WO2011122137A1 - 自動変速機の制御装置 - Google Patents
自動変速機の制御装置 Download PDFInfo
- Publication number
- WO2011122137A1 WO2011122137A1 PCT/JP2011/053116 JP2011053116W WO2011122137A1 WO 2011122137 A1 WO2011122137 A1 WO 2011122137A1 JP 2011053116 W JP2011053116 W JP 2011053116W WO 2011122137 A1 WO2011122137 A1 WO 2011122137A1
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- WIPO (PCT)
- Prior art keywords
- clutch
- vehicle
- control
- lockup
- lock
- Prior art date
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Classifications
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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
- 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
- F16H61/143—Control of torque converter lock-up clutches using electric control means
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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
- F16H2312/00—Driving activities
- F16H2312/02—Driving off
- F16H2312/022—Preparing to drive off
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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
- 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
- F16H61/68—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 specially adapted for stepped gearings
- F16H61/684—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 specially adapted for stepped gearings without interruption of drive
- F16H61/686—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 specially adapted for stepped gearings without interruption of drive with orbital gears
Definitions
- the present invention relates to a control device for an automatic transmission mounted on a vehicle, for example, and more particularly to a control device for an automatic transmission that starts a vehicle while controlling a clutch and a lock-up clutch of an automatic transmission mechanism.
- a torque converter is provided between an engine and an automatic transmission mechanism, and the torque converter is mainly provided with a lock-up clutch.
- the lockup clutch is generally locked up when the vehicle speed exceeds a predetermined speed, and reduces the fluid transmission loss in the fluid transmission device.
- the lockup clutch is released when the vehicle starts. Therefore, slipping occurs in the torque converter, and the vehicle is started while the engine speed increases. There is a problem that the increase in the engine speed at the start of the vehicle hinders the improvement of the fuel consumption of the vehicle.
- the flex start control is required to start the slip control of the lockup clutch immediately after the vehicle starts. Due to delays and delays in the movement response of the lock-up piston, it is difficult to immediately put the lock-up clutch into the slip state, and the engine speed may increase during that time, making it impossible to improve vehicle fuel efficiency. There's a problem.
- the present invention provides an automatic transmission that can start a vehicle that prevents the rotation of a drive source from rotating and the occurrence of a backlash shock, thereby improving the fuel consumption and the ride comfort of the vehicle.
- the object is to provide a control device.
- the present invention includes an automatic transmission mechanism (5) having a clutch (C-1) that is capable of shifting the rotation (Ne) of the drive source (2) and that is engaged when starting.
- In the control device (1) of the automatic transmission (3) provided with Range determination means (21) for determining a shift range including a travel range (for example, D); Stop determination means (22) for determining stop of the vehicle; A start intention operation detecting means (23) for detecting a start intention operation of the vehicle; In a state where the travel range (for example, D) is determined and the vehicle is stopped, the clutch (C-1) is controlled to be in a disengaged state so that the automatic transmission mechanism (5) is brought into a neutral state.
- a clutch control means (24) for controlling the start of the vehicle by controlling the engagement of the clutch (C-1) when detecting the intention to start the vehicle, When the travel range (for example, D) is determined and the stop of the vehicle is determined, the lock-up clutch (7) is engaged, and an operation to start the vehicle is detected.
- the lockup clutch control means (25) for controlling the lockup clutch (7) to engage at least in a slip region having a predetermined torque capacity.
- the output torque (Te) of the drive source (2) and the torque capacity (T C1 ) of the clutch (C-1) are a predetermined torque of the lockup clutch (7).
- the capacity is smaller than the capacity ( TL-UP 1), the vehicle is started while slip-controlling the clutch (C-1) while the lock-up clutch (7) is engaged. To do.
- the fluid transmission device includes a torque converter (4),
- the output torque (Te) of the drive source (2) and the torque capacity (T C1 ) of the clutch (C-1) are larger than the predetermined torque capacity (T L-UP 1) of the lockup clutch (7) Is characterized in that the vehicle is started using the torque increasing action of the torque converter (4) while the lock-up clutch (7) slips.
- the fluid transmission device includes a torque converter (4),
- the output torque (Te) of the drive source (2) and the torque capacity (T C1 ) of the clutch (C-1) are larger than the predetermined torque capacity (T L-UP 1) of the lockup clutch (7)
- the lockup clutch control means (25) releases the lockup clutch (7) and starts the vehicle using the torque increasing action of the torque converter (4).
- the present invention includes request output detection means (34) for detecting a driver's request output (TH), Vehicle speed detection means (32) for detecting the vehicle speed (V) of the vehicle;
- the lockup clutch control means (25) refers to the lockup control map (25map) based on the required output (TH) and the vehicle speed (V), and releases or slips the lockup clutch (7).
- Control engagement, Releasing area of the lock-up clutch (7) is a predetermined torque of the output torque of the driving source (2) (Te) and the torque capacity of the clutch (C1) (T C1) is the lock-up clutch (7)
- the present invention is characterized in that it corresponds to a state in which the capacity is larger than (T L-UP 1).
- the clutch control means controls the clutch to the non-engaged state and sets the automatic transmission mechanism to the neutral state when the travel range is determined and the vehicle is stopped. At the same time, when an operation to start the vehicle is detected, the clutch is engaged and controlled to start the vehicle.
- the lockup clutch control means determines the travel range and determines whether the vehicle is stopped. When the lockup clutch is engaged (that is, when the clutch is in the neutral state), and the operation of the vehicle's intention to start is detected, at least the lockup clutch is engaged in the slip region where the predetermined torque capacity is obtained. In other words, the lock-up clutch is engaged before the vehicle starts.
- the vehicle when the output torque of the drive source and the torque capacity of the clutch are smaller than the predetermined torque capacity of the lockup clutch, the vehicle is controlled while slip-controlling the clutch while the lockup clutch is engaged.
- the lockup clutch does not slip as described above, preventing the drive source from spinning up and improving the fuel efficiency of the vehicle. it can.
- the torque increasing action of the torque converter is used while the lockup clutch slips.
- the lockup clutch does not slip as described above, preventing the drive source from spinning up and improving the fuel efficiency of the vehicle.
- the required torque requested by the driver is large, a large output torque can be obtained and drivability can be ensured.
- the lockup clutch control means releases the lockup clutch, and the torque converter
- the lock-up clutch does not slip as described above to prevent the drive source from spinning up.
- the lock-up clutch is released without being slipped, so that the drag by the lock-up clutch can be eliminated and a larger torque increasing action can be obtained. Can do.
- the lockup clutch control means controls the release, slip and engagement of the lockup clutch with reference to the lockup control map based on the required output and the vehicle speed.
- the engagement state of the lockup clutch can be controlled without performing the calculation.
- the release region of the lockup clutch corresponds to a state where the output torque of the drive source and the torque capacity of the clutch are larger than the predetermined torque capacity of the lockup clutch. It is possible to start the vehicle using the torque increasing action.
- the block diagram which shows the control apparatus of the automatic transmission which concerns on this invention.
- the skeleton figure which shows the automatic transmission which can apply this invention.
- the flowchart which shows control of a lockup clutch.
- the flowchart which shows control of the clutch C-1.
- the flowchart which shows the apply control of clutch C-1.
- the flowchart which shows an example of the slip start control of the clutch C-1.
- the time chart which shows the time of the start in the engagement state of the lockup clutch when the throttle opening is low.
- the time chart which shows the time of the start in the state where the lock-up clutch is slipping when the throttle opening is high.
- the time chart which shows the time of start in the release state of the lockup clutch from a slip state when the throttle opening is a high opening.
- the time chart which shows the slip start control in case the throttle opening is a low opening.
- 4 is a time chart showing a slip start control for calculating a torque capacity of a clutch C-1 in consideration of an inertia torque.
- 4 is a time chart showing slip start control for calculating a torque capacity of a clutch C-1 that achieves a target constant speed ratio. 4 is a time chart showing slip start control for calculating a torque capacity of a clutch C-1 at which a target input rotation speed is constant.
