WO2014170960A1 - 車両の制御装置および方法 - Google Patents
車両の制御装置および方法 Download PDFInfo
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- WO2014170960A1 WO2014170960A1 PCT/JP2013/061317 JP2013061317W WO2014170960A1 WO 2014170960 A1 WO2014170960 A1 WO 2014170960A1 JP 2013061317 W JP2013061317 W JP 2013061317W WO 2014170960 A1 WO2014170960 A1 WO 2014170960A1
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- WIPO (PCT)
- Prior art keywords
- continuously variable
- variable transmission
- transmission unit
- friction clutch
- torque
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/188—Controlling power parameters of the driveline, e.g. determining the required power
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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
- F16H61/66—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 continuously variable gearings
- F16H61/662—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 continuously variable gearings with endless flexible members
- F16H61/66254—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 continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling
- F16H61/66259—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 continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling using electrical or electronical sensing or control means
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/02—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
- B60W10/101—Infinitely variable gearings
- B60W10/107—Infinitely variable gearings with endless flexible members
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
- B60W10/11—Stepped gearings
- B60W10/115—Stepped gearings with planetary gears
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/19—Improvement of gear change, e.g. by synchronisation or smoothing gear shift
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing the toothed gearing having orbital motion
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2510/00—Input parameters relating to a particular sub-units
- B60W2510/02—Clutches
- B60W2510/0275—Clutch torque
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/10—Change speed gearings
- B60W2710/1005—Transmission ratio engaged
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H2037/026—CVT layouts with particular features of reversing gear, e.g. to achieve compact arrangement
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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
- F16H61/66—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 continuously variable gearings
- F16H2061/6602—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 continuously variable gearings with at least two dynamo-electric machines for creating an electric power path inside the transmission device, e.g. using generator and motor for a variable power torque path
- F16H2061/6603—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 continuously variable gearings with at least two dynamo-electric machines for creating an electric power path inside the transmission device, e.g. using generator and motor for a variable power torque path characterised by changing ratio in the mechanical gearing
Definitions
- the present invention relates to a vehicle control apparatus and method in which a stepped transmission unit having a fixed transmission ratio and a continuously variable transmission unit that continuously changes the transmission ratio are provided in parallel between an input shaft and an output shaft. It is about.
- a stepped transmission unit having one or more fixed transmission ratios between an input shaft to which power output from a power source of a vehicle is input and an output shaft from which torque is output, and the transmission ratios are continuously and non-existent.
- a configuration is known in which a continuously variable transmission that changes in stages is arranged in parallel.
- the vehicle configured as described above is provided with a clutch for switching between a transmission path including a stepped transmission unit and a transmission path including a continuously variable transmission unit.
- the fixed gear ratio by the stepped transmission unit is set to a gear ratio that cannot be set by the continuously variable transmission unit.
- various control devices or control methods have been proposed for switching a route through which power is transmitted in accordance with the traveling state of the vehicle.
- Japanese Patent Laid-Open No. 03-061762 discloses a configuration for switching to a transmission path including the same.
- Japanese Patent Laid-Open No. 03-061762 describes that when switching from a transmission path including a stepped transmission unit to a transmission path including a continuously variable transmission unit, the shifting operation in the continuously variable transmission unit is prohibited until the switching is completed. Has been. Thereby, the gear ratio by the continuously variable transmission unit can be maintained at the maximum gear ratio from the start to the completion of the switching operation. Therefore, when the vehicle is switched to a traveling state in which power is transmitted via the transmission path including the continuously variable transmission unit, the vehicle can be driven while exhibiting a deceleration action by the maximum gear ratio.
- the present invention has been made paying attention to the above technical problem, and improves the shift response when switching from a transmission path including a stepped transmission unit to a transmission path including a continuously variable transmission unit. It is an object of the present invention to provide a configured vehicle control apparatus and method.
- the present invention provides a continuously variable transmission that continuously changes a gear ratio between an input shaft to which torque output from a power source is input and an output shaft that outputs torque;
- a stepped transmission unit capable of setting a gear ratio that cannot be set by the continuously variable transmission unit is provided in parallel, and is engaged in a traveling state in which torque is transmitted via a transmission path including the stepped transmission unit, and
- the first friction clutch is released in a traveling state in which torque is transmitted via a transmission path including a continuously variable transmission, and is engaged in a traveling state in which torque is transmitted via a transmission path including the continuously variable transmission.
- a second friction clutch that is disengaged in a traveling state in which torque is transmitted via a transmission path that includes the stepped transmission unit.
- the speed change operation in the continuously variable transmission unit is started. It is comprised so that it may make it.
- the control apparatus of the vehicle characterized by the above-mentioned.
- the gripping operation by the friction clutch is configured such that the gripping operation by the friction clutch is performed while the transmission gear ratio by the continuously variable transmission is changing.
- a vehicle control device characterized by the above.
- the present invention is characterized in that, in the above-described invention, the shifting operation of the continuously variable transmission unit is stopped when an inertia phase generated by a gripping change operation by the friction clutch is started. It is a control device.
- This invention is the vehicle control device according to the above-mentioned invention, characterized in that the speed change operation of the continuously variable transmission portion is resumed before the gripping change operation by the friction clutch is completed.
