WO2011111417A1 - 変速機構の制御装置およびその制御方法 - Google Patents
変速機構の制御装置およびその制御方法 Download PDFInfo
- Publication number
- WO2011111417A1 WO2011111417A1 PCT/JP2011/050674 JP2011050674W WO2011111417A1 WO 2011111417 A1 WO2011111417 A1 WO 2011111417A1 JP 2011050674 W JP2011050674 W JP 2011050674W WO 2011111417 A1 WO2011111417 A1 WO 2011111417A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- hydraulic pressure
- transmission mechanism
- output torque
- target output
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H61/06—Smoothing ratio shift by controlling rate of change of fluid pressure
- F16H61/061—Smoothing ratio shift by controlling rate of change of fluid pressure using electric control means
-
- 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
- F02D29/02—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 peculiar to engines driving vehicles; peculiar to engines driving variable pitch propellers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H61/06—Smoothing ratio shift by controlling rate of change of fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/20—Preventing gear creeping ; Transmission control during standstill, e.g. hill hold control
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2300/00—Purposes or special features of road vehicle drive control systems
- B60Y2300/18—Propelling the vehicle
- B60Y2300/18008—Propelling the vehicle related to particular drive situations
- B60Y2300/18016—Start-stop drive, e.g. in a traffic jam
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/60—Inputs being a function of ambient conditions
- F16H59/66—Road conditions, e.g. slope, slippery
- F16H2059/663—Road slope
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/20—Preventing gear creeping ; Transmission control during standstill, e.g. hill hold control
- F16H2061/205—Hill hold control, e.g. with torque converter or a friction device slightly engaged to keep vehicle stationary
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2312/00—Driving activities
- F16H2312/14—Going to, or coming from standby operation, e.g. for engine start-stop operation at traffic lights
Definitions
- the present invention relates to a control device for a transmission mechanism and a control method therefor.
- JP2002-47962A which includes a mechanical oil pump and an electric oil pump and supplies hydraulic pressure from an electric oil pump to a gear corresponding to a start shift position during idle stop control, is disclosed in JP2002-47962A.
- the present invention was invented to solve such a problem, and aims to reduce the uncomfortable feeling given to the driver when returning from idle stop control.
- a control device for a transmission mechanism includes a first clutch that is fastened when starting and a second clutch that is different from the first clutch, and hydraulic pressure is supplied to the first clutch and the second clutch.
- a control device of a transmission mechanism that controls a stepped transmission mechanism that is interlocked when the first clutch and the second clutch are completely engaged, and when returning from idle stop control that automatically stops the engine, Hydraulic control means is provided for controlling the hydraulic pressure supplied to the stepped transmission mechanism so that one clutch is in a completely engaged state and the second clutch is in a slip interlock state where the second clutch is not completely engaged.
- a speed change mechanism control method includes a first clutch that is fastened when starting and a second clutch that is different from the first clutch, and supplies hydraulic pressure to the first clutch and the second clutch.
- the stepped transmission mechanism is interlocked when the first clutch and the second clutch are completely engaged, and the first clutch is released when returning from idle stop control for automatically stopping the engine.
- the hydraulic pressure supplied to the transmission mechanism is controlled so as to be in a completely engaged state and a slip interlock state in which the second clutch is not completely engaged.
- the slip interlock state in which the second clutch is not completely engaged is reduced, thereby reducing the feeling of extrusion due to a temporary increase in the engine speed and reducing the sense of discomfort given to the driver. can do.
- FIG. 1 is a schematic configuration diagram of a vehicle equipped with a transmission control device according to a first embodiment of the present invention.
- FIG. 2 is a schematic configuration diagram of the transmission controller according to the first embodiment of the present invention.
- FIG. 3 is a flowchart for explaining return control from idle stop control according to the first embodiment of the present invention.
- FIG. 4 is a flowchart for explaining slip interlock release control in the first embodiment of the present invention.
- FIG. 5 is a time chart showing changes in acceleration in the first embodiment of the present invention.
- FIG. 6 is a time chart showing changes in acceleration and the like in the first embodiment of the present invention.
- FIG. 7 is a flowchart for explaining return control from idle stop control according to the second embodiment of the present invention.
- FIG. 1 is a schematic configuration diagram of a vehicle equipped with a transmission control device according to a first embodiment of the present invention.
- FIG. 2 is a schematic configuration diagram of the transmission controller according to the first embodiment of the present invention.
- FIG. 3 is
- FIG. 8 is a flowchart for explaining slip interlock release control according to the second embodiment of the present invention.
- FIG. 9 is a time chart showing changes in input torque, output torque, and the like of the subtransmission mechanism in the second embodiment of the present invention.
- FIG. 10 is a flowchart illustrating return control from idle stop control according to the third embodiment of the present invention.
- FIG. 11 is a flowchart for explaining slip interlock release control according to the third embodiment of the present invention.
- FIG. 12 is a time chart showing changes in input torque, output torque, and the like of the auxiliary transmission mechanism in the third embodiment of the present invention.
- FIG. 13 is a time chart showing changes in input torque, output torque, and the like of the auxiliary transmission mechanism when the third embodiment of the present invention is not used.
- FIG. 14 is a time chart showing changes in input torque, output torque and the like of the auxiliary transmission mechanism when the third embodiment of the present invention is used.
- the “transmission ratio” of a certain transmission mechanism is a value obtained by dividing the input rotational speed of the transmission mechanism by the output rotational speed of the transmission mechanism.
- the “lowest speed ratio” is the maximum speed ratio of the transmission mechanism, and the “highest speed ratio” is the minimum speed ratio of the transmission mechanism.
- FIG. 1 is a schematic configuration diagram of a vehicle equipped with a transmission control device according to a first embodiment of the present invention.
- This vehicle includes an engine 1 as a power source.
- the output rotation of the engine 1 is via a torque converter 2 with a lock-up clutch, a first gear train 3, a continuously variable transmission (hereinafter simply referred to as "transmission 4"), a second gear train 5, and a final reduction gear 6.
- transmission 4" continuously variable transmission
- the second gear train 5 is provided with a parking mechanism 8 that mechanically locks the output shaft of the transmission 4 at the time of parking.
- the vehicle includes a mechanical oil pump 10m that is driven by using a part of the power of the engine 1, an electric oil pump 10e that is driven by an electric motor, and a mechanical oil pump 10m or an electric oil pump 10e.
- a hydraulic pressure control circuit 11 that regulates the hydraulic pressure and supplies the hydraulic pressure to each part of the transmission 4, and a transmission controller 12 that controls the hydraulic pressure control circuit 11 and the like.
- the electric oil pump 10 e is driven by an electric motor that is driven by power supplied from the battery 13, and supplies hydraulic pressure to the hydraulic control circuit 11.
- the electric motor is controlled by a motor driver.
- hydraulic pressure cannot be supplied by the mechanical oil pump 10m, for example, when performing idle stop control in which the engine 1 automatically stops, the electric oil pump 10e supplies hydraulic pressure to the hydraulic control circuit 11.