- an automatic transmission 3 suitable for use in a vehicle of FF type front engine, front drive
- an output shaft 2a of an engine (E / G) 2 (see FIG. 1) as a drive source.
- the automatic transmission has an input shaft 8 that can be connected to the shaft, and includes a torque converter (fluid transmission) (T / C) 4 and an automatic transmission mechanism 5 with the axial direction of the input shaft 8 as the center. Yes.
- the torque converter 4 is interposed between the engine 2 and an automatic transmission mechanism 5 which will be described in detail later.
- the pump impeller 4a connected to the input shaft 8 of the automatic transmission 3 and the pump via the working fluid.
- the torque converter 4 is provided with a lock-up clutch 7, and when the lock-up clutch 7 is engaged, the rotation of the input shaft 8 of the automatic transmission 3 causes the input shaft of the automatic transmission mechanism 5 to rotate. 10 is transmitted directly.
- the stator 4c is fixed by the one-way clutch F in a state where the rotation of the turbine runner 4b is lower than the rotation of the pump impeller 4a, receives the reaction force of the oil flow, and generates a torque increasing action.
- the rotation of the runner 4b is exceeded, the engine runs idle and the oil flow does not act in the negative direction.
- the automatic transmission mechanism 5 includes a planetary gear SP and a planetary gear unit PU on the input shaft 10.
- the planetary gear SP is a so-called single pinion planetary gear that includes a sun gear S1, a carrier CR1, and a ring gear R1, and has a pinion P1 that meshes with the sun gear S1 and the ring gear R1.
- the planetary gear unit PU has a sun gear S2, a sun gear S3, a carrier CR2, and a ring gear R2 as four rotating elements.
- the long gearion PL that meshes with the sun gear S2 and the ring gear R2 and the sun gear S3.
- This is a so-called Ravigneaux type planetary gear that has meshing short pinions PS that mesh with each other.
- the sun gear S1 of the planetary gear SP is connected to a boss portion that is integrally fixed to the transmission case 9, and the rotation is fixed.
- the ring gear R1 is in the same rotation as the rotation of the input shaft 10 (hereinafter referred to as “input rotation”). Further, the carrier CR1 is decelerated by reducing the input rotation by the fixed sun gear S1 and the ring gear R1 that rotates, and is connected to the clutch C-1 and the clutch C-3.
- the sun gear S2 of the planetary gear unit PU is connected to a brake B-1 formed of a band brake so as to be freely fixed to the transmission case, and is connected to the clutch C-3 via the clutch C-3.
- the sun gear S3 is connected to the clutch C-1, so that the decelerated rotation of the carrier CR1 can be input.
- the carrier CR2 is connected to a clutch C-2 to which the rotation of the input shaft 10 is input, and the input rotation can be freely input through the clutch C-2, and the one-way clutch F-1 and Connected to the brake B-2, rotation in one direction with respect to the transmission case is restricted via the one-way clutch F-1, and rotation can be fixed via the brake B-2.
- the ring gear R2 is connected to a counter gear 11, and the counter gear 11 is connected to a drive wheel via a counter shaft and a differential device (not shown).
- the automatic transmission 3 configured as described above includes the clutches C-1 to C-3 and the brake B-1 at the first forward speed to the sixth forward speed and the reverse speed as shown in the operation table of FIG. ... B-2, the one-way clutch F-1 is operated, and the gear ratio of the shift stage is formed with a good step ratio. Further, each shift control is executed by re-engaging these clutches C-1 to C-3 and brakes B-1 to B-2, and at the time of driving the first forward speed at each shift speed (for example, Except at the time of starting), two of the clutches C-1 to C-3 and the brakes B-1 to B-2 are engaged to achieve each gear stage.
- the control device 1 of the automatic transmission includes a control unit (ECU) 20, which includes an input shaft rotation speed sensor 30, a shift position sensor 31, an output shaft rotation.
- a speed (vehicle speed) sensor (vehicle speed detection means) 32, a brake sensor 33, a throttle opening sensor (request output detection means) 34, and the like are connected, and the clutches C-1 to C of the automatic transmission mechanism 5 described above are connected.
- a hydraulic control device (V / B) 6 that hydraulically controls the brakes B-1 to B-2, the lockup clutch 7, and the like.
- the hydraulic control device 6 includes a plurality of linear solenoid valves for controlling the engagement pressure supplied to the hydraulic servos of the clutches C-1 to C-3 and the brakes B-1 to B-2. cage, in particular to the hydraulic control device 6, the engagement pressure of P C1, the tone pressure output closable linear solenoid valve SLC1 as an original pressure, for example, the line pressure P L is supplied to the hydraulic servo 40 of the clutch C1, A linear solenoid valve SLU capable of adjusting and outputting the engagement pressure P L-UP (internal pressure of the torque converter 4) of the lock-up clutch 7 with, for example, the secondary pressure P SEC as a source pressure is provided.
- the valve SLC1 and the linear solenoid valve SLU are configured to be controlled by a command from the control unit 20.
- control unit 20 includes a range determination unit 21, a stop determination unit 22, a start intention operation detection unit 23, a clutch control unit 24, and a lock-up control unit 25.
- the clutch control unit 24 includes An neutral control means 24a and an apply control means 24b having a slip start control means 24c are provided.
- the lockup control means 25 is provided with a stop-time lockup control means 25a, a start-up lockup control means 25b, a steady-state lockup control means 25c, and a lockup control map 25map.
- Clutch control means 24 of this instructs control the linear solenoid valve SLC1, and freely controlling the hydraulic pressure command value of the engagement pressure P C1, released states of the clutches C1, i.e.
- the lock-up control means 25 controls the linear solenoid valve SLU to freely control the hydraulic pressure command value of the engagement pressure P L-UP , and the lock-up piston is not shown in the state of pressing the lock-up clutch 7.
- the engagement / disengagement state of the lock-up clutch 7, that is, the release state (release region), the slip state (slip region), and the engagement state (engagement region) are freely controlled.
- the input shaft rotational speed sensor 30 detects the rotational speed of the input shaft 10 of the automatic transmission mechanism 5 (that is, the turbine rotational speed Nt of the turbine runner 4b).
- the shift position sensor 31 detects an operation position of a shift lever (or a position of a manual shaft interlocked with the shift lever) arranged in a driver's seat (not shown).
- the output shaft rotational speed sensor 32 detects the rotational speed of the counter gear 11 (or counter shaft) of the automatic transmission mechanism 5 (that is, the vehicle speed V and the output shaft rotational speed Nout).
- the brake sensor 33 detects a depression state (at least brake ON / OFF) of a brake pedal (not shown).
- the throttle opening sensor 34 detects a throttle opening (driving source required output) TH that is controlled mainly based on the accelerator opening.
- the range determination means 21 is based on detection of the shift lever position by the shift position sensor 31, P (parking) range (non-traveling range), R (reverse) range (traveling range), N (neutral) range (non-traveling) Range) and D (drive) range (traveling range) are included to determine which range is included.
- the stop determination means 22 determines whether or not the vehicle is stopped based on the detection result of the output shaft rotation speed (that is, the vehicle speed V) by the output shaft rotation speed sensor 32. For example, when the driver releases the brake on a slope or the like and the vehicle speed V becomes 0 or more (when the vehicle is not stopped), the throttle opening degree is turned on. If it is determined that the driver has started the vehicle, the driver detects that the driver has made an intention to start.
- step S1-3 the lock-up control means 25 proceeds to step S1-3 shown in FIG. Then, whether the start intention operation detecting means 23 detects that the throttle is ON by the throttle opening sensor 34 or whether the vehicle speed V is greater than 0 by the output shaft rotation speed (vehicle speed) sensor 32, or The system waits until either the brake OFF is detected by the brake sensor 33 (No in S1-3). Then, when the start intention operation detecting means 23 detects any of the throttle ON, the vehicle speed V is greater than 0, and the brake OFF (Yes in S1-3), it is determined that the driver has an intention to start and the vehicle is stopped. The lockup control is terminated and the process proceeds to step S1-4. When the driver's intention to start is detected in this way, the clutch control means 24 described later ends the neutral control and shifts to apply control (engagement control of the clutch C-1).
