WO2014017239A1 - 車両用自動変速機の制御装置 - Google Patents
車両用自動変速機の制御装置 Download PDFInfo
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- WO2014017239A1 WO2014017239A1 PCT/JP2013/067422 JP2013067422W WO2014017239A1 WO 2014017239 A1 WO2014017239 A1 WO 2014017239A1 JP 2013067422 W JP2013067422 W JP 2013067422W WO 2014017239 A1 WO2014017239 A1 WO 2014017239A1
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- clutch
- engine
- sticking
- lock
- automatic transmission
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units, or advanced driver assistance systems for ensuring comfort, stability and safety or drive control systems for propelling or retarding the vehicle
- B60W30/18—Propelling the vehicle
- B60W30/192—Mitigating problems related to power-up or power-down of the driveline, e.g. start-up of a cold engine
- B60W30/194—Mitigating problems related to power-up or power-down of the driveline, e.g. start-up of a cold engine related to low temperature conditions, e.g. high viscosity of hydraulic fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
- F02D9/02—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning induction conduits
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/02—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches
- B60W10/024—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches including control of torque converters
- B60W10/026—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches including control of torque converters of lock-up clutches
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units, or advanced driver assistance systems for ensuring comfort, stability and safety or drive control systems for propelling or retarding the vehicle
- B60W30/18—Propelling the vehicle
- B60W30/188—Controlling power parameters of the driveline, e.g. determining the required power
- B60W30/1884—Avoiding stall or overspeed of the engine
-
- 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
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/021—Introducing corrections for particular conditions exterior to the engine
- F02D41/0215—Introducing corrections for particular conditions exterior to the engine in relation with elements of the transmission
- F02D41/022—Introducing corrections for particular conditions exterior to the engine in relation with elements of the transmission in relation with the clutch status
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- 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
- F16H59/36—Inputs being a function of speed
- F16H59/46—Inputs being a function of speed dependent on a comparison between speeds
- F16H2059/465—Detecting slip, e.g. clutch slip ratio
-
- 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
- F16H61/14—Control of torque converter lock-up clutches
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/40—Engine management systems
Definitions
- the present invention relates to a control device for a vehicle automatic transmission having a torque converter with a lock-up clutch.
- a lockup clutch capable of mechanically connecting an output shaft of an engine and an input shaft of an automatic transmission is provided in a torque converter. Then, by engaging a lock-up clutch under certain conditions, the engine speed is kept low and fuel efficiency is improved.
- the lockup clutch is engaged when the gear set by the automatic transmission is a predetermined gear.
- slip control is performed in which the lockup clutch is slid without being completely engaged in accordance with the driving state of the vehicle.
- the target slip ratio corresponding to the operation state of the slip ratio of the lockup clutch is stored corresponding to the gear position, and the lockup is performed so that the actual slip ratio becomes the target slip ratio. Controls the clutch engagement capacity (feedback control).
- JP 2012-62998 A Japanese Patent Laid-Open No. 01-098759
- a transmission provided with a lockup clutch having a multi-plate clutch structure in which a plurality of clutch plates provided on a member on the engine side and a plurality of other clutch plates provided on a member on the automatic transmission side are alternately laminated.
- ATF low viscosity hydraulic oil
- the lock-up clutch is likely to stick, and the engine intake air amount (air amount) is increased from the normal operation state at the first in-gear after the engine start, so that the engine speed can be increased. Suppressing the decrease is being performed.
- the engine intake air amount continues to increase, so that the engine speed increases rapidly (so-called engine speed). There was a problem that a rise in the temperature) occurred.
- control is performed to increase the intake air amount of the engine only at the first in-gear after the engine start in which the friction due to the lock-up clutch sticking is high because the temperature of the hydraulic oil is low.
- the hydraulic oil temperature gradually rises and friction due to sticking of the lock-up clutch decreases, so that control for increasing the intake air amount of the engine is not performed.