- a check valve 14 is provided in the flow path through which oil discharged from the electric oil pump 10e flows.
- the electric oil pump 10e and the mechanical oil pump 10m are compared, the electric oil pump 10e is smaller than the mechanical oil pump 10m.
- the transmission 4 includes a belt-type continuously variable transmission mechanism (hereinafter referred to as “variator 20”) and an auxiliary transmission mechanism 30 provided in series with the variator 20. “Provided in series” means that the variator 20 and the auxiliary transmission mechanism 30 are provided in series in the power transmission path from the engine 1 to the drive wheels 7.
- the auxiliary transmission mechanism 30 may be directly connected to the output shaft of the variator 20 as in this example, or may be connected via another transmission or power transmission mechanism (for example, a gear train). Alternatively, the subtransmission mechanism 30 may be connected to the front stage (input shaft side) of the variator 20.
- the variator 20 includes a primary pulley 21, a secondary pulley 22, and a V belt 23 wound around the pulleys 21 and 22.
- Each of the pulleys 21 and 22 includes a fixed conical plate, a movable conical plate that is arranged with a sheave surface facing the fixed conical plate, and forms a V-groove between the fixed conical plate, and the movable conical plate.
- the hydraulic cylinders 23a and 23b are provided on the back surface of the movable cylinder to displace the movable conical plate in the axial direction.
- the auxiliary transmission mechanism 30 is a transmission mechanism having two forward speeds and one reverse speed.
- the subtransmission mechanism 30 is connected to a Ravigneaux type planetary gear mechanism 31 in which two planetary gear carriers are coupled, and a plurality of rotating elements constituting the Ravigneaux type planetary gear mechanism 31, and a plurality of frictions that change their linkage state.
- Fastening elements Low brake (first clutch) 32, High clutch (second clutch) 33, Rev brake 34
- the gear position of the auxiliary transmission mechanism 30 is changed.
- the gear position of the subtransmission mechanism 30 is the first speed. If the high clutch 33 is engaged and the low brake 32 and the rev brake 34 are released, the speed stage of the subtransmission mechanism 30 becomes the second speed having a smaller speed ratio than the first speed. Further, if the Rev brake 34 is engaged and the Low brake 32 and the High clutch 33 are released, the shift speed of the subtransmission mechanism 30 is reverse.
- the gear position of the subtransmission mechanism 30 is the first speed. Further, when the vehicle is stopped, when the engine 1 is stopped to return from the idle stop control for improving the fuel efficiency, the Low brake 32 is supplied with hydraulic pressure and completely engaged, and the High clutch 33 is slipped. Interlocked.
- the slip interlock state refers to a state where the high clutch 33 is not completely engaged and is in a predetermined slip state. Here, a state where the piston stroke of the high clutch 33 is completed and the high clutch 33 has moved to a position where it is not completely engaged is referred to as a slip interlock state. Moreover, it is said that making the High clutch 33 into a slip interlock state is slip interlock.
- the low brake 32, the high clutch 33, and the Rev brake 34 of the auxiliary transmission mechanism 30 each generate a transmission torque corresponding to the supplied hydraulic pressure.
- the high clutch 33 is held in a state where the supply of hydraulic pressure is started so as to be in the slip interlock state, and the piston stroke of the high clutch 33 is completed.
- the vehicle speed detected by the vehicle speed sensor 43 is zero
- the vehicle is determined to be stopped when conditions such as (1) and (2) are maintained for a predetermined time.
- the idle stop control is not started unless the oil pressure of the high clutch 33 detected by the oil pressure sensor 48 increases from zero to the oil pressure at which the slip interlock state is set. It should be noted that the idle stop control may be started when a time necessary for the high clutch 33 to enter the slip interlock state has elapsed. In this case, the necessary time is a time required for the hydraulic pressure of the high clutch 33 to rise from zero to the hydraulic pressure at which the slip interlock state is established.
- idle stop control is stopped when, for example, the brake pedal is depressed.
- the transmission controller 12 includes a CPU 121, a storage device 122 including a RAM and a ROM, an input interface 123, an output interface 124, and a bus 125 that interconnects them.
- the input interface 123 includes an output signal of an accelerator opening sensor 41 that detects an accelerator opening APO that is an operation amount of an accelerator pedal, an output signal of a rotation speed sensor 42 that detects an input rotation speed of the transmission 4, and a vehicle speed VSP.
- the output signal of the vehicle speed sensor 43 to detect, the output signal of the engine speed sensor 44 to detect the engine speed, the output signal of the inhibitor switch 45 to detect the position of the select lever, the output of the brake sensor 46 to detect the foot brake depression.
- a signal, a signal from the G sensor 47 that detects the inclination of the vehicle, an output signal from the hydraulic sensor 48 that detects the hydraulic pressure supplied to the high clutch 33, and the like are input.
- the storage device 122 stores a control program (FIG. 3) for controlling the auxiliary transmission mechanism 30 and the like.
- the CPU 121 reads and executes a control program stored in the storage device 122, performs various arithmetic processes on various signals input via the input interface 123, generates a control signal, and generates the generated control signal.
- the output is output to the hydraulic control circuit 11 and the electric oil pump 10e through the output interface 124.
- Various values used in the arithmetic processing by the CPU 121 and the arithmetic results are appropriately stored in the storage device 122.
- the hydraulic control circuit 11 includes a plurality of flow paths and a plurality of hydraulic control valves.
- the hydraulic control circuit 11 controls a plurality of hydraulic control valves on the basis of the shift control signal from the transmission controller 12 to switch the hydraulic pressure supply path and is necessary from the hydraulic pressure generated by the mechanical oil pump 10m and the electric oil pump 10e.
- the hydraulic pressure is adjusted and supplied to each part of the transmission 4. As a result, the gear ratio of the variator 20 and the gear position of the subtransmission mechanism 30 are changed, and the transmission 4 is shifted.
- idle top control is performed to stop the engine 1 and improve fuel efficiency.
- the slip interlock is opened and the vehicle is started.
- step S100 it is determined whether or not the slip interlock is being released.
- the slip interlock release flag is “1”. If the slip interlock release flag is “1”, it is determined that the slip interlock is being released, and the process proceeds to step S104. On the other hand, if the slip interlock release flag is “0”, it is determined that the slip interlock is not being released, and the process proceeds to step S101.
- step S101 the engine rotation speed sensor 44 detects the engine rotation speed Ne, and compares the engine rotation speed Ne with the start determination rotation speed. If the engine rotation speed Ne is greater than the start determination rotation, the process proceeds to step S102. If the engine rotation speed Ne is equal to or less than the start determination rotation, the current control is terminated. When returning from the idle stop control, the engine 1 is started and the engine rotational speed Ne gradually increases.
- the start determination rotational speed is a value set in advance, and is a value with which it can be determined that the engine 1 has started.
- the initial hydraulic pressure reduces the torque output from the subtransmission mechanism 30 so as to reduce the feeling of pushing given to the driver when the engine rotational speed Ne is temporarily increased, that is, when the engine 1 is blown up.
- the hydraulic pressure can be set to a range larger than the hydraulic pressure.