- step S1-4 the start-up lockup control means 25b of the lockup control means 25 starts start-up lockup control (startup L-UP control). Then, the start-up lockup control means 25b refers to a lockup control map 25map (see FIGS. 10 and 12), which will be described later in detail, and determines whether the lockup clutch 7 is engaged based on the relationship between the vehicle speed V and the throttle opening TH.
- the engagement pressure P L-UP of the lock-up clutch 7 is increased to a predetermined command value by commanding the linear solenoid valve SLU so as to be in the slip region, and the lock-up clutch 7 is engaged with a predetermined torque capacity. To do.
- step S1-5 shown in FIG.
- the clutch control means 24 which will be described later, finishes applying the clutch C-1, and waits until it is detected that the engagement of the clutch C-1 is completed (No in S1-5).
- the start-up lockup control is terminated, and the routine proceeds to step S1-6, where the steady-state lockup control means 25c is for steady running ( The routine proceeds to lock-up steady control (for normal running) (L-UP steady control), and the control of the lock-up clutch 7 at the time of start is terminated (S1-7).
- ON / OFF / slip control of the lockup clutch 7 is appropriately performed based on the vehicle speed V and the throttle opening TH while referring to the lockup control map 25map and the like.
- the release control for lowering the pressure is performed, that is, the clutch C-1 is slightly released to bring the automatic transmission mechanism 5 into a completely neutral state.
- the engagement pressure P C1 of the clutch C1 by the lower pressure than the stroke end pressure, it is possible to eliminate the drag loss of the clutch C1 in the neutral control completely, the load on the engine 2 It is possible to reduce the fuel consumption of the vehicle.
- step S2-3 whether the above-mentioned start intention operation detecting means 23 detects that the throttle is ON by the throttle opening sensor 34 or whether the vehicle speed V is greater than 0 by the output shaft rotational speed (vehicle speed) sensor 32.
- the system waits until either the brake OFF is detected by the brake sensor 33 (No in S2-3).
- the start intention operation detecting means 23 detects any of the throttle ON, the vehicle speed V is greater than 0, and the brake OFF (Yes in S2-3), it is determined that the driver has the start The end of neutral control is determined, and the process proceeds to step S2-4.
- step S2-4 the apply control means 24b of the clutch control means 24 starts the apply control of the clutch C-1 as shown in FIG. 6 (S2-4-1). Then, first, the apply control means 24b starts the fast fill control for performing the backlash operation of the hydraulic servo 40 of the clutch C-1 (S2-4-2).
- the first fill control for example, the magnitude of the hydraulic command value to be output and the time for executing the first fill (first fill time) are set based on the oil temperature, the time when the neutral control is executed, and the like.
- step S2-4-3 it is determined whether or not the first fill time has elapsed. The first fill control is continued until the first fill time has elapsed (No in S2-4-3).
- step S2-4-4 application control unit 24b starts the standby control for maintaining the hydraulic pressure command value of the engagement pressure P C1 to the high standby pressure than the stroke end pressure.
- the piston is gradually stroked to the engagement side from the dragged state.
- whether or not the clutch C-1 has started to be engaged depends on whether or not the turbine rotational speed Nt detected by the input shaft rotational speed sensor 30 has changed.
- S2-4-5 the standby pressure is maintained until the clutch C-1 starts to be engaged (No in S2-4-5), and then the clutch C-1 starts engaging.
- the standby control by the apply control unit 24b is terminated, and the process proceeds to Step S2-4-6.
- this standby pressure may be set after learning correction based on the engagement timing or the like in the previous engagement control of the clutch C-1 (may be the engagement control at the time of normal shifting).
- step S2-4-6 the slip start control means 24c of the apply control means 24b starts the slip start control.
- the slip start control means 24c first sets a slip start timer as a forced end time in order to prevent the slip start control from being prolonged for some reason.
- Slip start control as shown in FIG. 7 is started (S2-4-6-1). Note that the slip start control shown in FIG. 7 shows one of the three calculation methods (see FIGS. 15 to 17) described later in detail (as shown in FIG. 15) as an example.
- the slip start control does not decrease the rotational speed of the input shaft 10 of the automatic transmission mechanism 5 (that is, the turbine rotational speed Nt), and the rotational speed of the output shaft 11 of the automatic transmission mechanism 5 (that is, the output shaft rotational speed Nout).
- the turbine rotational speed Nt is not decreased. Therefore, the output shaft rotation speed Nout is increased while the lockup clutch 7 is engaged, and the gear ratio of the first forward speed can be established.
- the torque converter 4 and the lock-up clutch 7 are used.
- the torque capacity of the clutch C-1 that holds the rotation speed is calculated so that the rotation change of the output shaft rotation speed Nout does not occur (S2-4). -6-2).
- the torque capacity of the clutch C-1 (that is, the target rotational change required torque capacity) such that the rotational change of the output shaft rotational speed Nout becomes the target rotational change is calculated (S2-4-6-3).
- the required hydraulic pressure of the clutch C-1 is calculated from the total torque of the holding torque capacity and the target rotational change required torque capacity, and the engagement pressure P C1 of the hydraulic servo 40 of the clutch C-1 is hydraulically controlled by the calculated required hydraulic pressure. Then, the slip start control is finished (S2-4-6-5), and the process proceeds to step S2-4-7 in FIG.
- step S2-4-7 the apply control means 24b determines that the gear ratio calculated from, for example, the turbine rotational speed Nt and the output shaft rotational speed Nout becomes the gear ratio of the first forward speed. It is determined whether or not the engagement of the clutch C-1 is completed by the slip start control. If the engagement of the clutch C-1 is not completed (the gear ratio is not established) (No in S2-4-7), the process proceeds to step S2-4-8, and the period of the slip start timer is set. If the slip start timer period has not elapsed (No in S2-4-8), the slip start control is continued.
- step S2-4-9 the control is shifted to the engagement completion control of the clutch C-1.
- the completion of the engagement control of the clutch C1 increases the engagement pressure P C1 of the clutch C1 at a predetermined gradient and instructs the slip start control means 24c is the linear solenoid valve SLC1, the clutch C1 Wait until the engagement is completed (until the gear ratio is established) (No in S2-4-10).
- the engagement of the clutch C-1 is completed (Yes in S2-4-10)
- S2-4-11 the control of the clutch C-1 from the stop time described above to the start time is all finished (S2-5).
- FIG. 8 shows an example of traveling when the driver depresses the throttle opening TH at a low opening when the vehicle starts, and the clutch C-1 is slip-engaged while the lockup clutch is engaged. It explains along. For example, a state that the foot brake (Brake) is stopped is treading (ON) in N range, is the engagement pressure P C1 of the clutch C1 is 0 released the clutch C1 In addition, the engagement pressure P L-UP of the lockup clutch 7 is also 0, and the lockup clutch 7 is also released. Therefore, the engine speed Ne in the idle state is in a state where fluid is transmitted from the pump impeller 4a to the turbine runner 4b in the torque converter 4, and the turbine speed Nt is slightly lower than the engine speed Ne. It has become.
- the range determination means 21 detects the D range (based on the detection of the shift position sensor 31). Based on this determination, the stop-time lockup control means 25a of the lockup control means 25 determines the start of the stop-time lockup control (S1-2) and controls the linear solenoid valve SLU.
- the lock-up engagement pressure P L-UP after performing the first fill (backlash filling operation), the lock-up clutch 7 is slightly engaged with a small torque capacity T L-UP .
- the neutral control means 24a of the clutch control means 24 determines the start of the in-neutral control (S2-2), and controls the linear solenoid valve SLC1 to control the engagement pressure P C1 .
- the clutch C1 is at a slightly lower engagement pressure P C1 than the stroke end pressure to be play reduction immediately before engagement while the clutch C1 to the release state Wait in state.