- the present invention has been made in view of the above points, and its purpose is to provide a relatively simple control, in which the rotational speed of the engine decreases due to sticking of the lockup clutch, and the engine speed after the sticking is removed is rapidly increased. It is an object of the present invention to provide a control device for an automatic transmission that can prevent both of a serious rise.
- the present invention for solving the above-described problems is regulated by a torque converter (3) having a lock-up clutch (40) provided between an engine (1) and an automatic transmission (2) mounted on a vehicle.
- a hydraulic control device (6) for supplying hydraulic oil to the transmission mechanism (2a) and the torque converter (3) of the automatic transmission (2), and the hydraulic pressure supplied by the hydraulic control device (6) to control the transmission mechanism
- a control means (5) for controlling the setting of the gear ratio according to (2a) and the engagement state of the lock-up clutch (40), wherein the control means (5) is operated.
- the lockup clutch (40) Slip to calculate slip ratio Based on the calculating means (5), the oil temperature (T) of the hydraulic oil determined by the oil temperature determining means (5), and the slip ratio (S) calculated by the slip ratio calculating means (5), the lockup clutch Sticking determination means (5) for determining whether or not (40) is in a sticking state, and intake air amount varying means for changing the intake air amount of the engine (1) based on the determination of the sticking determination means (5) (9, 5), and the oil temperature determination means (5) is a low oil temperature at which the oil temperature (T) of the hydraulic oil is equal to or lower than a predetermined value (T1), and the slip ratio calculation means (5) When the slip ratio (S) calculated in step S is a high slip ratio equal to or greater than a predetermined value (S1), it is determined that the lockup clutch (40) is in
- the lock-up clutch sticking state is determined by the determination of the oil temperature of the hydraulic oil by the oil temperature determination means and the slip ratio of the lock-up clutch calculated by the slip ratio calculation means. The presence or absence of is determined. While it is determined that the lock-up clutch is in the sticking state, the engine intake air amount is increased. On the other hand, when the sticking state determination is canceled, the engine intake air amount is stopped from increasing. Do. As a result, in the region (timing) where the lock-up clutch sticks, the lock-up clutch sticks while effectively preventing the engine speed from decreasing due to an increase in the intake air amount of the engine. In the non-applied region (the region after sticking is eliminated), it is possible to prevent the engine speed from rapidly increasing (so-called engine surging) by stopping the increase in the intake air amount of the engine.
- the lock-up clutch (40) includes a plurality of clutch plates (41a) provided on the member (44) on the engine (1) side and another plurality provided on the member (42) on the automatic transmission (2) side. It may be a lockup clutch having a multi-plate clutch structure in which the clutch plates (41b) are alternately laminated.
- the low-viscosity hydraulic oil remains in the gap between the clutch plates, and the lockup clutch is likely to stick at low temperatures.
- symbol in said parenthesis shows the code
- the lock-up while the lock-up clutch is stuck, the lock-up can be effectively prevented while the engine speed is reduced while the lock-up clutch is stuck. After the clutch sticking is eliminated, the engine speed can be prevented from rapidly increasing (engine blow-up).
- FIG. 1 is a schematic view of a drive system of a vehicle including a control device for an automatic transmission according to an embodiment of the present invention.
- FIG. 2 is a diagram showing a torque converter 3 and a hydraulic control device (hydraulic circuit) 6 which will be described later.
- the vehicle according to the present embodiment includes an engine 1 and an automatic transmission 2 connected to the engine 1 via a fluid type torque converter 3.
- the automatic transmission 2 includes a stepped transmission mechanism 2a capable of setting a plurality of shift stages (for example, six forward speeds and one reverse speed) having different gear ratios.
- the vehicle also includes an FI-ECU 4 that controls the engine 1, an AT-ECU (control means) 5 that controls the automatic transmission 2 including the torque converter 3, a rotational drive of the torque converter 3, and a lock-up clutch that will be described later. And a hydraulic control device 6 for controlling the fastening (engagement) / release of a plurality of friction engagement elements provided in the transmission mechanism 2a of the automatic transmission 2.
