward by a reverse flow of hydraulic pressure from a normal discharge port by the variable mechanism.

In the supercharger surplus power recovery device of the internal combustion engine, it is desirable that the hydraulic mechanism includes a drain mechanism that drains the hydraulic pressure generated by the first hydraulic pump under the control of the controller and returns the hydraulic pressure to the first hydraulic pump.

As described above, the hydraulic mechanism includes the drain mechanism that drains the hydraulic pressure generated by the first hydraulic pump under the control of the controller and returns the hydraulic pressure to the first hydraulic pump, thereby supplying the hydraulic pressure from the first hydraulic pump to the operating device. The supply of hydraulic pressure from the first hydraulic pump to the second hydraulic pump and the supply of hydraulic pressure from the second hydraulic pump to the first hydraulic pump can be prevented from being performed.

The supercharger surplus power recovery device for an internal combustion engine according to the present invention includes an internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, and an exhaust gas of the internal combustion engine provided in an exhaust gas passage of the internal combustion engine. A supercharger that is rotationally driven by gas and supplies supercharged air to the internal combustion engine; a first hydraulic pump that is connected to the supercharger and is rotationally driven by the supercharger to generate hydraulic pressure; and the internal combustion engine A hydraulic mechanism that supplies hydraulic pressure to the operating equipment of the engine and operates the internal combustion engine; and a power source that is connected to a power source that generates rotational power and is rotated by the power source to supply hydraulic pressure to the operating equipment via the hydraulic mechanism. Two hydraulic pumps, a controller that controls the operation of the hydraulic mechanism, the first hydraulic pump, and the second hydraulic pump, and a first oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the second hydraulic pump to the operating device. Of internal combustion engines equipped with In excess power recovery device comprises a second oil passage for supplying hydraulic pressure to the working device from the first hydraulic pump is disposed in the hydraulic mechanism.

Alternatively, the supercharger surplus power recovery device for an internal combustion engine according to the present invention includes an internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, and an exhaust gas passage of the internal combustion engine. A turbocharger that is rotationally driven by the exhaust gas of the engine and that supplies supercharged air to the internal combustion engine, a turbine that is disposed in parallel with the supercharger in the exhaust gas path and is rotationally driven by the exhaust gas, and a turbine A first hydraulic pump that is connected and rotated by a turbine to generate hydraulic pressure, a hydraulic mechanism that supplies hydraulic pressure to an operating device of the internal combustion engine to operate the internal combustion engine, and a power source that generates rotational power. A second hydraulic pump that is rotationally driven by the power source and supplies hydraulic pressure to the operating device via the hydraulic mechanism; a controller that controls the operation of the hydraulic mechanism, the first hydraulic pump, and the second hydraulic pump; Arrangement In the supercharger surplus power recovery device for an internal combustion engine, which is provided with a first oil passage that supplies hydraulic pressure from the second hydraulic pump to the operating device, the hydraulic pressure is provided from the first hydraulic pump to the operating device. A second oil passage is provided.

Therefore, in an internal combustion engine in which an operation device for operating the engine is electronically controlled, the power transmission efficiency of the entire system of the supercharger surplus power recovery device of the internal combustion engine can be dramatically improved, and hydraulic devices It is possible to eliminate the redundant deployment, and thereby it is possible to greatly reduce the cost and facilitate the design.

It is a block diagram showing an example of a supercharger surplus power recovery device of an internal-combustion engine of the present invention. FIG. 2 is a circuit diagram showing a flow of a hydraulic circuit when the internal combustion engine of FIG. 1 is under a low load. FIG. 2 is a circuit diagram showing a flow of a hydraulic circuit at a medium load of the internal combustion engine of FIG. 1. FIG. 2 is a circuit diagram showing a flow of a hydraulic circuit when the internal combustion engine of FIG. FIG. 2 is a block diagram showing a supercharger surplus power recovery device for an internal combustion engine different from FIG. 1. FIG. 6 is a partial block diagram showing a supercharger surplus power recovery device for an internal combustion engine, which is further different from FIGS. 1 and 5. It is a block diagram which shows the supercharger surplus power recovery apparatus of the conventional internal combustion engine.

A mode for carrying out the supercharger surplus power recovery device for an internal combustion engine according to the present invention will be described in detail with reference to FIGS.