- the start-up lockup control means 25b of the lockup control means 25 is determined that the driver has an intention to start. Then, the start-up lockup control (S1-4) is determined to be started, and the lockup clutch 7 is engaged in the slip region so that the predetermined torque capacity T L-UP 1 is obtained. At this time, the start-up lockup control means 25b determines the engagement state (ON, OFF, slip state) of the lockup clutch 7 with reference to the lockup control map 25map shown in FIG. First, between time t2-1 and time t3-1, the throttle opening TH is 0% and the vehicle speed V (output shaft speed Nout) is small, so the engagement state in the slip region is selected. .
- the apply control means 24b of the clutch control means 24 determines that the driver has an intention to start.
- the above-described standby control (S2-4-4) is performed, and the slip start control means 24c starts the slip start control (S2-4-6).
- the vehicle starts to start (increase in the output shaft rotational speed Nout) while slip-controlling the clutch C-1.
- the lockup clutch 7 is engaged with the predetermined torque capacity T L-UP 1 and the torque capacity T C1 of the clutch C-1 and Since the input torque (hereinafter referred to as “engine torque”) Te from the engine 2 does not exceed the torque capacity T L-UP of the lock-up clutch 7, the lock-up clutch 7 does not slip and the engine speed Ne And the turbine speed Nt are the same, that is, the engine 2 is prevented from blowing up.
- engine torque input torque
- the slip start control means 24c performs a torque calculation of the clutch C-1 by a calculation method described in detail later. calculates the capacity T C1, by controlling the engagement pressure P C1 so that the calculated torque capacity T C1, the engagement pressure P C1 and the torque capacity T C1 is increased according to the throttle opening TH
- the torque capacity T L-uP of the lock-up clutch 7 i.e. with increasing engine torque Te, the engine rotational speed Ne and the turbine speed Nt increase.
- the lock-up clutch 7 is determined to be ON by the steady-state lock-up control means 25c. Then, the lockup engagement pressure P L-UP is swept up, and the lockup clutch 7 is engaged (ON). As a result, the vehicle is in a steady running state with the lockup ON at the first forward speed.
- FIG. 9 shows an example of traveling when the driver depresses the throttle opening TH at a high opening when the vehicle starts, and the clutch C-1 is slip-engaged while slipping the lock-up clutch. It explains along.
- the clutch C-1 is released, and the lockup clutch 7 is also released. . Therefore, the engine speed Ne in the idle state is in a state where fluid is transmitted by the torque converter 4, and the turbine speed Nt is slightly lower than the engine speed Ne.
- the stop-time lockup control means 25a of the lockup control means 25 starts the stop-time lockup control (S1-2).
- the lockup clutch 7 is slightly engaged so that the torque capacity TL-UP becomes small. Since the foot brake is ON, the throttle opening TH is 0%, and the vehicle speed V is 0, the neutral control means 24a of the clutch control means 24 determines the start of the in-neutral control (S2-2), and the first fill after (play reduction operation), at a slightly lower engagement pressure P C1 than the stroke end pressure clutch C1 is play reduction in state immediately before the engagement while the clutch C1 to the release state stand by.
- the start-up lockup control means 25b starts the start-up lockup control (S1-4). Judgment is made and the lockup clutch 7 is engaged in the slip region so that the predetermined torque capacity T L-UP 1 is obtained.
- the start-up lockup control means 25b determines the engagement state (ON, OFF, slip state) of the lockup clutch 7 with reference to the lockup control map 25map shown in FIG. First, between time t2-2 and time t3-2, as indicated by an arrow A in FIG. 10, the throttle opening TH is 0% and the vehicle speed V (output shaft speed Nout) is small. The engagement state at is selected.
- the apply control means 24b of the clutch control means 24 determines that the driver is willing to start, and the fast fill control (S2-4-2) ), The standby control (S2-4-4) described above is performed, and the slip start control means 24c starts the slip start control (S2-4-6) to control the clutch C-1 to slip. While starting the vehicle (increase in the output shaft rotation speed Nout) is started.
- the lockup clutch 7 is engaged with the predetermined torque capacity T L-UP 1 as described above, and the torque capacity T C1 of the clutch C-1 and Since the engine torque Te does not exceed the torque capacity TL-UP of the lockup clutch 7, the lockup clutch 7 does not slip, and the engine speed Ne and the turbine speed Nt are the same, that is, the engine 2 is prevented from blowing up.
- the slip start control means 24c performs a torque capacity T of the clutch C-1 by a calculation method described in detail later. calculates the C1, by controlling the engagement pressure P C1 so that the calculated torque capacity T C1, the engagement pressure P C1 and the torque capacity T C1 rises sharply in response to the throttle opening TH.
- the lockup control map 25map is in the slip region, and the engagement pressure P L-UP and the predetermined torque capacity of the lockup clutch 7 T L-UP 1 is maintained as it is, but the torque capacity T C1 and engine torque Te of the clutch C-1 exceed the torque capacity T L-UP of the lockup clutch 7, that is, the engine torque Te increases. Accordingly, the lockup clutch 7 is slipped, and torque transmission by the fluid transmission by the torque converter 4 is performed. That is, as shown in FIG. 9, the engine rotational speed Ne rises above the turbine rotational speed Nt.
- the slip state is maintained as it is at the time point t4-2, and then the vehicle speed V increases and the arrow A
- the lock-up ON (Lup ON) determination line is exceeded, the lock-up clutch 7 is determined to be ON by the steady-state lock-up control means 25c, and the lock-up engagement pressure P L-UP is swept up.
- the lockup clutch 7 is engaged (ON).
- the vehicle is in a steady running state with the lockup ON at the first forward speed.
- the stop-time lockup control means 25a of the lockup control means 25 starts the stop-time lockup control (S1-2).
- the lockup clutch 7 is slightly engaged so that the torque capacity TL-UP becomes small. Since the foot brake is ON, the throttle opening TH is 0%, and the vehicle speed V is 0, the neutral control means 24a of the clutch control means 24 determines the start of the in-neutral control (S2-2), and the first fill after (play reduction operation), at a slightly lower engagement pressure P C1 than the stroke end pressure clutch C1 is play reduction in state immediately before the engagement while the clutch C1 to the release state stand by.
- the start-up lockup control means 25b starts the start-up lockup control (S1-4) on the assumption that the driver intends to start. Judgment is made and the lockup clutch 7 is engaged in the slip region so that the predetermined torque capacity T L-UP 1 is obtained. At this time, the start-up lockup control means 25b determines the engagement state (ON, OFF, slip state) of the lockup clutch 7 with reference to the lockup control map 25map shown in FIG. First, between time t2-3 and time t3-3, as indicated by an arrow A in FIG. 12, the throttle opening TH is 0% and the vehicle speed V (output shaft speed Nout) is small. The engagement state at is selected.
- the apply control means 24b of the clutch control means 24 determines that the driver is willing to start, and the fast fill control (S2-4-2) ), The standby control (S2-4-4) described above is performed, and the slip start control means 24c starts the slip start control (S2-4-6) to control the clutch C-1 to slip. While starting the vehicle (increase in the output shaft rotation speed Nout) is started.
- the lockup clutch 7 is engaged with the predetermined torque capacity T L-UP 1 as described above, and the torque capacity T C1 of the clutch C-1 and Since the engine torque Te does not exceed the torque capacity TL-UP of the lockup clutch 7, the lockup clutch 7 does not slip, and the engine speed Ne and the turbine speed Nt are the same, that is, the engine 2 is prevented from blowing up.
- the slip start control means 24c uses the calculation method described later in detail to calculate the torque capacity T of the clutch C-1. calculates the C1, by controlling the engagement pressure P C1 so that the calculated torque capacity T C1, the engagement pressure P C1 and the torque capacity T C1 rises sharply in response to the throttle opening TH.