- the hydraulic pressure is supplied to the high clutch 33 and the high clutch 33 is engaged to stop the vehicle that has started to move due to its own weight.
- the hydraulic pressure is set in a range smaller than the hydraulic pressure to be caused.
- the initial hydraulic pressure is set according to the slope of the road surface on which the vehicle has stopped.
- the gradient is detected by the G sensor 47.
- the initial hydraulic pressure increases as the upward gradient increases.
- the gradient detected by the G sensor 47 is a downward gradient, the initial hydraulic pressure decreases as the downward gradient increases (the upward gradient decreases).
- the ascending slope is large, it is possible to reduce the vehicle from sliding down by increasing the initial hydraulic pressure.
- the descending slope is large, the initial hydraulic pressure is reduced, so that the decrease in driving force by the high clutch 33 can be reduced, and the vehicle can be started quickly without causing the driver to feel uncomfortable.
- step S102 a change amount (increase amount) ⁇ Ne per unit time of the engine rotation speed Ne is calculated, and it is determined whether or not the change amount Ne is equal to or less than a first predetermined value. Then, when the change amount ⁇ Ne is equal to or less than the first predetermined value, it is determined that the engine 1 finishes rising, and the process proceeds to step S103, and when the change amount Ne is larger than the first predetermined value, the engine 1 increases. Is determined not to end, and the current control is terminated. The amount of change ⁇ Ne becomes small immediately before the engine 1 finishes rising.
- the amount of change ⁇ Ne is obtained by converting the deviation between the engine speed Ne detected this time and the engine speed Ne detected last time into the amount of change per unit time. Further, the change amount ⁇ Ne per unit time may be calculated from the engine rotation speed Ne stored in the storage device 122.
- the first predetermined value is a value with which it is possible to determine that the racing of the engine 1 is finished when returning from the idle stop control, and is set to, for example, zero.
- the first predetermined value is set according to the gradient detected by the G sensor 47. When the gradient detected by the G sensor 47 is an ascending gradient, the first predetermined value increases as the ascending gradient increases. As a result, when the ascending slope is large, the timing for starting the slip interlock release control can be advanced.
- the first predetermined value increases as the downward gradient increases.
- the timing for starting the slip interlock release control can be advanced.
- the amount of change ⁇ Ne per unit time of the engine rotational speed Ne is calculated, but the deviation between the engine rotational speed Ne detected this time and the engine rotational speed Ne detected last time is compared with a predetermined amount of change. Also good.
- the engine speed Ne is stored in the storage device 122.
- the stored engine speed Ne is referred to as engine speed Ne ′.
- step S103 the slip interlock release flag is set to “1”. Thereby, slip interlock release control is started from the next control.
- the slip interlock release flag is set to “0” as an initial value.
- step S100 If it is determined in step S100 that the slip interlock release flag is “1”, slip interlock release control is performed in step S104.
- step S200 the command hydraulic pressure of the high clutch 33 is set.
- the command hydraulic pressure of the high clutch 33 is set so as to monotonously decrease from the initial hydraulic pressure with a predetermined opening gradient.
- the command hydraulic pressure of the high clutch 33 is calculated and set so that the amount of decrease per unit time becomes the second predetermined value.
- a hydraulic pressure obtained by subtracting a predetermined reduction amount from the previously calculated command hydraulic pressure to the High clutch 33 is calculated as the command hydraulic pressure to the High clutch 33.
- the predetermined decrease amount is a value calculated corresponding to the second predetermined value.
- the second predetermined value is set in advance by an experiment or the like, so that the shock given to the driver while the slip interlock is released is small, the feeling of pushing is reduced, and the feeling of stickiness at the start is not given to the driver. Is set.
- the second predetermined value is set according to the gradient detected by the G sensor 47. When the gradient detected by the G sensor 47 is an upward gradient, the second predetermined value increases as the upward gradient increases, and the predetermined opening gradient increases. As a result, the slip interlock is released early, and the vehicle can be prevented from sliding backward and the vehicle can be started quickly. When the gradient detected by the G sensor 47 is a downward gradient, the second predetermined value increases as the downward gradient increases. As a result, the slip interlock is released early and the vehicle can be started quickly.
- step S201 the hydraulic pressure of the high clutch 33 is controlled.
- the oil pressure of the high clutch 33 is controlled based on the set instruction oil pressure of the high clutch 33.
- step S105 it is determined whether or not the indicated hydraulic pressure to the high clutch 33 has become zero. If the command hydraulic pressure to the high clutch 33 is zero, the process proceeds to step S106. If the command hydraulic pressure to the high clutch 33 is not zero, the current control is terminated.
- step S106 the slip interlock release control is terminated.
- the slip interlock release flag is reset to “0”.
- the hydraulic pressure supplied to the high clutch 33 decreases from the initial hydraulic pressure with a predetermined release gradient, and the slip interlock is released.
- FIG. 5 is a time chart when the road surface on which the vehicle is stopped is flat.
- the engine speed Ne increases and the output torque of the torque converter 2 also increases.
- the hydraulic oil pressure is supplied from the electric oil pump 1 oe, but since the discharge pressure of the mechanical oil pump 10 m is large due to the increase in the engine rotation speed Ne, the oil pressure is supplied to the low brake 32 and the high clutch 33. The hydraulic pressure is increased.
- the hydraulic pressure of the high clutch 33 becomes the initial hydraulic pressure, and the high clutch 33 enters the slip interlock state according to the initial hydraulic pressure.
- the oil pressure of the Low brake 32 is indicated by a solid line
- the oil pressure of the High clutch 33 is indicated by a broken line.
- the engine rotation speed Ne becomes the start determination rotation speed.
- the timing when the hydraulic pressure of the High clutch 33 becomes the initial hydraulic pressure and the timing when the engine rotation speed Ne becomes the start determination rotation speed are the same, but the present invention is not limited to this.
- the slip interlock release flag is set to “1” and the slip interlock release control is started.
- the hydraulic pressure of the high clutch 33 gradually decreases, and the slip interlock is released.
- the first predetermined value is set to zero.
- the high clutch 33 When the interlock is performed, the high clutch 33 is completely engaged. Therefore, when the vehicle is started after returning from the idle stop control, the time until the high clutch 33 is released becomes long, and the startability of the vehicle is poor. It also gives the driver a feeling of rattling. In the present embodiment, by slip interlocking the high clutch 33, the acceleration applied to the vehicle rises faster than in the case of interlocking, and the startability of the vehicle is improved.
- the hydraulic pressure of the high clutch 33 becomes the initial hydraulic pressure, and the high clutch 33 enters a slip interlock state in which transmission torque corresponding to the initial hydraulic pressure is generated.
- the interlock release of the high clutch 33 is started at time t2, and the vehicle starts to move again. Therefore, when the high clutch 33 is interlocked, when returning from the idle stop control, the vehicle starts to move, temporarily stops by being interlocked, and then starts to move again by releasing the interlock. Gives the driver a sense of incongruity.