Reference numeral 1 in FIG. 1 shows, as an example, a low-speed diesel engine (power source, internal combustion engine) for propulsion mounted on a ship, and this engine 1 is required to operate the engine, for example, an exhaust valve, An operating device such as a fuel injection valve is an electronically controlled engine that is electronically controlled via hydraulic pressure, and a supercharger 5 that supplies supercharged air that is rotationally driven by the exhaust gas to the engine 1. It has.

The supercharger 5 includes a compressor 6 and a turbine 7, and the compressor 6 and the turbine 7 are connected by a rotating shaft 8. The turbine 7 is rotationally driven by the exhaust gas of the engine 1, and the compressor 6 is rotated by the turbine 7. Thereby, the air supply density of the engine 1 is increased, and the output of the engine is improved.

Note that the supercharger 5 is not necessarily limited to a single stage. Further, the engine 1 is not limited to a marine engine, and the type is not limited to a low-speed diesel engine. Includes gas engines fueled by natural gas, city gas, etc., and all other types of electronic control engines.

As shown in FIG. 1, a transmission 9 is connected to the rotating shaft 8 of the supercharger 5, and a variable displacement first hydraulic pump 10 is connected to the transmission 9. A transmission 3 is connected to one end of the crankshaft 2 of the engine 1, and a variable displacement second hydraulic pump 11 is connected to the transmission 3.

The second hydraulic pump 11 can be directly connected to the crankshaft 2 of the engine 1 without providing the transmission 3. In addition, the number of the first hydraulic pump 10 and the number of the second hydraulic pumps 11 described above is one in FIG. 1, but is merely an example, and a plurality of units may be provided.

The first hydraulic pump 10 and the second hydraulic pump 11 are incorporated in the hydraulic mechanism 20. In the hydraulic mechanism 20, one discharge port 11a of the second hydraulic pump 11 is connected to the oil passage 21, and the engine described above is passed through the check valve 31, the oil passage 22, the check valve 32, and the oil passage 23 in this order. The hydraulic pressure is supplied by being connected to the control circuit of the one operating device. A first oil passage is formed by the

oil passages

21, 22, and 23. The other discharge port 11 b of the second hydraulic pump 11 is connected to one discharge port 10 b of the first hydraulic pump 10 via an oil passage 24.

The other discharge port 10a of the first hydraulic pump 10 is connected to the oil passage 26, and the check valve 36, the oil passage 27, the oil passage 22, and the oil passage 23 are connected in this order to the operating device 51 of the engine 1 described above. Connected to the control circuit, it can supply hydraulic pressure. Further, the oil passage 27 is also connected to one discharge port 11 a of the second hydraulic pump 11 through the oil passage 22, the check valve 31, and the oil passage 21 in this order.

Note that the

discharge ports

10a and 10b of the first hydraulic pump 10 and the

discharge ports

11a and 11b of the second hydraulic pump 11 are both discharge ports. In practice, however, as will be described later, one of the two is a hydraulic discharge port and the other is a hydraulic intake depending on the operating state. However, in the supercharger surplus power recovery device of this internal combustion engine, Is also called a discharge port. The

oil passages

26, 27, 22, and 23 form a second oil passage, the

oil passages

26, 27, 22, and 21 form a third oil passage, and the

oil passages

21, 22, 27, and 26 form a fourth oil passage, respectively. The

The check valve 31 is integrated with the electromagnetic switching valve 41 to form the first check valve mechanism 30. The first check valve mechanism 30 is a check that forcibly allows a backflow of hydraulic pressure from the oil passage 22 to the oil passage 21, that is, the second hydraulic pump 11, by switching the electromagnetic switching valve 41 under the control of the controller 50. Has a release function.

When the check release function is OFF, the check valve 31 allows the hydraulic pressure to be supplied from the second hydraulic pump 11 to the control circuit of the operating device 51 through the oil passage 21 and from the oil passage 22 to the first. 2 A normal check function for preventing the backflow of hydraulic pressure to the hydraulic pump 11 is activated.

On the other hand, when the check release function is ON, as described above, the check valve 31 is forcibly opened to allow the backflow of hydraulic pressure from the oil passage 22 to the second hydraulic pump 11. In addition, an accumulator 45 is disposed between the second hydraulic pump 11 and the check valve 31 to absorb hydraulic pressure fluctuations caused by ocean waves, exhaust valve driving, fuel injection, and the like.