- Rotational output of the engine 1 is output to a crankshaft (output shaft of the engine 1) 26.
- the rotation of the crankshaft 26 is transmitted to the main shaft 27 of the automatic transmission 2 via the torque converter 3.
- the transmission mechanism 2a of the automatic transmission 2 includes a plurality of gear trains (gear trains) corresponding to a plurality of shift stages provided between the main shaft 27 and the counter shaft 28, and a plurality of clutches (friction engagement elements). Prepare. Each gear train is composed of a pair of drive gears and driven gears.
- the detailed configuration of the speed change mechanism 2a is not a characteristic part of the present invention, and thus detailed description using a skeleton diagram or the like is omitted. However, those skilled in the art can appropriately adopt the configuration of a known speed change mechanism. it can.
- a crankshaft rotational speed sensor 201 for detecting the rotational speed Ne of the crankshaft 26 (engine 1) is provided.
- a main shaft rotation number sensor 202 for detecting a rotation number (input shaft rotation number of the automatic transmission 2) Ni of the main shaft 27 is provided.
- a countershaft rotational speed sensor 203 for detecting the rotational speed of the countershaft 28 (the output shaft rotational speed of the automatic transmission 2) No is provided.
- the rotation speed data detected by each of the rotation speed sensors 201 to 203 is output to the AT-ECU 5.
- a vehicle speed sensor 204 for detecting the vehicle speed Nv is also provided.
- Vehicle speed data detected by the vehicle speed sensor 204 is output to the AT-ECU 5. Further, a throttle opening sensor 206 for detecting the throttle opening TH of the engine 1 is provided. The throttle opening data detected by the throttle opening sensor 206 is output to the FI-ECU 4. An intake valve 9 for adjusting the amount of air (intake air) supplied to the engine 1 is provided. The operation of the intake valve 9 is controlled by a command from the FI-ECU 4.
- an accelerator pedal opening sensor 207 for detecting an opening (accelerator pedal opening) AP of the accelerator pedal 8 is provided.
- the accelerator pedal opening degree data detected by the accelerator pedal opening degree sensor 207 is output to the FI-ECU 4.
- An oil temperature sensor 208 that detects the oil temperature TA of the hydraulic oil (ATF) of the automatic transmission 2 (hydraulic control device 6) is provided in the vicinity of an oil tank (not shown) in the hydraulic control device 6.
- the ATF temperature (oil temperature) data detected by the oil temperature sensor 208 is output to the AT-ECU 5.
- the vehicle of the present embodiment includes a shift device 60 that is operated by a driver via a shift lever.
- a shift device 60 that is operated by a driver via a shift lever.
- P parking
- R reverse travel
- N neutral
- D automatic transmission mode (normal mode)
- a shift lever position sensor 205 is provided in the vicinity of the shift device 60. The shift lever position sensor 205 detects the position of the shift lever operated by the driver.
- the FI-ECU 4 controls the output of the engine 1, that is, the rotational speed Ne of the engine 1, based on the detection data input from the sensors 202 to 208 and various data input from the AT-ECU 5.
- Rotational torque of the main shaft 27 is transmitted to the counter shaft 28 via a clutch and gear train (not shown in FIG. 1), a gear train of a secondary shaft and an idle shaft, and the like. Further, the rotational torque of the countershaft 28 is transmitted to the drive wheels of the vehicle via a gear train and a differential mechanism (not shown in FIG. 1).
- the torque converter 3 transmits torque via a fluid (hydraulic oil).
- the torque converter 3 includes a front cover 35, a pump impeller (pump impeller) 31 formed integrally with the front cover 35, and a front cover 35 and a pump impeller 31.
- the turbine impeller (turbine runner) 32 disposed opposite to the pump impeller 31 is interposed between the pump impeller 31 and the turbine impeller 32, and the stator shaft (fixed shaft) is interposed via the one-way clutch 33.
- a stator impeller 34 rotatably supported on 36. As shown in FIG.