- the vehicle since the high clutch 33 is slip-interlocked, the vehicle does not stop once, and the uncomfortable feeling given to the driver can be reduced.
- the high clutch 33 different from the starting low brake 32 is slip-interlocked to suppress a shock caused by the engine 1 being blown up and to reduce the feeling of extrusion given to the driver. (Corresponding to claim 1).
- the slip interlock release control is started when the change amount ⁇ Ne of the engine rotational speed Ne becomes equal to or less than the first predetermined value, the occurrence of shock due to the engine 1 being blown up can be reduced, and the feeling of extrusion can be reduced. .
- the hydraulic pressure of the high clutch 33 is decreased at a predetermined release gradient, so that the vehicle can be started with a reduced feeling of pushing given to the driver.
- the initial hydraulic pressure is increased, so that when the vehicle returns from the idle stop control, it is possible to reduce the vehicle from sliding backward, and to improve the startability of the vehicle.
- the rising of the output torque of the subtransmission mechanism 30 can be accelerated, and the vehicle can be prevented from sliding backward, thereby improving the startability of the vehicle. be able to.
- the supply of the hydraulic pressure of the high clutch 33 is started, and the high clutch 33 is slip-interlocked.
- the brake pedal is stepped down and returned from the idle stop control immediately after the idle stop control is performed. Even in this case, the high clutch 33 can be slip-interlocked reliably.
- the high clutch 33 can be reliably slip-interlocked when returning from the idle stop control.
- This embodiment is different in a method of calculating the command oil pressure to the high clutch 33 in the slip interlock release control when returning from the idle stop control.
- step S300 to step S302 Since the control from step S300 to step S302 is the same as the control from step S100 to step S102 of the first embodiment, description thereof is omitted here.
- step S303 an initial output torque value in the auxiliary transmission mechanism 30 at the start of the slip interlock release control is calculated.
- the initial output torque value is calculated as follows.
- A is a coefficient determined by the gear ratio, loss, etc. of the stepped transmission mechanism. Further, the transmission torque of the high gear is generated by supplying a predetermined hydraulic pressure to the high gear.
- the output torque T2out of the torque converter is transmitted to the stepped transmission mechanism, so that a member such as a gear is not disposed between the stepped transmission mechanism and the torque converter. If no loss occurs, the actual input torque T1in of the stepped transmission is equal to the output torque T2out of the torque converter.
- the output torque T2out of the torque converter is calculated based on the formula (2).
- ⁇ is the torque capacity of the torque converter
- t is the torque ratio
- the first gear train 3 and the transmission 4 are disposed between the torque converter 2 and the auxiliary transmission mechanism 30. Therefore, the actual input torque T1in input to the subtransmission mechanism 30 is multiplied by the output torque T2out calculated by the equation (2) by a coefficient B that takes into account the gear ratio and loss in the first gear train 3 and the transmission 4. It is expressed by doing.
- equation (1) becomes equation (3) in this embodiment.
- the output torque T2out is referred to as the input torque T3 of the auxiliary transmission mechanism 30 for convenience.
- the Low brake 32 is fastened by the hydraulic pressure supplied from the mechanical oil pump 10m, and the High clutch 33 is slip interlocked. That is, the torque capacity of the Low brake 32 can be secured.
- the input torque T3 at the start of the slip interlock release control can be calculated by the equation (2) using the engine rotational speed Ne detected in step S301. Further, the transmission torque of the high clutch 33 is generated according to the initial hydraulic pressure of the high clutch 33. Therefore, the actual output torque T1out at the start of the slip interlock release control is calculated based on the engine speed Ne. This actual output torque T1out becomes the output torque initial value at the start of the slip interlock release control.
- step S304 the slip interlock release flag is set to “1”.
- step S305 slip interlock release control is performed.
- the slip interlock release control will be described with reference to the flowchart of FIG.
- step S400 the target output torque T1o is calculated.
- the target output torque T1o is set such that the actual output torque T1out of the subtransmission mechanism 30 increases monotonously with a predetermined increase gradient from the output torque initial value.
- the target output torque T1o is calculated by adding the third predetermined value to the previously calculated actual output torque T1out ′.
- the third predetermined value is a value set in advance by experiments or the like.
- the driver is not given a feeling of jerking at the start and It is a value that gives a small shock.
- the target output torque T1o monotonously increases so that the increase amount per unit time becomes the predetermined increase amount.
- the third predetermined value is set according to the gradient detected by the G sensor 47.
- the gradient detected by the G sensor 47 is an upward gradient
- the third predetermined value increases as the upward gradient increases.
- the third predetermined value increases, the rising gradient of the target output torque T1o increases.
- the third predetermined value increases as the downward gradient increases.
- step S401 the transmission torque of the high clutch 33 is calculated.
- the transmission torque of the high clutch 33 is calculated by equation (5) using the target output torque T1o.
- High torque 33 transmission torque input torque T3 ⁇ B ⁇ target output torque T1o ⁇ A (5)
- the input torque T3 is calculated by the equation (2) using the engine speed Ne detected by the engine speed sensor 44.
- the transmission torque of the high clutch 33 is calculated so that the actual output torque T1out of the auxiliary transmission mechanism 30 increases monotonously with a predetermined rising gradient from the initial value of the output torque. That is, the transmission torque of the high clutch 33 decreases.
- step S402 the command hydraulic pressure of the high clutch 33 is set.
- the command hydraulic pressure of the high clutch 33 is calculated and set so as to realize the calculated transmission torque of the high clutch 33. That is, the command hydraulic pressure of the high clutch 33 is calculated so that the actual output torque T1out of the subtransmission mechanism 30 increases monotonously with a predetermined upward gradient from the output torque initial value.
- the third predetermined value increases as the ascending gradient increases or the descending gradient increases, and the increasing gradient of the target output torque T1o increases. Therefore, the amount of decrease per unit time in the command hydraulic pressure of the High clutch 33 increases as the ascending gradient increases or the descending gradient increases.
- step S403 the hydraulic pressure supplied to the high clutch 33 is controlled based on the command hydraulic pressure of the high clutch 33.
- the greater the upward gradient or the greater the downward gradient the greater the amount of decrease in hydraulic pressure supplied to the high clutch 33 per unit time.
- the greater the upward gradient the earlier the hydraulic pressure supplied to the High clutch 33 decreases, the slip interlock is released early, and the vehicle can be prevented from sliding backward, and the vehicle can be started quickly.
- the greater the downward gradient the faster the hydraulic pressure supplied to the high clutch 33 decreases, the slip interlock is released earlier, and the vehicle can be started quickly.
- the hydraulic pressure of the high clutch 33 is controlled so that the actual output torque T1out of the auxiliary transmission mechanism 30 increases monotonously with a predetermined rising gradient.
- step S306 it is determined whether or not the indicated hydraulic pressure of the high clutch 33 has become zero. If the command hydraulic pressure to the high clutch 33 is zero, the process proceeds to step S307. If the command hydraulic pressure to the high clutch 33 is not zero, the current control is terminated.
- step S307 the slip interlock release control is terminated.
- the slip interlock release flag is reset to “0”.
- the engine rotational speed Ne becomes the start determination rotational speed, and when the change amount ⁇ Ne of the engine rotational speed Ne becomes the first predetermined value or less at time t2, the output torque initial value at the start of the slip interlock release control is calculated. Then, slip interlock release control is started.
- the target output torque T1o of the subtransmission mechanism 30 is calculated so as to monotonically increase with a predetermined rising gradient from the output torque initial value. Further, the command hydraulic pressure of the high clutch 33 is set so as to achieve the target output torque T1o, and the command hydraulic pressure of the high clutch 33 decreases.
- the amount of decrease in the hydraulic pressure of the high clutch 33 per unit time can be increased by increasing the upward gradient of the target output torque T1o. Therefore, when returning from the idle stop control, the output torque T1out of the subtransmission mechanism 30 rises quickly, and the vehicle slippage can be reduced and the startability of the vehicle can be improved.
- This embodiment is different in the method of calculating the command oil pressure of the High clutch 33 in the slip interlock release control when returning from the idle stop control.
- step S500 and step S501 are the same as the control of step S100 and step S101 of the first embodiment, description thereof is omitted here.
- step S502 it is determined whether or not a predetermined time has elapsed since the engine rotational speed Ne has become larger than the start determination rotational speed.
- the predetermined time is a time during which it can be accurately determined that the engine 1 is larger than the start determination rotational speed. Thereby, it is possible to prevent the slip interlock start control from being started when the engine rotation speed Ne temporarily becomes higher than the start determination rotation speed.
- step S503 and step S504 Since the control in step S503 and step S504 is the same as that in step S303 and step S304 of the second embodiment, description thereof is omitted here.
- step S505 slip interlock release control is performed.
- the slip interlock release control will be described with reference to the flowchart of FIG.
- step S600 the target output torque T1o is calculated.
- the target output torque T1o is calculated based on the equation (6).
- Target output torque T1o ⁇ A (target output torque T1o ⁇ A) ′ + MAX ⁇ input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′, fourth predetermined value ⁇ Expression (6)
- (Target output torque T1o ⁇ A) ′” is the value of the target output torque T1o ⁇ A of the previous calculation, and is stored in the storage device 122.
- (Input torque T3 ⁇ B) ′” is the previously calculated input torque T3 ⁇ B, and is stored in the storage device 122.
- the fourth predetermined value is a preset value, which is the minimum increase amount of the target output torque T1o, and is a value that does not give the driver a feeling of stagnation at the start and reduces the shock given to the driver. is there.
- the fourth predetermined value is set according to the gradient detected by the G sensor 47. When the gradient detected by the G sensor 47 is an upward gradient, the fourth predetermined value increases as the upward gradient increases. When the gradient detected by the G sensor 47 is a downward gradient, the fourth predetermined value increases as the downward gradient increases.
- the fourth predetermined value is, for example, a value equal to the third predetermined value in the second embodiment.
- the engine 1 When returning from the idle stop control, the engine 1 is blown up, the engine speed Ne is temporarily increased, and converges to the idle speed. When the engine 1 blows up, the increase amount of the engine rotation speed Ne increases.
- “MAX ⁇ input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′, fourth predetermined value ⁇ ” returns from the idle stop control, the engine 1 is blown up, and the increase amount of the engine rotation speed Ne is large. In this case, “input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′” becomes larger than the fourth predetermined value. On the other hand, after the engine 1 is blown up, the fourth predetermined value becomes larger than “input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′”.
- the fourth predetermined value is set according to the upward gradient detected by the G sensor 47. When the fourth predetermined value increases, Max ⁇ input torque T3 ⁇ B- (input torque T3 ⁇ B) ', fourth predetermined value. The area where the fourth predetermined value is selected is widened by the value ⁇ .
- Target output torque T1o ⁇ A (target output torque T1o ⁇ A) '+ input torque T3 ⁇ B- (input torque T3 ⁇ B)' (7)
- Target output torque T1o ⁇ A ⁇ Input torque T3 ⁇ B (Target output torque T1o ⁇ A) ′ ⁇ (Input torque T3 ⁇ B) ′ Expression (8)
- Target output torque T1o ⁇ A (target output torque T1o ⁇ A) ′ + fourth predetermined value Expression (9)
- Equation (9) indicates that the target output torque T1o monotonously increases at a fourth predetermined value with respect to “(target output torque T1o ⁇ A) ′” calculated last time.
- step S601 the transmission torque of the high clutch 33 is calculated.
- “input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′” is greater than the fourth predetermined value, the transmission torque of the high clutch 33 is the transmission torque of the high clutch 33 at the time of the previous calculation.
- the fourth predetermined value is larger than “input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′”, it is calculated by the equation (5) using the calculated target output torque T1o.
- the transmission torque of the high clutch 33 is calculated so that the actual output torque T1out of the auxiliary transmission mechanism 30 increases monotonously with a predetermined rising gradient.
- a region in which the fourth predetermined value becomes larger than “input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′” becomes wider.
- step S602 the command hydraulic pressure of the high clutch 33 is set.
- the command hydraulic pressure of the high clutch 33 is calculated and set so as to realize the calculated transmission torque of the high clutch 33.
- “input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′” is larger than the fourth predetermined value, the command hydraulic pressure of the high clutch 33 becomes the command hydraulic pressure of the high clutch 33 at the previous calculation.
- the fourth predetermined value is larger than “input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′”
- the actual output torque T1out of the auxiliary transmission mechanism 30 increases monotonously with a predetermined rising gradient.
- the fourth predetermined value increases as the ascending gradient increases or the descending gradient increases, and the increasing gradient of the target output torque T1o increases. Therefore, the amount of decrease per unit time in the command hydraulic pressure of the High clutch 33 increases as the ascending gradient increases or the descending gradient increases.
- a region where the fourth predetermined value is larger than “input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′” is widened.
- the indicated hydraulic pressure of the High clutch 33 is initially set. The timing to drop from the hydraulic pressure is earlier.
- step S603 the hydraulic pressure supplied to the high clutch 33 is controlled based on the command hydraulic pressure of the high clutch 33.
- step S506 it is determined whether or not the indicated hydraulic pressure of the high clutch 33 has become zero. If the command hydraulic pressure to the high clutch 33 is zero, the process proceeds to step S507. If the command hydraulic pressure to the high clutch 33 is not zero, the current control is terminated.
- step S507 the slip interlock release control is terminated.
- the slip interlock release flag is reset to “0”.
- the slip interlock release control is started.
- the slip interlock release control is started.
- the fourth predetermined value becomes larger than “input torque T3 ⁇ B ⁇ (input torque T3 ⁇ B) ′”. Therefore, the target output torque T1o is calculated so as to increase monotonously as shown in Expression (9). Further, the command hydraulic pressure of the high clutch 33 is set so as to achieve the target output torque T1o, and the command hydraulic pressure of the high clutch 33 decreases.
- FIG. 13 is a time chart when this embodiment is not used, and when the second embodiment is used.
- FIG. 14 is a time chart when this embodiment is used.
- the case where the response of the hydraulic pressure supplied to the high clutch 33 is slow will be described.
- the target output torque T1o of the auxiliary transmission mechanism 30 is calculated so as to increase monotonously.
- the actual hydraulic pressure of the high clutch 33 does not increase when the engine speed Ne increases. Therefore, the feeling of extrusion due to the increase in the engine rotation speed Ne increases.
- the increase of the engine speed Ne is finished, the actual hydraulic pressure of the high clutch 33 is increased. Therefore, the actual output torque T1out of the high clutch 33 decreases and the vehicle decelerates. As a result, the change (amplitude) of the actual output torque T1out of the high clutch 33 is increased, and the uncomfortable feeling given to the driver is increased.
- the command hydraulic pressure of the high clutch 33 decreases even if the engine rotation speed Ne increases again. The occurrence of shock associated with the rise cannot be suppressed.
- the target output torque T1o is calculated by comparing the deviation between “input torque T3 ⁇ B” calculated this time and “(input torque T3 ⁇ B) ′” calculated last time and the fourth predetermined value.
- the instruction hydraulic pressure of the High clutch 33 is maintained, so that the vehicle that has started does not decelerate, and the uncomfortable feeling given to the driver can be reduced.
- the response of the hydraulic pressure is slow, the change (amplitude) of the output torque T1out of the auxiliary transmission mechanism 30 can be reduced, and the uncomfortable feeling given to the driver can be reduced.
- the timing at which slip interlock release control is performed can be advanced by increasing the fourth predetermined value as the ascending gradient increases. Therefore, when returning from the idle stop control, the output torque T1out of the subtransmission mechanism 30 rises quickly, so that the vehicle can be lowered and the vehicle startability can be improved.
- the amount of decrease in the hydraulic pressure of the high clutch 33 per unit time can be increased by increasing the fourth predetermined value. Therefore, when returning from the idle stop control, the output torque T1out of the subtransmission mechanism 30 rises quickly, so that the vehicle can be lowered and the vehicle startability can be improved.
- the vehicle including the continuously variable transmission and the auxiliary transmission mechanism 30 has been described.
- the present invention is not limited to this.
- the second predetermined value or the like in the first embodiment is set based on the gradient detected by the G sensor 47, but the second predetermined value or the like may be set based on the gradient at the time of starting the vehicle. You may set for every predetermined time based on the gradient detected for every subsequent predetermined time.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Control Of Transmission Device (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Control Of Driving Devices And Active Controlling Of Vehicle (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
Description
Claims (12)
- 発進時に締結される第1クラッチ(32)と、前記第1クラッチ(32)とは異なる第2クラッチ(33)とを備え、前記第1クラッチ(32)と前記第2クラッチ(33)とに油圧が供給されて、前記第1クラッチ(32)と前記第2クラッチ(33)とが完全に締結するとインターロックされる有段変速機構(30)を制御する変速機構の制御装置であって、
エンジン(1)を自動停止するアイドルストップ制御から復帰する場合に、前記第1クラッチ(32)が完全締結状態となり、前記第2クラッチ(33)が完全に締結しないスリップインターロック状態となるように前記有段変速機構(30)に供給する油圧を制御する油圧制御手段(12)を備える変速機構の制御装置。 - 前記油圧制御手段(12)は、前記エンジン回転速度の単位時間当たりの増加量が第1の所定値よりも小さくなった時に前記第2クラッチ(33)に供給される前記油圧の低下を開始する請求項1に記載の変速機構の制御装置。
- 前記油圧制御手段(12)は、前記第2クラッチ(33)に供給する前記油圧が単位時間当たりの減少量が第2所定値となるように前記第2クラッチ(33)に供給する前記油圧を制御する請求項1または2に記載の変速機構の制御装置。
- 前記油圧制御手段(12)は、
前回算出された目標出力トルクに、第3所定値を加算することで目標出力トルクを算出する目標出力トルク算出手段(12)を備え、
前記目標出力トルク算出手段(12)によって算出された前記目標出力トルクに基づいて、前記第2クラッチ(33)に供給する前記油圧を制御する請求項1または2に記載の変速機構の制御装置。 - 前記油圧制御手段(12)は、
前記エンジン回転速度に基づいて前記有段変速機構の入力トルクを算出し、今回算出された前記有段変速機構(30)の入力トルクと前回算出された前記有段変速機構(30)の入力トルクとの偏差と、第4所定値とに基づいて前記有段変速機構(30)の目標出力トルクを算出する目標出力トルク算出手段(12)とを備え、
前記目標出力トルク算出手段(12)によって算出された前記目標出力トルクに基づいて、前記第2クラッチ(33)に供給する前記油圧を制御する請求項1に記載の変速機構の制御装置。 - 前記目標出力トルク算出手段(12)は、前記偏差が前記第4所定値よりも大きい場合には前記偏差を前回算出された目標出力トルクに加算し、前記偏差が前記第4所定値よりも小さい場合には前記第4所定値を前回算出された目標出力トルクに加算して今回演算される目標出力トルクを算出する請求項5に記載の変速機構の制御装置。
- 前記車両の進行方向における路面の勾配を検出する勾配検出手段(47)を備え、
前記車両の進行方向における路面の上り勾配が大きいほど前記初期油圧は大きい請求項1から6のいずれか一つに記載の変速機構の制御装置。 - 前記車両の進行方向における路面の勾配を検出する勾配検出手段(47)を備え、
前記油圧制御手段(12)は、前記車両の進行方向における路面の上り勾配が大きいほど、前記第2クラッチ(33)に供給する前記油圧を前記初期油圧から下げるタイミングを早くする請求項1から7のいずれか一つに記載の変速機構の制御装置。 - 前記車両の進行方向における路面の勾配を検出する勾配検出手段(47)を備え、
前記油圧制御手段(12)は、前記車両の進行方向における路面の上り勾配が大きいほど前記第2クラッチ(33)に供給する油圧の単位時間当たりの減少量を大きくする請求項1から8のいずれか一つに記載の変速機構の制御装置。 - 前記油圧制御手段(12)は、前記車両が停車した時に前記第2クラッチ(33)が前記スリップインターロック状態となるように前記第2クラッチ(33)への油圧供給を開始する請求項1から9のいずれか1つに記載の変速機構の制御装置。
- 前記アイドルストップ制御は、前記第2クラッチ(33)がスリップインターロック状態となった後に開始される請求項1から10のいずれか一つに記載の変速機構の制御装置。
- 発進時に締結される第1クラッチ(32)と、前記第1クラッチ(32)とは異なる第2クラッチ(33)とを備え、前記第1クラッチ(32)と前記第2クラッチ(33)とに油圧が供給されて、前記第1クラッチ(32)と前記第2クラッチ(33)とが完全に締結するとインターロックされる有段の変速機構の制御方法であって、