Also, the check valve 36 and the electromagnetic switching valve 42 form a second check valve mechanism 35. The second check valve mechanism 35 is a check that forcibly allows the backflow of hydraulic pressure from the oil passage 27 to the oil passage 26, that is, the first hydraulic pump 10 by switching the electromagnetic switching valve 42 under the control of the controller 50. Has a release function.

When the check release function is OFF, the check valve 31 allows the hydraulic pressure to be supplied from the first hydraulic pump 10 to the control circuit of the operating device 51 and the check valve 31 through the oil passage 26. Oil passage 2
A normal check function that prevents the backflow of hydraulic pressure from 7 to the oil passage 26, that is, the first hydraulic pump 10, works. On the other hand, when the check release function is ON, as described above, the check valve 31 is forcibly opened to return the hydraulic pressure from the oil passage 27 to the oil passage 26, that is, the first hydraulic pump 10. Is acceptable.

An electromagnetic opening / closing valve 44 is disposed between the oil passage 26 and the oil passage 24, and when the electromagnetic opening / closing valve 44 is opened, the oil pressure of the oil passage 26 is drained to the oil passage 24 to increase the oil pressure of the oil passage 26. Can be opened. The oil path 26, the electromagnetic on-off valve 44, and the oil path 24 constitute a drain mechanism.

The controller 50 detects, for example, the intake air suction temperature, the supply air pressure downstream of the supercharger 5 and the like by means of sensors, and, based on the detected supply air pressure, intake temperature, etc., as described later. The operations of the hydraulic pump 10, the second hydraulic pump 11, the

electromagnetic switching valves

41 and 42, the electromagnetic on-off valve 44, and the like are electrically controlled. The controller 50 may control the operations of the first hydraulic pump 10, the second hydraulic pump 11, the

electromagnetic switching valves

41 and 42, the electromagnetic opening / closing valve 44, and the like using parameters other than the above-described supply pressure and suction temperature. is there.

Next, the operation of the supercharger surplus power recovery device of the internal combustion engine will be described. When starting the internal combustion engine, the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in FIG. 2 to turn off the check release function of the first check valve mechanism 30 and 2 The electromagnetic switching valve 42 of the check valve mechanism 35 is operated to turn off the check release function of the second check valve mechanism 35. Further, the electromagnetic opening / closing valve 44 is closed.

Therefore, the check valve 31 prohibits the backflow of hydraulic pressure from the oil passage 22 to the oil passage 21, and the check valve 36 prohibits the backflow of hydraulic pressure from the oil passage 27 to the oil passage 26. Then, the controller 50 rotates the electric motor 52 to generate a hydraulic pressure necessary for starting by the hydraulic pump 53 and supplies the hydraulic pressure to the control circuit of the operating device 51. At this time, the check valve 32 also prevents backflow of hydraulic pressure from the oil passage 23 to the oil passage 22.

Next, when the internal combustion engine is at a low load, for example, from the start to a load of 35%, the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 to turn on the first check valve mechanism 30. While turning off the check release function, the electromagnetic switching valve 42 of the second check valve mechanism 35 is operated to turn on the check release function of the second check valve mechanism 35. For this reason, the check valve 36 is forcibly opened to allow the backflow of hydraulic pressure from the oil passage 27 to the oil passage 26.

The hydraulic pressure generated by the second hydraulic pump 11 is supplied to the control circuit of the operating device 51 via the oil passage 21, the check valve 31, the oil passage 22, the check valve 32, and the oil passage 23 in this order. The At the same time, the hydraulic pressure generated by the second hydraulic pump 11 flows through the oil passage 21, the check valve 31, the oil passage 22, the oil passage 27, the forcibly opened check valve 36, and the oil passage 26 in this order. And supplied to the discharge port 10a of the first hydraulic pump 10 to urge the rotation of the first hydraulic pump 10.

That is, the rotation of the supercharger 5 connected to the first hydraulic pump 10 is energized by the hydraulic pressure generated by the second hydraulic pump 11 so that the supercharging at the time of low load, which tends to be insufficient, is properly performed. To be done. Note that the variable displacement first hydraulic pump 10 can rotate the supercharger 5 in the forward direction also by the backflow of the hydraulic pressure from the discharge port 10a by the variable mechanism.