- crankshaft 26 is connected to a pump impeller 31 of the torque converter 3 via a front cover 35, and the turbine impeller 32 is connected to a main shaft (input shaft of the automatic transmission 2) 27.
- a lockup clutch 40 is provided between the turbine impeller 32 and the front cover 35.
- the lockup clutch 40 of the present embodiment includes a clutch hub 42 provided on the turbine impeller 32 side and a clutch drum 44 provided on the front cover 35 side, and a plurality of clutch plates 41 a attached to the clutch hub 42.
- the lockup clutch has a multi-plate clutch structure in which a plurality of other clutch plates 41b attached to the clutch drum 44 are alternately stacked.
- the space inside the front cover 35 is partitioned into a first oil chamber 37 on the front cover 35 side and a second oil chamber 38 on the turbine impeller 32 side by a movable member 39 having a piston 39a.
- the movable member 39 is movable in accordance with changes in the hydraulic pressures of the first oil chamber 37 and the second oil chamber 38.
- the clutch plate 41a, 41b is pressed and engaged by the piston 39a. The release is switched.
- the lock-up clutch 40 is engaged (fastened) when the hydraulic pressure of the first oil chamber 37 becomes higher than the hydraulic pressure of the second oil chamber 38 under the control of the hydraulic control device 6, while the hydraulic pressure of the first oil chamber 37 is increased.
- the engagement is released when the hydraulic pressure of the second oil chamber 38 becomes lower.
- the hydraulic control device (hydraulic circuit) 6 is an oil pump OP that supplies hydraulic oil in an oil tank (not shown), a regulator valve 21 that regulates the supply pressure from the oil pump OP to a line pressure, and a regulator valve 21 that regulates the pressure. Is further controlled to supply the torque converter 3 with a further regulated pressure of the hydraulic oil, and supply control of the hydraulic oil regulated by the torque converter pressure regulating valve 22 to the first oil chamber 37 and the second oil chamber 38 is performed.
- An LC shift valve 23 to be performed, an LC control valve 24 for controlling the hydraulic pressure of hydraulic oil supplied to the second oil chamber 38, a linear solenoid 25 for supplying signal pressure to the LC control valve 24, and the like are provided.
- the AT-ECU 5 controls the hydraulic control device 6 based on the detection data input from the sensors 202 to 208 and various data input from the FI-ECU 4. Therefore, the hydraulic control device 6 supplies hydraulic oil of line pressure PL (hydraulic pressure) to each of a plurality of friction engagement elements (clutch) (not shown) included in the transmission mechanism 2a of the automatic transmission 2. Thereby, the engagement / disengagement (engagement operation) of the plurality of friction engagement elements can be selectively performed and set to any one of the plurality of shift speeds.
- line pressure PL hydraulic pressure
- the hydraulic control device 6 controls the slip ratio indicating how much the rotational drive of the crankshaft 26 is transmitted to the main shaft 27 by supplying hydraulic oil of hydraulic pressure to the pump impeller 31 of the torque converter 3. At the same time, by supplying hydraulic oil of hydraulic pressure to the oil chambers 37 and 38 of the lockup clutch 40, the lockup clutch 40 is controlled to be engaged (fastened) under predetermined conditions such as when the vehicle is cruising. To do.
- a lockup capacity (fastening force of the lockup clutch 40) is generated by the differential pressure between the first oil chamber 37 and the second oil chamber 38. That is, the discharge pressure (line pressure) of the hydraulic fluid discharged from the oil pump OP is regulated by the torque converter pressure regulating valve 22, and the regulated hydraulic fluid is represented by an internal pressure P1 in FIG. 3 flows into the first oil chamber 37 of the lockup clutch 40.
- the hydraulic oil regulated by the torque converter regulating valve 22 is regulated to a necessary pressure by the LC control valve 24, and the lock-up clutch 40 is connected via the LC shift valve 23 as shown by the piston pressure P2 in FIG. Into the second oil chamber 38.
- the LC shift valve 23 switches on / off (engagement / release) of the lockup clutch 40 by controlling on / off of the hydraulic pressure to the second oil chamber 38.