- the present invention is characterized in that, in the above invention, when the transmission torque capacity in the second friction clutch is determined to be equal to or greater than a predetermined value, the shift operation in the continuously variable transmission unit is resumed.
- This is a vehicle control device.
- the continuously variable transmission unit includes a pair of pulleys, and a difference between the rotational speed of the output shaft and the rotational speed of the driven pulley in the continuously variable transmission unit is within a predetermined value.
- the vehicle control device is configured to restart the speed change operation in the continuously variable transmission.
- each of the first friction clutch and the second friction clutch includes a hydraulic actuator, and when it is determined that the hydraulic pressure of the second friction clutch has exceeded a predetermined value, the continuously variable The vehicle control device is configured to restart the speed change operation in the speed change portion.
- the continuously variable transmission unit that continuously changes the gear ratio between the input shaft to which the torque output from the power source is input and the output shaft that outputs the torque cannot be set by the continuously variable transmission unit.
- a first friction clutch that is released in a traveling state in which torque is transmitted via a clutch, and a first friction clutch that is engaged in a traveling state in which torque is transmitted via a transmission path that includes the continuously variable transmission
- the stepped transmission is
- the path for transmitting torque to That when to start the shift operation in , the continuously-variable transmission portion is a control
- the speed change operation in the continuously variable transmission unit is started. This is a vehicle control method.
- the gripping change operation by the friction clutch is performed by the friction clutch while the gear ratio by the continuously variable transmission is changing. It is a control method.
- This invention is the vehicle control method according to the above invention, characterized in that the shifting operation of the continuously variable transmission portion is stopped when the inertia phase generated by the gripping change operation by the friction clutch is started.
- This invention is the vehicle control method according to the above invention, characterized in that the shifting operation of the continuously variable transmission portion is resumed before the gripping change operation by the friction clutch is completed.
- the present invention provides the vehicle control method according to the above invention, wherein when the transmission torque capacity in the second friction clutch is determined to be equal to or greater than a predetermined value, the speed change operation in the continuously variable transmission is resumed. is there.
- the continuously variable transmission unit includes a pair of pulleys, and a difference between the rotational speed of the output shaft and the rotational speed of the driven pulley in the continuously variable transmission unit is within a predetermined value.
- the shift operation in the continuously variable transmission unit is resumed when the determination is made.
- each of the first friction clutch and the second friction clutch includes a hydraulic actuator, and when it is determined that the hydraulic pressure of the second friction clutch has exceeded a predetermined value, the continuously variable A vehicle control method characterized by resuming a speed change operation in a speed change portion.
- the present invention when switching from the transmission path including the stepped transmission unit to the transmission path including the continuously variable transmission unit, before the transmission torque capacity of the friction clutch engaged at the time of switching starts to increase, Since the speed change operation of the speed change part is started, it is possible to prevent the speed change ratio by the continuously variable speed change part from being delayed with respect to the target speed change ratio, and to improve the speed change response. In addition, since the time required to complete the engagement of the clutch is not increased while the shift shock is reduced, the load acting on the friction material in the friction clutch can be suppressed. Therefore, the durability of the friction clutch can be improved. Further, the switching control of the transmission path and the control in the speed change operation of the continuously variable transmission can be controlled independently, and the control can be prevented from becoming complicated. Therefore, transmission path switching control and shift control for improving shift response can be realized with a simple control structure.
- a vehicle control device is a continuously variable transmission that is mounted on a vehicle and continuously changes a gear ratio between an input shaft that receives power output from a power source and an output shaft that outputs power.
- a stepped transmission unit comprising a gear mechanism having one or a plurality of predetermined transmission ratios provided in parallel with the continuously variable transmission unit.
- a clutch mechanism for switching between a transmission path including the continuously variable transmission unit and a transmission path including the stepped transmission unit is provided. Accordingly, the present invention is configured to operate the clutch mechanism and the continuously variable transmission unit when switching the transmission path of the power from the transmission path including the stepped transmission unit to the transmission path including the continuously variable transmission unit. Has been.
- FIG. 1 shows an example of a power train targeted by the present invention, and particularly schematically shows a power transmission path from a power source to a drive wheel via a transmission.
- the power train described here is a mechanism that changes the speed ratio represented by the ratio between the rotational speed N in of the input shaft 4 and the rotational speed N out of the output shaft 8.
- the continuously variable transmission unit 7 and the stepped transmission unit 20 are included.
- the power source 1 is constituted by an internal combustion engine (E / G) such as a gasoline engine. In the following description, the power source 1 will be described as the engine 1.
- a torque converter 3 with a lock-up clutch is connected to the crankshaft 2 of the engine 1.
- the torque converter 3 has a configuration that is conventionally known as a fluid transmission device.
- a turbine runner 3c is disposed opposite to the pump impeller 3b integrated with the front cover 3a, and a stator 3d held via a one-way clutch (not shown) is interposed between the pump impeller 3b and the turbine runner 3c.
- a one-way clutch (not shown) is interposed between the pump impeller 3b and the turbine runner 3c.
- the front cover 3a is connected to the crankshaft 2, and the front cover 3a and the pump impeller 3b rotate integrally with the crankshaft 2.
- the turbine runner 3 c is connected to the input shaft 4 and rotates integrally with the input shaft 4.