The controller 50 reads the intake air intake temperature detected by the sensor, the supply air pressure in the supply passage on the downstream side of the supercharger 5, and the like. Further, the necessary power for energizing the supercharger 5 is set in the controller 50 for each engine load. The controller 50 controls the power for energizing the supercharger 5 by appropriately changing the capacity of the variable displacement type first hydraulic pump 10 based on the supply pressure, the suction temperature, and the like.

Next, at a medium load of the internal combustion engine, for example, during a load of 35 to 50%, the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in FIG. The non-return release function 30 is turned off and the electromagnetic on-off valve 44 is opened.

When the electromagnetic on-off valve 44 is opened, the hydraulic pressure generated by the first hydraulic pump is drained from the oil passage 26 to the oil passage 24 through the electromagnetic on-off valve 44 and released, so that the pressure is low and the check is not performed. It does not flow through the valve 36 to the high pressure oil passage 27. In this case, the first hydraulic pump 10 that is rotationally driven by the supercharger 5 is in a so-called no-load operation, but a constant pressure of hydraulic pressure is discharged to cool the system.

On the other hand, the hydraulic pressure generated by the second hydraulic pump 11 is supplied to the control circuit of the operating device 51 through the oil passage 21, the check valve 31, the oil passage 22, the check valve 32, and the oil passage 23. Although the hydraulic pressure generated by the second hydraulic pump 11 is relatively high, the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in FIG. 3 to release the check of the first check valve mechanism 30. Since the function is OFF, the oil pressure in the oil passage 27 does not flow to the oil passage 26 through the check valve 36 due to the normal check function of the check valve 36.

As described above, when the internal combustion engine is at a medium load, for example, during a load of 35 to 50%, the first hydraulic pump 10 is in a no-load operation and the hydraulic pressure is supplied to the operating device 51 only by the second hydraulic pump 11. The If it is necessary to disconnect the hydraulic pressure between the first hydraulic pump 10 on the supercharger 5 side and the second hydraulic pump 11 on the engine 1 side, for example, in the case of an emergency stop, the same as described above Operation is performed.

Next, when the internal combustion engine is at a high load, for example, when the load is 50% or more, the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in FIG. The check release function of the mechanism 30 is turned on, and the electromagnetic switching valve 42 of the second check valve mechanism 35 is operated to turn off the check release function of the second check valve mechanism 35. Further, the electromagnetic on-off valve 44 is closed.

For this reason, the check valve 31 of the first check valve mechanism 30 is forcibly opened to allow a backflow of hydraulic pressure from the oil passage 22 to the oil passage 21, that is, the second hydraulic pump 11. The check valve 36 of the second check valve mechanism 35 also allows the flow of hydraulic pressure from the oil passage 26 to the oil passage 27 by a normal check function.

Therefore, the hydraulic pressure generated by the first hydraulic pump 10 is supplied to the control circuit of the operating device 51 through the oil passage 26, the check valve 36, the oil passage 27, the check valve 32, and the oil passage 23 in this order. Is done. For example, when the load is 50% or more, all of the hydraulic pressure required by the operating device 51 can be supplied from the first hydraulic pump 10.

Also, when the engine 1 is under a high load, the first hydraulic pump 10 can generate a hydraulic pressure that is, for example, about twice that required for the operating device 51. For this reason, the hydraulic pressure generated by the first hydraulic pump 10 passes through the oil passage 26, the check valve 36, the oil passage 27, the oil passage 22, the check valve 31, and the oil passage 21 in this order. 11 is also supplied to the discharge port 11a to urge the rotation of the second hydraulic pump 11.

That is, the rotation of the engine 1 connected to the second hydraulic pump 11 is energized by the hydraulic pressure generated by the first hydraulic pump 10. The controller 50 adjusts the hydraulic power recovered from the supercharger 5 by appropriately changing the capacity of the first hydraulic pump 10 based on the maximum power recoverable from the supercharger 5 set in advance.

As shown in FIG. 5, the second hydraulic pump 11 may be connected not to the engine but to an electric motor (power source) 54 that generates rotational power in the same manner as the engine. As this electric motor 54, for example, an induction motor is used. The number of revolutions of the induction motor is determined by the frequency of the power system, and always rotates at a constant speed. For this reason, the rotation speed control of the electric motor 54 by the above-described hydraulic mechanism 20 or the like is not particularly required.

