WO2011111169A1 - 駆動力制御装置 - Google Patents
駆動力制御装置 Download PDFInfo
- Publication number
- WO2011111169A1 WO2011111169A1 PCT/JP2010/053888 JP2010053888W WO2011111169A1 WO 2011111169 A1 WO2011111169 A1 WO 2011111169A1 JP 2010053888 W JP2010053888 W JP 2010053888W WO 2011111169 A1 WO2011111169 A1 WO 2011111169A1
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- WO
- WIPO (PCT)
- Prior art keywords
- engine
- hydraulic pressure
- automatic transmission
- engagement
- vehicle
- 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
- F16H61/0021—Generation or control of line pressure
- F16H61/0025—Supply of control fluid; Pumps therefore
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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
- F16H59/14—Inputs being a function of torque or torque demand
- F16H59/18—Inputs being a function of torque or torque demand dependent on the position of the accelerator pedal
- F16H2059/186—Coasting
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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
- F16H2312/14—Going to, or coming from standby operation, e.g. for engine start-stop operation at traffic lights
-
- 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
- F16H61/0021—Generation or control of line pressure
- F16H61/0025—Supply of control fluid; Pumps therefore
- F16H61/0028—Supply of control fluid; Pumps therefore using a single pump driven by different power sources
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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
- F16H61/0021—Generation or control of line pressure
- F16H61/0025—Supply of control fluid; Pumps therefore
- F16H61/0031—Supply of control fluid; Pumps therefore using auxiliary pumps, e.g. pump driven by a different power source than the engine
-
- 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
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19149—Gearing with fluid drive
- Y10T74/19158—Gearing with fluid drive with one or more controllers for gearing, fluid drive, or clutch
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19149—Gearing with fluid drive
- Y10T74/19158—Gearing with fluid drive with one or more controllers for gearing, fluid drive, or clutch
- Y10T74/19163—Gearing with fluid drive with one or more controllers for gearing, fluid drive, or clutch with interrelated controls
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/20—Control lever and linkage systems
- Y10T74/20012—Multiple controlled elements
- Y10T74/20018—Transmission control
- Y10T74/20024—Fluid actuator
Definitions
- the present invention relates to a driving force control device for a vehicle such as an automobile, and more particularly to a technical field of a driving force control device that performs driving force control when the vehicle is traveling inertially.
- the present invention has been made in view of the above-described problems, for example, and an object of the present invention is to propose a driving force control device capable of appropriately performing shift control even when the vehicle is in a free-run state.
- the driving force control device of the present invention is mounted on a vehicle, and transmits power between the engine and the automatic transmission according to the degree of engagement with the engine and the automatic transmission.
- Engaging means that can adjust the degree of the engine, an oil pump that generates hydraulic pressure by rotation of the drive shaft of the engine, the engine is stopped, and power between the engine and the automatic transmission is stopped by the engaging means.
- the first hydraulic pressure which is the hydraulic pressure of the automatic transmission, is necessary for performing the shift when the automatic transmission is shifted in a free-run state in which the vehicle travels with the transmission disconnected.
- the driving force control device is mounted on a vehicle such as an automobile.
- the engagement means such as a clutch can adjust the degree of power transmission between the engine and the automatic transmission according to the degree of engagement.
- Oil pump generates hydraulic pressure by rotation of engine drive shaft.
- the oil pump is a trochoidal oil pump including an inner rotor having trochoidal external teeth and an outer rotor having internal teeth engaging with the external teeth.
- the inner rotor is driven to rotate with the rotation of the drive shaft of the engine, the inner teeth and the outer teeth are engaged with each other, so that the outer rotor also rotates, and hydraulic pressure is generated due to the rotation of both rotors. .
- control means comprising a memory, a processor, etc.
- the control means is capable of automatic shifting in a free-run state where the vehicle travels with the engine stopped and the transmission of power between the engine and the automatic transmission cut off by the engaging means.
