JP2007211621A - Supercharging device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a small-sized and highly efficient supercharging device which quickly increases power taken out from an engine. <P>SOLUTION: A hydraulic pump 22 discharges a hydraulic oil utilizing the power of the engine 10 or the power of a vehicle when a clutch 24 is engaged. An accumulator 28 stores the energy of the hydraulic oil discharged from the hydraulic pump 22. When a stop valve 30 is open, the hydraulic motor 32 drives a turbocharger 16 utilizing the energy of the hydraulic oil stored in the accumulator 28 to assist the supercharging by the turbocharger 16. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a supercharging device that pressurizes engine intake gas capable of driving a load.

  Related arts of a supercharging device that pressurizes intake gas of an engine (internal combustion engine) are disclosed in Patent Documents 1 and 2 below. The supercharging device of Patent Document 1 is a hydraulically driven supercharging device that drives a hydraulic turbine by hydraulic pressure. More specifically, hydraulic oil pressurized by a hydraulic pump driven by an internal combustion engine is supplied to the hydraulic turbine via a hydraulic pipe, and rotates the hydraulic turbine. The rotation of the hydraulic turbine is increased by a speed increasing mechanism built in the hydraulic turbine, and rotationally drives the supercharged impeller. The intake gas of the internal combustion engine is pressurized by the rotational drive of the supercharged impeller.

  The supercharging device disclosed in Patent Document 2 is a so-called electric assist turbocharger including an electric motor capable of rotationally driving a compressor impeller that compresses intake air. More specifically, the supercharging device of Patent Document 2 is configured to rotationally drive a compressor impeller by a turbine impeller rotated by exhaust of the engine, and compress intake air by the rotational drive of the compressor impeller. Furthermore, a regenerative generator, a battery that can be charged using the regenerative power collected by the regenerative generator, a turbo motor that can rotationally drive the compressor impeller using the power charged in the battery, and regenerative power generation And an inverter for driving the turbo electric motor.

JP-A-8-200083 JP 2004-270602 A

  In Patent Document 1, a so-called supercharger is realized in which supercharging is performed by converting the driving force of the engine into hydraulic pressure and rotationally driving the hydraulic turbine with this hydraulic pressure. However, since the power necessary for rotational driving (supercharging) of the hydraulic turbine is directly taken out from the engine drive shaft, a power loss always occurs, resulting in a decrease in engine efficiency.

  In Patent Document 2, an electric motor is used to assist supercharging by a turbocharger, and a battery and an inverter are provided for supplying electric power to the electric motor. However, if the power that can be generated by the motor is increased in order to quickly increase the supercharging pressure, the physique of the motor increases, and the physique of the battery and the inverter also increases. As a result, the supercharger is increased in size and cost.

  An object of the present invention is to provide a small and highly efficient supercharging device capable of quickly increasing the power that can be extracted from an engine.

  The supercharging device according to the present invention employs the following means in order to achieve the above-described object.

  A supercharging device according to the present invention is a supercharging device that pressurizes intake gas of an engine capable of driving a load, and supercharges the engine by using energy of engine exhaust gas. A hydraulic pump capable of discharging hydraulic oil using engine power or load power, a pressure accumulator that stores energy of hydraulic oil discharged from the hydraulic pump, and hydraulic oil stored in the pressure accumulator And a hydraulic motor capable of driving the supercharger using the energy of the above.

  In the present invention, since the supercharger can be driven using the energy of hydraulic oil stored in advance in the pressure accumulator, it is necessary to increase the power to be extracted from the engine by supercharging. The supercharger can be driven efficiently without being consumed for driving the supercharger. And since the supercharger is driven using hydraulic pressure with high output density, the supercharging pressure can be increased quickly and the supercharger can be reduced in size compared with the case where the supercharger is driven by an electric motor. Can be realized. Therefore, according to the present invention, the power that can be extracted from the engine can be quickly increased, and the turbocharger can be reduced in size and efficiency.