- a linear solenoid pressure P3 as a pilot pressure is applied to the LC control valve 24.
- the internal pressure of the second oil chamber 38 is controlled. Thereby, the fastening force of the lockup clutch 40 is adjusted, and slip control is performed.
- the hydraulic control device 6 supplies lubricating oil for lubricating the main shaft 27 and the counter shaft 28 of the speed change mechanism 2a, a secondary shaft and an idle shaft (not shown) to the main shaft 27 and the counter shaft 28, and the like.
- the low-viscosity hydraulic oil (ATF) remains in the gaps between the plurality of clutch plates of the lock-up clutch 40, so that the lock-up clutch 40 is locked up at a low temperature.
- An event (a so-called sticking event) occurs in which the clutch plate of the clutch 40 is dragged by another adjacent clutch plate.
- the hydraulic oil is in a low temperature state, such as immediately after the engine 1 is started in a cryogenic environment, the friction generated on the clutch plates 41a and 41b of the lockup clutch 40 during a load change such as in-gear by the transmission mechanism 2a.
- the rotational speed of the engine 1 is reduced by the force (friction).
- control is performed to increase the intake air amount of the engine 1 during in-gear or the like by the speed change mechanism 2a as compared with that during normal operation.
- Control for suppressing a decrease in the rotational speed of the engine 1 is performed.
- the slip ratio of the lock-up clutch 40 is determined by the rotation speed of the engine 1 detected by the crankshaft rotation speed sensor 201 and the rotation of the main shaft (input shaft) 27 of the automatic transmission 2 detected by the main shaft rotation speed sensor 202. Calculate from the number.
- FIG. 3 is a flowchart for explaining a procedure for determining sticking of the lock-up clutch 40 in the engine speed reduction control.
- FIG. 4 is a timing chart showing changes in various values when the engine speed reduction control is performed. The timing chart of FIG. 4 shows changes in the gear stage (shift stage) set by the transmission mechanism 2a, the sticking determination flag of the lockup clutch 40, the slip ratio of the lockup clutch 40, and the intake air amount of the engine 1. Yes.
- step ST1 it is first determined whether or not the oil temperature sensor 208 for detecting the oil temperature of the hydraulic oil is in a failure (failure) state (step ST1). As a result, if the oil temperature sensor 208 is in a failed state (YES), the sticking determination flag FL of the lockup clutch 40 is set to FL ⁇ 0 (no sticking) (step ST2). On the other hand, if the oil temperature sensor 208 is not in a failed state (NO), it is subsequently determined whether or not the slip rate S of the lockup clutch 40 is a high slip rate equal to or greater than a predetermined value S1 (S ⁇ S1) ( Step ST3).
- the slip ratio (ETRW) S of the lockup clutch 40 is not greater than or equal to the predetermined value S1 (high slip ratio) (NO)
- the sticking determination flag FL of the lockup clutch 40 is set to FL ⁇ 0 (no sticking).
- the slip rate S of the lock-up clutch 40 is equal to or greater than the predetermined value S1 (high slip rate) (YES)
- the oil temperature TA of the hydraulic oil (ATF) detected by the oil temperature sensor 208 is continuously the predetermined value TA1. It is then determined whether the temperature is low (TA ⁇ TA1) (step ST4).
- the sticking determination flag FL of the lockup clutch 40 is set to FL ⁇ 0 (no sticking) (step ST2).
- the sticking determination flag FL of the lockup clutch 40 is set to FL ⁇ 1 (sticking) (step ST5).
- control is performed to vary the intake air amount of the engine 1. That is, as shown in the timing chart of FIG. 4, the sticking determination flag of the lock-up clutch 40 at the time of in-gear (time t1) when the gear stage (shift stage) of the transmission mechanism 2a is switched from the neutral (N) to the drive (D).
- the intake air amount A2 is set so that the intake air amount of the engine 1 is increased from the intake air amount A1 during normal operation. Thereby, even if the lockup clutch 40 is sticking, it can prevent that the rotation speed of the engine 1 falls.