- the slip-up control map 25map switches from the slip region to the lock-up OFF region. Therefore, at time t4-3, the start-up lockup control means 25b starts sweeping down the engagement pressure P L-UP of the lockup clutch 7, and accordingly, the torque capacity T L-UP of the lockup clutch 7 is reached. Is gradually lowered, and then the lock-up clutch 7 is released. As a result, the lock-up clutch 7 is released, torque transmission of the lock-up clutch 7 is lost, torque transmission by the fluid transmission by the torque converter 4 is performed, and the torque increase action of the torque converter 4 is affected by the lock-up clutch 7.
- the engine torque Te is increased without being interfered with and is input to the input shaft 10 of the automatic transmission mechanism 5, and the driver increases the accelerator opening (throttle opening) as compared with the case of FIG. A larger output torque can be obtained, and drivability is ensured. That is, as shown in FIG. 11, the engine speed Ne increases significantly higher than the turbine speed Nt.
- the slip start control is performed when the clutch C-1 is engaged while slipping while the lockup clutch 7 is engaged in the slip region, and the turbine speed Nt does not decrease. Even when the clutch C-1 is shifted from the general neutral control to the engaged state, that is, when the lockup clutch 7 is released, the neutral control may return to the first forward speed. Since the occurrence of inertia shock can be suppressed by using this control, a case where the clutch C-1 is shifted to the engaged state from the general neutral control will be described as an example.
- the standby control is terminated at the time point tb-1,
- the routine proceeds to slip start control by the slip start control means 24c (S2-4-6).
- the engagement pressure P C1 of the clutch C-1 is calculated and hydraulically controlled so that the turbine speed Nt does not decrease by, for example, three calculation methods described later.
- the gear ratio of the first forward speed is established, and the output shaft rotational speed Nout also increases.
- the engagement of the clutch C-1 is completed based on the fact that the gear ratio calculated from the turbine rotational speed Nt and the output shaft rotational speed Nout becomes the gear ratio of the first forward speed.
- the slip start control unit 24c is commanded to the linear solenoid valve SLC1 is soaring the engagement pressure P C1 of the clutch C1 at a predetermined gradient, the time td-1 was increased to the line pressure P L corresponding to, to complete the engagement of the clutch C-1, and ends the slip start control (S2-4-11, S2-5).
- the brake OFF is detected at the time point ta-2, the standby control of the clutch C-1 is performed, and the clutch C-1 starts to be engaged. If it is determined, the standby control is terminated at time tb-2, and the routine proceeds to slip start control by the slip start control means 24c. After this, for example, even if the accelerator pedal is depressed by the driver and the throttle opening TH increases, the gear ratio (transmission progress rate) decreases so that the turbine rotational speed Nt does not decrease by, for example, three calculation methods described later.
- the hydraulic pressure control is performed by calculating the engagement pressure P C1 of the clutch C-1 so as not to occur.
- the clutch C-1 is engaged based on the fact that the gear ratio calculated from the turbine speed Nt and the output shaft speed Nout becomes the gear ratio of the first forward speed.
- the slip start control unit 24c is commanded to the linear solenoid valve SLC1 is soaring the engagement pressure P C1 of the clutch C1 at a predetermined gradient, the line pressure P L corresponding to up to the time td-2 To complete the engagement of the clutch C-1 and finish the slip start control.
- the slip start control unit 24c sets a target completion time TA, for example by adding the current throttle opening TH sets the target turbine speed N targ at the target end time TA.
- the speed ratio (speed ratio between the pump impeller 4a and the turbine runner 4b) in the current torque converter 4 is “e current ”
- the capacity coefficient of the torque converter 4 at the current speed ratio is “C (e current )”
- the torque transmitted by the lockup clutch 7 is “T L-UP ”
- the torque sharing of the clutch C-1 is “Tdiv C1 ”
- T C1 -change (I ⁇ ) ⁇ (Tdiv C1 ) (4) (S2-4-6-3 in FIG. 7),
- the above calculation formula (5) is based on the total torque including the inertia torque (I ⁇ ) generated in the input torque (t ⁇ C ⁇ Ne 2 + T L ⁇ UP ) from the engine 2 based on the total torque. 1 torque capacity T C1 is calculated.
- the clutch control means 24 controls the clutch C-1 to the non-engaged state when the D range is determined and the vehicle is stopped. Then, the automatic transmission mechanism 5 is neutrally controlled, and when an operation to start the vehicle is detected, the clutch C-1 is engaged to control slip start, while the lockup control means (lock The up-clutch control means) 25 is engaged with the lock-up clutch 7 in the engaged state and the vehicle start intention operation in a state where the D range is determined and the vehicle is stopped (that is, during neutral control).
- the lock-up clutch 7 upon detection of, before since at least the lock-up clutch 7 is controlled to engage the slip region to be a predetermined torque capacity T L-uP 1, that is, before starting of the vehicle Since the lock-up clutch 7 is engaged, the lock-up clutch 7 can be immediately engaged in the slip region even immediately after starting (preventing a delay in engagement of the lock-up clutch 7). As a result, it is possible to prevent the engine speed Ne from being blown up immediately after starting, and to improve the fuel efficiency of the vehicle. When the engine speed Ne is low, that is, the output torque required by the driver is small, and torque smaller than the predetermined torque capacity TL-UP is input to the lockup clutch 7. Since the lock-up clutch 7 is stably engaged, the vehicle can be started without causing a back-shock, and the ride comfort can be improved.
- the torque capacity T C1 of the engine torque Te and the clutch C1 is larger than the predetermined torque capacity T L-UP of the lock-up clutch 7, the torque increases the action of the torque converter 4 with a slip lock-up clutch 7 is
- the lockup clutch 7 does not slip as described above, and the engine speed Ne is prevented from rising and the fuel consumption of the vehicle is reduced.
- a large output torque Tout can be obtained and drivability can be secured.
- the lockup control means 25 actively releases the lockup clutch 7.
- the vehicle can also be started using the torque increasing action of the torque converter 4.
- the lockup clutch 7 does not slip as described above.
- the output is larger than when the lock-up clutch 7 is dragged. Torque Tout can be obtained and drivability can be ensured. That is, when the vehicle is started using the torque increasing action of the torque converter 4, the lock-up clutch 7 is released without being slipped, so that the drag-up by the lock-up clutch 7 can be eliminated and a larger torque increasing action can be achieved. Can be obtained.
- the lockup control means 25 controls the release, slip and engagement of the lockup clutch 7 with reference to the lockup control map 25map based on the throttle opening TH (that is, the required output) and the vehicle speed V.
- the engagement state of the lockup clutch 7 can be controlled without performing complicated calculations.
- the control apparatus 1 is applied to the automatic transmission 3 that can achieve, for example, the sixth forward speed and the reverse speed.
- the automatic transmission 3 can achieve, for example, the sixth forward speed and the reverse speed.
- a multi-stage automatic transmission, a belt-type continuously variable transmission, a toroidal-type continuously variable transmission can be used as long as the automatic transmission has a lock-up clutch and a slip start control after neutral control of the combined clutch for power transmission.
- the present invention can be applied to any automatic transmission such as a transmission.
- start control by slip engagement of the clutch C-1 with the lock-up clutch engaged has been described.
- the scene in which the control is executed is, for example, road conditions or traveling You may make it select according to an environment etc.
- starting conditions such as uphill and downhill roads, sport modes, high and low oil temperatures, and running in traffic jams
- execution of this start control is canceled and normal start control (lock-up clutch It is conceivable to select a control for engaging the clutch C-1 while releasing the clutch.
- the neutral control in which the engagement pressure P C1 of the clutch C-1 is controlled to a pressure lower than the stroke end pressure has been described.
- the general neutral control that is, The present invention can be applied even when the engagement pressure P C1 is controlled to be close to the stroke end pressure.
- lock-up clutch 7 In the present embodiment, the detailed structure of the lock-up clutch 7 is not described. Of course, a single-plate lock-up clutch, a multi-plate lock-up clutch, a so-called two-way lock-up clutch, or 3 The present invention can be applied to any lock-up clutch structure such as a way-type lock-up clutch.
