KR20170124622A - Supercharger surplus power recovery device for internal combustion engine - Google Patents

Abstract

(Problem) The power transmission efficiency can be dramatically improved, and redundant equipment of hydraulic devices can be excluded.
An internal combustion engine (1) in which an operating device (51) for operating an engine is electronically controlled via an oil pressure, a turbocharger (5), and a first hydraulic pump 10, a hydraulic mechanism 20, a second hydraulic pump 11 that is rotationally driven by the power source 1 to supply hydraulic pressure to an operating device, a first hydraulic pump, a second hydraulic pump, A first oil passage 21 for supplying hydraulic pressure to the operating device from the second hydraulic pump, a second oil passage 26 for supplying hydraulic pressure to the operating device from the first hydraulic pump, , 27, 22, 23). A third flow path for supplying hydraulic pressure from the first hydraulic pump to the second hydraulic pump, a fourth flow path for supplying hydraulic pressure from the second hydraulic pump to the first hydraulic pump, , 26).

Description

Technical Field [0001] The present invention relates to a supercharger surplus power recovery device for an internal combustion engine,

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

BACKGROUND ART [0002] Conventionally, in an internal combustion engine such as a diesel engine or a gas engine, a supercharger (turbocharger) rotates the turbine by the exhaust gas of the engine, increases the air supply density by the compressor rotated by the turbine, And to improve it.

However, even if the turbocharger is installed in such a manner to effectively utilize the exhaust energy, exhaust energy is surplus at the time of high load (high output) of the engine, and the waste exhaust energy is used without waste, It is strongly demanded in terms of protection.

In order to make effective use of surplus exhaust energy of the engine, for example, a generator is connected to a supercharger, and the generator is rotationally driven by a supercharger to perform power generation (for example, refer to Patent Documents 1 and 2). In this case, the surplus exhaust energy of the engine is directly converted into electric energy, and it is used for the in-ship facilities of the ship equipped with this engine.

However, if the supercharger is connected to the generator and used as electric energy, the exhaust energy of the engine is not sufficiently utilized in the case where the in-board power consumption is low, and thus the surplus exhaust energy of the engine is effectively utilized In addition to improving fuel efficiency, it has become a pressing issue in terms of environmental protection.

Therefore, the applicant of the present application, as a unique technology, has effectively utilized the surplus exhaust energy of the engine. The hydraulic pump is connected to the supercharger of the internal combustion engine to rotate the hydraulic pump by the supercharger to generate the hydraulic pressure, Many supercharger surplus power recovery devices for an internal combustion engine for recovering surplus exhaust energy by hydraulic pressure have been developed (for example, see Patent Documents 3 and 4).

For example, in the invention described in Patent Documents 3 and 4, a hydraulic pump is connected to a crankshaft of an internal combustion engine, and a hydraulic pump connected to the hydraulic pump and the supercharger is connected by a flow path, The hydraulic pump connected to the crankshaft of the internal combustion engine by the hydraulic pump at the supercharger side is rotationally driven as a hydraulic motor and the surplus power of the supercharger is used for the elastic support of the internal combustion engine, ~ 4% can be recovered. Thereby, the surplus exhaust energy of the internal combustion engine can be utilized in a considerable extent.

On the other hand, in recent internal combustion engines, an electronic control engine for electronically controlling opening and closing operations of an exhaust valve and a fuel injection valve via hydraulic pressure is mainly used for the purpose of improving fuel consumption and reducing NOx emission amount. There is a possibility that almost all of the internal combustion engines mounted on a ship scheduled to be constructed are electronic control engines (see, for example, Patent Document 5).

That is, in the electronically controlled internal combustion engine, the opening and closing timings of the exhaust valve and the fuel injection valve are appropriately changed by the electronic controller to arbitrarily adjust the internal cylinder pressure to improve the engine performance of the internal combustion engine . In addition, for example, since the oil pressure supplied for operating the exhaust valve or the fuel injection valve is different for each engine load, and the consumption amount of the operating oil also changes depending on the engine load, the hydraulic pressure is controlled by the variable mechanism of the variable displacement hydraulic pump .

7, the variable displacement hydraulic pump is driven by a shaft force transmitted from a crankshaft of the internal combustion engine 100 via a transmission, but the hydraulic pump 103 is not shown in the drawing Driven by a motor-driven hydraulic pump. The latter electric motor ultimately uses the electric power generated by the generator, which is rotated by the power of the auxiliary internal combustion engine separate from the one described above or the electric power generated by the electric motor, so that the fuel efficiency of the entire internal combustion engine is increased accordingly. The hydraulic power required to operate the exhaust valve or the fuel injection valve generally corresponds to about 2% of the engine power.

Japanese Utility Model Publication No. 61-200423 Japanese Laid-Open Patent Publication No. 2004-346803 Japanese Patent Application Laid-Open No. 2006-242051 Japanese Laid-Open Patent Publication No. 2011-214458 Japanese Laid-Open Patent Publication No. 2010-209747

As described above, in the conventional supercharger surplus power recovery device of the internal combustion engine, the surplus power of the exhaust gas is recovered as the hydraulic power by rotationally driving the hydraulic pump with the power of the turbocharger, and the hydraulic motor Is rotationally driven by this hydraulic power to urge the crankshaft so as to reduce the fuel consumption of the engine.

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

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 occurs also in this hydraulic pump. For this reason, in the conventional supercharger surplus power recovery device in the electronically controlled internal combustion engine, there is a problem that the power transmission efficiency of the entire system is low.