Then, when the engine is under a high load, the above-described surplus hydraulic pressure supplied from the first hydraulic pump 10 generates electric power by operating the motor 54 as a generator, and this electric power is supplied to the power system. Since electric power required in a ship or the like is usually generated by a generator that is rotationally driven by an engine, the fuel efficiency of the engine can be improved as a result. In addition, since the operation of the supercharger surplus power recovery device for the internal combustion engine at the time of low load, medium load, and high load of the engine is the same as that of the engine 1 described above, the description thereof is omitted.

As shown in FIG. 6, a power turbine 55 is disposed in the exhaust gas passage 4 of the engine in parallel with the supercharger 5 via a flow rate adjusting valve 56, and the first hydraulic pump 10 is connected to the power turbine 55. Good. The operation of the supercharger surplus power recovery device for the internal combustion engine at the time of medium load and high load of the engine in this case is the same as that of the engine 1 described above. However, structurally, the rotation of the supercharger 5 cannot be directly urged through the first hydraulic pump 10 by the hydraulic pressure generated by the second hydraulic pump 11 when the engine is under a low load. Others are the same as in the case of the supercharger 5 described above, and the description is omitted.

Further, the first hydraulic pump described above is not necessarily a variable displacement type, and may be a fixed displacement type. If it is a fixed capacity type, a large space can be saved. However, when the first hydraulic pump is of a fixed displacement type, the pump cannot be rotated forward by the backflow of the hydraulic pressure from the discharge port. It cannot be added.

Therefore, in order to perform the same operation as that of the above-described supercharger surplus power recovery device of the internal combustion engine when the engine 1 is under low load, medium load, and high load, a normal hydraulic intake is also used during the backflow of hydraulic pressure. It is necessary to partially change the configuration of the hydraulic mechanism 20 so that the flow into the pump can be made. Others are the same as in the case of the variable displacement type second hydraulic pump 10 described above, and thus the description thereof is omitted.

As described above, the supercharger surplus power recovery device of the internal combustion engine is connected to the supercharger 5 or the power turbine 55, and is rotated by the supercharger 5 or the power turbine 55 to generate hydraulic pressure. 1 The hydraulic pump 10 can directly supply hydraulic pressure to the operating device 51 of the engine 1 without going through the engine 1 or the electric motor 52 which is a power source.

In addition, the conventional second hydraulic pump that is rotationally driven by this power source and supplies hydraulic pressure to the operating equipment via the hydraulic mechanism supplies the hydraulic pressure required for operation to the operating equipment when the internal combustion engine is under a high load. Must be supplied in large quantities. For this reason, the required capacity or number of second hydraulic pumps is determined according to the maximum discharge amount. However, in the supercharger surplus power recovery device of the internal combustion engine, even when the turbocharger 5 is driven to rotate by exhaust energy, especially at the high load where the maximum discharge amount is required, there is still surplus, the first hydraulic pressure The pump 10 directly supplies hydraulic pressure to the operating device 51 via the second oil passage.

For this reason, the required capacity or the number of the second hydraulic pumps 11 can be reduced by the amount of hydraulic pressure supplied from the first hydraulic pump 10, and the cost can be reduced. Further, the power loss that increases in accordance with the discharge amount can be reduced as the required capacity or the number of the second hydraulic pumps 11 decreases.

The most notable point here is that it is possible to eliminate the hydraulic pump of the supercharger surplus power recovery device connected to the crankshaft of the engine, which was necessary in the conventional supercharger surplus power recovery device of the internal combustion engine. Therefore, it is possible to eliminate all the power loss generated by the hydraulic pump. Further, it is possible to eliminate all the hydraulic mechanisms that are necessary for the conventional first hydraulic pump to urge the hydraulic pump connected to the crankshaft of the engine.

Therefore, it is no longer necessary to equip the hydraulic pumps, valves, safety devices, pipes, etc. that constitute the hydraulic mechanism of the turbocharger surplus power recovery device of the conventional internal combustion engine, and the cost can be greatly reduced. Further, around the internal combustion engine in which a large number of auxiliary machines are arranged in a complicated manner, it is not necessary to overlap the surplus power recovery device of the supercharger and the hydraulic mechanism of the engine operating device, thereby facilitating the design. it can.