- the torque converter is to be locked up as a lock-up clutch, it is possible to obtain a torque increasing action of the torque converter by slipping the lock-up clutch in particular, but a fluid coupling that cannot obtain a torque increasing action, etc. It is needless to say that even if this fluid transmission device is used, the blow-up of the rotation of the drive source can be suppressed by applying this control.
- the hydraulic control device for a starting device can be used as a control device for an automatic transmission mounted on a passenger car, a truck, etc., and in particular, after performing neutral control by a clutch of an automatic transmission mechanism, Used to start a vehicle by engaging with it, and used in a control device for an automatic transmission in which the rotation of a drive source is prevented from blowing up at the time of start by slip control of a lock-up clutch, and improvement in fuel consumption is required. Is preferred.
Abstract
Description
走行レンジ(例えばD)を含むシフトレンジを判定するレンジ判定手段(21)と、
車輌の停車を判定する停車判定手段(22)と、
車輌の発進意思の操作を検出する発進意思操作検出手段(23)と、
前記走行レンジ(例えばD)が判定され、かつ前記車輌の停車が判定された状態で、前記クラッチ(C-1)を非係合状態に制御して前記自動変速機構(5)をニュートラル状態にすると共に、前記車輌の発進意思の操作を検出した際に、前記クラッチ(C-1)を係合制御して前記車輌を発進制御するクラッチ制御手段(24)と、
前記走行レンジ(例えばD)が判定され、かつ前記車輌の停車が判定された状態で、前記ロックアップクラッチ(7)を係合状態にすると共に、前記車輌の発進意思の操作を検出した際に、少なくとも前記ロックアップクラッチ(7)が所定トルク容量となるスリップ領域で係合するように制御するロックアップクラッチ制御手段(25)と、を備えたことを特徴とする。
前記駆動源(2)の出力トルク(Te)及び前記クラッチ(C-1)のトルク容量(TC1)が前記ロックアップクラッチ(7)の所定トルク容量(TL-UP1)よりも大きい場合には、前記ロックアップクラッチ(7)がスリップしつつ前記トルクコンバータ(4)のトルク増大作用を用いて前記車輌を発進させてなることを特徴とする。
前記駆動源(2)の出力トルク(Te)及び前記クラッチ(C-1)のトルク容量(TC1)が前記ロックアップクラッチ(7)の所定トルク容量(TL-UP1)よりも大きい場合には、前記ロックアップクラッチ制御手段(25)が前記ロックアップクラッチ(7)を解放し、前記トルクコンバータ(4)のトルク増大作用を用いて前記車輌を発進させてなることを特徴とする。
前記車輌の車速(V)を検出する車速検出手段(32)と、
前記要求出力(TH)と前記車速(V)との関係に対応して、前記ロックアップクラッチ(7)の解放領域、スリップ領域、係合領域が設定されたロックアップ制御マップ(25map)と、を備え、
前記ロックアップクラッチ制御手段(25)は、前記要求出力(TH)と前記車速(V)とに基づき前記ロックアップ制御マップ(25map)を参照して、前記ロックアップクラッチ(7)の解放、スリップ、係合を制御してなり、
前記ロックアップクラッチ(7)の解放領域は、前記駆動源(2)の出力トルク(Te)及び前記クラッチ(C-1)のトルク容量(TC1)が前記ロックアップクラッチ(7)の所定トルク容量(TL-UP1)よりも大きくなる状態に対応されたことを特徴とする。
まず、本発明を適用し得る自動変速機3の概略構成について図2に沿って説明する。図2に示すように、例えばFFタイプ(フロントエンジン、フロントドライブ)の車輌に用いて好適な自動変速機3は、駆動源としてのエンジン(E/G)2(図1参照)の出力軸2aに接続し得る自動変速機の入力軸8を有しており、該入力軸8の軸方向を中心としてトルクコンバータ(流体伝動装置)(T/C)4と、自動変速機構5とを備えている。
つづいて、本発明に係る自動変速機の制御装置1について、主に図1に沿って説明する。
ついで、車輌の停車時から発進時におけるロックアップクラッチ7の制御、即ち、ロックアップ制御手段25によるロックアップ制御について図1を参照しつつ図4に沿って説明する。例えばレンジ判定手段21によりDレンジが判定されている状態で(NレンジからDレンジにされた場合を含む)、かつ停車判定手段22により車輌の停車が判定されると、図4に示すように、本発明に係るロックアップクラッチの制御を開始し(S1-1)、ロックアップ制御手段25の停車時ロックアップ制御手段25aは、停車時ロックアップ制御(停車時L-UP制御)を実行し(S1-2)、不図示のロックアップリレーバルブをロックアップ位置に切換え、ロックアップクラッチ7のファーストフィル(いわゆるガタ詰め動作)を行ったのち、該ロックアップクラッチ7が微小なトルク容量となるように係合する。この際、クラッチC-1は後述するようにインニュートラル制御中であり、自動変速機構5の入力軸10(タービンランナ4b)は略々空転状態にあるため、該ロックアップクラッチ7はスリップせずに係合状態となる。
ついで、停車時から発進時におけるクラッチC-1制御、即ち、クラッチ制御手段24によるインニュートラル制御とアプライ制御とについて、図1を参照しつつ図5乃至図7に沿って説明する。例えばレンジ判定手段21によりDレンジが判定されている状態で、かつ停車判定手段22により車輌の停車が判定されると(車輌停車中におけるN-Dシフトも含む)、図5に示すように、クラッチC-1の制御を開始し(S2-1)、クラッチ制御手段24のニュートラル制御手段24aは、インニュートラル制御を開始する(S2-2)。ニュートラル制御手段24aは、このインニュートラル制御を開始すると、例えばリニアソレノイドバルブSLC1を指令制御して、クラッチC-1の係合圧PC1をストロークエンド圧(即ち油圧サーボ40がガタ詰めした状態)よりも低い圧にする解放制御を行い、つまりクラッチC-1を僅かに解放して自動変速機構5を完全なニュートラル状態にする。このようにクラッチC-1の係合圧PC1をストロークエンド圧よりも低い圧にすることで、ニュートラル制御中のクラッチC-1の引き摺りロスを完全に無くすことができ、エンジン2に対する負荷を軽減し、つまり車輌の燃費向上を図ることが可能となる。
つづいて、車輌の発進時に運転者がスロットル開度THを低開度で踏み込んだ場合にあって、ロックアップクラッチを係合したままクラッチC-1をスリップ係合する場合の走行例を図8に沿って説明する。例えばNレンジでフットブレーキ(Brake)が踏圧(ON)されて停車している状態にあっては、クラッチC-1の係合圧PC1が0であって該クラッチC-1が解放されており、また、ロックアップクラッチ7の係合圧PL-UPも0であって該ロックアップクラッチ7も解放されている。そのため、アイドル状態にあるエンジン回転数Neは、トルクコンバータ4においてポンプインペラ4aからタービンランナ4bに流体伝動されている状態であり、タービン回転数Ntは、該エンジン回転数Neよりも僅かに低い状態となっている。
つづいて、車輌の発進時に運転者がスロットル開度THを高開度で踏み込んだ場合にあって、ロックアップクラッチをスリップさせつつクラッチC-1をスリップ係合する場合の走行例を図9に沿って説明する。上記図8の場合と同様に、例えばNレンジでフットブレーキが踏圧されて停車している状態にあっては、クラッチC-1が解放されており、また、ロックアップクラッチ7も解放されている。そのため、アイドル状態にあるエンジン回転数Neは、トルクコンバータ4により流体伝動されている状態であり、タービン回転数Ntは、該エンジン回転数Neよりも僅かに低い状態となっている。
つづいて、図9の場合と同様に、車輌の発進時に運転者がスロットル開度THを高開度で踏み込んだ場合の別の実施形態として、ロックアップクラッチのスリップ状態から解放状態に移行しつつクラッチC-1をスリップ係合して車輌を発進させる場合の走行例を図11に沿って説明する。上記図9の場合と同様に、例えばNレンジでフットブレーキが踏圧されて停車している状態にあっては、クラッチC-1が解放されており、また、ロックアップクラッチ7も解放されている。そのため、アイドル状態にあるエンジン回転数Neは、トルクコンバータ4により流体伝動されている状態であり、タービン回転数Ntは、該エンジン回転数Neよりも僅かに低い状態となっている。