In addition, as shown in Fig. 7, in the supercharger surplus power recovery apparatus of the conventional electronically controlled internal combustion engine, the surplus power recovery apparatus 101 for the supercharger and the surplus power recovery apparatus 101 for the supercharger, A hydraulic pump, a valve, a safety device, and a piping for system configuration need to be redundantly installed in both hydraulic pressure devices (hereinafter, also referred to as engine operation devices) 102, resulting in an increase in cost.

Further, in the vicinity of the internal combustion engine where a large number of auxiliary machines are arranged and arranged, the redundant arrangement of the supercharger surplus power recovery device 101 and the machinery necessary for the engine operation device 102 is large There is also the problem that they are shackles.

SUMMARY OF THE INVENTION It is an object of the present invention to provide an internal combustion engine in which an operating device for operating an engine is electronically controlled via an oil pressure, And it is an object of the present invention to provide a supercharger surplus power recovery device for an internal combustion engine capable of eliminating redundant arrangements of hydraulic equipment, thereby greatly reducing cost and facilitating design .

In order to solve the above-described problems, the supercharger surplus power recovery device of the internal combustion engine of the present invention comprises an internal combustion engine in which an operating device for operating the engine is electronically controlled via an oil pressure, A first hydraulic pump which is rotationally driven by the exhaust gas of the internal combustion engine to supply the supercharged air supply to the internal combustion engine, a first hydraulic pump connected to the supercharger and rotationally driven by the supercharger to generate the hydraulic pressure, A second hydraulic pump connected to a power source for generating a rotational power and rotationally driven by the prime mover to supply hydraulic pressure to the operating device via the hydraulic device, A controller that controls the operation of the hydraulic pump and the second hydraulic pump, and a second hydraulic pump A supercharger surplus power recovery device for an internal combustion engine having a first flow path for supplying hydraulic pressure to an operating device, the supercharger surplus power recovery device comprising a second flow path formed in the hydraulic mechanism and supplying hydraulic pressure to the operating device from the first hydraulic pump have.

Another supercharger surplus power recovery device of an internal combustion engine according to the present invention is an supercharger surplus power recovery device for an internal combustion engine that includes an internal combustion engine in which an operating device for operating an engine is electronically controlled via an oil pressure, A turbine rotatably driven by the exhaust gas and arranged in parallel with the turbocharger in the exhaust gas path to supply supercharged air to the internal combustion engine; A first hydraulic pump, a hydraulic mechanism that operates the internal combustion engine by supplying hydraulic pressure to an operating device of the internal combustion engine, and a control unit that is connected to a power source for generating a rotational power, rotatively driven by the power source, A second hydraulic pump that supplies the hydraulic pressure to the first hydraulic pump, and a second hydraulic pump that controls the operation of the hydraulic mechanism, A supercharger surplus power recovery device for an internal combustion engine, comprising a controller, a controller, a controller, a controller, a controller, and a controller. The controller is operable to control the hydraulic pump. And a second flow path for supplying hydraulic pressure to the device.

Here, the above-mentioned operating device for operating the engine refers to a device such as an exhaust valve, a fuel injection valve and the like necessary for operating the internal combustion engine, and the power source for generating the rotational power is, for example, , And electric motors. However, all of the above-described operating devices for operating the engine and the power source for generating the rotational power are merely examples, and the present invention is not limited thereto.

As described above, the supercharger surplus power recovery device of the internal combustion engine of the present invention comprises a first hydraulic pump connected to a supercharger or a turbine and rotationally driven by the supercharger or turbine to generate hydraulic pressure, The hydraulic pressure can be directly supplied to the operating device of the internal combustion engine without interposing the power source.

On the other hand, in a conventional supercharger surplus power recovery device of an internal combustion engine in which an operating device for operating an engine is electronically controlled, a hydraulic pump connected to a supercharger and rotationally driven by the supercharger or turbine to generate hydraulic pressure, A power source such as an electric motor driven by the power generated by the internal combustion engine or the internal combustion engine rotates the hydraulic pump connected to the crankshaft of the engine and drives the hydraulic pump necessary for supplying the hydraulic pressure to the operating device .

Here, the second hydraulic pump, which is rotationally driven by the power source and supplies the 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. Therefore, the required capacity or logarithm of the second hydraulic pump must be determined according to this maximum discharge amount.

However, in the supercharger surplus power recovery device of the internal combustion engine according to the present invention, even when the supercharger is driven to rotate by the exhaust energy during the load in which the maximum discharge amount is required, there is still surplus. So that the hydraulic pressure can be supplied to the operating device.

Therefore, the required capacity or the number of the second hydraulic pump can be reduced by the supply amount of the hydraulic pressure from the first hydraulic pump, and the cost can be reduced. It is also possible to reduce the power loss which is increased depending on the discharge amount and the reduction of the required capacity or the number of the second hydraulic pump.

It is most important to note that in a supercharger surplus power recovery device of a conventional internal combustion engine, a hydraulic pump connected to the crankshaft of the internal combustion engine is added by the hydraulic pressure generated by the hydraulic pump rotationally driven by the turbocharger, The power loss occurs when the power is converted into the rotational power of the motor.

However, in the supercharger surplus power recovery device of the internal combustion engine of the present invention, as described above, surplus exhaust energy is directly supplied to the operating device via the second flow path as the hydraulic pressure, The supercharger surplus power recovery device of the conventional internal combustion engine can be excluded. That is, the hydraulic pump connected to the crankshaft of the internal combustion engine can be excluded, and the power loss generated by the hydraulic pump can be completely eliminated.