As described above, when the engine 1 is under a high load, the first hydraulic pump 10 can generate a hydraulic pressure that is, for example, about twice that required for the operating device. In the supercharger surplus power recovery device of the internal combustion engine, the controller 50 supplies a part of the hydraulic pressure generated by the first hydraulic pump 10 to the operating device 51 at the time of high load, and the first hydraulic pump 10 generates it. Since the remaining hydraulic pressure is supplied to the second hydraulic pump 11, it is possible to effectively use the excess exhaust energy of the engine 1 at the time of high load as the hydraulic pressure required for the operating device 51 without power loss due to the hydraulic pump. In addition, the rotation of the power source to which the second hydraulic pump 11 is connected can be urged by the hydraulic pressure generated by the first hydraulic pump 10.

For this reason, for example, when the power source is the engine 1, fuel efficiency is improved directly, and when the power source is the electric motor 52, this is operated as a generator to generate electric power. The fuel consumption of the entire internal combustion engine can be improved.

The above-described supercharger surplus power recovery device for an internal combustion engine is merely an example, and various modifications can be made based on the gist of the present invention, and they are not excluded from the scope of the present invention. Further, in the above-described supercharger surplus power recovery device for an internal combustion engine, a load up to 35% is a low load, a load 35 to 50% is a medium load, and a load 50% or more is a high load. However, it is different depending on the type and usage form of the internal combustion engine, and is not limited thereto.

The supercharger surplus power recovery device for an internal combustion engine according to the present invention is not necessarily mounted on the above-described ship if the operating device for operating the engine is an electronic control through a hydraulic pressure and has a supercharger. It is not limited to the low-speed diesel engines for propulsion that are used, but can be widely used for all kinds of internal combustion engines and for all types of internal combustion engines.

1 Engine (power source, internal combustion engine)
2 crankshaft 3 transmission 4 exhaust gas path 5 supercharger 6 compressor 7 turbine 8 rotary shaft 9 transmission 10 first

hydraulic pumps

10a, 10b, 11a, 11b discharge port 11 second hydraulic pump 20

hydraulic mechanisms

21,22 23, 24, 26, 27 Oil passage 30 First

check valve mechanism

31, 32, 36 Check valve 35 Second

check valve mechanism

41, 42 Electromagnetic switching valve 44 Electromagnetic switching valve 45 Accumulator 50 Controller 51 Actuating device 52 Electric motor 53 Hydraulic pump 54 Electric motor (power source)
55 Power turbine 56 Flow rate adjusting valve 100 Internal combustion engine 101 Supercharger surplus power recovery device 102 Engine operating device 103 Hydraulic pump