つづいて、上記スリップ発進制御手段24cによるクラッチC-1のスリップ発進制御の概要について図13及び図14に沿って説明する。本スリップ発進制御は、クラッチC-1をスリップさせつつ係合させることで車輌を発進させる際にあって、自動変速機構5の入力軸10の回転数(即ちタービン回転数Nt)が低下しないように制御するものである。なお、図13及び図14、後述する図15~図17における時点taから時点tdまでが例えば図8の時点t2-1から時点t4-1までの期間に相当するものである。また、図13の走行例ではスロットル開度THが0%のままであった場合、図14の走行例ではアクセルが踏まれてスロットル開度THが上昇した場合、をそれぞれ示すものである。
つづいて、スリップ発進制御手段24cによるスリップ発進制御において、自動変速機構5にて発生するイナーシャトルクから係合圧PC1を演算する演算手法について図15に沿って説明する。
I=TC_intertia2+GR_intertia・・・(1)
となる。
ω=(Ntarg-Nout×G1ST)/(TA-cnt_C1Slip)・・・(2)
となる。
TC1-CONT=(C(ecurrent)×Ne2×t(ecurrent)+TL-UP)×(TdivC1)・・・(3)
で算出され(図7のS2-4-6-2)、
クラッチC-1の出力側部材の回転数NC1における目標回転変化分として必要なトルク容量「TC1-change」は、
TC1-change=(Iω)×(TdivC1)・・・(4)
で算出され(図7のS2-4-6-3)、
クラッチC-1の出力側部材の回転数NC1における目標回転変化として必要なトルク容量は、
TC1=TC1-CONT+TC1-change=(C(ecurrent)×Ne2×t(ecurrent)+TL-UP+Iω)×(TdivC1)・・・(5)
となる。
次に、スリップ発進制御手段24cによるスリップ発進制御において、タービン回転数Ntとエンジン回転数Neとの速度比を一定に算出することで係合圧PC1を演算する演算手法について図16に沿って説明する。
TC1=(C(etarg)×Ne2×t(etarg))×(TdivC1)・・・(6)
となる。
ついで、スリップ発進制御手段24cによるスリップ発進制御において、目標一定タービン回転数Nttargを一定値として算出することで係合圧PC1を演算する演算手法について図17に沿って説明する。
etarg=Nttarg/Ne
として算出され、つまりエンジン回転数Neが変化しても、タービン回転数Ntが一定となるように目標速度比etargが算出される。そして、この目標速度比etargとなるトルク容量TC1は、上記数式(6)と同様に、
TC1=(C(etarg)×Ne2×t(etarg))×(TdivC1)・・・(6)’
となるが、目標速度比etargがエンジン回転数Neの変化に応じて変化するので、結果的にタービン回転数Ntが一定となるように演算される。
以上説明したように本自動変速機の制御装置1によると、クラッチ制御手段24が、Dレンジが判定され、かつ車輌の停車が判定された状態で、クラッチC-1を非係合状態に制御して自動変速機構5をニュートラル制御すると共に、車輌の発進意思の操作を検出した際に、クラッチC-1を係合制御して車輌をスリップ発進制御し、一方で、ロックアップ制御手段(ロックアップクラッチ制御手段)25が、Dレンジが判定され、かつ車輌の停車が判定された状態で(つまりニュートラル制御中に)、ロックアップクラッチ7を係合状態にすると共に、車輌の発進意思の操作を検出した際に、少なくともロックアップクラッチ7が所定トルク容量TL-UP1となるスリップ領域で係合するように制御するので、つまり車輌の発進前に先にロックアップクラッチ7を係合させておくので、発進直後にあってもロックアップクラッチ7を直ぐにスリップ領域で係合状態にすることができて(ロックアップクラッチ7の係合遅れを防止することができて)、発進直後におけるエンジン回転数Neの吹き上がりを防止することができ、車輌の燃費向上を図ることができる。また、エンジン回転数Neが低回転の状態にあっては、つまり運転者が要求する出力トルクが小さく、ロックアップクラッチ7に所定トルク容量TL-UPよりも小さなトルクが入力されるので、該ロックアップクラッチ7が安定的に係合状態にあり、揺り返しショックを生じることなく車輌を発進させることができ、乗り心地の向上を図ることができる。
2 駆動源(エンジン)
3 自動変速機
4 流体伝動装置、トルクコンバータ
5 自動変速機構
7 ロックアップクラッチ
21 レンジ判定手段
22 停車判定手段
23 発進意思操作検出手段
24 クラッチ制御手段
25 ロックアップクラッチ制御手段(ロックアップ制御手段)
25map ロックアップ制御マップ
32 車速検出手段(出力軸回転速度センサ)
34 要求出力検出手段(スロットル開度センサ)
C-1 クラッチ
Te 駆動源の出力トルク(エンジントルク)
TC1 クラッチのトルク容量
TL-UP1 所定トルク容量
Ne 駆動源の回転(エンジン回転数)
TH 運転者の要求出力(スロットル開度)
V 車速
Claims (5)
- 駆動源の回転を変速し得ると共に、発進時に係合されるクラッチを有する自動変速機構と、前記駆動源と前記自動変速機構との間に介在された流体伝動装置と、前記流体伝動装置をロックアップし得るロックアップクラッチと、を備えた自動変速機の制御装置において、
走行レンジを含むシフトレンジを判定するレンジ判定手段と、
車輌の停車を判定する停車判定手段と、
車輌の発進意思の操作を検出する発進意思操作検出手段と、
前記走行レンジが判定され、かつ前記車輌の停車が判定された状態で、前記クラッチを非係合状態に制御して前記自動変速機構をニュートラル状態にすると共に、前記車輌の発進意思の操作を検出した際に、前記クラッチを係合制御して前記車輌を発進制御するクラッチ制御手段と、
前記走行レンジが判定され、かつ前記車輌の停車が判定された状態で、前記ロックアップクラッチを係合状態にすると共に、前記車輌の発進意思の操作を検出した際に、少なくとも前記ロックアップクラッチが所定トルク容量となるスリップ領域で係合するように制御するロックアップクラッチ制御手段と、を備えた、
ことを特徴とする自動変速機の制御装置。 - 前記駆動源の出力トルク及び前記クラッチのトルク容量が前記ロックアップクラッチの所定トルク容量よりも小さい場合には、前記ロックアップクラッチを係合したまま前記クラッチをスリップ制御しながら前記車輌を発進させてなる、
ことを特徴とする請求項1記載の自動変速機の制御装置。 - 前記流体伝動装置は、トルクコンバータからなり、
前記駆動源の出力トルク及び前記クラッチのトルク容量が前記ロックアップクラッチの所定トルク容量よりも大きい場合には、前記ロックアップクラッチがスリップしつつ前記トルクコンバータのトルク増大作用を用いて前記車輌を発進させてなる、
ことを特徴とする請求項1または2記載の自動変速機の制御装置。 - 前記流体伝動装置は、トルクコンバータからなり、
前記駆動源の出力トルク及び前記クラッチのトルク容量が前記ロックアップクラッチの所定トルク容量よりも大きい場合には、前記ロックアップクラッチ制御手段が前記ロックアップクラッチを解放し、前記トルクコンバータのトルク増大作用を用いて前記車輌を発進させてなる、
ことを特徴とする請求項1または2記載の自動変速機の制御装置。 - 運転者の要求出力を検出する要求出力検出手段と、
前記車輌の車速を検出する車速検出手段と、
前記要求出力と前記車速との関係に対応して、前記ロックアップクラッチの解放領域、スリップ領域、係合領域が設定されたロックアップ制御マップと、を備え、
前記ロックアップクラッチ制御手段は、前記要求出力と前記車速とに基づき前記ロックアップ制御マップを参照して、前記ロックアップクラッチの解放、スリップ、係合を制御してなり、
前記ロックアップクラッチの解放領域は、前記駆動源の出力トルク及び前記クラッチのトルク容量が前記ロックアップクラッチの所定トルク容量よりも大きくなる状態に対応された、
ことを特徴とする請求項4記載の自動変速機の制御装置。
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Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5035376B2 (ja) | 2010-03-26 | 2012-09-26 | トヨタ自動車株式会社 | 車両用ロックアップクラッチの制御装置 |
JP5434868B2 (ja) * | 2010-09-28 | 2014-03-05 | アイシン・エィ・ダブリュ株式会社 | 自動変速機の制御装置、および、自動変速機の制御プログラム |
JP5772627B2 (ja) * | 2012-01-26 | 2015-09-02 | アイシン・エィ・ダブリュ株式会社 | 車両用伝動装置 |
JP5767997B2 (ja) * | 2012-03-29 | 2015-08-26 | ジヤトコ株式会社 | 車両の発進制御装置及び発進制御方法 |