- the first hydraulic pressure and the first hydraulic pressure are set on condition that the first hydraulic pressure, which is the hydraulic pressure of the automatic transmission, does not reach the second hydraulic pressure, which is the hydraulic pressure required to perform the shift.
- the degree of engagement of the engagement means is controlled according to the hydraulic pressure difference between the two hydraulic pressures (that is, the shortage of hydraulic pressure).
- controlling the degree of engagement of the engagement means according to the hydraulic pressure difference between the first hydraulic pressure and the second hydraulic pressure means that the hydraulic pressure corresponding to the hydraulic pressure difference between the first hydraulic pressure and the second hydraulic pressure is the oil pressure. This means that the degree of engagement of the engagement means is controlled so that the rotational speed of the drive shaft of the engine that can be generated by the pump can be obtained.
- the shift of the automatic transmission in the free-run state is, for example, when the vehicle speed naturally increases or decreases, so that the running state of the vehicle changes from a predetermined upshift point or a predetermined downshift according to the automatic transmission. It means a shift performed when a point is straddled.
- the engine speed is essentially zero.
- the transmission of power between the engine and the automatic transmission that is, the drive wheel side
- it is desirable that the automatic transmission is not shifted from the viewpoint of reducing reactive energy.
- a relatively high hydraulic pressure and a relatively large amount of hydraulic oil flow are required to perform the shift of the automatic transmission.
- the oil pump that generates the hydraulic pressure by the rotation of the drive shaft of the engine cannot generate the hydraulic pressure during the free-run state. If the hydraulic oil is generated by the electric oil pump during the shift of the automatic transmission in the free-run state, the required capacity of the electric oil pump becomes relatively large, and the electric power for driving the electric oil pump Since the amount becomes relatively large, there is a risk that the fuel consumption may deteriorate due to the power balance, or the manufacturing cost may increase.
- the first hydraulic pressure which is the hydraulic pressure of the automatic transmission
- the degree of engagement of the engagement means is controlled in accordance with the hydraulic pressure difference between the first hydraulic pressure and the second hydraulic pressure on the condition that the second hydraulic pressure, which is the first hydraulic pressure, is not reached.
- the driving force control apparatus of the present invention it is possible to appropriately perform shift control even when the vehicle is in a free-run state.
- the control means when the control means controls the degree of engagement according to the hydraulic pressure difference, the control means further determines the degree of engagement according to the engine speed. to correct.
- control means controls the degree of engagement of the engagement means according to the hydraulic pressure difference (that is, the shortage of hydraulic pressure)
- the control means further performs the engagement according to the engine speed. Correct the degree.
- the engagement force (that is, the degree of engagement) of the arithmetic engagement means and the actually required engagement force are different due to, for example, variations in products, deterioration with time, etc. It turns out that there is.
- feedback control is performed with the difference between the current engine speed (ie, measured value) and the engine control target speed (ie, theoretical value) as a deviation, and the engaging force of the engaging means Is corrected.
- the shift control can be performed more appropriately.
- the driving force control apparatus further includes a torque converter disposed between the engine and the engagement means and having a lock-up clutch, and the control means further includes When shifting to the run state, the lock-up clutch is engaged on the condition that the rotational speed of the engine becomes zero.
- the torque converter having the lock-up clutch is disposed between the engine and the engaging means. That is, the input shaft of the torque converter is connected to the drive shaft of the engine, and the output shaft of the torque converter is connected to one end of the engaging means.
- the torque converter includes a lock-up clutch, a pump impeller, a turbine liner, a stator, and the like.
- the lockup clutch includes a torque converter cover and a lockup piston. The input shaft of the torque converter is connected to the pump impeller via the torque converter cover, and the output shaft of the torque converter is connected to the turbine liner and the lockup piston.
- the oil pump is connected to the pump impeller of the torque converter via a connecting member, for example. Therefore, the oil pump generates hydraulic pressure by the rotation of the torque converter cover of the torque converter that is rotated due to the rotation of the drive shaft of the engine.