In addition to this, it is possible to eliminate all the hydraulic mechanisms required for adding the hydraulic pump, which is conventionally required, to the crankshaft of the internal combustion engine. Therefore, there is no need to redundantly install the hydraulic pump, the valves, the safety device, the piping, and the like, which constitute the hydraulic mechanism of the supercharger surplus power recovery device of the conventional internal combustion engine, so that a considerable cost reduction can be achieved. Further, in the vicinity of the internal combustion engine in which a large number of swirling flows are arranged and formed, the overlapping arrangement of the surplus power recovery device of the supercharger and the hydraulic mechanism of the engine operation device becomes unnecessary, and designing can be facilitated.

In the supercharger surplus power recovery device of the internal combustion engine, it is preferable that the controller supplies the hydraulic pressure generated by the first hydraulic pump to the operating device via the second flow path at the time of the high load of the internal combustion engine.

In this manner, the controller supplies the hydraulic pressure generated by the first hydraulic pump directly to the operating device via the second flow path at the time of the high load of the internal combustion engine, so that the surplus exhaust energy of the internal combustion engine at the time of high load, As shown in Fig.

In the supercharger surplus power recovery device of the internal combustion engine, it is preferable that the supercharger surplus power recovery device further includes a third flow path formed in the hydraulic mechanism and supplying the hydraulic pressure from the first hydraulic pump to the second hydraulic pump.

In this way, by additionally providing a third flow path formed in the hydraulic mechanism and supplying the hydraulic pressure from the first hydraulic pump to the second hydraulic pump, even when the hydraulic pressure is supplied from the first hydraulic pump to the operating device, The second hydraulic pump is driven to rotate by the hydraulic pressure generated by the first hydraulic pump through the third flow path so that the rotation of the power source can be added.

For example, when the power source is an internal combustion engine, direct fuel economy can be improved. When the power source is an electric motor, the power source is operated as a generator to perform power generation. As a result, can do.

In the supercharger surplus power recovery device of the 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 flow path at the time of a high load, To the second hydraulic pump via the third flow path.

When the internal combustion engine is at a high load, for example, the first hydraulic pump is capable of generating a hydraulic pressure about twice the hydraulic pressure required for the operating device. Therefore, the controller supplies a part of the hydraulic pressure generated by the first hydraulic pump to the operating device via the second flow path at the time of a high load, and controls the remaining part of the hydraulic pressure generated by the first hydraulic pump through the third flow path 2 hydraulic pump, it is possible to effectively utilize the surplus exhaust energy of the internal combustion engine at the time of high load as the hydraulic pressure necessary for the operating device without power loss, and also to use the second hydraulic pump by the hydraulic pressure generated by the first hydraulic pump The rotation of the connected power source can be added.

For example, when the power source is an internal combustion engine, direct fuel economy can be improved. When the power source is an electric motor, the power source is operated as a generator to perform power generation. As a result, can do.

In the supercharger surplus power recovery device of the internal combustion engine, the second hydraulic pump is composed of a variable displacement type hydraulic pump, and the hydraulic mechanism allows supply of the hydraulic pressure to the operating device from the second hydraulic pump, A reverse function to prevent reverse flow of the hydraulic pressure from the downstream side of the first hydraulic pump to the second hydraulic pump and a reverse function to forcibly reverse the hydraulic pressure to the second hydraulic pump from the downstream side of the first hydraulic path And the second flow path is formed such that its operating device side is connected to the downstream side of the first check valve mechanism of the first flow path and the third check valve mechanism is formed by connecting the third check valve mechanism with the third check valve mechanism, It is preferable that the flow path is formed by connecting the second hydraulic pump side to the downstream side of the first check valve mechanism of the first flow path.

With the hydraulic mechanism having such a configuration, the controller can turn off the reverse release function of the first check valve mechanism, so that the second hydraulic pump can supply the hydraulic pressure to the operating device of the internal combustion engine, The hydraulic pressure generated by the pump can be supplied to the operating device of the internal combustion engine. Since the second hydraulic pump is composed of the variable displacement type hydraulic pump, the controller turns on the reverse release function of the first check valve mechanism to supply the hydraulic pressure generated by the first hydraulic pump to the second pump The rotation of the second hydraulic pump composed of the variable displacement type hydraulic pump, that is, the rotation of the power source to which the second hydraulic pump is connected, can be added.

That is, the hydraulic pressure mechanism can be simplified by the above-described configuration. Further, in the variable displacement type hydraulic pump, the hydraulic pump can be normally rotated by the reverse mechanism of the hydraulic pressure from the usual discharge port by the variable mechanism.

In the supercharger surplus power recovery device of the internal combustion engine, it is preferable that the supercharger surplus power recovery device further comprises a fourth flow path formed in the hydraulic mechanism and supplying the hydraulic pressure from the second hydraulic pump to the first hydraulic pump.

In this manner, by additionally providing a fourth flow path formed in the hydraulic mechanism and supplying the hydraulic pressure from the second hydraulic pump to the first hydraulic pump, the hydraulic pressure generated by the second hydraulic pump is supplied through the fourth flow path 1 hydraulic pump, so that the supercharging capability of the supercharger can be increased by adding the rotation of the first hydraulic pump. Thus, even if the exhaust gas energy is insufficient and the supercharging is insufficient, can do.

In the supercharger surplus power recovery device of the internal combustion engine, the controller supplies the hydraulic pressure generated by the second hydraulic pump to the first hydraulic pump via the fourth flow path at the time of the bottom of the internal combustion engine, It is desirable to increase the supercharging capability of the supercharger.

As described above, the controller supplies the hydraulic pressure generated by the second hydraulic pump to the first hydraulic pump through the fourth flow path and increases the supercharging capability of the supercharger by adding the rotation of the first hydraulic pump to the low- , It is possible to carry out a sufficient supercharge for the internal combustion engine even in a case where the exhaust gas energy is insufficient and the supercharging shortage is likely to be insufficient.