- the rotational speed N in the rotation speed N t and the input shaft 4 of the turbine runner 3c is configured to have the same rotational speed.
- a lock-up clutch 3e that rotates integrally with the turbine runner 3c is disposed to face the inner surface of the front cover 3a.
- the one-way clutch described above is provided between the stator 3d and a fixing member such as a casing.
- the forward / reverse switching mechanism 5 is arranged on the same axis as the input shaft 4.
- the forward / reverse switching mechanism 5 switches between a forward state in which the rotational direction of the power transmitted from the input shaft 4 is transmitted without changing and a reverse state in which the rotational direction of the power transmitted from the input shaft 4 is reversed and transmitted.
- the forward / reverse switching mechanism 5 is configured by a so-called differential mechanism in which three rotating elements make a differential action with each other. That is, this type of differential mechanism is conventionally known in various ways, and any of the differential mechanisms can be employed in the forward / reverse switching mechanism in the present invention.
- the forward / reverse switching mechanism 5 is constituted by a double pinion type planetary gear mechanism.
- the forward / reverse switching mechanism 5 includes a sun gear 5s that is an external gear, a ring gear 5r that is an internal gear disposed concentrically with the sun gear 5s, and a first pinion gear 5P that meshes with the sun gear 5s. 1 , a second pinion gear 5P 2 meshed with the first pinion gear 5P 1 and the ring gear 5r, and a carrier 5c holding the first and second pinion gears 5P 1 and 5P 2 so as to be capable of rotating and revolving.
- the sun gear 5s is configured to rotate integrally with the input shaft 4, and constitutes an input element in the planetary gear mechanism.
- a brake mechanism B that selectively stops the rotation of the ring gear 5r is provided.
- the ring gear 5r constitutes a reaction force element in the planetary gear mechanism.
- the brake mechanism B is provided between the ring gear 5r and a fixing member 91 such as a casing, and can be constituted by a friction brake such as a multi-plate brake or a meshing brake.
- the carrier 5c rotates integrally with a drive gear 21 of the stepped transmission unit 20, which will be described later, and constitutes an output element in the planetary gear mechanism. Furthermore, between the carrier 5c and the sun gear 5s, the first clutch mechanism C 1 for rotating integrally the entire planetary gear mechanism by connecting the carrier 5c and the sun gear 5s are provided.
- the first clutch mechanism C 1 is a mechanism for connecting or disconnecting the input shaft 4 and the stepped transmission unit 20.
- the first clutch mechanism C 1 is configured to transmit directly to the carrier 5c is the output element of the torque of the input shaft 4. That is, the first clutch mechanism C 1 can selectively transmit or block torque between the input shaft 4 and the stepped transmission unit 20.
- the first clutch mechanism C 1 in the present invention the transfer torque capacity in response to the engagement force is made by gradually increasing or decreasing wet or dry friction clutch.
- the first clutch mechanism C 1 of this embodiment is provided with a hydraulic actuator connected to the hydraulic circuit (not shown), and is configured to operate by changing the pressure P C1 of the hydraulic actuator. Therefore, since the engagement force is varied by increasing or decreasing the first clutch mechanism C 1 hydraulic (engagement pressure) P C1, transmission of the first clutch mechanism C 1 by controlling the change of the pressure P C1 It is configured to control a change in torque capacity.
- the planetary gear mechanism constituting the forward / reverse switching mechanism 5 can be represented by a conventionally known collinear diagram. Specifically, the sun gear 5s, the ring gear 5r, and the carrier 5c are represented by three lines parallel to each other, and the line indicating the sun gear 5s and the line indicating the carrier 5c are located at the left and right ends, and the reaction force is at the center thereof. A line indicating the ring gear 5r as an element is arranged. When the distance between the line indicating the sun gear 5s and the line indicating the carrier 5c is “1”, the distance between the line indicating the ring gear 5r and the line indicating the carrier 5c is the number of teeth of the sun gear 5s and the teeth of the ring gear 5r.
- the distance from the base line O of each line indicates the number of rotations of each rotating element. Therefore, the rotation speed and rotation direction of each rotating element in the planetary gear mechanism can be represented by the alignment chart.
- a stepped transmission unit 20 including a transmission path including a continuously variable transmission unit 7 that continuously changes a transmission gear ratio between an input shaft 4 and an output shaft 8 and a gear train having an inherent transmission gear ratio. are provided in parallel with the transmission path.
- the gear ratio by the continuously variable transmission unit 7 is described as a variable gear ratio gamma 1, describes a gear ratio by the geared transmission unit 20 and the fixed gear ratio gamma 2.
- the continuously variable transmission unit 7 is configured by a conventionally known belt type continuously variable transmission. Specifically, in the continuously variable transmission unit 7, the primary shaft 6 and the secondary shaft 44 are provided in parallel, and the primary pulley 30 that is a driving side member that rotates integrally with the primary shaft 6 and the secondary shaft 44 are integrated. A secondary pulley 40, which is a driven side member that rotates automatically, and a belt 7a wound around these pulleys 30 and 40. Accordingly, the pulleys 30 and 40 are configured to change the winding radius of the belt 7a to be larger or smaller by changing the width of the groove around which the belt 7a is wound to wide or narrow. That is configured to be able to alter the groove width belt 7a is wound is varied continuously and steplessly variable gear ratio gamma 1.