US9488267B2 (en) * | 2012-09-14 | 2016-11-08 | Ford Global Technologies, Llc | Line pressure control with input shaft torque measurement |
KR101484253B1 (ko) * | 2012-10-08 | 2015-01-16 | 현대자동차 주식회사 | 자동변속기의 발진 제어방법 |
US9200686B2 (en) * | 2012-10-25 | 2015-12-01 | GM Global Technology Operations LLC | Binary clutch assembly control in neutral-to-drive or neutral-to-reverse transmission shifts |
DE102013001019A1 (de) * | 2013-01-22 | 2014-07-24 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Verfahren zum Auslösen eines Warnsignals bei einem Fehlverhalten beim Betrieb eines Kraftfahrzeugs |
JP5983857B2 (ja) * | 2013-02-26 | 2016-09-06 | アイシン・エィ・ダブリュ株式会社 | 変速機の制御装置および制御方法 |
CN105960556B (zh) * | 2014-02-05 | 2018-02-13 | 舍弗勒技术股份两合公司 | 用于防止机动车滑行的方法 |
US10753472B2 (en) | 2014-02-28 | 2020-08-25 | Aisin Aw Co., Ltd. | Control device for vehicle driving device |
JP6269415B2 (ja) * | 2014-09-24 | 2018-01-31 | マツダ株式会社 | 自動変速機の制御装置及び制御方法 |
JP6274060B2 (ja) * | 2014-09-25 | 2018-02-07 | マツダ株式会社 | 車両の制御装置及び制御方法 |
JP6191576B2 (ja) * | 2014-10-22 | 2017-09-06 | マツダ株式会社 | 車両の制御装置及び制御方法 |
JP6304094B2 (ja) * | 2015-03-26 | 2018-04-04 | トヨタ自動車株式会社 | ロックアップクラッチの制御装置 |
JP2016200270A (ja) * | 2015-04-14 | 2016-12-01 | トヨタ自動車株式会社 | 車両の制御装置 |
DE112016004869T5 (de) * | 2016-01-28 | 2018-07-19 | Aisin Aw Co., Ltd. | Übertragungsvorrichtung |
JP6269703B2 (ja) * | 2016-02-24 | 2018-01-31 | トヨタ自動車株式会社 | 車両用動力伝達装置の油圧制御装置 |
JP6598976B2 (ja) * | 2016-03-04 | 2019-11-06 | ジヤトコ株式会社 | 自動変速機の故障箇所検出装置及びこれを備えた自動変速機 |
JP6660483B2 (ja) * | 2016-10-26 | 2020-03-11 | ジヤトコ株式会社 | 車両の制御装置及び車両の制御方法 |
CN108223783B (zh) * | 2017-12-28 | 2019-06-28 | 吉孚汽车技术(浙江)有限公司 | 一种液力变矩器的控制方法 |
JP7275024B2 (ja) * | 2019-12-27 | 2023-05-17 | 株式会社クボタ | 作業車両 |
CN112032298B (zh) * | 2020-11-05 | 2021-02-23 | 盛瑞传动股份有限公司 | 液力变矩器的换挡控制方法及装置、电子设备及存储介质 |
CN113847423B (zh) * | 2021-09-29 | 2023-01-20 | 柳州赛克科技发展有限公司 | 一种液力变矩器起步控制方法及系统 |
CN114962623B (zh) * | 2022-05-17 | 2023-09-15 | 上汽通用五菱汽车股份有限公司 | 车辆起步控制的方法、装置、计算机设备和可读存储介质 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003343718A (ja) * | 2002-05-24 | 2003-12-03 | Toyota Motor Corp | 車輌の発進制御装置 |
JP2004263733A (ja) * | 2003-02-28 | 2004-09-24 | Mazda Motor Corp | 変速機の制御装置 |
JP2005003193A (ja) * | 2003-05-16 | 2005-01-06 | Toyota Motor Corp | 車両用ロックアップクラッチの制御装置 |
JP2008116005A (ja) * | 2006-11-07 | 2008-05-22 | Toyota Motor Corp | ロックアップクラッチを備えた自動変速機を搭載した車両の制御装置および制御方法ならびにその制御方法を実現するプログラムおよび記録媒体 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3642018B2 (ja) * | 2000-10-27 | 2005-04-27 | 日産自動車株式会社 | トルクコンバータのスリップ制御装置 |
DE10314324A1 (de) * | 2003-03-28 | 2004-10-07 | Zf Friedrichshafen Ag | Hydrodynamischer Wandler mit einer Primärkupplung |
JP2005016563A (ja) | 2003-06-23 | 2005-01-20 | Toyota Motor Corp | 車両用ロックアップクラッチの制御装置 |
JP4418404B2 (ja) * | 2005-03-09 | 2010-02-17 | ジヤトコ株式会社 | クラッチ制御装置及びクラッチ制御方法 |
JP4760065B2 (ja) * | 2005-03-11 | 2011-08-31 | トヨタ自動車株式会社 | 自動変速機の制御装置 |
JP2006300206A (ja) * | 2005-04-20 | 2006-11-02 | Toyota Motor Corp | 車両用ロックアップクラッチの制御装置 |
JP2008128437A (ja) * | 2006-11-24 | 2008-06-05 | Honda Motor Co Ltd | 車両のクリープ制御装置 |
JP4598005B2 (ja) * | 2007-01-25 | 2010-12-15 | 本田技研工業株式会社 | 車両用自動変速機の制御装置 |
JP2009047272A (ja) * | 2007-08-22 | 2009-03-05 | Aisin Aw Co Ltd | ロックアップクラッチ付き流体伝動装置 |
JP5266843B2 (ja) * | 2008-03-31 | 2013-08-21 | アイシン・エィ・ダブリュ株式会社 | クラッチの制御装置 |
-
2010
- 2010-03-31 JP JP2010082527A patent/JP5387481B2/ja not_active Expired - Fee Related
-
2011
- 2011-02-09 US US13/023,593 patent/US8682552B2/en not_active Expired - Fee Related
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- 2011-02-15 CN CN201180007846.2A patent/CN102741594B/zh not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003343718A (ja) * | 2002-05-24 | 2003-12-03 | Toyota Motor Corp | 車輌の発進制御装置 |
JP2004263733A (ja) * | 2003-02-28 | 2004-09-24 | Mazda Motor Corp | 変速機の制御装置 |
JP2005003193A (ja) * | 2003-05-16 | 2005-01-06 | Toyota Motor Corp | 車両用ロックアップクラッチの制御装置 |
JP2008116005A (ja) * | 2006-11-07 | 2008-05-22 | Toyota Motor Corp | ロックアップクラッチを備えた自動変速機を搭載した車両の制御装置および制御方法ならびにその制御方法を実現するプログラムおよび記録媒体 |
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