The supercharger surplus power recovery device of the internal combustion engine further includes a third flow path formed in the hydraulic mechanism and supplying hydraulic pressure to the second hydraulic pump from the first hydraulic pump, Wherein the hydraulic mechanism includes a function of inhibiting the supply of hydraulic pressure to the second hydraulic pump from the first hydraulic pump and preventing the reverse flow of the hydraulic pressure from the second hydraulic pump to the first hydraulic pump, And a second check valve mechanism having a throttle releasing function for forcibly allowing the second hydraulic pump to reverse the hydraulic pressure to the first hydraulic pump under the control of the controller is provided in the third flow path, Is preferably composed of the third flow path.

In this way, it is possible to further include a third flow path disposed in the hydraulic mechanism and supplying the hydraulic pressure from the first hydraulic pump to the second hydraulic pump, wherein the first hydraulic pump is a variable displacement type hydraulic pump, A second hydraulic pump for supplying hydraulic pressure to the second hydraulic pump from the first hydraulic pump and a reverse function for preventing reverse flow of the hydraulic pressure from the second hydraulic pump to the first hydraulic pump, A second check valve mechanism having a check valve releasing function that allows a reverse flow of the hydraulic pressure to the first hydraulic pump from the first hydraulic pump is provided in the third flow path and the fourth flow path is made of the third flow path, The hydraulic pressure generated by the second hydraulic pump can be supplied to the first hydraulic pump through the third flow path, whereby the rotation of the supercharger connected to the first hydraulic pump is performed. Can.

That is, the hydraulic pressure mechanism can be simplified by the above-described configuration. In addition, as described above, in the variable displacement hydraulic pump, the hydraulic pump can be charged by reverse flow of the hydraulic pressure from the usual discharge port by the variable mechanism.

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

By providing 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 in this way, the supply of hydraulic pressure to the operating device from the first hydraulic pump , It is possible to prevent both the supply of the hydraulic pressure from the first hydraulic pump to the second hydraulic pump and the supply of the hydraulic pressure from the second hydraulic pump to the first hydraulic pump.

The supercharger surplus power recovery device of the internal combustion engine of the present invention includes an internal combustion engine in which an operating device for operating an engine is electronically controlled via an oil pressure, A first hydraulic pump connected to the turbocharger to be rotationally driven by the turbocharger to generate the hydraulic pressure, and a hydraulic mechanism for supplying the hydraulic pressure to the operating device of the internal combustion engine to operate the internal combustion engine A second hydraulic pump connected to a power source for generating a rotational power and rotatably driven by the power source and supplying hydraulic pressure to the operating device via a hydraulic mechanism, and a second hydraulic pump connected to the hydraulic mechanism, the first hydraulic pump, And a controller that is arranged in the hydraulic mechanism to supply hydraulic pressure to the operating device from the second hydraulic pump, A supercharger surplus power recovery device for an internal combustion engine having one flow path, the supercharger surplus power recovery device comprising a second flow path formed in the hydraulic mechanism and supplying hydraulic pressure to the operating device from the first hydraulic pump.

Alternatively, the supercharger surplus power recovery device of the internal combustion engine of the present invention comprises an internal combustion engine in which an operating device for operating the engine is electronically controlled via an oil pressure, and a supercharger surplus power recovery device which is disposed in the exhaust gas path of the internal combustion engine, A turbine rotatably driven to supply supercharged air to the internal combustion engine; a turbine rotatably driven by the exhaust gas, the turbine being disposed in parallel with the supercharger in the exhaust gas passage; A hydraulic pump connected to a power source for generating a rotational power, rotatably driven by the prime mover, and operable to apply hydraulic pressure to the operating device via a hydraulic device; A second hydraulic pump to supply the hydraulic pressure to the first hydraulic pump, And a first flow path formed in the hydraulic mechanism and supplying hydraulic pressure to the operating device from the second hydraulic pump, characterized in that the supercharger surplus power recovery device is arranged in the hydraulic mechanism and is operated from the first hydraulic pump And a second flow path for supplying hydraulic pressure to the device.

Therefore, in the internal combustion engine in which the operating 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 the redundant arrangement of the hydraulic devices can be eliminated Therefore, it is possible to achieve a remarkable cost reduction and an easy design.

1 is a block diagram showing an example of a supercharger surplus power recovery device for an internal combustion engine according to the present invention.
Fig. 2 is a circuit diagram showing the flow of the hydraulic circuit of the internal combustion engine of Fig. 1 at the time of low load; Fig.
Fig. 3 is a circuit diagram showing the flow of the hydraulic circuit of the internal combustion engine of Fig. 1; Fig.
4 is a circuit diagram showing the flow of the hydraulic circuit at the time of high load of the internal combustion engine of Fig.
5 is a block diagram showing a supercharger surplus power recovery device of an internal combustion engine different from that of FIG.
Fig. 6 is a partial block diagram showing a supercharger surplus power recovery device of an internal combustion engine different from that of Figs. 1 and 5. Fig.
7 is a block diagram showing a supercharger surplus power recovery device of a conventional internal combustion engine.

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment for implementing a supercharger surplus power recovery device of an internal combustion engine according to the present invention will be described in detail with reference to Figs. 1 to 6. Fig.

1 shows a low speed diesel engine (a power source, an internal combustion engine) for propulsion mounted on a ship as an example. The engine 1 has an exhaust valve, a fuel injection valve An electronic control engine in which an operating device such as a valve is electronically controlled via an oil pressure and a turbocharger 5 for rotatingly driven by the exhaust gas and supplying supercharged air to the engine 1. [

The turbocharger 5 is composed of a compressor 6 and a turbine 7. The compressor 6 and the turbine 7 are connected to each other by a rotary 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. [ As a result, the air supply density of the engine 1 is increased, and the output of the engine is improved.