- the primary pulley 30 is configured to rotate integrally with the primary shaft 6 disposed on the same axis as the input shaft 4, and is disposed on the opposite side of the engine 1 with the forward / reverse switching mechanism 5 interposed therebetween in the axial direction. ing.
- the primary shaft 6 and the input shaft 4 are configured to rotate integrally. That is, the primary shaft 6 is connected so as to rotate integrally with the sun gear 5 s of the forward / reverse switching mechanism 5.
- the primary pulley 30 includes a fixed sheave 31 that is integrated with the primary shaft 6, and a movable sheave 32 that is fitted to the primary shaft 6 so as to be movable in the axial direction and approaches or separates from the fixed sheave 31. Yes.
- a thrust applying mechanism 33 that applies a thrust for moving the movable sheave 32 toward the fixed sheave 31.
- the thrust applying mechanism 33 is disposed on the back side of the movable sheave 32, that is, on the opposite side of the fixed sheave 31 with the movable sheave 32 sandwiched in the axial direction.
- the thrust imparting mechanism 33 includes an electric actuator, a hydraulic actuator, and the like, and is configured to generate an axial thrust for imparting to the movable sheave 32.
- the primary shaft 6 and the input shaft 4 are configured to rotate integrally, the primary shaft 6 may be described as the input shaft 4 in the following description. .
- the secondary pulley 40 is arranged so that the rotation center axis of the secondary pulley 40 is parallel to the rotation center axis of the primary pulley 30.
- the secondary pulley 40 includes a fixed sheave 41 integrated with the secondary shaft 44, and a movable sheave 42 that is configured to be movable in the axial direction with respect to the secondary shaft 44 and that approaches or is separated from the fixed sheave 41. I have. Further, a thrust imparting mechanism 43 that imparts thrust to move the movable sheave 42 toward the fixed sheave 41 is provided.
- the thrust applying mechanism 43 is disposed on the back side of the movable sheave 42 in the axial direction, that is, on the opposite side of the fixed sheave 41 with the movable sheave 42 interposed therebetween.
- the thrust applying mechanism 43 includes an electric actuator, a hydraulic actuator, and the like, and is configured to generate an axial thrust for applying to the movable sheave 42.
- a second clutch mechanism C 2 that selectively connects the secondary shaft 44 and the output shaft 8 is provided between the secondary pulley 40 and the output shaft 8. Further, the second clutch mechanism C 2 is configured to directly transmit the torque of the secondary shaft 44 to the output shaft 8. That is, the second clutch mechanism C 2 can selectively transmit or block torque between the continuously variable transmission unit 7 and the output shaft 8.
- the second clutch mechanism C 2 in the present invention, the transfer torque capacity in response to the engagement force is made by gradually increasing or decreasing wet or dry friction clutch.
- the second clutch mechanism C 2 in this embodiment is provided with a hydraulic actuator connected to the hydraulic circuit (not shown), and is configured to operate by changing the pressure P C2 of the hydraulic actuator.
- the transmission of the second clutch mechanism C 2 by controlling the change of the oil pressure P C2 It is configured to control a change in torque capacity.
- the hydraulic actuator in which the second clutch mechanism C 2 comprising the hydraulic chamber may be connected to an accumulator (not shown).
- the stepped transmission unit having one or a plurality of fixed transmission ratios will be described.
- the stepped transmission unit is a reduction mechanism that sets a fixed transmission ratio ⁇ 2 that is larger than the maximum transmission ratio ⁇ 1max that can be set by the continuously variable transmission unit 7 or the minimum transmission ratio ⁇ that can be set by the continuously variable transmission unit 7.
- This is a speed increasing mechanism that sets a fixed speed ratio ⁇ 2 smaller than 1 min .
- the stepped transmission unit 20 of this specific example is configured as a speed reduction mechanism, and the rotation direction of the drive gear 21 that is the drive side rotation member and the rotation of the driven gear 25 that is the driven side rotation member.
- a counter shaft 23 for making the direction the same is provided between the input shaft 4 and the output shaft 8.
- the drive gear 21 is integrally connected to the carrier 5 c that is an output element of the forward / reverse switching mechanism 5 and meshes with the counter driven gear 22.
- the counter driven gear 22 is formed with a larger diameter than the drive gear 21. That is, the counter driven gear 22 has more teeth than the drive gear 21. Therefore, when torque is transmitted from the drive gear 21 toward the counter driven gear 22, the first gear pair composed of the drive gear 21 and the counter driven gear 22 is configured to generate a speed reducing action.
- the counter drive gear 24 has a smaller diameter than the counter driven gear 22 and meshes with the driven gear 25.
- the counter drive gear 24 is formed with a smaller diameter than the driven gear 25. That is, the number of teeth of the counter drive gear 24 is smaller than the number of teeth of the driven gear 25. Accordingly, when torque is transmitted from the counter drive gear 24 toward the driven gear 25, the second gear pair composed of the counter drive gear 24 and the driven gear 25 is configured to reduce the speed.
- the driven gear 25 is fitted to be rotatable relative to the output shaft 8 on the outer peripheral side of the output shaft 8, it is connected to the output shaft 8 by the third clutch mechanism C 3 to be described later integrally Rotate.
- the stepped transmission unit 20 is configured such that the rotation direction of the drive gear 21 and the rotation direction of the output shaft 8 are the same direction. Therefore, the fixed gear ratio ⁇ 2 by the stepped transmission unit 20 is the gear ratio between the drive gear 21 and the counter driven gear 22 (gear ratio i 1 ) and the gear ratio between the counter drive gear 24 and the driven gear 25. It is a value obtained by multiplying (gear ratio i 2 ). Further, the stepped transmission unit 20 shown in FIG. 1 is configured such that the fixed transmission ratio ⁇ 2 is larger than the maximum transmission ratio ⁇ 1max that can be set by the continuously variable transmission unit 7.
- the third clutch mechanism C 3 is provided between the driven gear 25 and the output shaft 8, it is configured to selectively connect the driven gear 25 and the output shaft 8. That is, the third clutch mechanism C 3 can selectively transmit or block torque between the stepped transmission unit 20 and the output shaft 8. Therefore, in the transmission path including the geared transmission unit 20, the first clutch mechanism C 1 is provided, and the output shaft 8 side third clutch mechanism C 3 is provided on the input shaft 4 side. Further, as described above, since the first clutch mechanism C 1 is made of the friction clutch, the third clutch mechanism C 3 is configured to switch between the two states of the engagement between the driven gear 25 and the output shaft 8 and the released state The transmission torque capacity need not take a value between 0% and 100%. Therefore, the third clutch mechanism C 3 is constituted by meshing clutch such as a dog clutch or the synchromesh mechanism.
- the spline formed on the clutch gear 55 that rotates integrally with the driven gear 25 is formed on the sleeve 53 together with the spline formed on the hub 51 that rotates integrally with the output shaft 8.
- the driven gear 25 is configured to be connected to the output shaft 8 by being fitted to the spline.
- the third clutch mechanism C 3 in this specific example, a rotating synchronous device, the output shaft 8 is a synchronous-side member, causing equally by the frictional force the rotational speed of the driven gear 25 is the synchronized-side member It is configured as follows.
- the sleeve 53 is configured to move in the axial direction by an appropriate actuator (not shown), and a control device for electrically controlling the operation of the actuator is provided.
- the vehicle Ve shown in FIG. 1 is an example configured to be suitable for an FF (front engine / front drive) vehicle, and torque is output from the output shaft 8 to the front differential 12 that is the final reduction gear via the reduction gear mechanism 10.
- Is configured to output Specifically, an output gear 9 is attached to the output shaft 8, and a large-diameter gear 10a meshing with the output gear 9 is attached to the reduction gear shaft 10b.
- a small-diameter gear 10c is attached to the reduction gear shaft 10b, and the small-diameter gear 10c meshes with the ring gear 11 of the front differential 12.
- the front differential 12 is configured to transmit torque transmitted via the ring gear 11 from the left and right drive shafts 13 to drive wheels (not shown).
- an electronic control unit (not shown) is used as a controller for controlling the engagement operation or the release operation of each clutch mechanism C 1 , C 2 , C 3 and the brake mechanism B and controlling the speed change operation of the continuously variable transmission unit 7.
- the electronic control unit is configured to include an arithmetic processing unit (CPU), a storage unit (RAM and ROM), and a microcomputer mainly having an input / output interface. Moreover, it is comprised so that a signal may be input into the electronic control unit from various sensors (not shown).
- the storage device of the electronic control device stores various data together with various control programs, and is configured to execute various arithmetic processes. Therefore, the electronic control unit is configured to perform various arithmetic processes based on the input detection signal and stored data, and output an instruction signal for performing various controls according to the result of the arithmetic process. ing.
- the electronic control unit calculates a required driving force based on the accelerator opening Acc and the vehicle speed V, and controls the vehicle so that the required power calculated based on the required driving force can be output. That is, the electronic control unit controls switching between the transmission path including the stepped transmission unit 20 and the transmission path including the continuously variable transmission unit 7 based on the accelerator opening Acc and the vehicle speed V, and in the continuously variable transmission unit 7. It is configured to perform shift control. That is, an instruction signal for operating each of the clutch mechanisms C 1 , C 2 , C 3 and the brake mechanism B is output from the electronic control unit according to the traveling state of the vehicle Ve, and there is no power transmission path through which power is transmitted. The operation of switching from the transmission path including the stepped transmission unit 7 to the transmission path including the stepped transmission unit 20 or from the transmission path including the stepped transmission unit 20 to the transmission path including the continuously variable transmission unit 7 is performed. It is configured.
- FIG. 4 shows a table showing the engagement and disengagement states of the clutch mechanisms C 1 , C 2 , C 3 and the brake mechanism B according to the traveling state of the vehicle Ve. Note that “ON” shown in FIG. 4 indicates engagement, “OFF” indicates release, and “ON” in parentheses indicates that the engagement state is transitively engaged. Show.
- the driven gear 25 in the geared transmission unit 20 is coupled to the output shaft 8 by the third clutch mechanism C 3. Therefore, the torque output from the engine 1 is transmitted from the input shaft 4 to the output shaft 8 via the stepped transmission 20. That is, the stepped transmission 20 that is a speed reduction mechanism generates a speed reduction action, the amplified torque is transmitted to the output shaft 8, and the output shaft 8 rotates in the forward traveling direction.