- the lockup clutch is engaged by the control means on condition that the engine speed becomes zero when the vehicle shifts to the free-run state. For this reason, generation
- the rotation speed of the oil pump can reach the target rotation speed.
- control means further controls the automatic transmission so that a shift frequency is reduced on condition that the vehicle is in the free-run state.
- FIG. 1 is a block diagram showing the configuration of the drive control apparatus according to the present embodiment.
- a solid line indicates a mechanical connection (linkage)
- a dotted line indicates a signal
- a one-dot chain line indicates a hydraulic pressure supply
- a two-dot chain line indicates an electrical connection.
- FIG. 1 for convenience of explanation, only the portion directly related to the present embodiment is shown, and the other members are not shown.
- a driving force control device 100 is mounted on a vehicle 1, and includes an engine (engine) 11, an automatic transmission 12, a mechanical oil pump 13, an electric oil pump 14, a power storage device (power source) 15, and an ECU ( (Electronic Control Unit) 20.
- the engine 11 is a main power source for driving the vehicle, and is constituted by an internal combustion engine such as a gasoline engine or a diesel engine.
- the engine 11 includes at least one of an alternator, an electronic throttle, a variable valve mechanism, and a variable compression ratio mechanism that can change the characteristics of the engine 11.
- the axle 121 of the automatic transmission 12 is selectively connected to the drive shaft of the engine 11 via the input clutch 122.
- the input clutch 122 as an example of the “engagement means” according to the present invention is a hydraulic friction engagement device that is an engagement element often used in a known vehicle transmission, and is overlapped with each other.
- this is a wet multi-plate engagement device in which a plurality of friction plates are pressed by a hydraulic actuator.
- a mechanical oil pump 13 includes, for example, an inner rotor having trochoidal external teeth connected to a drive shaft of the engine 11 and internal teeth that engage with the external teeth. It is a trochoid type oil pump provided with an outer rotor which has. When the inner rotor is driven to rotate in accordance with the rotation of the drive shaft of the engine 11, the inner teeth and the outer teeth are engaged with each other, so that the outer rotor also rotates, and hydraulic pressure is generated due to the rotation of both rotors. To do.
- the electric oil pump 14 is driven by electric power supplied from a power storage device 15 such as a lead storage battery, and supplies hydraulic pressure to the automatic transmission 12 mainly when the vehicle 1 is free running.
- the electric oil pump 14 is an auxiliary oil pump, and its capacity is relatively small.
- the driving force control device 100 may include a stock pressure device that can hold the hydraulic pressure of the hydraulic oil in the automatic transmission 12 for a certain period, instead of the electric oil pump 14.
- the ECU 20 causes the vehicle 1 to travel in a state where the engine 10 is stopped and the transmission of power between the engine 10 and the automatic transmission 12 is cut off by the input clutch 122.
- the first hydraulic pressure that is the hydraulic pressure of the automatic transmission 12 does not reach the second hydraulic pressure that is the hydraulic pressure required to perform the shift.
- the degree of engagement of the input clutch 122 is controlled according to the hydraulic pressure difference between the first hydraulic pressure and the second hydraulic pressure.
- the driving force control device 100 includes one or more rotation sensors (not shown) capable of grasping the rotation state of the automatic transmission 12 such as the vehicle speed of the vehicle 1, the rotation speed of the engine 11, and the rotation speed of the mechanical oil pump. Further).
- a part of the functions of the ECU 20 for various electronic controls of the vehicle 1 is used as a part of the driving force control device 100.
- step S101 the ECU 20 determines whether or not the vehicle 1 is in a free-run state.
- step S101: No the ECU 20 executes the process of step S101 again.
- step S101 when it is determined that the vehicle 1 is in the free-run state (step S101: Yes), the ECU 20 determines the automatic transmission based on, for example, the shift line related to the automatic transmission 12, the current vehicle speed of the vehicle 1, and the like. It is determined whether or not 12 shifts are necessary (step S102). When it is determined that shifting of the automatic transmission 12 is not required (step S102: No), the ECU 20 executes the process of step S101.
- step S102 determines that shifting of the automatic transmission 12 is necessary.
- the ECU 20 determines that the current hydraulic oil pressure or supply flow rate in the automatic transmission 12 causes the automatic transmission 12 to shift. It is determined whether or not the hydraulic oil pressure or supply flow rate required for the operation is lower (that is, whether or not the hydraulic pressure or supply flow rate is insufficient) (step S103).
- step S103 the ECU 20 executes a process of step S108 described later.
- step S103 When it is determined that the hydraulic pressure or supply flow rate of the current hydraulic oil in the automatic transmission 12 is less than the hydraulic pressure or supply flow rate of the hydraulic oil necessary for performing the shift of the automatic transmission 12 (step S103: Yes).
- the ECU 20 calculates the rotational speed of the mechanical oil pump 13 necessary to make up for the shortage of hydraulic pressure and supply flow rate (step S104).
- the maximum discharge flow rate of the electric oil pump 14 is Q1
- the necessary flow rate required to generate the hydraulic pressure required for shifting the automatic transmission 12 is Q2.
- the discharge flow rate Q3 is obtained as Q2-Q1.
- the required rotational speed of the mechanical oil pump 13 is obtained from the relationship between the rotational speed of the mechanical oil pump 13 and the discharge flow rate as shown in FIG.
- FIG. 3 is a characteristic diagram showing an example of the relationship between the rotational speed of the mechanical oil pump and the discharge flow rate.
- step S104 the ECU 20 further determines the engagement force of the input clutch 122 from the calculated rotational speed of the mechanical oil pump 13 and the current vehicle speed of the vehicle 1.
- the engagement force of the input clutch 122 necessary to achieve the calculated rotational speed of the mechanical oil pump 13 is:
- the final engagement force of the input clutch 122 is determined by calculating the loss torque with respect to the target rotation speed of the engine 11 (that is, the calculated rotation speed of the mechanical oil pump 13).
- the torque loss mainly includes mechanical loss due to rotation of the engine 11, pump loss generated in the four steps of suction, compression, expansion and exhaust, mechanical loss of the mechanical oil pump 13 directly connected to the engine 11, And inertia torque due to rotation change can be considered. Therefore, if these losses are factored into the process of obtaining the engagement force of the input clutch 122 using a control model or a map, an accurate (ie, final) engagement force of the input clutch 122 can be obtained.
- step S104 the ECU 20 determines whether the negative torque when the input clutch 122 is engaged is large (step S105). When it is determined that the negative torque is not large (step S105: No), the ECU 20 executes a process of step S107 described later.
- the ECU 20 controls the characteristics of the engine 11 by controlling at least one of an alternator, an electronic throttle, a variable valve mechanism, and a variable compression ratio mechanism, for example. To change. Specifically, for example, when the input clutch 122 is engaged, the pumping loss is reduced by reducing the compression ratio, changing the lift amount or opening / closing timing of the intake / exhaust valve, or increasing the throttle opening. To do. The ECU 20 again determines the engagement force of the input clutch 122 according to the changed characteristics of the engine 11.
- the ECU 20 engages the input clutch 122 based on the determined engagement force of the input clutch 122 (step S107), and then starts shifting the automatic transmission 12 (step S108).
- the engaging force of the input clutch 122 in arithmetic may be different from the actually required engaging force due to, for example, product variations and deterioration over time. Therefore, in this embodiment, feedback control is performed with the difference between the current rotational speed of the engine 11 and the rotational speed of the control target of the engine 11 as a deviation, and the engaging force of the input clutch 122 is corrected.
- learning control for reflecting the corrected engagement force obtained by the feedback control in the next control may be incorporated. Thereby, it is possible to control the input clutch 122 appropriately from the beginning of the control.