Claims

An operating device (51) for operating the engine is electronically controlled via hydraulic pressure, and the internal combustion engine (1) is disposed in an exhaust gas passage of the internal combustion engine and is rotationally driven by the exhaust gas of the internal combustion engine, A supercharger (5) for supplying supercharged air to the internal combustion engine, a first hydraulic pump (10) connected to the supercharger and driven to rotate by the supercharger to generate hydraulic pressure; Connected to a hydraulic mechanism (20) for operating the internal combustion engine by supplying hydraulic pressure to the operating device of the internal combustion engine to operate the internal combustion engine, and a power source (1, 54) for generating rotational power. A second hydraulic pump (11) that is rotationally driven by a power source and supplies hydraulic pressure to the operating device via the hydraulic mechanism, and controls the operations of the first hydraulic pump, the second hydraulic pump, and the hydraulic mechanism. A controller (50); In the supercharger surplus power recovery device for an internal combustion engine, comprising a first oil passage (21, 22, 23) that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the second hydraulic pump to the operating device. A supercharger surplus power of an internal combustion engine, comprising a second oil passage (26, 27, 22, 23) disposed in a hydraulic mechanism and supplying hydraulic pressure from the first hydraulic pump to the operating device. Recovery device.
An internal combustion engine in which an operating device for operating the engine is electronically controlled via hydraulic pressure, and an exhaust gas passage (4) of the internal combustion engine, which is rotationally driven by the exhaust gas of the internal combustion engine, is connected to the internal combustion engine. A supercharger (5) for supplying supercharged air, and a turbine (55) disposed in parallel to the supercharger in the exhaust gas path and rotated by the exhaust gas of the internal combustion engine; A first hydraulic pump (10) connected to the turbine and driven to rotate by the turbine to generate hydraulic pressure; and supplying the hydraulic pressure to the operating device of the internal combustion engine to operate the operating device to operate the internal combustion engine. A hydraulic mechanism (20) to be operated, a second hydraulic pump connected to a power source for generating rotational power and driven to rotate by the power source to supply hydraulic pressure to the operating device via the hydraulic mechanism; 1 A pressure pump, a second hydraulic pump, a controller that controls the operation of the hydraulic mechanism, and a first oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the second hydraulic pump to the operating device. The supercharger surplus power recovery device for an internal combustion engine includes a second oil passage that is disposed in the hydraulic mechanism and supplies hydraulic pressure from the first hydraulic pump to the operating device. Charger surplus power recovery device.
The controller (50) operates the hydraulic pressure generated by the first hydraulic pump (10) during the high load of the internal combustion engine (1) via the second oil passage (26, 27, 22, 23). The supercharger surplus power recovery device for an internal combustion engine according to claim 1 or 2, characterized in that the supercharger surplus power recovery device is supplied to the device (51).
A third oil passage (26, 27, 22, 21) that is disposed in the hydraulic mechanism (20) and supplies hydraulic pressure from the first hydraulic pump (10) to the second hydraulic pump (11) is further provided. The supercharger surplus power recovery device for an internal combustion engine according to any one of claims 1 to 3.
The controller (50) passes a part of the hydraulic pressure generated by the first hydraulic pump (10) at a high load of the internal combustion engine (1) through the second oil passage (26, 27, 22, 23). Then, the remaining hydraulic pressure generated by the first hydraulic pump is supplied to the second hydraulic pump (11) via the third oil passage (26, 27, 22, 21). The supercharger surplus power recovery device for an internal combustion engine according to claim 4, wherein the supercharger surplus power recovery device is supplied.
The second hydraulic pump (11) is a variable displacement hydraulic pump, and the hydraulic mechanism (20) allows the supply of hydraulic pressure from the second hydraulic pump to the operating device (51) and the first hydraulic pump. A non-return function for preventing a back flow of hydraulic pressure from the downstream side of one oil passage (21, 22, 23) to the second hydraulic pump and the downstream of the first oil passage by control of the controller (50). The first oil passage is provided with a first check valve mechanism (30) having a non-return release function that allows backflow of hydraulic pressure from the side to the second hydraulic pump, and the second oil passages (26, 27, 22, 23) is formed by connecting the operating device side to the downstream side of the first check valve mechanism of the first oil passage, and the third oil passage (26, 27, 22, 21) The second hydraulic pump side is connected to the downstream side of the first check valve mechanism of the first oil passage. It is formed Te supercharger excess power recovery apparatus for an internal combustion engine according to claim 4 or 5, characterized in.
And a fourth oil passage (21, 22, 27, 26) disposed in the hydraulic mechanism (20) for supplying hydraulic pressure from the second hydraulic pump (11) to the first hydraulic pump (10). The supercharger surplus power recovery device for an internal combustion engine according to claim 1.
The controller (50) transmits the hydraulic pressure generated by the second hydraulic pump (11) at a low load of the internal combustion engine (1) via the fourth oil passages (21, 22, 27, 26). The supercharging of the internal combustion engine according to claim 7, wherein the supercharging capability of the supercharger (5) is increased by supplying the hydraulic pressure to a single hydraulic pump (10) to urge the rotation of the first hydraulic pump. Machine excess power recovery device.
A third oil passage (26, 27, 22, 21) disposed in the hydraulic mechanism (20) for supplying hydraulic pressure from the first hydraulic pump (10) to the second hydraulic pump (11); The first hydraulic pump is a variable displacement hydraulic pump, and the hydraulic mechanism allows the supply of hydraulic pressure from the first hydraulic pump to the second hydraulic pump and from the second hydraulic pump to the first hydraulic pump. A check function for preventing backflow of hydraulic pressure to the hydraulic pump, and a check release function for forcibly allowing backflow of hydraulic pressure from the second hydraulic pump to the first hydraulic pump under the control of the controller (50); The second check valve mechanism (35) having the above is provided in the third oil passage, and the fourth oil passage (21, 22, 27, 26) comprises the third oil passage. Supercharger surplus motion of internal combustion engine according to 7 or 8 Recovery system.
The hydraulic mechanism (20) includes drain mechanisms (26, 44, 24) that drain the hydraulic pressure generated by the first hydraulic pump (10) under the control of the controller (50) and return it to the first hydraulic pump. The supercharger surplus power recovery apparatus for an internal combustion engine according to any one of claims 1 to 9, further comprising: