WO2012025951A1 - 車両の制御装置 - Google Patents
車両の制御装置 Download PDFInfo
- Publication number
- WO2012025951A1 WO2012025951A1 PCT/JP2010/005183 JP2010005183W WO2012025951A1 WO 2012025951 A1 WO2012025951 A1 WO 2012025951A1 JP 2010005183 W JP2010005183 W JP 2010005183W WO 2012025951 A1 WO2012025951 A1 WO 2012025951A1
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- WIPO (PCT)
- Prior art keywords
- output
- engine
- control device
- internal combustion
- clutch
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
Definitions
- the present invention relates to a control device for a vehicle equipped with an internal combustion engine that transmits driving force to a manual transmission.
- a vehicle equipped with a manual transmission has a manual clutch, and rotation output from an engine as an internal combustion engine is transmitted to a transmission mechanism that constitutes the manual transmission via the manual clutch. Yes.
- a dry single-plate friction clutch is adopted, which is connected to the flywheel connected to the engine output shaft and the input shaft of the transmission mechanism according to the operation of the clutch pedal.
- the transmission mechanism is generally constituted by a constant meshing type or a synchronous meshing type manual transmission.
- a transmission mechanism includes an input-side main shaft, an output-side main shaft, and a counter shaft, and a plurality of gears are respectively installed on these shafts.
- positioned on the countershaft comprise the several gear pair comprised by meshing
- the gears provided on the main shafts can each idle on the shafts.
- a sleeve can be connected to each side of the gear provided on each main shaft.
- the sleeve can be moved in the axial direction by a shift fork connected to the shift lever.
- the gear moves the sleeve. Via the main shaft. Therefore, the output rotation of the engine is shifted by the gear ratio between the gear fixed to the main shaft by the sleeve and the gear meshing with the gear, and is transmitted to the drive wheels.
- the shift operation in a vehicle equipped with such a manual transmission and a manual clutch will be described.
- the driver depresses the clutch pedal while returning the depressed accelerator pedal to shift the clutch from the transmission state to the disconnected state.
- the shift lever is operated so that the transmission mechanism forms a desired shift stage.
- the clutch pedal is gradually returned to operate the clutch to gradually shift from the disengaged state to the transmitting state, and the driving force from the engine is driven through the speed change mechanism. Transmit to the wheel.
- the driver can optimize the operation of returning the accelerator pedal at the start of the speed change, the operation of depressing the clutch pedal, the operation of returning the clutch pedal at the end of the speed change, and the operation of depressing the accelerator pedal. It is possible.
- the vehicle control device disclosed in Patent Document 1 is configured to control the output of an engine mounted on a vehicle equipped with a manual transmission and a manual clutch, and when the depression of the accelerator pedal is finished, the clutch When the pedal operation has started, the engine output reduction speed due to the release of the accelerator pedal is increased than usual, and when the clutch pedal operation has not started, the engine output is reduced by the normal reduction speed. It is supposed to let you.
- the vehicle control device disclosed in Patent Document 1 can reduce the torsional torque accumulated in the drive system component when the shift is started, so that the drive system component when the clutch shifts to the disengaged state. Collision noise and vibration caused by collisions between them were reduced.
- the present invention has been made to solve the above-described conventional problems, and it is an object of the present invention to provide a vehicle control device that can improve drivability during shifting in a vehicle equipped with a manual transmission. .
- a vehicle control apparatus includes a switching means that can be switched between a shut-off state that shuts off power between an internal combustion engine and a drive wheel and a transmission state that transmits the power, and Switching operation means for operating to switch between the shut-off state and the transmission state, request output determining means for determining the magnitude of the required output for the internal combustion engine, and depending on the magnitude of the required output
- a control device for controlling the output of the internal combustion engine, the operation speed detecting means for detecting the operation speed of the switching operation means, and when the switching means has shifted to the shut-off state
- Output correction means for correcting the output of the internal combustion engine in accordance with the operation speed detected by the operation speed detection means so as to stop the output of the internal combustion engine.
- the vehicle control apparatus corrects the output of the internal combustion engine in accordance with the operation speed of the switching operation means, and therefore, when the driver does not properly harmonize the operation of the switching operation means and the output increasing operation by the driver.
- the output of the internal combustion engine becomes 0 when the switching means shifts to the shut-off state, the occurrence of vibration due to the release of the torsional torque accumulated in the drive system parts can be prevented, or the internal combustion engine It is possible to prevent engine blow-up.
- the output correction means calculates a shutoff timing at which the switching means is shut off based on the operation speed detected by the operation speed detection means, and stops the output of the internal combustion engine at the shutoff timing. It is characterized by that.
- the vehicle control apparatus can bring the timing at which the output of the internal combustion engine stops closer to the timing at which the switching means enters the shut-off state, so that when the switching means shifts to the shut-off state, it accumulates in the drive system components. It is possible to prevent the occurrence of vibration due to the release of the torsional torque, and to prevent the internal combustion engine from being blown up.
- the output correction unit starts the transition from the transmission state to the cut-off state on condition that the operation speed detected by the operation speed detection unit is equal to or greater than a predetermined threshold.
- the output of the internal combustion engine is stopped when the magnitude of the required output at the time is greater than or equal to a first predetermined value.
- the vehicle control device stops the output under the internal combustion engine when it is determined that the output of the internal combustion engine is not sufficiently lowered and the engine blows up at the timing when the switching unit is in the shut-off state. be able to. Thereby, it is possible to prevent the occurrence of racing when shifting.
- the vehicle control device corrects the output to the internal combustion engine when the operation speed of the switching operation means is high, and is stored in the drive system components when the switching means enters the shut-off state. By reducing the torsional torque, vibrations can be prevented from occurring in the vehicle.
- the output correction unit starts the transition from the transmission state to the cut-off state on condition that the operation speed detected by the operation speed detection unit is equal to or greater than a predetermined threshold.
- the output of the internal combustion engine is increased until the switching means shifts to the shut-off state when the magnitude of the required output at the time is equal to or smaller than a second predetermined value smaller than the first predetermined value.
- the vehicle control device increases the output of the internal combustion engine so that the switching unit is shut off. It is possible to prevent the torsional torque from being accumulated in the drive system components when the state is reached. As a result, the torsional torque is released at the time of shifting, thereby preventing the occurrence of vibration due to the collision between the drive system components.
- the switching speed of the switching operation means is high, compared to the case where the switching speed is low, the switching between the parts generated when the torsional torque accumulated in the drive system parts is released when the switching means enters the shut-off state.
- the vehicle control device corrects the output to the internal combustion engine when the operation speed of the switching operation means is high, and is stored in the drive system components when the switching means enters the shut-off state. By reducing the torsional torque, vibrations can be prevented from occurring in the vehicle.
- the output correction means corrects the output of the internal combustion engine so that the output torque of the internal combustion engine follows the torque capacity of the switching means.
- the output correcting means corrects the output of the internal combustion engine by controlling the intake air amount adjusting means. It is characterized by.
- the vehicle control apparatus appropriately controls the output of the internal combustion engine by adjusting the amount of air sucked into the internal combustion engine when the switching unit shifts to the released state, and the collision due to the release of the torsional torque. It is possible to prevent the generation of sound and vibrations and the occurrence of engine blow-up.
- fuel supply amount adjusting means for adjusting a supply amount of fuel supplied to the internal combustion engine is provided, and the output correcting means corrects the output of the internal combustion engine by controlling the fuel supply amount adjusting means. It is characterized by doing.
- the vehicle control apparatus can adjust the output of the internal combustion engine regardless of whether or not the vehicle is equipped with a means for adjusting the amount of air taken into the internal combustion engine. It is possible to prevent the occurrence of collision noise and vibration due to the release of torsional torque and the occurrence of a blow-up of the internal combustion engine during the transition.
- drivability at the time of shifting can be improved in a vehicle equipped with a manual transmission.
- FIG. 1 is a schematic configuration diagram of an engine according to a first embodiment of the present invention. It is sectional drawing of the clutch mechanism which concerns on the 1st Embodiment of this invention. It is a timing chart of the engine output correction control according to the first embodiment of the present invention. It is a figure which shows the timing chart of the engine output correction
- the power train mounted on the vehicle 1 mainly includes an engine 11 as an internal combustion engine, a manual transmission 12 that can realize a shift by a driver's operation, and the manual transmission 12 from the engine 11. And a clutch mechanism 13 capable of interrupting transmission of torque to the motor.
- the engine 11 includes a plurality of substantially cylindrical cylinders, a cylinder block fixed to the vehicle body via an engine mount, a piston housed in each cylinder so as to be slidable in the axial direction, and a cylinder block An intake port 17 and an exhaust port 18 are formed in the cylinder head.
- a combustion chamber 19 is defined by the cylinder block, the cylinder head, and the piston.
- a 4-cylinder gasoline engine will be described as an example.
- the combustion chamber 19 is connected to the intake pipe 23 and the exhaust pipe 28.
- the intake pipe 23 is provided with an electronic throttle device 26 having a throttle valve 25, a surge tank 22, and an intake manifold 21, and air outside the vehicle 1 passes through the throttle valve 25, the surge tank 22 and the intake manifold 21. And is supplied to the combustion chamber 19.
- An air cleaner 24 is installed at the air inlet of the intake pipe 23.
- the throttle valve 25 is rotatably installed in the intake pipe 23 and is rotated by an actuator.
- the actuator rotates the throttle valve 25 according to the amount of depression of an accelerator pedal 61 described later.
- the exhaust pipe 28 is provided with an exhaust manifold 27 and an exhaust purification catalyst 31 composed of a three-way catalyst. Exhaust gas exhausted from the combustion chamber 19 passes through the exhaust manifold 27 and the exhaust purification catalyst 31 to the engine. 11 is discharged to the outside.
- each intake port 17 In the vicinity of each intake port 17, an injector 29 for injecting fuel is installed. Above each combustion chamber 19, a spark plug 16 for igniting an air-fuel mixture of gasoline and air is installed.
- the injector 29 is opened when energized by an engine control device 10 described later, and injects fuel into the combustion chamber 19.
- the injected fuel mixes with the air sucked in the combustion chamber 19 to constitute an air-fuel mixture.
- the engine 11 has a plurality of cylinders 15 forming a combustion chamber 19, and each cylinder 15 accommodates a piston 38 in a reciprocating manner.
- the piston 38 is connected to the crankshaft 32 via a connecting rod 39, and the reciprocating motion of the piston 38 is converted into a rotational motion by the connecting rod 39 and transmitted to the crankshaft 32 as an output shaft. Yes.
- the engine 11 includes an intake valve 66 for opening and closing an opening where the intake pipe 23 and the combustion chamber 19 are connected, and an exhaust for opening and closing an opening where the exhaust pipe 28 and the combustion chamber 19 are connected. And a valve 67.
- the intake valve 66 and the exhaust valve 67 are urged in a direction to close the opening by a valve spring 68.
- the engine 11 further includes an intake camshaft 69 and an exhaust camshaft 70 that are rotated by the crankshaft 32.
- the intake camshaft 69 is installed substantially above the intake valve 66
- the exhaust camshaft 70 is installed substantially above the exhaust valve 67.
- the engine 11 further includes an ignition plug 16, an igniter 71 that transmits an ignition signal to the ignition plug 16, and an ignition coil 72 that applies a high voltage to the ignition plug 16.
- the air-fuel mixture in the combustion chamber 19 is ignited by the discharge from the spark plug 16 and burns.
- the piston 38 is reciprocated by the high-temperature and high-pressure combustion gas generated by this combustion, and the crankshaft 32 is rotated via the connecting rod 39. As a result, the driving force of the engine 11 is obtained.
- the engine 11 further includes a valve timing mechanism 73 for changing the relative rotation phase of the intake camshaft 69 with respect to the crankshaft 32 and changing the valve timing of the intake valve 66 with respect to the crank angle.
- the engine 11 further includes a working angle varying mechanism 74 for making the working angle CA of the intake valve 66 variable as a valve characteristic.
- the operating angle is a valve opening period of the intake valve 66 expressed by a crank angle corresponding to the rotation of the intake camshaft 69.
- the intake valve 66 is configured such that, for example, when the operating angle CA decreases, the maximum lift amount also decreases. Further, as the operating angle CA decreases, the valve opening timing IVO and the valve closing timing IVC of the intake valve 66 approach each other. Therefore, the smaller the operating angle CA, the shorter the valve opening period and the smaller the maximum lift amount, so that the amount of air taken into the cylinder 15 decreases.
- the operating angle variable mechanism 74 includes an intermediate drive mechanism 75 installed in each cylinder 15 and a control shaft 76.
- the intermediate drive mechanism 75 includes an input arm 77 and an output arm 78 installed on the control shaft 76, and a power transmission slider gear 79 interposed between the control shaft 76, the input arm 77 and the output arm 78. ing.
- the input arm 77 swings up and down with the control shaft 76 as a fulcrum according to the rotation of the intake camshaft 69. Since the swing of the input arm 77 is transmitted to the output arm 78 via the slider gear 79, the output arm 78 is swung up and down. As a result, the intake valve 66 is driven and opened by the swing of the output arm 78. It comes to speak.
- the control shaft 76 is moved in the axial direction by the electric actuator 80.
- the engine control device 10 is configured to control the operating angle variable mechanism 74 and to change the operating angle CA of the intake valve 66 by energizing an electric motor (not shown).
- the vehicle 1 further includes a crank angle sensor 81, a cam angle sensor 82, an operating angle sensor 83, an air flow meter 84, and a throttle sensor 85.
- the crank angle sensor 81 generates a pulse signal every time the crankshaft 32 rotates by a certain angle.
- the cam angle sensor 82 detects the rotation angle of the intake camshaft 69.
- the air flow meter 84 detects the amount of intake air flowing through the intake pipe 23.
- the throttle sensor 85 detects the throttle opening.
- the working angle sensor 83 estimates the working angle CA of the intake valve 66 based on the amount of movement of any movable part of the working angle variable mechanism 74 in cooperation with the engine control device 10.
- the engine control device 10 receives signals from a crank angle sensor 81, a cam angle sensor 82, an operating angle sensor 83, an air flow meter 84, and a throttle sensor 85. Further, the engine control device 10 controls the throttle valve 25, the injector 29, the spark plug 16, and the operating angle variable mechanism 74 so that the air-fuel ratio in the engine 11 approaches the stoichiometric air-fuel ratio based on signals received from these sensors. .
- the crankshaft 32 is connected to an input shaft 33 that constitutes an input shaft of the manual transmission 12 via the clutch mechanism 13.
- the clutch mechanism 13 as switching means according to the present invention is switched between a transmission state in which the rotation of the crankshaft 32 is transmitted to the input shaft 33 and a cutoff state in which the transmission to the input shaft 33 is blocked. .
- the transition of the state between the transmission state and the cutoff state in the clutch mechanism 13 corresponds to the depression amount of the clutch pedal 35 operated by the driver, that is, the clutch stroke Cstr, and the clutch pedal 35 is not depressed.
- the clutch mechanism 13 In the state, the clutch mechanism 13 is in a transmission state, and the rotation of the crankshaft 32 is transmitted to the input shaft 33.
- the clutch pedal 35 when the clutch pedal 35 is depressed, the clutch mechanism 13 is in a disconnected state, and transmission of rotation from the crankshaft 32 to the input shaft 33 is blocked.
- the clutch pedal 35 constitutes a switching operation means according to the present invention.
- the manual transmission 12 is configured to decelerate the rotation of the input shaft 33 and rotate the output shaft 36 by any one of a plurality of gear trains having different gear ratios. Further, in the manual transmission 12, the power transmission path between the input shaft 33 and the output shaft 36 is switched according to the operation of the shift lever 37 by the driver, and the speed ratio corresponding to the transmission path is set. It is like that.
- the shift lever 37 has a neutral position for interrupting transmission of power between the input shaft 33 and the output shaft 36 in the manual transmission 12, and the rotational directions of the input shaft 33 and the output shaft 36 are opposite to each other.
- a reverse position for moving the vehicle 1 backward and a 1st to 6th speed position associated with a predetermined gear ratio of the manual transmission 12 are taken.
- the clutch mechanism 13 is configured by a so-called dry single-plate friction clutch.
- the clutch mechanism 13 includes a disc-shaped flywheel 42 that rotates integrally with the crankshaft 32, a clutch disc 43 that rotates integrally with the input shaft 33, and an annular shape that presses the clutch disc 43 toward the flywheel 42.
- a pressure plate 44, a disk-shaped diaphragm spring 45 that applies a pressing force to the pressure plate 44, and a clutch cover 46 that rotates integrally with the flywheel 42 are provided.
- the flywheel 42 is rotated by the torque output from the engine 11 via the crankshaft 32.
- the clutch disc 43, the pressure plate 44, and the diaphragm spring 45 are accommodated between the flywheel 42 and the clutch cover 46 so that their axes coincide with each other.
- the clutch disk 43 is splined to the input shaft 33. Therefore, the clutch disk 43 can move in the axial direction of the input shaft 33 while rotating integrally with the input shaft 33.
- the pressure plate 44 is in contact with the annular outer peripheral portion 45a of the diaphragm spring 45 and is pressed toward the flywheel 42 by the diaphragm spring 45. By this pressing, the pressure plate 44 presses the clutch disk 43, and a frictional force is generated between the clutch disk 43 and the flywheel 42. By this frictional force, the flywheel 42 and the clutch disc 43 are engaged, that is, the clutch is connected, and the flywheel 42 and the clutch disc 43 rotate together. In this way, power transmission from the engine 11 to the manual transmission 12 is performed.
- the diaphragm spring 45 has a disk shape with a raised central portion, and has a structure in which a plurality of tongue-shaped levers toward the center are formed on the inner peripheral side of the annular outer peripheral portion 45a.
- the tip of the tongue-shaped lever corresponding to the central portion of the diaphragm spring 45 is a central portion 45b, and the vicinity of the boundary between the annular outer peripheral portion 45a and the tongue-shaped lever is a support portion 45c.
- the diaphragm spring 45 since the diaphragm spring 45 has a structure in which the central portion 45b is raised, it functions as a disc spring.
- the diaphragm spring 45 has a support portion 45 c held between the end portions 46 a of the clutch cover 46, an outer peripheral portion 45 a in contact with the pressure plate 44, and a central portion 45 b in contact with the tip of the release sleeve 55.
- a master cylinder (not shown) is provided in the vicinity of the clutch pedal 35 (see FIG. 1).
- the master cylinder is composed of a piston and a liquid chamber, and the tip of the piston is connected to the clutch pedal 35.
- the master cylinder is configured so that its piston protrudes and retracts with respect to the cylinder portion as the clutch pedal 35 is operated.
- a release cylinder 52 is provided in the vicinity of the release fork 54.
- the release cylinder 52 is composed of a piston and a liquid chamber, and the tip of the piston is connected to the end of the release fork 54 (the upper end of FIG. 2).
- the cylinder part of the master cylinder and the cylinder part of the release cylinder 52 are communicated with each other via a clutch pipe 53.
- the cylinder portion of the master cylinder, the cylinder portion of the release cylinder 52, and the clutch pipe 53 are filled with clutch fluid.
- the output shaft 36 of the manual transmission 12 is connected to the left and right drive wheels 59 via a propeller shaft 56, a differential gear 57 and a drive shaft 58.
- the vehicle 1 further includes an engine control device 10 that constitutes a control device of the vehicle 1.
- the engine control device 10 is configured by a known ECU (Electronic Control Unit).
- the engine control device 10 controls the magnitude of torque output from the engine 11.
- the engine control device 10 is a micro that includes a CPU (Central Processing Unit), a RAM (Random Access Memory), a ROM (Read Only Memory), an input port, an output port, and the like that are connected to each other via a bidirectional bus. Consists of a computer.
- the CPU performs output control of the engine 11 and the like by performing signal processing according to a program and a map stored in advance in the ROM while using a temporary storage function of the RAM.
- a signal output from the output port is transmitted to an actuator (not shown) or the like via an A / D converter.
- the engine control device 10 determines the opening degree of the throttle valve 25 of the electronic throttle device 26, the fuel injection amount and timing in the injector 29, and the spark plug 16 based on signals input from the sensors described above and sensors described later. Ignition timing, etc. are controlled.
- the vehicle 1 further includes an engine speed sensor 40, an input shaft speed sensor 64, and a vehicle speed sensor 65.
- the engine speed sensor 40 outputs a signal representing the speed of the crankshaft 32 to the engine control device 10 so that the engine control device 10 detects the engine speed Ne based on this signal. It has become.
- the vehicle speed sensor 65 is configured to output a signal representing the number of rotations of the output shaft 36 of the manual transmission 12 to the engine control device 10, and the engine control device 10 calculates the vehicle speed V based on this signal. It has become.
- the input shaft rotational speed sensor 64 outputs a signal representing the rotational speed of the input shaft 33 of the manual transmission 12 to the engine control apparatus 10.
- the vehicle 1 includes an accelerator pedal 61 and an accelerator opening sensor 62.
- the accelerator opening sensor 62 is composed of, for example, an electronic position sensor using a hall element. When the accelerator pedal 61 is operated by the driver, the accelerator opening sensor 62 indicates the accelerator opening Apedal indicating the position of the accelerator pedal 61. Is output to the engine control device 10.
- the engine control device 10 causes the engine 11 to generate the required engine torque Tereq corresponding to the accelerator opening Apedal, the opening of the throttle valve 25 of the electronic throttle device 26, the timing of fuel injection in the injector 29, and the ignition in the spark plug 16. The timing is controlled. Therefore, in the present embodiment, accelerator opening sensor 62 and engine control device 10 constitute requested output determining means for determining the magnitude of the required output for the internal combustion engine.
- the engine control device 10 constitutes control means for controlling the output of the internal combustion engine according to the magnitude of the required output.
- the vehicle 1 includes a clutch stroke sensor 63.
- the clutch stroke sensor 63 transmits a signal corresponding to the depression amount of the clutch pedal 35, that is, a clutch stroke Cstr, to the engine control apparatus 10.
- the clutch stroke sensor 63 directly detects the clutch stroke by contacting the clutch pedal 35.
- the clutch stroke sensor 63 is not limited to this, and the clutch stroke Cstr such as the operating state of the master cylinder or the release cylinder 52 described above is not limited thereto. The operating state of the member whose operating state changes in response to this may be detected.
- the engine control device 10 calculates the operation speed of the clutch pedal 35 based on the signal input from the clutch stroke sensor 63.
- the clutch stroke sensor 63 and the engine control device 10 constitute an operation speed detection means for detecting the operation speed of the switching operation means.
- the engine control device 10 calculates the timing Toff when the clutch mechanism 13 is switched from the transmission state to the cutoff state based on the operation speed of the clutch pedal 35.
- the engine control device 10 corrects the throttle opening TA so that the output of the engine 11 becomes 0 at the timing Toff based on the current accelerator opening Apedal.
- the engine control device 10 calculates the change rate ⁇ TA of the throttle opening TA based on the current accelerator opening Apedal and the timing Toff at which the clutch mechanism 13 changes from the transmission state to the shut-off state. Correction is made so that the change rate of the throttle opening degree TA according to the operation of the pedal 61 becomes the calculated change rate ⁇ TA. That is, the engine control apparatus 10 corrects the output of the engine 11 so that the output of the engine 11 becomes 0 at the timing Toff, that is, the output of the engine 11 is stopped. Therefore, in the present embodiment, the engine control device 10 constitutes an output correction unit according to the present invention.
- the engine control device 10 determines that the operation of the clutch pedal 35 by the driver is interrupted based on a signal input from the clutch stroke sensor 63, such as when the clutch stroke Cstr is reduced, the throttle opening degree is reduced. The correction is finished.
- a return operation of the accelerator pedal 61 is started by the driver.
- the engine control device 10 detects that the clutch pedal 35 has started to be depressed at time T2 based on the signal input from the clutch stroke sensor 63 (see the solid line 93).
- time Toff based on the operation speed of the clutch pedal 35.
- time T5 corresponds to time Toff.
- the output torque Te of the engine 11 becomes 0 at time T4 earlier than time T5 (see broken line 94). Therefore, at time T5 when the clutch mechanism 13 is switched from the transmission state to the cutoff state, a negative torque transmitted from the drive wheels 59 to the engine 11 is generated, and the gears constituting the crankshaft 32, the input shaft 33, and the manual transmission 12 are generated. Torsional torque is accumulated in the drive system components such as the output shaft 36 and the like.
- the engine control device 10 calculates the change rate dTA of the throttle opening so that the output torque Te of the engine 11 becomes 0 at the time Toff (see the solid line 95), and controls the electronic throttle device 26. Then, the throttle valve 25 is closed at the throttle opening changing speed dTA. Therefore, in the present embodiment, the engine control device 10 and the electronic throttle device 26 constitute intake air amount adjusting means according to the present invention.
- the change rate dTA of the throttle opening is calculated as a time difference ⁇ T between time T3 when the engine control apparatus 10 starts output correction to the engine 11 and time T5, and the throttle opening TA detected at time T3. Is divided by the time difference ⁇ T.
- a solid line 96 represents the torque capacity Tclt of the clutch mechanism 13 corresponding to the clutch stroke Cstr
- solid lines 97 and 99 represent the output torque Te of the engine 11.
- time T1 the return operation of the accelerator pedal 61 is started by the driver (see the solid line 97).
- the engine control device 10 detects that the clutch pedal 35 has started to be depressed based on the signal input from the clutch stroke sensor 63 at time T2 (see the solid line 96), it calculates the operation speed of the clutch pedal 35, Based on the calculated operation speed, a timing Toff at which the clutch mechanism 13 changes from the transmission state to the cutoff state is calculated.
- time T4 corresponds to time Toff.
- the engine control device 10 calculates the change rate dTA of the throttle opening so that the output torque Te of the engine 11 becomes zero at the time Toff (see the solid line 99), and controls the electronic throttle device 26. Then, the throttle valve 25 is closed at the throttle opening changing speed dTA.
- the engine control device 10 determines whether or not the operation speed dCstr of the clutch pedal 35 is equal to or higher than a predetermined value A [mm / s] (step S11).
- This predetermined value A is transmitted to the clutch mechanism 13 even when torsional torque is accumulated in the drive shaft components such as the crankshaft 32, the input shaft 33, the gears constituting the manual transmission 12, and the output shaft 36. Is set to a speed at which no collision noise or vibration between drive system parts due to the release of torsional torque occurs in the vehicle 1 or when the driver does not feel the vibration uncomfortable. It is determined in advance by experimental measurement.
- the predetermined value A may be 0. In this case, the engine control device 10 always executes engine output correction control at the time of shifting regardless of the operation speed of the clutch pedal 35.
- step S11 When the engine control device 10 determines that the operation speed dCstr of the clutch pedal 35 is equal to or higher than the predetermined value A (YES in step S11), the engine control device 10 proceeds to step S12. On the other hand, when it is determined that the operation speed dCstr of the clutch pedal 35 is less than the predetermined value A (NO in step S11), the process proceeds to RETURN.
- the engine control device 10 calculates the timing Toff when the clutch mechanism 13 shifts from the transmission state to the cutoff state based on the operation speed of the clutch pedal 35 (step S12), and acquires the throttle opening degree TA (step S12). Step S13).
- the engine control device 10 calculates a change speed dTA of the throttle opening TA at which the current throttle opening TA becomes 0 at the timing Toff (step S14).
- the engine control device 10 corrects the throttle opening degree TA so that the throttle valve 25 is closed at the change speed dTA, and controls the electronic throttle device 26 so as to achieve the corrected throttle opening degree (step S15).
- the engine control apparatus 10 corrects the output of the engine 11 in accordance with the operation speed dCstr of the clutch pedal 35. Therefore, the driver operates the clutch pedal 35 and increases the output during shifting. Even when the harmony with the operation is not appropriate, by correcting the output of the engine 11 at the time when the clutch mechanism 13 shifts from the transmission state to the cutoff state, the drive resulting from the release of the torsional torque accumulated in the drive system components It is possible to prevent the occurrence of collision noise and vibration between system parts, and to prevent the engine 11 from being blown up.
- control apparatus of the vehicle 1 can approximate the timing when the output of the engine 11 stops to the timing when the clutch mechanism 13 becomes the disconnected state from the transmission state, when the clutch mechanism 13 shifts from the transmission state to the cutoff state.
- the present invention is not limited to this, and the time when the throttle opening TA is decreased according to a predetermined function.
- the throttle opening may be 0 at Toff.
- the engine control apparatus 10 has been described based on the case where the timing Toff at which the clutch mechanism 13 shifts from the transmission state to the cutoff state based on the signal input from the clutch stroke sensor 63 has been described.
- the engine control apparatus 10 may calculate the timing Toff when the clutch mechanism 13 shifts from the transmission state to the cutoff state using a plurality of clutch switches instead of the clutch stroke sensor 63.
- the engine control apparatus 10 calculates the operation speed of the clutch pedal 35 from the time difference between the timings when the signals respectively input from the two clutch switches are switched from the OFF signal to the ON signal.
- the engine control device 10 directly corrects the value of the accelerator opening input from the accelerator opening sensor 62 instead of correcting the throttle opening TA, and outputs the engine 11 according to the corrected accelerator opening. By controlling this, the output of the engine 11 may become 0 at the timing T1.
- the engine control apparatus 10 demonstrated the case where the output of the engine 11 was set to 0 by timing Toff by correct
- the engine control apparatus 10 controls fuel injection amount. By doing so, the output of the engine 11 may be set to 0 at the timing Toff.
- the engine control device 10 constitutes a fuel supply amount adjusting means according to the present invention.
- the engine control device 10 calculates the timing Toff at which the clutch mechanism 13 shifts from the transmission state to the cutoff state, and performs control so that the output of the engine 11 becomes 0 at this timing Toff.
- the engine control device 10 corrects the output of the engine 11 in accordance with the magnitude of the accelerator opening Apedal when the operation of the clutch pedal 35 is started.
- the output of the engine 11 may be controlled to be zero when the clutch mechanism 13 shifts from the transmission state to the cutoff state.
- the configuration of the engine control device according to the second embodiment is substantially the same as the configuration of the engine control device according to the first embodiment described above, and each component is shown in FIGS. Description will be made using the same reference numerals as those of the first embodiment shown, and only differences will be described in detail.
- the engine control device 10 reduces the torsional torque accumulated in the drive system components when the clutch mechanism 13 shifts from the transmission state to the cutoff state. As a result, the collision noise between the drive system components and the vibration of the vehicle 1 are reduced.
- the engine control device 10 executes the following engine output correction control.
- the predetermined value B constitutes a predetermined threshold according to the present invention, and is set in the same manner as the predetermined value A in the first embodiment described above.
- the engine control device 10 acquires the accelerator opening Apedal of the accelerator pedal 61 when the clutch pedal 35 starts to be operated by the driver.
- the engine control device 10 does not reach 0 when the clutch mechanism 13 shifts from the transmission state to the shut-off state, and the engine 11 is blown up. Therefore, the value of the accelerator opening Apedal input from the accelerator opening sensor 62 is corrected to zero. Further, the engine control device 10 stops the smoothing control that is normally executed when the throttle opening degree TA is set to zero. Therefore, the engine control apparatus 10 according to the present embodiment starts the transition from the transmission state to the cutoff state on condition that the operation speed detected by the operation speed detection means is equal to or greater than a predetermined threshold. When the magnitude of the required output at this time is equal to or greater than the first predetermined value, an output correction means for stopping the output of the internal combustion engine is configured. Further, the predetermined value C constitutes a first predetermined value according to the present invention.
- the engine control device 10 may set the predetermined value C according to the operation speed dCsrt of the clutch pedal 35.
- the predetermined value C is set to increase as the operation speed dCsrt increases.
- the engine control device 10 is driven when the clutch mechanism 13 shifts from the transmission state to the cutoff state. Since the torsional torque is accumulated in the system parts, and the collision sound between the drive system parts and the vibration in the vehicle 1 are generated, the accelerator opening Apedal input from the accelerator opening sensor 62 is increased. ing. Therefore, the engine control apparatus 10 according to the present embodiment starts the transition from the transmission state to the cutoff state on the condition that the operation speed detected by the operation speed detection means is equal to or greater than a predetermined threshold.
- a correcting means is configured to increase the output of the internal combustion engine until the switching means shifts to the shut-off state.
- the accelerator opening Apedal corresponding to the second predetermined value is 0
- the accelerator opening Apedal corresponding to the second predetermined value is greater than 0 and greater than C.
- the value may be a small value and the accelerator opening Apedal can be zero when the clutch mechanism 13 shifts from the transmission state to the cutoff state.
- FIG. 7 is a timing chart showing changes in the torque capacity Tclt of the clutch mechanism 13 and the output torque Te of the engine 11 when the vehicle 1 is shifted.
- a solid line 101 represents the torque capacity Tclt of the clutch mechanism 13 and solid lines 102 and 104. Represents the output torque Te of the engine 11.
- the engine control device 10 detects that the clutch pedal 35 has started to be operated by the driver at time T1, and calculates the operation speed of the clutch pedal 35. Further, the torque capacity Tclt of the clutch mechanism 13 starts to decrease by the operation of the clutch pedal 35 (see the solid line 101).
- the engine control device 10 acquires the value of the accelerator opening Apedal at time T2.
- the clutch mechanism 13 is operated according to the normal reduction in the accelerator pedal opening Apedal. Since the output torque Te of the engine 11 becomes 0 (see the broken line 103) at time T4 later than time T3 when the torque capacity Tclt becomes 0 (see the broken line 103), a racing occurs. Note that the broken line 103 is curved in the vicinity of time T4 because of the execution of the annealing control.
- the engine control device 10 corrects the accelerator opening Apedal to 0 and stops the smoothing control for the throttle opening TA at time T2. As a result, the output torque Te of the engine 11 decreases and becomes 0 at time T3. The time from time T2 to time T3 represents a time lag until the throttle valve 25 is closed.
- the engine control device 10 corrects to add ⁇ Apedal to the accelerator opening Apedal between time T2 and time T3 so that the output torque of the engine 11 becomes 0 at time T3. As a result, the output torque Te of the engine 11 increases and becomes 0 at time T3.
- the engine control device 10 determines whether or not the operation speed dCstr of the clutch pedal 35 is equal to or higher than a predetermined value B [mm / s] (step S21).
- the predetermined value B is equal to the collision sound between the drive system parts or the vehicle 1 due to the release of the torsional torque when the clutch mechanism 13 shifts from the transmission state to the cutoff state.
- the speed is set so as not to cause the vibration of the vehicle or to make the driver feel uncomfortable, and is determined in advance by experimental measurement.
- step S21 When the engine control device 10 determines that the operation speed dCstr of the clutch pedal 35 is equal to or higher than the predetermined value B (YES in step S21), the engine control device 10 proceeds to step S22. On the other hand, when it is determined that the operation speed dCstr of the clutch pedal 35 is less than the predetermined value B (NO in step S21), the process proceeds to RETURN.
- the engine control device 10 determines whether or not the accelerator opening Apedal is equal to or greater than a predetermined value C (step S22). As described above, if the correction to the output of the engine 11 is not performed, the predetermined value C is an opening at which the accelerator opening does not become zero when the clutch mechanism 13 shifts from the transmission state to the cutoff state. It is determined in advance by experimental measurement.
- step S22 If the engine control apparatus 10 determines that the accelerator opening Apedal is equal to or greater than the predetermined value C (YES in step S22), the engine control apparatus 10 proceeds to step S23, sets the accelerator opening Apedal to 0, and performs smoothing control. It is turned off (step S24).
- step S22 if the engine control apparatus 10 determines that the accelerator opening Apedal is less than the predetermined value C (NO in step S22), the engine control apparatus 10 proceeds to step S25.
- step S25 the engine control device 10 determines whether or not the accelerator opening Apedal is zero.
- Step S25 When it is determined that the accelerator opening Apedal is 0 (YES in Step S25), the engine control device 10 proceeds to Step S26 and adds the correction value ⁇ Apedal to the accelerator opening Apedal until the timing Toff.
- step S25 if the engine control apparatus 10 determines that the accelerator opening Apedal is not 0 (NO in step S25), the engine control apparatus 10 proceeds to RETURN.
- the engine control apparatus 10 allows the engine to operate when the operation speed of the clutch pedal 35 is equal to or higher than the predetermined value B and the torsional torque accumulated in the drive system parts is rapidly eliminated. Since the output correction control is executed, vibration generated in the vehicle 1 can be reliably prevented.
- the accelerator pedal opening Apedal when the clutch pedal 35 is operated is equal to or greater than the predetermined value C
- the accelerator pedal opening Apedal is corrected to 0, so that when the clutch mechanism 13 shifts from the transmission state to the cutoff state. It is possible to prevent the engine 11 from blowing up.
- the engine control device 10 executes the engine output correction control when the clutch mechanism 13 shifts from the transmission state to the cutoff state.
- the engine control device 10 may execute engine output correction control when the clutch mechanism 13 shifts from the disconnected state to the transmission state.
- the engine control device 10 acquires the accelerator opening Apedal when detecting that the clutch pedal 35 starts to be returned at, for example, the above-described predetermined value B [mm / s] or more. And if this accelerator opening Apedal is more than predetermined value, the engine control apparatus 10 will correct
- the amount of decrease in the accelerator opening is calculated based on the operation speed of the clutch pedal 35, at which time a predetermined torque capacity Tclt is reached. At this timing, the predetermined output torque Te of the engine 11 is applied to the engine 11. Generate.
- the predetermined torque capacity Tclt is the torque capacity when the clutch mechanism 13 is shifted to the transmission state
- the predetermined output torque Te of the engine 11 is the clutch mechanism 13 is shifted to the transmission state. This means the output torque obtained by experimental measurement so that no collision noise between drive system components or vibration of the vehicle 1 occurs.
- the acquired accelerator pedal position is corrected to increase. To do. Similar to the decrease amount, this increase amount is also obtained by experimental measurement so that no collision noise between drive system components or vibration of the vehicle 1 occurs when the clutch mechanism 13 shifts to the transmission state.
- the engine control device 10 corrects the output of the engine 11 according to the magnitude of the accelerator opening Apedal at the time when the operation of the clutch mechanism 13 is started, so that the clutch mechanism 13 transmits.
- the case where control is performed so that the output of the engine 11 becomes 0 at the time of transition from the state to the shut-off state has been described.
- the engine control device 10 performs the engine 11 at the time of shifting By causing the output torque of the clutch mechanism 13 to follow the torque capacity of the clutch mechanism 13, when the clutch mechanism 13 shifts from the transmission state to the cutoff state, a collision noise between drive system components and vibration of the vehicle 1 are generated due to the release of the torsional torque. You may make it prevent.
- the configuration of the engine control apparatus according to the third embodiment is substantially the same as the configuration of the engine control apparatus according to the first embodiment described above, and each component is shown in FIGS. Description will be made using the same reference numerals as those of the first embodiment shown, and only differences will be described in detail.
- FIG. 9 is a timing chart showing changes in the torque capacity Tclt of the clutch mechanism 13 and the output torque Te of the engine 11 when the vehicle 1 is shifted.
- the solid line 106 indicates the torque capacity Tclt of the clutch mechanism 13 and the solid line 107 indicates the engine. 11 output torques Te.
- the engine control device 10 calculates the torque capacity Tclt of the clutch mechanism 13 based on the signal input from the clutch stroke sensor 63, and the output torque Te of the engine 11 is calculated.
- the output of the engine 11 is adjusted according to the operating speed of the clutch pedal 35 so as to follow the torque capacity Tclt of the clutch mechanism 13 (see the solid line 107).
- the engine control device 10 acquires the torque capacity Tclt of the clutch mechanism 13 by referring to the clutch torque map when the clutch pedal 35 starts to be depressed.
- the clutch torque map associates the depression amount of the clutch pedal 35 input from the clutch stroke sensor 63 with the torque capacity Tclt of the clutch mechanism 13 and is stored in advance in the ROM.
- the engine control apparatus 10 acquires the throttle opening degree TA based on a signal input from the throttle sensor 85, the engine control apparatus 10 acquires the output torque Te of the engine 11 with reference to the engine torque map.
- the output torque Te of the engine 11 is calculated from the accelerator opening Apedal and the engine speed Ne.
- the engine control device 10 stores in advance an engine torque map in which the accelerator opening Apedal, the engine speed Ne, and the output torque Te of the engine 11 are associated with each other.
- the engine control device 10 corrects the output torque Te of the engine 11 acquired from the engine torque map when control for adjusting the output torque of the engine 11 such as valve timing control is being executed. .
- the engine control device 10 starts to depress the clutch pedal 35, and the difference between the torque capacity Tclt of the clutch mechanism 13 and the output torque Te of the engine 11 acquired as described above becomes equal to or less than a predetermined value indicated by an arrow 109. In this case, correction of the output torque Te of the engine 11 is started so that this difference does not spread at least.
- the predetermined value is determined such that the output torque Te of the engine 11 does not exceed the torque capacity Tclt of the clutch mechanism 13 due to a control error of the torque capacity Tclt of the clutch mechanism 13 or fluctuation due to an external factor.
- the engine control apparatus 10 executes output control of the engine 11 based on a guard map stored in advance in the ROM.
- the guard map uses the torque capacity Tclt of the clutch mechanism 13 as a guard value Tguard, and the required accelerator torque Tereq calculated from the current accelerator opening Apedal, engine speed Ne, and engine torque map is a guard value.
- the engine control device 10 converts the command engine torque Teins guarded by Tguard to the engine 11 and outputs the command engine torque Teins calculated by the guard map.
- the output torque Te of the engine 11 becomes 0 at T3, which is the timing immediately before the torque capacity Tclt of the clutch mechanism 13 becomes 0 at time T4. Therefore, when the clutch mechanism 13 shifts from the transmission state to the cutoff state. It is possible to prevent the torsional torque from being accumulated in the drive system parts.
- the engine output correction control will be described with reference to FIG.
- the process described below is realized by a program stored in advance in the ROM, and is executed by the CPU on condition that the clutch stroke sensor 63 detects that the clutch pedal 35 has started to be depressed.
- the engine output correction control may be executed only when the operation speed dCstr of the clutch pedal 35 is equal to or higher than a predetermined value.
- the engine control device 10 calculates the torque capacity Tclt of the clutch mechanism 13 with reference to the clutch torque map (step S31).
- the engine control apparatus 10 calculates the throttle opening degree TA based on the accelerator opening degree Apedal detected by the accelerator opening degree sensor 62, the engine control apparatus 10 calculates the required engine torque Tereq with reference to the engine torque map (step S32). ).
- the engine control device 10 sets a guard value Tguard for the requested engine torque Tereq with reference to the guard map shown in FIG. 10 (step S33).
- step S34 the engine control device 10 compares the required engine torque Tereq calculated in step S32 with the guard value Tguard set in step S33 (step S34). If the engine control apparatus 10 determines that the requested engine torque Tereq does not exceed the guard value Tgurad (NO in step S34), the engine control apparatus 10 proceeds to step S35. On the other hand, if it is determined that the required engine torque Tereq exceeds the guard value Tgurad (YES in step S34), the process proceeds to step S36.
- step S35 the engine control device 10 sets the requested engine torque Tereq to the target engine torque Teins. Then, the electronic throttle device 26 is controlled so that the output torque Te of the engine 11 becomes the target engine torque Teins.
- step S36 the engine control device 10 sets the guard value Tgurad to the target engine torque Teins, and controls the electronic throttle device 26 so that the output torque Te of the engine 11 becomes the target engine torque Teins.
- the engine control device 10 determines whether or not the torque capacity Tclt of the clutch mechanism 13 has become zero. If the engine control apparatus 10 determines that the torque capacity Tclt has become 0 (YES in step S37), the engine control apparatus 10 proceeds to RETURN.
- step S37 if it is determined that the torque capacity Tclt is not 0 (NO in step S37), the process proceeds to step S31.
- the engine control apparatus 10 allows the engine 11 when the torque capacity Tclt of the clutch mechanism 13 starts to decrease due to the clutch mechanism 13 starting to shift from the transmission state to the cutoff state.
- the output of the engine 11 so that the output torque Te transmitted from the clutch mechanism 13 to the clutch mechanism 13 follows the torque capacity Tclt of the clutch mechanism 13, the drive system components when the clutch mechanism 13 changes from the transmission state to the cutoff state. It is possible to prevent the twisting torque from being accumulated in the engine 11 and to prevent the engine 11 from being blown up.
- the vehicle control device has an effect of improving drivability during shifting in a vehicle including a manual transmission, and transmits a driving force to the manual transmission. This is useful for a control device for a vehicle equipped with an internal combustion engine.
Abstract
Description
以下、本発明の第1の実施の形態に係る車両1の制御装置について、図1ないし図6を参照して説明する。まず、構成について説明する。
本発明の第2の実施の形態に係るエンジン制御装置について、図7および図8を参照して説明する。
本発明の第3の実施の形態に係るエンジン制御装置について、図9ないし図11を参照して説明する。
10 エンジン制御装置
11 エンジン
12 手動変速機
13 クラッチ機構
15 気筒
17 吸気ポート
18 排気ポート
19 燃焼室
25 スロットル弁
26 電子スロットル装置
29 インジェクタ
32 クランクシャフト
33 インプットシャフト
35 クラッチペダル
36 アウトプットシャフト
37 シフトレバー
38 ピストン
39 コネクティングロッド
40 エンジン回転数センサ
43 クラッチディスク
44 プレッシャープレート
46 クラッチカバー
52 レリーズシリンダ
54 レリーズフォーク
55 レリーズスリーブ
56 プロペラシャフト
59 駆動輪
61 アクセルペダル
62 アクセル開度センサ
63 クラッチストロークセンサ
76 コントロールシャフト
85 スロットルセンサ
Claims (7)
- 内燃機関と駆動輪の間の動力を遮断する遮断状態と伝達する伝達状態との間で切り替え可能な切替手段と、前記切替手段を前記遮断状態と前記伝達状態との間で切り替えるよう操作するための切替操作手段と、前記内燃機関に対する要求出力の大きさを判断する要求出力判断手段と、前記要求出力の大きさに応じて前記内燃機関の出力を制御する制御手段と、を備えた車両の制御装置であって、
前記切替操作手段の操作速度を検出する操作速度検出手段と、
前記切替手段が前記遮断状態に移行したときに前記内燃機関の出力が停止するよう、前記操作速度検出手段により検出された操作速度に応じて前記内燃機関の出力を補正する出力補正手段と、を備えることを特徴とする車両の制御装置。 - 前記出力補正手段は、前記操作速度検出手段により検出された操作速度に基づいて、前記切替手段が遮断状態となる遮断タイミングを算出し、前記遮断タイミングにおいて前記内燃機関の出力を停止させることを特徴とする請求項1に記載の車両の制御装置。
- 前記出力補正手段は、前記操作速度検出手段により検出された操作速度が予め定められた閾値以上であることを条件に、前記切替手段が前記伝達状態から前記遮断状態に移行を開始した際における前記要求出力の大きさが第1の所定値以上である場合に、前記内燃機関の出力を停止させることを特徴とする請求項1に記載の車両の制御装置。
- 前記出力補正手段は、前記操作速度検出手段により検出された操作速度が予め定められた閾値以上であることを条件に、前記切替手段が前記伝達状態から前記遮断状態に移行を開始した際における前記要求出力の大きさが、前記第1の所定値より小さい第2の所定値以下である場合に、前記切替手段が前記遮断状態に移行するまで前記内燃機関の出力を増加させることを特徴とする請求項1に記載の車両の制御装置。
- 前記出力補正手段は、前記内燃機関の出力トルクを前記切替手段のトルク容量に追従させるよう前記内燃機関の出力を補正することを特徴とする請求項1に記載の車両の制御装置。
- 前記内燃機関に吸入される空気量を調節する吸入空気量調節手段を備え、
前記出力補正手段は、前記吸入空気量調節手段を制御することにより前記内燃機関の出力を補正することを特徴とする請求項1ないし請求項5のいずれか1の請求項に記載の車両の制御装置。 - 前記内燃機関に供給される燃料の供給量を調節する燃料供給量調節手段を備え、
前記出力補正手段は、前記燃料供給量調節手段を制御することにより前記内燃機関の出力を補正することを特徴とする請求項1ないし請求項5のいずれか1の請求項に記載の車両の制御装置。
Priority Applications (4)
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PCT/JP2010/005183 WO2012025951A1 (ja) | 2010-08-23 | 2010-08-23 | 車両の制御装置 |
CN201080030712.8A CN102510939B (zh) | 2010-08-23 | 2010-08-23 | 车辆的控制装置 |
JP2011513810A JP5062366B2 (ja) | 2010-08-23 | 2010-08-23 | 車両の制御装置 |
DE112010005819.9T DE112010005819B4 (de) | 2010-08-23 | 2010-08-23 | Steuerungsgerät eines Fahrzeugs |
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PCT/JP2010/005183 WO2012025951A1 (ja) | 2010-08-23 | 2010-08-23 | 車両の制御装置 |
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PCT/JP2010/005183 WO2012025951A1 (ja) | 2010-08-23 | 2010-08-23 | 車両の制御装置 |
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JP (1) | JP5062366B2 (ja) |
CN (1) | CN102510939B (ja) |
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WO2016088223A1 (ja) * | 2014-12-03 | 2016-06-09 | アイシン精機株式会社 | 車両用駆動装置 |
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KR101575536B1 (ko) * | 2014-10-21 | 2015-12-07 | 현대자동차주식회사 | 디젤 하이브리드 차량에서 에어 컨트롤 밸브 제어 방법 |
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JP2004231021A (ja) * | 2003-01-30 | 2004-08-19 | Hitachi Ltd | 車速制御と変速制御を協調制御する車両制御装置及び方法 |
JP2006207430A (ja) * | 2005-01-26 | 2006-08-10 | Toyota Motor Corp | 車両の制御装置 |
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JPS5912140A (ja) * | 1982-07-12 | 1984-01-21 | Mazda Motor Corp | エンジンのスロツトル弁制御装置 |
JP3315881B2 (ja) * | 1996-11-27 | 2002-08-19 | 本田技研工業株式会社 | 車両用動力伝達装置 |
JP2006161561A (ja) * | 2004-12-02 | 2006-06-22 | Toyota Motor Corp | 内燃機関の燃料噴射制御装置 |
JP2007153317A (ja) * | 2005-11-09 | 2007-06-21 | Nissan Motor Co Ltd | 車両走行制御装置及び車両走行制御方法 |
-
2010
- 2010-08-23 WO PCT/JP2010/005183 patent/WO2012025951A1/ja active Application Filing
- 2010-08-23 DE DE112010005819.9T patent/DE112010005819B4/de not_active Expired - Fee Related
- 2010-08-23 CN CN201080030712.8A patent/CN102510939B/zh not_active Expired - Fee Related
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Patent Citations (2)
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JP2004231021A (ja) * | 2003-01-30 | 2004-08-19 | Hitachi Ltd | 車速制御と変速制御を協調制御する車両制御装置及び方法 |
JP2006207430A (ja) * | 2005-01-26 | 2006-08-10 | Toyota Motor Corp | 車両の制御装置 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2016088223A1 (ja) * | 2014-12-03 | 2016-06-09 | アイシン精機株式会社 | 車両用駆動装置 |
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DE112010005819B4 (de) | 2014-01-16 |
JPWO2012025951A1 (ja) | 2013-10-28 |
CN102510939B (zh) | 2013-07-24 |
JP5062366B2 (ja) | 2012-10-31 |
DE112010005819T5 (de) | 2013-06-06 |
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