- step S109 determines whether or not the shift of the automatic transmission 12 has been completed.
- step S109: No the ECU 20 executes the process of step S109 again.
- step S109 when it is determined that the shift of the automatic transmission 12 has ended (step S109: Yes), the ECU 20 releases the input clutch 122 (step S110). Note that the ECU 20 restores the characteristics of the engine 11 only when the characteristics of the engine 11 are changed in the process of step S106.
- the mechanical oil pump 13 can be operated to the minimum necessary by immediately releasing the input clutch 122. As a result, it is possible to reduce the load on the input clutch 122 and reduce a sense of discomfort.
- FIGS. 4 and 5 A second embodiment of the driving force control apparatus of the present invention will be described with reference to FIGS.
- the configuration is the same as that of the first embodiment except that a torque converter having a lockup is arranged between the engine and the automatic transmission. Therefore, in the second embodiment, the description overlapping with that of the first embodiment is omitted, and the same reference numerals are given to the common portions in the drawings, and only FIGS. 4 and 5 are basically different only. The description will be given with reference.
- FIG. 4 is a conceptual diagram showing a configuration of a torque converter that constitutes a part of the driving force control apparatus according to the present embodiment.
- the torque converter 16 includes a lockup clutch, a pump impeller 162, a turbine liner 163, and a stator 165.
- the lockup clutch includes a torque converter cover 161 and a lockup piston 164.
- the input shaft of the torque converter 16 has one end connected to the drive shaft of the engine 11 and the other end connected to the pump impeller 162 via the torque converter cover 161.
- the output shaft of the torque converter 16 has one end connected to the input clutch 122 and the other end connected to the turbine liner 163 and the lockup piston 164.
- the stator 165 has, for example, a one-way clutch (not shown) and has a torque amplification function. Engagement and release of the lockup clutch is controlled by the hydraulic pressure of oil supplied to the torque converter 16. The rotational speed of the output shaft of the torque converter 16 matches the turbine rotational speed.
- the mechanical oil pump 13 is connected to the pump impeller 162 of the torque converter 16 via a connecting member.
- the inner rotor is driven to rotate along with the rotation of the pump impeller 162 of the torque converter 16, the inner teeth and the outer teeth are engaged, so the outer rotor also rotates, and hydraulic pressure is generated due to the rotation of both rotors. Is done.
- step S201 the ECU 20 determines whether or not the vehicle 1 is in a free-run state.
- step S201: No the ECU 20 executes the process of step S201 again.
- step S201 when it is determined that the vehicle 1 is in the free-run state (step S201: Yes), the ECU 20 determines whether or not the lockup clutch is engaged (step S202). When it is determined that the lockup clutch is not engaged (step S202: No), the ECU 20 determines whether or not the input clutch 122 is completely released (step S203).
- step S203: No When it is determined that the input clutch 122 has not been completely released (step S203: No), the ECU 20 executes the process of step S201. On the other hand, when it is determined that the input clutch 122 is completely released (step S203: Yes), the ECU 20 determines whether or not the rotational speed of the engine 11 is zero (step S204).
- step S204: No When it is determined that the rotation speed of the engine 11 is not zero (step S204: No), the ECU 20 executes the process of step S204 again. On the other hand, when it is determined that the rotation speed of the engine 11 is zero (step S204: Yes), the ECU 20 engages the lockup clutch (step S205).
- the lockup clutch is engaged before the input clutch 122 is started to be engaged in step S107 in FIG. 2, the lockup clutch is engaged when the input clutch 122 is engaged. Compared with the case where it does, the period until the shifting of the automatic transmission 12 is completed can be shortened. In addition, since the oil flow in the torque converter 16 can be shut off by engaging the lockup clutch, the effect of reducing the consumption flow rate can be expected.
- step S202 when it is determined that the lockup clutch is engaged (step S202: Yes), the ECU 20 determines whether or not the input clutch 122 is released (step S206). When it is determined that the input clutch 122 has been released (step S206: Yes), the ECU 20 releases the lockup clutch (step S207).