Further, the turbocharger 5 is not necessarily limited to the single stage. Further, the engine 1 is not limited to the marine engine, and the type is not limited to the low-speed diesel engine. Natural gas, gas engines such as city gas, and any other type of electronic control engine.

1, the transmission 9 is connected to the rotary shaft 8 of the turbocharger 5, and the variable displacement first hydraulic pump 10 is connected to the transmission 9. As shown in Fig. A transmission 3 is connected to one end of a 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 may be directly connected to the crankshaft 2 of the engine 1 without forming the transmission 3. [ 1, each of the first hydraulic pump 10 and the second hydraulic pump 11 described above is only one, but may be a plurality of pumps.

The first hydraulic pump 10 and the second hydraulic pump 11 are mounted in the hydraulic mechanism 20. In the hydraulic mechanism 20, one discharge port 11a of the second hydraulic pump 11 is connected to the flow path 21, and the check valve 31, the flow path 22, the check valve 32, 23 in this order, and is connected to the control circuit of the operating device of the above-described engine 1 to supply the hydraulic pressure. The first flow path is formed by the flow paths 21, 22, The other discharge port 11b of the second hydraulic pump 11 is connected to one discharge port 10b of the first hydraulic pump 10 via a flow path 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 interposed in this order, Can be connected to the control circuit of the operating device 51 of the engine 1 to supply the hydraulic pressure. The oil passage 22 is connected to one of the discharge ports 11a of the second hydraulic pump 11 via the check valve 31 and the oil passage 21 in this order in a manner branched from the oil passage 27 .

The discharge ports 10a and 10b of the first hydraulic pump 10 described above and the discharge ports 11a and 11b of the second hydraulic pump 11 are all provided as discharge ports. Actually, however, as will be described later, one of them serves as a discharge port of the hydraulic pressure and the other serves as an inlet of the hydraulic pressure according to the operating state. However, in the supercharger surplus power recovery device of this internal combustion engine, . A third flow path is formed by the flow paths 26, 27, 22 and 21 and a fourth flow path is formed by the flow paths 21, 22, 27, Respectively.

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 configured such that the electronic switching valve 41 is switched under the control of the controller 50 to forcibly change the flow path 21 from the flow path 22 to the flow path 21 for the second hydraulic pump 11 And has a reverse release function that allows reverse flow of the hydraulic pressure.

The check valve 31 permits supply of the hydraulic pressure to the control circuit of the operating device 51 via the flow path 21 from the second hydraulic pump 11, A normal reverse function for preventing the reverse flow of the hydraulic pressure from the oil passage 22 to the second hydraulic pump 11 acts.

On the other hand, when the disengagement releasing function is ON, as described above, the check valve 31 is forcibly opened to allow the reverse flow of the hydraulic pressure from the oil passage 22 to the second oil pressure pump 11. An accumulator 45 is disposed between the second hydraulic pump 11 and the check valve 31 to absorb the fluctuation of the hydraulic pressure caused by a marine wave, an exhaust valve drive, fuel injection, or the like.

In addition, the check valve 36 is formed integrally with the electromagnetic switching valve 42 to form the second check valve mechanism 35. The second check valve mechanism 35 is configured such that the electronic switching valve 42 is switched under the control of the controller 50 to force the flow path 27 from the flow path 26 to the flow path 26, And has a reverse release function that allows reverse flow of the hydraulic pressure.

The check valve 31 is connected to the control circuit of the operating device 51 via the oil line 26 from the first hydraulic pump 10 and the supply of the hydraulic pressure to the check valve 31 And also functions as a normal reverse function for preventing the reverse flow of the oil pressure from the oil passage 27 to the oil passage 26, that is, the first hydraulic pump 10. The check valve 31 is forcibly opened to allow the oil pressure from the oil passage 27 to the oil passage 26, that is, the oil pressure to the first hydraulic pump 10, as described above, Backflow is allowed.

Closing valve 44 is disposed between the flow path 26 and the flow path 24 so that the hydraulic pressure of the flow path 26 is drained to the flow path 24 and the flow path 26 Can be opened. The flow path 26, the electromagnetic on-off valve 44, and the flow path 24 constitute a drain mechanism.

The controller 50 detects the intake temperature of the air supply, the air supply pressure on the downstream side of the turbocharger 5, and the like based on the detected air supply pressure, the suction temperature, and the like The first hydraulic pump 10, the second hydraulic pump 11, the electromagnetic switching valves 41 and 42, the electromagnetic switching valve 44, and the like. The controller 50 also controls the first hydraulic pump 10, the second hydraulic pump 11, the electromagnetic switching valves 41 and 42, and the electromagnetic opening / closing valve (not shown) by using parameters other than the above- 44) may be controlled.

Next, the operation of the supercharger surplus power recovery device of the internal combustion engine will be described. The controller 50 activates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in Fig. 2 to turn OFF the inhibition release function of the first check valve mechanism 30 At the same time, the electromagnetic switching valve 42 of the second check valve mechanism 35 is operated to turn off the non-return canceling function of the second check valve mechanism 35. In addition, the electromagnetic opening / closing valve 44 is closed.