  In one aspect of the present invention, a power interrupting mechanism that interrupts power between a power transmission path from an engine to a load and the hydraulic pump is provided, so that the driving state of the hydraulic pump can be adjusted by the power interrupting mechanism. . In this aspect, when the load is decelerated, the power transmission path and the hydraulic pump are connected by a power interruption mechanism, so that the hydraulic pump can be driven using the regenerative energy of the load, and the hydraulic oil energy is reduced. It can be stored efficiently in the pressure accumulator.

  In one aspect of the present invention, the drive torque of the hydraulic pump can be reduced by providing a first speed increasing mechanism capable of increasing the speed of power extracted through a power transmission path from the engine to a load and transmitting the speed to the hydraulic pump. Since it can be made small, the hydraulic pump can be miniaturized and the mountability can be improved. Furthermore, when the power interrupting mechanism is provided, the torque capacity of the power interrupting mechanism can be reduced by reducing the driving torque of the hydraulic pump, and the power interrupting mechanism can be downsized and mounted. .

  In one aspect of the present invention, a hydraulic motor is provided by a supercharger by including a one-way power transmission mechanism that allows power transmission from the hydraulic motor to the supercharger and cuts power transmission from the supercharger to the hydraulic motor. It can be prevented from being driven.

  In one aspect of the present invention, the second speed increasing mechanism capable of increasing the power of the hydraulic motor and transmitting it to the supercharger is provided, so that the rotational speed of the hydraulic motor can be increased without significantly increasing the speed. A rotating supercharger can be driven.

  In one aspect of the present invention, the drive state of the hydraulic motor can be adjusted by the adjustment valve by including the adjustment valve that adjusts the supply state of the hydraulic oil from the pressure accumulator to the hydraulic motor.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out the present invention (hereinafter referred to as embodiments) will be described with reference to the drawings.

  FIG. 1 is a diagram showing a schematic configuration of a vehicle drive system including a supercharging device according to an embodiment of the present invention. An output shaft 10-1 of the engine (internal combustion engine) 10 is connected to an input shaft of the transmission 14, and the power generated by the engine 10 is shifted by the transmission 14. The output shaft of the transmission 14 is connected to the drive wheels 19, and the power changed by the transmission 14 is transmitted to the drive wheels 19 and used for driving the vehicle. As described above, the power generated by the engine 10 is used for driving a load such as driving a vehicle.

  The turbocharger (turbocharger) 16 includes a turbine 18 and a compressor 20 that are connected via a shaft (rotary shaft) 17. The turbine 18 is rotationally driven using the energy of the exhaust gas of the engine 10. The compressor 20 pressurizes the intake gas of the engine 10 by being rotationally driven together with the turbine 18.

  In this way, the turbocharger 16 performs supercharging by pressurizing the intake gas of the engine 10 using the energy of the exhaust gas of the engine 10, but when the engine 10 has a low rotation speed, the compressor 20 (turbine Since the rotational speed of 18) is also low, the pressure (supercharging pressure) of the intake gas output from the compressor 20 is also low. Even if the throttle opening (accelerator opening) is increased from this state, a time delay, so-called turbo lag, occurs until the number of rotations of the compressor 20 increases and the boost pressure increases. In the present embodiment, in order to suppress this turbo lag, supercharging by the turbocharger 16 is assisted using the energy of the hydraulic oil. Hereinafter, a configuration example for that purpose will be described.

  The hydraulic pump 22 can be rotationally driven by using the power of the engine 10 or the power of the vehicle, pumps up the hydraulic oil stored in the reservoir 23, gives energy to the hydraulic oil, and discharges it. Between the output shaft 10-1 of the engine 10 and the rotary shaft of the hydraulic pump 22, a speed increasing mechanism (first speed increasing mechanism) 26 and a clutch (electromagnetic clutch) 24 as a power interrupting mechanism are provided. ing. When the clutch 24 is released, no power is transmitted between the output shaft 10-1 of the engine 10 and the rotary shaft of the hydraulic pump 22. That is, the hydraulic pump 22 is not driven to rotate.

  On the other hand, when the clutch 24 is engaged, power is transmitted between the output shaft 10-1 of the engine 10 and the rotary shaft of the hydraulic pump 22. When the engine 10 generates power for driving the vehicle (drive wheels 19), a part of the power of the engine 10 is taken out by the output shaft 10-1 of the engine 10 and accelerated by the speed increasing mechanism 26. Then, the increased power is transmitted to the rotating shaft of the hydraulic pump 22, whereby the hydraulic pump 22 is driven to rotate. Further, when the vehicle is decelerated, a part of the power of the vehicle is taken out by the output shaft 10-1 of the engine 10 and accelerated by the speed increasing mechanism 26, and this increased power is applied to the rotating shaft of the hydraulic pump 22. By being transmitted, the hydraulic pump 22 is rotationally driven. However, the position for extracting the power transmitted to the hydraulic pump 22 is not limited to the output shaft 10-1 of the engine 10, and the power is transmitted at an arbitrary position on the power transmission path from the engine 10 to the drive wheels 19. It can be taken out and transmitted to the hydraulic pump 22. As described above, in the present embodiment, the hydraulic pump 22 is switched by disengaging the power between the power transmission path from the engine 10 to the drive wheel 19 and the hydraulic pump 22 by switching the release / engagement of the clutch 24. It is possible to perform the drive control. The power extracted through the power transmission path from the engine 10 to the drive wheel 19 can be increased by the speed increasing mechanism 26 and transmitted to the hydraulic pump 22.

  The accumulator 28 provided as a pressure accumulator stores the energy of the hydraulic oil discharged from the hydraulic pump 22. The pressure sensor 29 detects the pressure P of the hydraulic oil accumulated in the accumulator 28. An oil passage 25 for connecting the hydraulic pump 22 and the accumulator 28 allows the flow of hydraulic oil from the hydraulic pump 22 to the accumulator 28 and blocks the flow of hydraulic oil from the accumulator 28 to the hydraulic pump 22. A check valve 27 is provided. The check valve 27 prevents the backflow of hydraulic oil from the accumulator 28 to the hydraulic pump 22.

  The hydraulic motor 32 generates power using the energy of the hydraulic oil stored in the accumulator 28, and the turbocharger 16 (compressor 20) can be driven to rotate by this power. An oil passage 31 for connecting the accumulator 28 and the hydraulic motor 32 is provided with a stop valve 30 that adjusts the supply state of hydraulic oil energy from the accumulator 28 to the hydraulic motor 32. When the stop valve 30 is closed, the supply of hydraulic oil energy from the accumulator 28 to the hydraulic motor 32 is interrupted. That is, the hydraulic motor 32 is not driven to rotate. On the other hand, when the stop valve 30 is open, the supply of hydraulic oil energy from the accumulator 28 to the hydraulic motor 32 is allowed, and the hydraulic motor 32 is rotationally driven by supplying the hydraulic oil energy to the hydraulic motor 32. Is done. Thus, by controlling the supply state of the hydraulic oil energy from the accumulator 28 to the hydraulic motor 32 by opening / closing control of the stop valve 30, it is possible to perform drive control of the hydraulic motor 32.

  Between the rotating shaft of the hydraulic motor 32 and the shaft 17 of the turbocharger 16, a one-way clutch 34 as a one-way power interrupting mechanism and a speed increasing mechanism (second speed increasing mechanism) 36 are provided. FIG. 1 shows an example in which the one-way clutch 34 is disposed between the hydraulic motor 32 and the speed increasing mechanism 36. The one-way clutch 34 allows power transmission from the hydraulic motor 32 to the turbocharger 16 by its engagement, and cuts off power transmission from the turbocharger 16 to the hydraulic motor 32 by its release (idling). The speed increasing mechanism 36 can increase the speed of the power transmitted from the hydraulic motor 32 via the one-way clutch 34 and transmit it to the turbocharger 16. In this way, by transmitting the power of the hydraulic motor 32 to the turbocharger 16 and driving the compressor 20 to rotate, supercharging by the turbocharger 16 can be assisted (supercharging assist is performed). In addition, since the shaft 17 of the turbocharger 16 rotates at, for example, an ultra high rotation speed of 100,000 rpm or more, the speed increasing mechanism 36 here is, for example, a planetary roller (traction drive) in order to suppress vibration and noise. It is preferable to use a speed increasing mechanism of the formula.