- the sticking determination flag FL of the lockup clutch 40 is switched to FL ⁇ 0 (no sticking). Stop the control to increase the intake air amount. That is, the intake air amount of the engine 1 is returned to the intake air amount A1 during normal operation. As a result, it is possible to effectively prevent a sudden increase in the rotational speed of the engine 1 (so-called engine 1).
- the lockup clutch 40 is detected by the hydraulic oil temperature TA detected by the oil temperature sensor 208 and the calculated slip ratio of the lockup clutch 40.
- the sticking state is detected, and the sticking determination of the lockup clutch 40 is performed based on the sticking state. While the lock-up clutch 40 is determined to be in the sticking state, the intake air amount of the engine 1 is increased as compared with that during normal operation. On the other hand, when the determination of the sticking state is released, the intake air of the engine 1 is increased. Control to stop the increase in quantity.
- the transmission mechanism included in the automatic transmission according to the above embodiment is a stepped transmission mechanism capable of setting a plurality of shift stages, but the transmission mechanism included in the automatic transmission according to the present invention is a stepped transmission mechanism. Not only the speed change mechanism but also a continuously variable speed change mechanism capable of setting the speed ratio steplessly according to the hydraulic pressure supplied by the hydraulic control device.
Abstract
Description
なお、上記の括弧内の符号は、後述する実施形態における構成要素の符号を本発明の一例として示したものである。
Claims (2)
- 車両に搭載したエンジンと自動変速機との間に設けたロックアップクラッチ付きのトルクコンバータと、
調圧した作動油を前記自動変速機が有する変速機構及び前記トルクコンバータに供給する油圧制御装置と、
前記油圧制御装置の供給油圧を制御することで、前記変速機構による変速比の設定及び前記ロックアップクラッチの締結状態を制御する制御手段と、を備える車両用自動変速機の制御装置であって、
前記制御手段は、
前記作動油の温度を判定する油温判定手段と、
前記エンジンの出力回転数と前記自動変速機の入力回転数とに基づいて前記ロックアップクラッチのスリップ率を算出するスリップ率算出手段と、
前記油温判定手段で判定した前記作動油の油温と、前記スリップ率算出手段で算出したスリップ率とに基づいて、前記ロックアップクラッチが張り付き状態であるか否かを判定する張り付き判定手段と、
前記張り付き判定手段の判定に基づいて、前記エンジンの吸入空気量を可変させる吸入空気量可変手段と、を備え、
前記油温判定手段は、前記作動油の油温が所定値以下の低油温であり、かつ、前記スリップ率算出手段で算出したスリップ率が所定値以上の高スリップ率のときに、前記ロックアップクラッチが張り付き状態であると判定し、
前記吸入空気量可変手段は、前記張り付き判定手段で前記ロックアップクラッチの張り付き状態と判定されている間は、前記エンジンの吸入空気量を通常の運転状態よりも増加させる制御を行う一方、前記張り付き状態の判定が解除された場合には、前記エンジンの吸入空気量の増加を停止する制御を行う
ことを特徴とする車両用自動変速機の制御装置。 - 前記ロックアップクラッチは、前記エンジン側の部材に設けた複数のクラッチ板と、前記自動変速機側の部材に設けた他の複数のクラッチ板とを交互に積層してなる多板クラッチ構造のロックアップクラッチである
ことを特徴とする請求項1に記載の車両用自動変速機の制御装置。
Priority Applications (5)
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CN201380038443.3A CN104471218B (zh) | 2012-07-27 | 2013-06-25 | 车辆用自动变速器的控制装置 |
DE201311003697 DE112013003697T5 (de) | 2012-07-27 | 2013-06-25 | Steuervorrichtung für Automatikgetriebe für Fahrzeug |
US14/417,431 US9340210B2 (en) | 2012-07-27 | 2013-06-25 | Control device for automatic transmission for vehicle |
JP2014526826A JP5936690B2 (ja) | 2012-07-27 | 2013-06-25 | 車両用自動変速機の制御装置 |
CA2879056A CA2879056C (en) | 2012-07-27 | 2013-06-25 | Control device for automatic transmission for vehicle |
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JP2012166971 | 2012-07-27 |