- the total speed ratio ⁇ 4 in this case is a speed ratio obtained by multiplying the fixed speed ratio ⁇ 2 by the stepped speed change unit 20 and the speed ratio ⁇ 3 by the planetary gear mechanism constituting the forward / reverse switching mechanism 5.
- the total speed ratio ⁇ 4 is a speed ratio represented by a ratio between the rotational speed N in of the input shaft 4 and the rotational speed N out of the output shaft 8. Further, as described above, in this specific example, the fixed speed ratio ⁇ 2 is a speed ratio larger than the maximum speed ratio ⁇ 1max . Accordingly, when starting in the forward direction, the forward / reverse switching mechanism 5 is integrally rotated as a whole, so that the total speed ratio ⁇ 4 is represented by a fixed speed ratio ⁇ 2 and is larger than the maximum speed ratio ⁇ 1max. .
- the torque of the output shaft 8 is transmitted from the output gear 9 to the left and right drive wheels via the reduction gear mechanism 10 and the front differential 12, and a large driving force is generated in the drive wheels, so that the vehicle starts.
- the continuously variable transmission unit 7 is connected to the input shaft 4 and the sun gear via the primary shaft 6 even when torque is transmitted via the transmission path including the stepped transmission unit 20. It is always connected to 5s. Therefore, the torque which the engine 1 is output, is transmitted to the pulley 30 and 40 of the continuously variable transmission unit 7, as described above, at the time of start is in the state where second clutch mechanism C 2 is released, secondary The shaft 44 and the output shaft 8 are separated so as not to transmit torque. Therefore, when torque is transmitted via the transmission path including the stepped transmission 20, torque is not transmitted between the input shaft 4 and the output shaft 8 via the continuously variable transmission 7. The so-called interlock state will not occur.
- This control is a gripping change control conventionally known as clutch-to-clutch control.
- clutch-to-clutch control With this configuration, the torque of the output shaft 8 changes smoothly, causing a shift shock and a feeling of strangeness. It can be avoided or suppressed. Therefore, replacement gripping in the control of switching the path in which the power is transmitted from the transmission path including the geared transmission unit 20 to the transmission path including the continuously variable transmission unit 7, the first clutch mechanism C 1 and the second clutch mechanism C 2 Metropolitan Control is included.
- the transmission path switching control process executed by the electronic control unit and the operation of the vehicle Ve by executing the switching control will be specifically described.
- the state of the vehicle Ve before executing the transmission path switching control is such that the variable gear ratio ⁇ 1 is the maximum gear ratio ⁇ 1max and the total gear ratio ⁇ 4 is larger than the maximum gear ratio ⁇ 1max .
- the first oil pressure P C1 of the clutch mechanism C 1 is a hydraulic ie full engagement pressure first clutch mechanism C 1 is fully engaged, the second clutch mechanism for the second clutch mechanism C 2 is released C the second hydraulic P C2 is zero.
- the transmission path switching control described here is control performed while the rotation speed N out of the output shaft 8 is increasing, that is, upshift control.
- the engagement operation or the release operation in each of the clutch mechanisms C 1 and C 2 and the brake mechanism B and the shift operation by the continuously variable transmission unit 7 are configured to operate independently. Therefore, the electronic control device is configured to independently control the transmission path switching control by controlling the engagement operation and the release operation and the shift control in the continuously variable transmission unit 7.
- the electronic control unit requests the total speed ratio ⁇ 4 to be a speed ratio smaller than the maximum speed ratio ⁇ 1max , or the input shaft speed N in (or the engine speed N e or the turbine speed N t ). And a stepped transmission unit when it is determined that there is a request for a rotational speed smaller than the input shaft rotational speed N in configured by the total gear ratio ⁇ 4.
- An instruction signal for starting control for switching the power transmission path from the transmission path including 20 to the transmission path including the continuously variable transmission unit 7 is output.
- the electronic control device outputs an instruction signal for switching the transmission path after outputting an instruction signal for controlling the shift operation in the continuously variable transmission unit 7. It is configured.
- the electronic control device outputs an instruction signal for operating the thrust applying mechanism 33 and changes the groove width of the primary pulley 30 by controlling the thrust applying mechanism 33 by electric control or hydraulic control.
- the electronic control unit determines that the increased vehicle speed V has reached a predetermined vehicle speed during forward travel in which torque is transmitted via the transmission path including the stepped transmission unit 20, or the output shaft rotational speed N When it is determined that out has reached a predetermined number of revolutions, an instruction signal for shifting the above-described continuously variable transmission unit 20 and an instruction signal for starting switching control of the transmission path are output. Also good.
- the electronic control unit may perform control so that the speed change operation of the continuously variable transmission unit 7 is started before the clutch re-holding control is started.
- the speed change control in the continuously variable transmission unit 7 is started. That is, the variable speed ratio ⁇ 1 by the continuously variable transmission unit 7 starts to decrease from t 1 .
- the shift is started to reduce its variable speed ratio gamma 1. That is, this shift control is an upshift control in the continuously variable transmission unit 7.
- the actual variable speed ratio gamma 1 rate of change due to the continuously variable transmission unit 7 for the target gear ratio of the continuously variable transmission section 7 (shift speed) is increased.
- variable gear ratio gamma 1 is the maximum speed ratio gamma 1max
- the variable gear ratio gamma 1 is toward the maximum speed ratio gamma 1max to the target gear ratio abruptly Then, it gradually decreases toward the target gear ratio. That is, in this shift control, the variable gear ratio gamma 1 change rate (reduction rate) is greatest immediately after the shift start in the process of change toward the target speed ratio, is configured such that the change rate is gradually reduced ing.
- the gripping sort control of the clutch is started. That is, the hydraulic pressure P C1 of the first clutch mechanism C 1 at the full engagement pressure in a state where the shift control has advanced to some extent, that is, in a state where the rate of decrease of the variable gear ratio ⁇ 1 by the continuously variable transmission 7 is relatively small. Begins to decline.
- the second clutch mechanism C 2 hydraulic P C2 that is released in the hydraulic zero starts to rise.
- the first start slipping clutch mechanism C 1 and the second clutch mechanism C 2 together with the first torque transfer capacity of the clutch mechanism C 1 in response to the oil pressure P C1 starts to decrease from the full engagement pressure starts to decrease the second transfer torque capacity of the clutch mechanism C 2 according to the hydraulic pressure P C2 starts to increase from zero starts to increase.
- the hydraulic pressure P C2 of the second clutch mechanism C 2 increases in the initial control stage while the hydraulic pressure P C1 of the first clutch mechanism C 1 is maintained at the full engagement pressure. You may start.
- the electronic control unit outputs the instruction signal for operating the second clutch mechanism C 2 from the released state to the engaged state, the second set the target torque transfer capacity of the clutch mechanism C 2, the target torque transfer capacity Is configured to output an instruction signal based on.
- the electronic control unit is configured to set the target torque transfer capacity based on the input torque obtained by adding the inertia torque of the second input-side member of the clutch mechanism C 2.
- the target transmission torque capacity torque transfer capacity obtained by correcting the inertia torque component of the second clutch mechanism C 2.
- the electronic control unit the linear solenoid valve for actuating the connected accumulator to the second hydraulic chamber of the clutch mechanism C 2, an instruction signal to the target engagement pressure based on the target transmission torque capacity output Is configured to do.
- the first oil pressure P C1 of the clutch mechanism C 1 is zero, the second clutch mechanism C 2 hydraulic P C2 is controlled to rise to a predetermined fluid pressure.
- the predetermined fluid pressure including for example a hydraulic or the second clutch mechanism C 2 is a predetermined transmitted torque capacity, and accumulation start pressure by an unshown accumulator second clutch mechanism C 2 hydraulic P C2 starts to rise.
- the first clutch mechanism C 1 is released, and since the second torque transfer capacity of the clutch mechanism C 2 is increased to a predetermined value, the inertia phase in the gripping sort control of the clutch is started.
- the engine rotational speed Ne decreases, so the turbine rotational speed Nt that is equal to the input shaft rotational speed Nin is descend. Therefore, when the inertia phase starts, the total speed ratio ⁇ 4 represented by the ratio between the turbine speed N t and the output shaft speed N out starts to decrease. Further, in the continuously variable transmission unit 7, the input shaft rotational speed N in decreases while the variable speed ratio ⁇ 1 is maintained at the maximum speed ratio ⁇ 1max , whereby the secondary pulley rotational speed N p2 decreases.
- variable speed ratio ⁇ 1 When the variable speed ratio ⁇ 1 is decreased in the state where the turbine rotational speed N t is increasing and the total speed ⁇ 4 is constant, the secondary pulley that constitutes the continuously variable transmission unit 7.
- the rotational speed N P2 increases. Accordingly, as shown in FIG. 2, the secondary pulley rotational speed N P2 in a state in which the variable gear ratio gamma 1 continues to decrease from time t 2 to t 4, the variable gear ratio gamma 1 is maximum speed at time t 1 earlier It increases at a greater rate of change than the secondary pulley rotation speed N P2 in the state of specific gamma 1max.
- the variable gear ratio gamma 1 which has been lowered becomes the target speed ratio
- a shift operation in the continuously variable transmission unit 7 is completed.
- the electronic control unit in a state in which the overall speed ratio gamma 4 has decreased, the shift operation in the continuously variable transmission unit 7 is controlled to end. That is, the electronic control unit, before gripping sort control of the clutch is completed, i.e. before the second hydraulic Pc2 of the clutch mechanism C 2 is fully engagement pressure, as the shift operation in the continuously variable transmission unit 7 is completed Control.
- the electronic control unit based on the input signals from a sensor for detecting the groove width to the primary pulley 30, a variable gear ratio gamma 1 is being configured to determine whether it is the target speed ratio Also good. That is, the electronic controller may be configured to variably speed ratio gamma 1 determines whether or not a target speed ratio due to the feedback control.
- the electronic control device executes a synchronization determination process between the secondary pulley rotation speed Np2 and the output shaft rotation speed Nout .
- the electronic control unit changes the second rotational speed of the second clutch mechanism C while monitoring the shift state in the continuously variable transmission unit 7 because the synchronous rotational speed changes with the state of the shift operation in the continuously variable transmission unit 7.
- 2 is configured to perform the synchronization determination process while updating the synchronization determination rotation speed in 2 . For example, since the secondary pulley rotational speed N p2 changes as the variable speed ratio ⁇ 1 changes, the electronic control unit detects the speed change in the continuously variable transmission unit 7 or the change rate of the secondary pulley rotational speed N p2.