- step S208 determines whether or not the vehicle 1 has returned to the free-run state.
- step S208: Yes the ECU 20 executes the process of step S207.
- step S208: No the ECU 20 executes the process of step S201.
- the rotational speed of the engine 11 is released by releasing the lock-up clutch.
- the acceleration changes due to the release of the input clutch 122 can be suppressed.
- the uncomfortable feeling can be reduced, which is very advantageous in practice.
- a third embodiment of the driving force control apparatus of the present invention will be described with reference to FIG.
- the third embodiment is the same as the configuration of the first embodiment except that the reference relating to the shift of the automatic transmission is different. Accordingly, the description of the third embodiment that is the same as that of the first embodiment is omitted, and common portions in the drawing are denoted by the same reference numerals, and only fundamentally different points are described with reference to FIG. explain.
- the shift line in the free-run state of the vehicle 1 is made different from that in the normal time (that is, in the non-free-run state). Thereby, deterioration of controllability can be prevented.
- the upshift and the downshift are performed at a higher vehicle speed than usual, it is possible to avoid the case where the shortage of hydraulic pressure or the like cannot be compensated even if the input clutch 122 is completely engaged.
- FIG. 6 shows an example of the relationship between the transmission vehicle speed and the engine speed when the input clutch is engaged.
- FIG. 7 is an example of a coast down shift pattern when the automatic transmission is a stepped automatic transmission.
- the automatic transmission 12 is a stepped automatic transmission, as shown in FIG. 7, in the free-run state, the number of shifts is reduced by skipping the shift stage within a range that does not cause a sense of incongruity. . Thereby, consumption of the hydraulic fluid flow rate can be suppressed.
- FIG. 8 is an example of a coast down shift pattern when the automatic transmission is a continuously variable transmission.
- the number of shifts is reduced by fixing the gear ratio within a certain vehicle speed range, as shown in FIG.
Abstract
Description
先ず、本発明に係る駆動力制御装置の第1実施形態について、図1乃至図3を参照して説明する。
本発明の駆動力制御装置に係る第2実施形態を、図4及び図5を参照して説明する。第2実施形態では、エンジンと自動変速機との間にロックアップを有するトルクコンバータが配置されている以外は、第1実施形態の構成と同様である。よって、第2実施形態について、第1実施形態と重複する説明を省略すると共に、図面上における共通箇所には同一符号を付して示し、基本的に異なる点についてのみ、図4及び図5を参照して説明する。
本発明の駆動力制御装置に係る第3実施形態を、図6を参照して説明する。第3実施形態では、自動変速機の変速に係る基準が異なる以外は、第1実施形態の構成と同様である。よって、第3実施形態について、第1実施形態と重複する説明を省略すると共に、図面上における共通箇所には同一符号を付して示し、基本的に異なる点についてのみ、図6を参照して説明する。
本実施形態の駆動力制御装置に係る第1変形例について、図7を参照して説明する。
本実施形態の駆動力制御装置に係る第2変形例について、図8を参照して説明する。
Claims (4)
- 車両に搭載され、
エンジンと、
自動変速機と、
係合の度合いに応じて、前記エンジン及び前記自動変速機間の動力の伝達の程度を調整可能な係合手段と、
前記エンジンの駆動軸の回転により油圧を発生させるオイルポンプと、
前記エンジンが停止し、且つ前記係合手段により前記エンジン及び前記自動変速機間の動力の伝達が切断された状態で前記車両が走行するフリーラン状態において、前記自動変速機の変速が行われる際に、前記自動変速機の油圧である第1油圧が前記変速を実施するために必要とされる油圧である第2油圧に達しないことを条件に、前記第1油圧及び前記第2油圧の油圧差に応じて前記係合の度合いを制御する制御手段と