The check valve 31 prohibits the reverse flow of the hydraulic pressure from the flow path 22 to the flow path 21 and the check valve 36 prohibits the reverse flow of the hydraulic pressure from the flow path 27 to the flow path 26 . The controller 50 rotates the electric motor 52 and generates a hydraulic pressure required for starting by the hydraulic pump 53 and supplies the generated hydraulic pressure to the control circuit of the operating device 51. [ At this time, the check valve 32 also prevents the reverse flow of the hydraulic pressure from the flow path 23 to the flow path 22. [

Next, the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 during a low load of the internal combustion engine, for example, from startup to load 35% The electronic control valve 42 of the second check valve mechanism 35 is operated so that the disable function of the check valve mechanism 30 is turned OFF and the electronic control valve 42 of the second check valve mechanism 35 is turned ON, . For this reason, the check valve 36 is forcibly opened to permit the reverse flow of the hydraulic pressure from the flow path 27 to the flow path 26.

The oil pressure generated by the second hydraulic pump 11 flows through the oil passage 21, the check valve 31, the oil passage 22, the check valve 32 and the oil passage 23 in this order, (51). The oil pressure generated by the second hydraulic pump 11 is supplied to the oil passage 21 through the check valve 31, the oil passage 22, the oil passage 27, the check valve 36 forcibly opened by the valve, The first hydraulic pump 10 is supplied to the discharge port 10a of the first hydraulic pump 10 in this order and the rotation of the first hydraulic pump 10 is added.

That is, by the oil pressure generated by the second hydraulic pump 11, the rotation of the turbocharger 5 connected to the first hydraulic pump 10 is added, so that the supercharging of the low load that is likely to be short of the supercharger is appropriately performed . In addition, the first variable displacement hydraulic pump 10 can also power the supercharger 5 by the variable mechanism by the reverse flow of the hydraulic pressure from the discharge port 10a.

The controller 50 reads and inputs the intake temperature of the air supply detected by the sensor, the air supply pressure to the air supply on the downstream side of the turbocharger 5, and the like. In addition, the necessary power for adding the turbocharger 5 is set for each engine load in the controller 50. The controller 50 appropriately changes the capacity of the first hydraulic pump 10 of the variable capacity type on the basis of the supply pressure, the suction temperature, and the like, and controls the power for adding the supercharger 5.

Next, the controller 50 activates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in Fig. 3 so as to switch between the first state (first state) and the second state Off function of the check valve mechanism 30 is turned off and the electromagnetic on-off valve 44 is opened.

When the electromagnetic opening / closing 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 via the electromagnetic opening / closing valve 44, There is no possibility that it flows through the valve 36 and flows into the high-pressure flow path 27. In this case, the first hydraulic pump 10 rotationally driven by the turbocharger 5 is in a no-load operation, but the hydraulic pressure of a certain pressure is discharged for cooling the system.

On the other hand, the hydraulic pressure generated by the second hydraulic pump 11 is supplied to 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 And is supplied to the control circuit. The hydraulic pressure generated by the second hydraulic pump 11 is relatively high but the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in Fig. The oil pressure of the oil passage 27 does not flow through the check valve 36 and flows into the oil passage 26 due to the normal non-return function of the check valve 36. As a result,

As described above, when the internal combustion engine is heavy, for example, when the load is in the range of 35 to 50%, the first hydraulic pump 10 becomes no-load operation and the operating device 51 receives the hydraulic pressure only by the second hydraulic pump 11 . When it is necessary to cut off the interlocking of the hydraulic pressure between the first hydraulic pump 10 on the side of the turbocharger 5 and the second hydraulic pump 11 on the side of the engine 1, , The same operation as described above is performed.

Next, when the internal combustion engine is at a high load, for example, at a load of 50% or more, the controller 50 operates the electromagnetic switching valve 41 of the first check valve mechanism 30 shown in Fig. The electronic control valve 42 of the second check valve mechanism 35 is operated so that the disable function of the check valve mechanism 30 is turned OFF and the electronic control valve 42 of the second check valve mechanism 35 is turned OFF . In addition, the electromagnetic opening / closing valve 44 is closed.

Therefore, the check valve 31 of the first check valve mechanism 30 is forcibly opened to permit the reverse flow of hydraulic pressure from the oil line 22 to the oil line 21, that is, the second oil pressure pump 11 . The check valve 36 of the second check valve mechanism 35 also permits the flow of the hydraulic pressure from the flow path 26 to the flow path 27 rather than the normal check function.

The hydraulic pressure generated by the first hydraulic pump 10 is supplied to the first hydraulic pump 10 via 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 supplied to the control circuit of the device (51). 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.

When the engine 1 is at a high load, the first hydraulic pump 10 can generate an oil pressure of, for example, about twice the hydraulic pressure required for the operating device 51. Therefore, the oil pressure generated by the first hydraulic pump 10 is supplied to the hydraulic pump 10 in the order of this sequence (check valve), the check valve 36, the flow path 27, the flow path 22, the check valve 31, And is also supplied to the discharge port 11a of the second hydraulic pump 11 to apply the rotation of the second hydraulic pump 11. [

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

As shown in Fig. 5, the second hydraulic pump 11 may be connected to an electric motor (power source) 54 that generates rotational power in place of the engine, like 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 rotation. Therefore, the rotational speed control of the electric motor 54 by the above-described hydraulic mechanism 20 or the like is not particularly required.

When the engine is at a high load, the surplus hydraulic pressure supplied from the first hydraulic pump 10 causes the electric motor 54 to operate as a generator to generate electric power, and this electric power is supplied to the electric power system. The power required for a ship or the like is normally generated by a generator rotationally driven by an engine, and consequently, fuel economy of the engine can be improved. In addition, since the operation of the supercharger surplus power recovery device of the internal combustion engine at the time of low load, heavy load, and high load of the engine is the same as that of the engine 1 described above, the description is omitted.