  The electronic control unit 42 is configured as a microprocessor centered on a CPU, and includes a ROM that stores a processing program, a RAM that temporarily stores data, and an input / output port. The electronic control unit 42 includes a signal indicating a throttle opening A detected by a throttle opening sensor (not shown), a signal showing an engine rotation speed Ne detected by an engine rotation sensor (not shown), a turbine A signal indicating the turbine rotation speed Nt detected by the rotation sensor (not shown), a signal indicating the vehicle speed V detected by the vehicle speed sensor (not shown), and a signal indicating the pressure P of the accumulator 28 from the pressure sensor 29 Etc. are input through the input port. On the other hand, the electronic control unit 42 controls the release / engagement of the clutch 24 to control the hydraulic pump 22 by controlling the release / engagement of the clutch 24 and the hydraulic pressure by controlling the opening and closing of the stop valve 30. A hydraulic motor control signal or the like for controlling the drive of the motor 32 is output via the output port.

  Next, the operation of the drive system according to the present embodiment, particularly the operation for assisting supercharging by the turbocharger 16 will be described.

  When supplying hydraulic oil to the accumulator 28 (accumulating the pressure in the accumulator 28), the electronic control unit 42 engages the clutch 24 and connects the engine 10 to the drive wheels 19 as shown in FIG. And the hydraulic pump 22 are connected to rotate the hydraulic pump 22. An example of the conditions for engaging the clutch 24 (rotating the hydraulic pump 22) is when the vehicle is decelerated. When the vehicle is decelerated, the clutch 24 is engaged (the power transmission path from the engine 10 to the driving wheel 19 and the hydraulic pump 22 are connected), and as shown in FIG. Since the pump 22 can be rotationally driven, the hydraulic oil energy necessary for supercharging assistance (rotational driving of the hydraulic motor 32) can be stored in the accumulator 28 using regenerative energy. Here, when the hydraulic pump 22 is rotationally driven, a part of the power of the vehicle is increased by the speed increasing mechanism 26 and then transmitted to the hydraulic pump 22. However, when the pressure P of the accumulator 28 by the pressure sensor 29 is equal to or higher than the set value P1, the electronic control unit 42 determines that the hydraulic oil energy is sufficiently stored in the accumulator 28, and the vehicle is decelerated. Even if it exists, the clutch 24 is not engaged (the hydraulic pump 22 is not rotationally driven). The electronic control unit 42 can determine whether or not the vehicle is decelerating based on, for example, the time change rate dV / dt of the vehicle speed V and the brake operation amount B (detected by a sensor (not shown)).

  As shown in FIG. 2, when the stop valve 30 is closed, the supply of hydraulic oil from the accumulator 28 to the hydraulic motor 32 is stopped. Even if the turbocharger 16 is rotationally driven by the energy of the exhaust gas of the engine 10, power transmission from the turbocharger 16 to the hydraulic motor 32 is cut off by the release (idling) of the one-way clutch 34. At this time, supercharging assistance is not performed.