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PCT/JP2013/067422 WO2014017239A1 (ja) | 2012-07-27 | 2013-06-25 | 車両用自動変速機の制御装置 |
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US (1) | US9340210B2 (ja) |
JP (1) | JP5936690B2 (ja) |
CN (1) | CN104471218B (ja) |
CA (1) | CA2879056C (ja) |
DE (1) | DE112013003697T5 (ja) |
WO (1) | WO2014017239A1 (ja) |
Cited By (4)
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CN105276164A (zh) * | 2014-07-16 | 2016-01-27 | 本田技研工业株式会社 | 自动变速器的控制装置 |
CN106015558A (zh) * | 2015-03-26 | 2016-10-12 | 丰田自动车株式会社 | 锁止离合器的控制装置 |
US9709165B2 (en) | 2014-07-16 | 2017-07-18 | Honda Motor Co., Ltd. | Control apparatus for automatic transmission |
JP2018168911A (ja) * | 2017-03-29 | 2018-11-01 | 本田技研工業株式会社 | 制御装置および制御システム |
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WO2014169019A2 (en) * | 2013-04-12 | 2014-10-16 | Dana Limited | Monitoring and prognostic system and method for determining a remaining useful life of lubricant in wet clutch transmissions |
US9958060B2 (en) * | 2015-12-08 | 2018-05-01 | Caterpillar Inc. | Hydraulic system for a torque converter |
JP6801580B2 (ja) * | 2017-05-19 | 2020-12-16 | トヨタ自動車株式会社 | 車両の制御装置 |
KR101956605B1 (ko) | 2017-08-11 | 2019-03-12 | 현대오트론 주식회사 | 댐퍼 클러치 고착 해소 장치 및 방법 |
DE102017215796A1 (de) * | 2017-09-07 | 2019-03-07 | Zf Friedrichshafen Ag | Verfahren zur Symptomerkennung eines Defektes einer Wandlerüberbrückungskupplung oder einer Anfahrkupplung oder einer Störung in der Ansteuerkette der Wandlerüberbrückungskupplung oder der Anfahrkupplung eines Kraftfahrzeugs umfassend ein Automatgetriebe, ein Doppelkupplungsgetriebe oder ein automatisiertes Schaltgetriebe |
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US10697539B2 (en) * | 2018-05-02 | 2020-06-30 | GM Global Technology Operations LLC | Evaluation of a torque converter clutch position based on accumulated slip |
DE102019204993B4 (de) | 2019-04-08 | 2023-01-05 | Zf Friedrichshafen Ag | Verfahren zur Detektion eines Leitraddefektes in einem hydrodynamischen Drehmomentwandler eines Kraftfahrzeugs |
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- 2013-06-25 CA CA2879056A patent/CA2879056C/en not_active Expired - Fee Related
- 2013-06-25 CN CN201380038443.3A patent/CN104471218B/zh active Active
- 2013-06-25 US US14/417,431 patent/US9340210B2/en active Active
- 2013-06-25 JP JP2014526826A patent/JP5936690B2/ja active Active
- 2013-06-25 WO PCT/JP2013/067422 patent/WO2014017239A1/ja active Application Filing
- 2013-06-25 DE DE201311003697 patent/DE112013003697T5/de not_active Withdrawn
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Also Published As
Publication number | Publication date |
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CN104471218A (zh) | 2015-03-25 |
CN104471218B (zh) | 2017-03-08 |
US9340210B2 (en) | 2016-05-17 |
US20150191174A1 (en) | 2015-07-09 |
CA2879056A1 (en) | 2014-01-30 |
DE112013003697T5 (de) | 2015-04-09 |
JPWO2014017239A1 (ja) | 2016-07-07 |
CA2879056C (en) | 2017-01-03 |
JP5936690B2 (ja) | 2016-06-22 |
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