A power turbine 55 is arranged in parallel with the turbocharger 5 in the exhaust gas passage 4 of the engine via a flow rate regulating valve 56, 1 hydraulic pump 10 may be connected. In this case, operation of the supercharger surplus power recovery device of the internal combustion engine at the time of heavy engine load and high load is the same as that of the engine 1 described above. However, the rotation of the supercharger 5 can not be directly added via the first hydraulic pump 10 by the hydraulic pressure generated by the second hydraulic pump 11 at the bottom of the engine due to its structure. Except for this, it is the same as that in the case of the supercharger 5 described above, and the description is omitted.

The first hydraulic pump described above is not necessarily a variable capacity type, but may be a fixed capacity type. When the fixed capacity type is employed, a considerable space saving can be achieved. However, when the first hydraulic pump is of the fixed capacity type, since the pump can not be charged due to the reverse flow of the hydraulic pressure from the discharge port, the supercharger 5, Can not be added.

Therefore, in order to perform the same operation as that of the supercharger surplus power recovery device of the internal combustion engine at the time of low load, heavy load, and high load of the engine 1, It is necessary to partially change the configuration of the hydraulic mechanism 20 and the like as it is possible to flow into the pump. The description is omitted because it is the same as that in the case of the second variable displacement hydraulic pump 10 described above.

As described above, the supercharger surplus power recovery device of the present internal combustion engine is connected to the turbocharger 5 or the power turbine 55, and is driven by the turbocharger 5 or the power turbine 55 to generate the hydraulic pressure The hydraulic pump 10 can directly supply the hydraulic pressure to the operating device 51 of the engine 1 without interposing the engine 1 or the motor 52 as the power source.

The second hydraulic pump, which is rotationally driven by this power source and that supplies hydraulic pressure to the operating device via the hydraulic mechanism, is required to supply a large amount of hydraulic pressure required for operation to the operating device at the time of high load of the internal combustion engine do. Therefore, the required capacity or the number of the second hydraulic pump is determined according to the maximum discharge amount. However, in the supercharger surplus power recovery apparatus of this internal combustion engine, especially when the maximum discharge amount is required, there is still surplus even if the supercharger 5 is rotated by the exhaust energy, so that the first hydraulic pump 10 And the hydraulic pressure is directly supplied to the operating device 51 via the second flow path.

Therefore, the required capacity or the number of the second hydraulic pump 11 can be reduced by the supply amount of the hydraulic pressure from the first hydraulic pump 10, and the cost can be reduced. It is also possible to reduce the power loss, which increases with the discharge amount, as the required capacity or the number of the second hydraulic pump 11 decreases.

It should be noted that the hydraulic pump of the supercharger surplus power recovery device connected to the crankshaft of the engine which was necessary in the supercharger surplus power recovery device of the conventional internal combustion engine can be excluded, All of the power loss can be eliminated. It is also possible to exclude all of the hydraulic mechanisms required for adding the hydraulic pump connected to the crankshaft of the engine by the conventional first hydraulic pump.

Therefore, there is no need to redundantly install the hydraulic pump, the valves, the safety device, the piping, and the like, which constitute the hydraulic mechanism of the supercharger surplus power recovery device of the conventional internal combustion engine, so that a considerable cost reduction can be achieved. Further, in the vicinity of the internal combustion engine in which a large number of swirling flows are arranged and formed, the overlapping arrangement of the surplus power recovery device of the supercharger and the hydraulic mechanism of the engine operation device becomes unnecessary, and designing can be facilitated.

As described above, at the time of high load of the engine 1, the first hydraulic pump 10 can generate, for example, about two times the hydraulic pressure 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 a high load, 10) is supplied to the second hydraulic pump 11, the surplus exhaust energy of the engine 1 at the time of high load can be supplied to the operating device 51 as the required hydraulic pressure without the power loss by the hydraulic pump And the rotation of the power source to which the second hydraulic pump 11 is connected can be added by the hydraulic pressure generated by the first hydraulic pump 10. [

Therefore, when the power source is the engine 1, for example, direct fuel economy can be improved. When the power source is the electric motor 52, the power source is operated as a generator to perform power generation. As a result, The fuel efficiency of the entire engine can be improved.

Further, the supercharger surplus power recovery device of the above-described internal combustion engine is merely an example, and various modifications are possible based on the object of the present invention, and they are not excluded from the scope of the present invention. In the supercharger surplus power recovery device of the above-described internal combustion engine, the load is 35% to 35%, the load is 35 to 50%, and the load is 50% or more. However, The type of the internal combustion engine, the type of use, and the like. However, the present invention is not limited thereto.

Industrial availability

In the supercharger surplus power recovery device of the internal combustion engine of the present invention, if the operating device for operating the engine is electronically controlled via the hydraulic pressure, and if it is an internal combustion engine having a turbocharger, It is not limited to an engine, and can be widely used in all types of internal combustion engines and in all types of internal combustion engines.

1: Engine (power source, internal combustion engine)
2: Crankshaft
3: Transmission
4: With exhaust gas
5: supercharger
6: Compressor
7: Turbine
8:
9: Transmission
10: First hydraulic pump
10a, 10b, 11a, 11b:
11: Second hydraulic pump
20: Hydraulic equipment
21, 22, 23, 24, 26, 27:
30: First check valve mechanism
31, 32, 36: check valve
35: second check valve mechanism
41, 42: Electronic switching valve
44: Electronic opening / closing valve
45: Accumulator
50: Controller
51: Operating device
52: Electric motor
53: Hydraulic pump
54: electric motor (power source)
55: Power turbine
56: Flow regulating valve
100: Internal combustion engine
101: supercharger surplus power recovery device
102: engine actuating device
103: Hydraulic pump

Claims (10)