  On the other hand, when the supercharging assist is performed, the electronic control unit 42 opens the stop valve 30 and supplies the hydraulic oil energy stored in the accumulator 28 to the hydraulic motor 32 as shown in FIG. The motor 32 is rotationally driven. As the conditions for performing supercharging assist (opening the stop valve 30), for example, a condition that the throttle opening A is equal to or greater than a predetermined value A1 and the turbine speed Nt is lower than the predetermined value Nt1, or the throttle opening A is predetermined. The condition etc. which are more than value A1 and engine speed Ne is lower than predetermined value Ne1 can be mentioned. When the stop valve 30 is switched from the closed state to the open state, the hydraulic motor 32 is rotated by the energy of the hydraulic oil, and the rotational speed Nm of the hydraulic motor 32 increases. When the rotational speed Nm of the hydraulic motor 32 reaches Nt × γ (γ is a gear ratio of the speed increasing mechanism 36, γ <1), the released one-way clutch 34 is engaged, whereby the hydraulic motor After the power of 32 is increased by the speed increasing mechanism 36, the power is transmitted to the turbocharger 16, and the compressor 20 is rotationally driven by the power of the hydraulic motor 32. Thus, the intake gas of the engine 10 can be pressurized using the power of the hydraulic motor 32 in addition to the energy of the exhaust gas of the engine 10. That is, supercharging assistance can be performed.

  When the hydraulic oil energy stored in the accumulator 28 is released and the rotational speed Nm of the hydraulic motor 32 decreases, the engaged one-way clutch 34 is released. By releasing the one-way clutch 34, the rotational drive of the hydraulic motor 32 by the power of the turbocharger 16 (turbine 18) is prevented. When stopping the supercharging assist, the electronic control unit 42 closes the stop valve 30 to stop the supply of hydraulic oil from the accumulator 28 to the hydraulic motor 32. As the conditions for stopping the supercharging assist (closing the stop valve 30), for example, the condition that the turbine rotational speed Nt is equal to or higher than a predetermined value Nt2 (Nt2> Nt1), or the engine rotational speed Ne is equal to or higher than a predetermined value Ne2 ( A condition such as Ne2> Ne1) can be given.

  In the present embodiment described above, supercharging assistance can be performed by rotationally driving the turbocharger 16 (compressor 20) using the energy of hydraulic oil, so the pressure of the intake gas of the engine 10 (supercharging pressure) ) Can be increased quickly and turbo lag can be reduced. Since the compressor 20 can be rotationally driven (supercharging assist is performed) using the energy of the hydraulic oil stored in advance in the accumulator 28, the power extracted from the engine 10 by supercharging, such as during vehicle acceleration, can be obtained. When it is necessary to increase the amount, the supercharging assist can be efficiently performed without consuming a part of the power of the engine 10 for the supercharging assist. Therefore, the power that can be extracted from the engine 10 can be increased efficiently and promptly. In addition, since supercharging assistance is performed by using hydraulic pressure with high output density, the supercharging pressure can be increased quickly and the supercharging device can be downsized compared to a configuration in which supercharging assistance is performed by an electric motor. Can be realized.

  Further, in this embodiment, the clutch 24 is engaged at the time of deceleration of the vehicle (the hydraulic pump 22 is rotationally driven), so that the hydraulic oil energy necessary for supercharging assistance (rotational drive of the hydraulic motor 32) is supplied to the vehicle. The kinetic energy (regenerative energy) can be efficiently stored in the accumulator 28. Therefore, supercharging assistance using the energy of hydraulic oil can be performed efficiently.

  Further, in the present embodiment, the driving torque of the hydraulic pump 22 can be reduced by transmitting the power used for rotational driving of the hydraulic pump 22 to the hydraulic pump 22 after being accelerated by the speed increasing mechanism 26. As a result, the hydraulic pump 22 can be reduced in size, and the mountability can be improved. Furthermore, by reducing the driving torque of the hydraulic pump 22, the torque capacity of the clutch 24 can be reduced, and the clutch 24 can be downsized and mounted.

  In the present embodiment, the power of the hydraulic motor 32 is increased by the speed increasing mechanism 36 and then transmitted to the turbocharger 16 so that the turbo motor 16 rotates at high speed without significantly increasing the rotation speed of the hydraulic motor 32. The charger 16 (compressor 20) can be driven to rotate.