を備えることを特徴とする駆動力制御装置。 - 前記制御手段は、前記油圧差に応じて前記係合の度合いを制御する際に、更に、前記エンジンの回転数に応じて前記係合の度合いを補正することを特徴とする請求項1に記載の駆動力制御装置。
- 前記エンジンと前記係合手段との間に配置され、ロックアップクラッチを有するトルクコンバータを更に備え、
前記制御手段は、更に、前記車両が前記フリーラン状態へ移行する際に、前記エンジンの回転数がゼロとなったことを条件に、前記ロックアップクラッチを係合させる
ことを特徴とする請求項1に記載の駆動力制御装置。 - 前記制御手段は、更に、前記車両が前記フリーラン状態であることを条件に、変速頻度が低下するように前記自動変速機を制御することを特徴とする請求項1に記載の駆動力制御装置。
Priority Applications (5)
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PCT/JP2010/053888 WO2011111169A1 (ja) | 2010-03-09 | 2010-03-09 | 駆動力制御装置 |
DE112010005368T DE112010005368T5 (de) | 2010-03-09 | 2010-03-09 | Antriebskraftsteuerungsgerät |
JP2010541642A JP5177234B2 (ja) | 2010-03-09 | 2010-03-09 | 駆動力制御装置 |
CN201080002017.0A CN102257297B (zh) | 2010-03-09 | 2010-03-09 | 驱动力控制装置 |
US13/001,889 US8522644B2 (en) | 2010-03-09 | 2010-03-09 | Driving force control apparatus |
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PCT/JP2010/053888 WO2011111169A1 (ja) | 2010-03-09 | 2010-03-09 | 駆動力制御装置 |
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WO2011111169A1 true WO2011111169A1 (ja) | 2011-09-15 |
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US (1) | US8522644B2 (ja) |
JP (1) | JP5177234B2 (ja) |
CN (1) | CN102257297B (ja) |
DE (1) | DE112010005368T5 (ja) |
WO (1) | WO2011111169A1 (ja) |
Cited By (1)
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WO2017051678A1 (ja) * | 2015-09-24 | 2017-03-30 | ジヤトコ株式会社 | 車両のセーリングストップ制御方法及び制御装置 |
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US9834217B2 (en) * | 2015-10-28 | 2017-12-05 | Ford Global Technologies, Llc | System and method for performing an engine stop and start for a rolling vehicle |
DE102017206375A1 (de) * | 2016-05-13 | 2017-11-16 | Robert Bosch Gmbh | Getriebeanordnung für einen Fahrantrieb, Fahrantrieb mit der Getriebeanordnung und Verfahren zur Steuerung der Getriebeanordnung |
JP6922173B2 (ja) * | 2016-08-29 | 2021-08-18 | 日産自動車株式会社 | 無段変速機の制御方法及び制御装置 |
JP6805657B2 (ja) * | 2016-09-08 | 2020-12-23 | 日産自動車株式会社 | 無段変速機及び無段変速機の制御方法 |
US11131351B2 (en) * | 2017-10-31 | 2021-09-28 | Honda Motor Co., Ltd. | Clutch control device |
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- 2010-03-09 JP JP2010541642A patent/JP5177234B2/ja not_active Expired - Fee Related
- 2010-03-09 US US13/001,889 patent/US8522644B2/en active Active
- 2010-03-09 DE DE112010005368T patent/DE112010005368T5/de active Pending
- 2010-03-09 WO PCT/JP2010/053888 patent/WO2011111169A1/ja active Application Filing
- 2010-03-09 CN CN201080002017.0A patent/CN102257297B/zh not_active Expired - Fee Related
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Also Published As
Publication number | Publication date |
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CN102257297B (zh) | 2015-09-09 |
US20110219903A1 (en) | 2011-09-15 |
JPWO2011111169A1 (ja) | 2013-06-27 |
JP5177234B2 (ja) | 2013-04-03 |
CN102257297A (zh) | 2011-11-23 |
DE112010005368T5 (de) | 2012-12-20 |
US8522644B2 (en) | 2013-09-03 |
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