エンジン(1)を自動停止するアイドルストップ制御から復帰する場合に、前記第1クラッチ(32)を完全締結状態とし、前記第2クラッチ(33)を完全に締結しないスリップインターロック状態とするように前記変速機構に供給する油圧を制御すること変速機構の制御方法。
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11753080.8A EP2546554B1 (en) | 2010-03-09 | 2011-01-17 | Control device for transmission mechanism and control method for same |
KR1020127026275A KR101418198B1 (ko) | 2010-03-09 | 2011-01-17 | 변속 기구의 제어 장치 및 그 제어 방법 |
RU2012142836/11A RU2509243C1 (ru) | 2010-03-09 | 2011-01-17 | Устройство управления и способ управления для трансмиссионного механизма |
US13/576,267 US8892323B2 (en) | 2010-03-09 | 2011-01-17 | Control device and method for stepped transmission ensuring smooth transition in engine idle stop and resumption cycle |
BR112012022660-6A BR112012022660B1 (pt) | 2010-03-09 | 2011-01-17 | dispositivo de controle e método de controle para mecanismo de transmissão |
MX2012009032A MX2012009032A (es) | 2010-03-09 | 2011-01-17 | Dispositivo de control y metodo de control para mecanismo de transmision. |
CN201180006607.5A CN102713366B (zh) | 2010-03-09 | 2011-01-17 | 变速机构的控制装置及其控制方法 |
EP14183775.7A EP2824367B1 (en) | 2010-03-09 | 2011-01-17 | Control device for transmission mechanism |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010-052374 | 2010-03-09 | ||
JP2010052374A JP5331734B2 (ja) | 2010-03-09 | 2010-03-09 | 変速機構の制御装置およびその制御方法 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011111417A1 true WO2011111417A1 (ja) | 2011-09-15 |
Family
ID=44563247
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2011/050674 WO2011111417A1 (ja) | 2010-03-09 | 2011-01-17 | 変速機構の制御装置およびその制御方法 |
Country Status (9)
Country | Link |
---|---|
US (1) | US8892323B2 (ja) |
EP (2) | EP2546554B1 (ja) |
JP (1) | JP5331734B2 (ja) |
KR (1) | KR101418198B1 (ja) |
CN (1) | CN102713366B (ja) |
BR (1) | BR112012022660B1 (ja) |
MX (1) | MX2012009032A (ja) |
RU (1) | RU2509243C1 (ja) |
WO (1) | WO2011111417A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
RU2588406C2 (ru) * | 2011-12-16 | 2016-06-27 | Дзе Гейтс Корпорейшн | Непрерывно изменяемая трансмиссия, система сцепления, транспортное средство. |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5237981B2 (ja) * | 2010-03-09 | 2013-07-17 | ジヤトコ株式会社 | 自動変速機およびその制御方法 |
JP5464134B2 (ja) * | 2010-12-02 | 2014-04-09 | アイシン・エィ・ダブリュ株式会社 | ロックアップ装置およびその制御方法 |
US8958960B2 (en) * | 2011-08-31 | 2015-02-17 | Jatco Ltd | Coast stop vehicle |
US9625034B2 (en) | 2013-09-30 | 2017-04-18 | Jatco Ltd | Control device for stepped transmission mechanism |
JP6322819B2 (ja) * | 2013-12-20 | 2018-05-16 | 日産自動車株式会社 | ハイブリッド車両の駆動装置 |
DE102014222947A1 (de) * | 2014-11-11 | 2016-05-12 | Zf Friedrichshafen Ag | Verfahren zum Bestimmen eines Entleerverhaltens eines hydraulisch betätigbaren Schaltelementes eines Getriebes |
WO2017033742A1 (ja) | 2015-08-25 | 2017-03-02 | ジヤトコ株式会社 | 車両用駆動制御装置及び車両用駆動制御装置の制御方法 |
MX2018005192A (es) * | 2015-10-30 | 2018-08-01 | Nissan Motor | Metodo de control de parada automatica y dispositivo de control de parada automatica. |
JP6717905B2 (ja) | 2018-09-21 | 2020-07-08 | 株式会社Subaru | パーキングロック装置 |
RU2709639C1 (ru) * | 2018-10-30 | 2019-12-19 | Федеральное государственное бюджетное образовательное учреждение высшего образования "Горский государственный аграрный университет" | Способ управления приводом электромобиля и устройство для его осуществления |
CN113719556B (zh) * | 2020-05-26 | 2023-04-07 | 蜂巢传动科技河北有限公司 | 车辆的离合器的控制方法、装置及车辆 |
US11420609B2 (en) | 2020-12-14 | 2022-08-23 | Allison Transmission, Inc. | System and method for controlling engine stop-start events |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03123153U (ja) * | 1990-03-27 | 1991-12-16 | ||
JPH07217737A (ja) * | 1994-01-31 | 1995-08-15 | Mitsubishi Motors Corp | 自動変速機のクリープ制御装置 |
JPH09317864A (ja) * | 1996-05-27 | 1997-12-12 | Toyota Motor Corp | 自動変速機の制御装置 |
JP2002047962A (ja) | 2000-08-03 | 2002-02-15 | Toyota Motor Corp | エンジン自動停止始動装置 |
JP2007271019A (ja) * | 2006-03-31 | 2007-10-18 | Mazda Motor Corp | 自動変速機の制御装置 |
JP2009250417A (ja) * | 2008-04-10 | 2009-10-29 | Jatco Ltd | 自動変速機の制御装置 |
JP2010006326A (ja) * | 2008-06-30 | 2010-01-14 | Mazda Motor Corp | 車両の制御装置 |
JP2010014168A (ja) * | 2008-07-02 | 2010-01-21 | Mazda Motor Corp | 車両の制御装置 |
JP2010052374A (ja) | 2008-08-29 | 2010-03-11 | Toyoda Gosei Co Ltd | 曲がりホースの製造方法 |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SU1791174A1 (ru) * | 1991-04-26 | 1993-01-30 | Bruss Polt I | Способ управления коробкой передач и устройство для его осуществления |
JP3417505B2 (ja) * | 1995-05-12 | 2003-06-16 | アイシン・エィ・ダブリュ株式会社 | 自動変速機の制御装置 |
JP3196076B2 (ja) * | 1998-12-25 | 2001-08-06 | 本田技研工業株式会社 | 原動機付車両 |
JP3429226B2 (ja) * | 1999-07-23 | 2003-07-22 | 本田技研工業株式会社 | 車両用動力伝達装置の制御装置 |
JP2002257220A (ja) * | 2001-03-02 | 2002-09-11 | Jatco Ltd | 自動変速機の制御装置 |
US6589134B2 (en) * | 2001-09-27 | 2003-07-08 | Delphi Technologies, Inc. | System with controller and method for controlling a park-interlock device in a vehicle |
JP4200679B2 (ja) * | 2002-02-18 | 2008-12-24 | アイシン・エィ・ダブリュ株式会社 | 車輌の制御装置 |
JP3915698B2 (ja) * | 2002-12-27 | 2007-05-16 | アイシン・エィ・ダブリュ株式会社 | ハイブリッド車輌の制御装置 |