  Further, in the present embodiment, power transmission from the turbocharger 16 to the hydraulic motor 32 is interrupted by releasing the one-way clutch 34, so that the hydraulic motor 32 is rotationally driven by the turbocharger 16 when supercharging assist is not performed. Can be prevented (dragging of the hydraulic motor 32). Furthermore, by providing the one-way clutch 34 between the hydraulic motor 32 and the speed increasing mechanism 36, the idling speed when the one-way clutch 34 is released can be reduced, and drag loss when the one-way clutch 34 is released is reduced. be able to.

  Next, another configuration example of this embodiment will be described.

  In the above description of the present embodiment, the hydraulic pump 22 is driven to rotate using the kinetic energy of the vehicle by engaging the clutch 24 during deceleration of the vehicle. However, in the present embodiment, the hydraulic pump 22 can be driven to rotate by engaging the clutch 24 even when the vehicle is not decelerated. For example, when the pressure P of the accumulator 28 is lower than a set value P2 (P2 <P1), it is possible to engage the clutch 24 and rotate the hydraulic pump 22 using the power of the engine 10.

  In this embodiment, the electronic control unit 42 controls the supply flow rate of hydraulic oil from the accumulator 28 to the hydraulic motor 32 by performing duty control that repeatedly opens and closes the stop valve 30 when performing supercharging assist. You can also In this case, the duty ratio of the stop valve 30 (ratio at which the stop valve 30 is opened) can be reduced so that the supply flow rate of the hydraulic oil to the hydraulic motor 32 decreases with an increase in the turbine rotational speed Nt. In addition, the duty ratio of the stop valve 30 can be reduced so that the supply flow rate of the hydraulic oil to the hydraulic motor 32 decreases as the engine speed Ne increases. By this control, the supercharging pressure when performing the supercharging assist can be appropriately controlled. In this embodiment, instead of the stop valve 30, a flow rate control valve capable of adjusting the supply flow rate of hydraulic oil from the accumulator 28 to the hydraulic motor 32 is provided, and the electronic control unit 42 provides supercharging assistance. When performing, the supply flow rate of the hydraulic oil to the hydraulic motor 32 can be controlled by driving the flow control valve.

  In the present embodiment, instead of the pressure sensor 29, a pressure switch that outputs a signal corresponding to the pressure of the hydraulic oil accumulated in the accumulator 28 may be provided. For example, the pressure switch outputs an H (high) level signal when the pressure of the accumulator 28 is equal to or higher than a set value, and outputs an L (low) level signal when the pressure of the accumulator 28 is lower than the set value. can do.

  In the present embodiment, as shown in FIG. 4, a one-way clutch 34 may be disposed on the shaft 17 of the turbocharger 16. According to the configuration shown in FIG. 4, the turbocharger 16 and the speed increasing mechanism 36 can be disconnected by releasing the one-way clutch 34 when supercharging assist is not performed, so that the rotational inertia of the turbocharger 16 can be reduced. Can do.

  In the configuration example shown in FIG. 4, vibration / noise can be reduced by using, for example, a wedge roller type planetary roller mechanism (traction drive mechanism) shown in FIGS. 5 and 6 as the one-way clutch 34. In the wedge roller type planetary roller mechanism 34 shown in FIGS. 5 and 6, the ring roller 34 r is connected to the hydraulic motor 32, and the sun roller 34 s is connected to the shaft 17 of the turbocharger 16. The rotating shaft of the sun roller 34s is eccentric with respect to the rotating shaft of the ring roller 34r. Between the sun roller 34s and the ring roller 34r, pinion rollers 34p1, 34p2, and 34p3 that are rotatable with respect to the carrier are disposed, and the rotation of the carrier is fixed. The diameter of the pinion roller 34p1 is set larger than the diameters of the pinion rollers 34p2 and 34p3. The pinion rollers 34p1 and 34p2 are supported in a state in which the position of the rotating shaft does not move, whereas the pinion roller 34p3 is supported so that the position of the rotating shaft can move with a wedge angle α. ing.