An internal combustion engine (1) comprising: an internal combustion engine (1) in which an operating device (51) for operating an engine is electronically controlled via an oil pressure; A first hydraulic pump 10 connected to the turbocharger to be rotationally driven by the turbocharger to generate a hydraulic pressure, and a second hydraulic pump 10 for supplying hydraulic pressure to the operating device of the internal combustion engine, A hydraulic power source (20) for operating the internal combustion engine by operating an operating device, and a power source (1, 54) for generating a rotational power, which is rotationally driven by the power source, A controller (50) for controlling the operation of the first hydraulic pump, the second hydraulic pump, and the hydraulic mechanism, and a second hydraulic pump A supercharger surplus power recovery device for an internal combustion engine, comprising first fluid paths (21, 22, 23) arranged in a fluid pressure mechanism and supplying hydraulic pressure from the second hydraulic pump to the operating device, And a second flow path (26, 27, 22, 23) for supplying hydraulic pressure to the operating device from the first hydraulic pump. An internal combustion engine, comprising: an internal combustion engine in which an operating device for operating an engine is electronically controlled via an oil pressure; and an engine (1) disposed in an exhaust gas passage (4) of the internal combustion engine, A turbine (55) rotatably driven by the exhaust gas of the internal combustion engine and arranged in parallel with the turbocharger in the exhaust gas passage; a turbine (55) connected to the turbine and rotated by the turbine A hydraulic device (20) for operating the internal combustion engine by supplying hydraulic pressure to the operating device of the internal combustion engine to operate the operating device, and a second hydraulic pump Which is connected to the power source for supplying the hydraulic pressure to the operating device via the hydraulic mechanism and is rotationally driven by the power source, A first hydraulic pressure pump, a second hydraulic pump, and a controller for controlling operations of the first hydraulic pump, the second hydraulic pump, and the hydraulic mechanism, and a second hydraulic pump disposed in the hydraulic mechanism for supplying hydraulic pressure to the operating device from the second hydraulic pump. Wherein the supercharger surplus power recovery device of the internal combustion engine is provided with a second flow path which is disposed in the hydraulic pressure mechanism and supplies the hydraulic pressure from the first hydraulic pressure pump to the operating device, Power recovery device. 3. The method according to claim 1 or 2,
The controller 50 controls the hydraulic pressure generated by the first hydraulic pump 10 at the time of high load of the internal combustion engine 1 via the second flow paths 26, 27, 22, 51) of the internal combustion engine. 4. The method according to any one of claims 1 to 3,
(26, 27, 22, 21) arranged in the hydraulic mechanism (20) and supplying hydraulic pressure to the second hydraulic pump (11) from the first hydraulic pump Wherein the supercharger surplus power recovery device of the internal combustion engine. 5. The method of claim 4,
The controller 50 controls a part of the hydraulic pressure generated by the first hydraulic pump 10 during the high load of the internal combustion engine 1 via the second flow paths 26, 27, 22, And supplies the remainder of the hydraulic pressure generated by the first hydraulic pump to the second hydraulic pump 11 via the third flow paths 26, 27, 22, The supercharger surplus power recovery device of the internal combustion engine. The method according to claim 4 or 5,
The second hydraulic pump 11 is composed of a variable capacity type hydraulic pump and the hydraulic mechanism 20 allows supply of the hydraulic pressure to the operating device 51 from the second hydraulic pump, A reverse function of preventing reverse flow of the hydraulic pressure to the second hydraulic pump from the downstream side of the first oil passages (21, 22, 23), and a reverse function of forcibly controlling the reverse side of the first oil passage Wherein the first oil passage (26, 27, 22, 23) is provided with a first check valve mechanism (30) having a check valve releasing function that allows reverse flow of hydraulic pressure to the second hydraulic pump from the first oil passage , The operating device side is formed to be connected to the downstream side of the first check valve mechanism of the first flow passage, and the third flow path (26, 27, 22, 21) The first check valve mechanism is connected to the downstream side of the first check valve mechanism, Supercharger excess power recovery system for an internal combustion engine characterized in that the. The method according to claim 1,
And further includes fourth flow paths 21, 22, 27, 26 arranged in the hydraulic mechanism 20 for supplying hydraulic pressure to the first hydraulic pump 10 from the second hydraulic pump 11 Wherein the supercharger surplus power recovery device of the internal combustion engine. 8. The method of claim 7,
The controller (50) controls the hydraulic pressure generated by the second hydraulic pump (11) at the bottom of the internal combustion engine (1) through the fourth flow paths (21, 22, 27, 26) To the pump (10) to increase the supercharging capability of the turbocharger (5) by adding the rotation of the first hydraulic pump to the supercharger surplus power recovery device of the internal combustion engine. 9. The method according to claim 7 or 8,
Further comprising third flow paths (26, 27, 22, 21) arranged in the hydraulic mechanism (20) for supplying hydraulic pressure from the first hydraulic pump (10) to the second hydraulic pump (11) Wherein the first hydraulic pump comprises a variable displacement type hydraulic pump, the hydraulic mechanism permits supply of the hydraulic pressure to the second hydraulic pump from the first hydraulic pump, A reverse function for preventing reverse flow of the hydraulic pressure to the first hydraulic pump and a reverse release function for forcibly allowing reverse flow of the hydraulic pressure to the first hydraulic pump from the second hydraulic pump under the control of the controller Characterized in that a second check valve mechanism (35) is provided in the third flow path and the fourth flow path (21, 22, 27, 26) comprises the third flow path. Device. 10. The method according to any one of claims 1 to 9,
The hydraulic mechanism 20 includes a drain mechanism 26, 44, 24 for draining the hydraulic pressure generated by the first hydraulic pump 10 under the control of the controller 50 and returning the hydraulic pressure to the first hydraulic pump And the supercharger surplus power recovery device of the internal combustion engine.

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