JP2005233357A (ja) * | 2004-02-23 | 2005-09-02 | Jatco Ltd | 自動変速機の油圧制御装置 |
JP4319151B2 (ja) * | 2005-01-21 | 2009-08-26 | ジヤトコ株式会社 | 自動変速機の制御装置 |
JP4640044B2 (ja) * | 2005-06-01 | 2011-03-02 | トヨタ自動車株式会社 | 自動車およびその制御方法 |
JP4569493B2 (ja) * | 2005-06-06 | 2010-10-27 | 日産自動車株式会社 | ハイブリッド車両のオイルポンプ駆動制御装置 |
FR2920382B1 (fr) * | 2007-08-31 | 2009-10-30 | Renault Sas | Dispositif et procede de determination d'une cartographie du couple transmis par un embrayage equipant un vehicule automobile. |
JP5157344B2 (ja) * | 2007-09-25 | 2013-03-06 | アイシン・エィ・ダブリュ株式会社 | 自動変速機の制御装置 |
JP4363486B2 (ja) * | 2008-01-22 | 2009-11-11 | トヨタ自動車株式会社 | 無段変速機の制御装置および制御方法 |
JP5158108B2 (ja) * | 2009-03-04 | 2013-03-06 | 株式会社デンソー | 車両制御装置 |
JP5229572B2 (ja) * | 2009-03-25 | 2013-07-03 | アイシン・エィ・ダブリュ株式会社 | 車両用制御装置及び車両駆動システム |
-
2010
- 2010-03-09 JP JP2010052374A patent/JP5331734B2/ja active Active
-
2011
- 2011-01-17 MX MX2012009032A patent/MX2012009032A/es active IP Right Grant
- 2011-01-17 EP EP11753080.8A patent/EP2546554B1/en active Active
- 2011-01-17 KR KR1020127026275A patent/KR101418198B1/ko active IP Right Grant
- 2011-01-17 CN CN201180006607.5A patent/CN102713366B/zh active Active
- 2011-01-17 BR BR112012022660-6A patent/BR112012022660B1/pt active IP Right Grant
- 2011-01-17 US US13/576,267 patent/US8892323B2/en active Active
- 2011-01-17 RU RU2012142836/11A patent/RU2509243C1/ru active
- 2011-01-17 WO PCT/JP2011/050674 patent/WO2011111417A1/ja active Application Filing
- 2011-01-17 EP EP14183775.7A patent/EP2824367B1/en active Active
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03123153U (ja) * | 1990-03-27 | 1991-12-16 | ||
JPH07217737A (ja) * | 1994-01-31 | 1995-08-15 | Mitsubishi Motors Corp | 自動変速機のクリープ制御装置 |
JPH09317864A (ja) * | 1996-05-27 | 1997-12-12 | Toyota Motor Corp | 自動変速機の制御装置 |
JP2002047962A (ja) | 2000-08-03 | 2002-02-15 | Toyota Motor Corp | エンジン自動停止始動装置 |
JP2007271019A (ja) * | 2006-03-31 | 2007-10-18 | Mazda Motor Corp | 自動変速機の制御装置 |
JP2009250417A (ja) * | 2008-04-10 | 2009-10-29 | Jatco Ltd | 自動変速機の制御装置 |
JP2010006326A (ja) * | 2008-06-30 | 2010-01-14 | Mazda Motor Corp | 車両の制御装置 |
JP2010014168A (ja) * | 2008-07-02 | 2010-01-21 | Mazda Motor Corp | 車両の制御装置 |
JP2010052374A (ja) | 2008-08-29 | 2010-03-11 | Toyoda Gosei Co Ltd | 曲がりホースの製造方法 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
RU2588406C2 (ru) * | 2011-12-16 | 2016-06-27 | Дзе Гейтс Корпорейшн | Непрерывно изменяемая трансмиссия, система сцепления, транспортное средство. |
Also Published As
Publication number | Publication date |
---|---|
US20120298462A1 (en) | 2012-11-29 |
BR112012022660B1 (pt) | 2020-12-29 |
EP2546554A1 (en) | 2013-01-16 |
US8892323B2 (en) | 2014-11-18 |
MX2012009032A (es) | 2012-09-07 |
KR20130000403A (ko) | 2013-01-02 |
BR112012022660A2 (pt) | 2020-09-01 |
CN102713366A (zh) | 2012-10-03 |
EP2824367A1 (en) | 2015-01-14 |
RU2509243C1 (ru) | 2014-03-10 |
JP2011185379A (ja) | 2011-09-22 |
JP5331734B2 (ja) | 2013-10-30 |
KR101418198B1 (ko) | 2014-07-09 |
EP2546554B1 (en) | 2015-04-15 |
CN102713366B (zh) | 2014-12-17 |
EP2546554A4 (en) | 2013-12-11 |
EP2824367B1 (en) | 2020-03-11 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5331734B2 (ja) | 変速機構の制御装置およびその制御方法 | |
JP6513264B2 (ja) | 車両用無段変速機の制御装置 | |
JP5728422B2 (ja) | ベルト式無段変速機の変速制御装置 | |
JP5116789B2 (ja) | 変速機の油圧制御装置およびその制御方法 | |
JP5712296B2 (ja) | コーストストップ車両、及びその制御方法 | |
JP5767958B2 (ja) | コーストストップ車両およびコーストストップ車両の制御方法 | |
JP6039094B2 (ja) | 有段変速機構の制御装置 | |
JP5750162B2 (ja) | 車両制御装置、及びその制御方法 | |
EP2436953A2 (en) | Coast stop vehicle and control method thereof | |
JP5728575B2 (ja) | コーストストップ車両、及びその制御方法 | |
JP5820931B2 (ja) | 車両制御装置および車両制御方法 | |
WO2015012104A1 (ja) | 車両の制御装置、およびその制御方法 | |
JP6182318B2 (ja) | 車両制御装置および車両制御方法 | |
JP5084870B2 (ja) | 車両のトルクダウン制御装置 | |
KR20170117148A (ko) | 차량 제어 장치 및 차량의 제어 방법 | |
JP6725254B2 (ja) | 車両の制御装置 | |
JP5903351B2 (ja) | 車両制御装置および車両制御方法 | |
WO2014021118A1 (ja) | 車両用の自動変速機 | |
JP5782176B2 (ja) | 無段変速機の変速制御装置及び変速制御方法 | |
JP2008309267A (ja) | 自動変速機の制御装置 | |
JP6019013B2 (ja) | 車両制御装置、及び車両制御方法 | |
JP2013249920A (ja) | 車両のニュートラル制御装置 | |
JP2019031999A (ja) | 無段変速機の制御装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201180006607.5 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 11753080 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2011753080 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13576267 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: MX/A/2012/009032 Country of ref document: MX |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2947/KOLNP/2012 Country of ref document: IN |
|
ENP | Entry into the national phase |
Ref document number: 20127026275 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2012142836 Country of ref document: RU |
|
REG | Reference to national code |
Ref country code: BR Ref legal event code: B01A Ref document number: 112012022660 Country of ref document: BR |
|
ENP | Entry into the national phase |
Ref document number: 112012022660 Country of ref document: BR Kind code of ref document: A2 Effective date: 20120906 |