  As shown in FIG. 5, when the ring roller 34r rotates clockwise in FIG. 5 by the power of the hydraulic motor 32, the pinion roller 34p3 moves in the upper right direction (wedge direction) in FIG. From the hydraulic motor 32 to the turbocharger 16 is allowed. On the other hand, as shown in FIG. 6, when the sun roller 34s rotates counterclockwise in FIG. 6 by the power of the turbocharger 16, the pinion roller 34p3 moves in the diagonally downward left direction (opposite to the wedge direction) in FIG. Thus, power transmission from the sun roller 34s to the ring roller 34r, that is, power transmission from the turbocharger 16 to the hydraulic motor 32 is cut off. Therefore, the function of the one-way clutch can be realized. Further, it is possible to realize a function of a speed increasing mechanism for increasing the power of the hydraulic motor 32 and transmitting it to the turbocharger 16.

  In the configuration example shown in FIG. 4, for example, the one-way clutch and the speed increase can be achieved by driving the ring gear of the planetary gear mechanism in the direction of the rotation axis by the actuator and switching the coupling / non-coupling between the ring gear and the pinion gear. The function of the mechanism can be realized.

  As mentioned above, although the form for implementing this invention was demonstrated, this invention is not limited to such embodiment at all, and can be implemented with a various form in the range which does not deviate from the summary of this invention. Of course.

1 is a diagram showing a schematic configuration of a vehicle drive system including a supercharging device according to an embodiment of the present invention. It is a figure explaining operation | movement of the supercharging apparatus which concerns on embodiment of this invention. It is a figure explaining operation | movement of the supercharging apparatus which concerns on embodiment of this invention. It is a figure which shows the other schematic structure of the supercharging apparatus which concerns on embodiment of this invention. It is a figure which shows the structural example of a one-way clutch. It is a figure which shows the structural example of a one-way clutch.

Explanation of symbols

  10 engine, 14 transmission, 16 turbocharger, 18 turbine, 19 drive wheel, 20 compressor, 22 hydraulic pump, 24 clutch, 26, 36 speed increasing mechanism, 27 check valve, 28 accumulator, 29 pressure sensor, 30 stop valve 32 Hydraulic motor, 34 One-way clutch, 42 Electronic control unit.

Claims (7)

A supercharging device for pressurizing engine intake gas capable of driving a load,
A turbocharger that supercharges the engine using the energy of the exhaust gas of the engine;
A hydraulic pump capable of discharging hydraulic oil using engine power or load power;
A pressure accumulator that stores the energy of the hydraulic oil discharged from the hydraulic pump;
A hydraulic motor capable of driving the turbocharger using the energy of the hydraulic oil stored in the pressure accumulator;
A supercharging device comprising: The supercharging device according to claim 1,
A supercharging device comprising a power interrupting mechanism for interrupting power between a power transmission path from an engine to a load and a hydraulic pump. The supercharging device according to claim 2,
A turbocharger, wherein the power transmission path and the hydraulic pump are connected by a power interrupt mechanism when the load is decelerated. The supercharging device according to any one of claims 1 to 3,
A supercharging device comprising a first speed increasing mechanism capable of speeding up power transmitted through a power transmission path from an engine to a load and transmitting the speed to a hydraulic pump. The supercharging device according to any one of claims 1 to 4,
A supercharging device comprising a one-way power transmission mechanism that allows power transmission from a hydraulic motor to a supercharger and interrupts power transmission from the supercharger to the hydraulic motor. The supercharging device according to any one of claims 1 to 5,
A supercharging device comprising a second speed increasing mechanism capable of increasing the power of a hydraulic motor and transmitting it to a supercharger. The supercharging device according to any one of claims 1 to 6,
A supercharging device comprising an adjustment valve for adjusting a supply state of hydraulic oil from a pressure accumulator to a hydraulic motor.

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