- the continuously variable transmission unit 7 is configured to monitor a shift state.
- the electronic control unit may be configured to calculate the synchronization determination rotational speed using the speed change rate or the change rate of the secondary pulley rotational speed Np2 . Then, when the electronic control unit determines that the secondary pulley rotation speed Np2 and the output shaft rotation speed Nout are synchronized, this electronic path switching control process ends.
- the second hydraulic P C2 of the clutch mechanism C 2 will become fully engaged pressure to fully engage the the secondary shaft 44 and the output shaft 8, a secondary pulley rotational speed N p2 and the output shaft rotational speed N out and are synchronously while gripping sort control of the switching control i.e. the clutch of the transmission path is completed.
- the total speed ratio ⁇ 4 when torque is transmitted via the transmission path including the continuously variable transmission portion 7 is the same as the speed ratio ⁇ 3 by the planetary gear mechanism constituting the forward / reverse switching mechanism 5 and the variable speed change.
- the speed ratio obtained by multiplying the ratio gamma 1 the rotation speed and are the same the speed ratio gamma 3 input element speed and the primary pulley 30 of the sun gear 5s of at the planetary gear mechanism is 1, variable speed It becomes ratio ⁇ 1.
- the first clutch mechanism C 1 is released and the second clutch mechanism C 2 is fully engaged, the running state (second running the transmission of torque via the continuously variable transmission unit 7 is stably performed after the state), the third clutch mechanism C 3 is released. That is, the stepped transmission unit 20 is also disconnected from the output shaft 8.
- torque is transmitted from the input shaft 4 to the sun gear 5s in the forward / reverse switching mechanism 5, but the ring gear 5r and the carrier 5c can freely rotate, so the entire forward / reverse switching mechanism 5 is integrated.
- the rotational speed difference between the rotating elements constituting the forward / reverse switching mechanism 5 is reduced. Therefore, it is possible to suppress power loss and durability reduction, or noise or vibration in the forward / reverse switching mechanism 5.
- the third clutch mechanism C 3 is engaged clutches be constituted by, a third clutch mechanism C 3 can be released during running.
- control and operation at time T 1 shown in FIG. 3 is configured similarly to the control and operation at time t 1 shown in FIG. 2 described above with reference to FIG.
- control and operation at times T 2 , T 3 and T 6 shown in FIG. 3 are the same as the control and operation at times t 2 , t 3 and t 6 shown in FIG.
- the change of the variable gear ratio ⁇ 1 is stopped at time T 4 shown in FIG.
- the electronic control unit first to release the clutch mechanism C 1, and the second clutch gripping sort control for engaging the clutch mechanism C 2, when the inertia phase starts, the continuously variable transmission unit 7 Is configured to output an instruction signal for stopping the shifting operation.
- the change of the variable gear ratio ⁇ 1 is stopped when the total gear ratio ⁇ 4 starts to decrease.
- the first clutch mechanism oil pressure P C1 of the C 1 is controlled to zero, control for increasing the second clutch mechanism C 2 hydraulic P C2 to the predetermined fluid pressure It is configured similarly to the control and operation at time t 4 when FIG. 2 described above.
- the electronic control unit is configured to output an instruction signal for resuming the shifting operation by the continuously variable transmission unit 7 that has been stopped during the clutch re-holding control. That is, the electronic control unit outputs the instruction signal from the start to the completion of the clutch re-holding control. For example, when the electronic control unit determines that the difference between the total transmission ratio ⁇ 4 and the maximum transmission ratio ⁇ 1max by the continuously variable transmission unit 7 is equal to or less than a predetermined value set in advance, or the secondary pulley rotational speed N p2 When it is determined that the difference from the output shaft rotational speed Nout is equal to or less than a predetermined value set in advance, the instruction signal is output.
- the electronic control unit a second hydraulic P C2 of the clutch mechanism C 2, when the difference between the full engagement pressure of the second clutch mechanism C 2 is equal to or less than the predetermined value, outputs the instruction signal It may be configured to. Or, if the difference between the transmission torque capacity of the second clutch mechanism C 2, with a predetermined value as the transmission torque capacity when the hydraulic P C2 is fully engaged pressure is equal to or less than the predetermined value, The instruction signal is output. In short, it is only necessary to control so that the shifting operation of the continuously variable transmission unit 7 is resumed before the clutch holding control is completed. It is preferable that the speed change operation is resumed.
- variable gear ratio gamma 1 begins to decrease again. Also, in the original resuming the shift operation in the continuously variable transmission unit 7, the actual variable speed ratio gamma 1 rate of change due to the continuously variable transmission unit 7 for the target gear ratio of the continuously variable transmission section 7 (shift speed) is increased.
- the electronic control unit When the shifting control of the continuously variable transmission unit 7 is resumed, the electronic control unit, when the second clutch mechanism C 2 is completed fully engaged, and the shift speed in the continuously variable transmission unit 7, the speed change by the gripping sort control of the clutch A shift speed synchronization process for matching the speed is executed.
- the electronic control unit is configured to execute a control process for matching the rate of change of the total speed ratio ⁇ 4 and the rate of change of the variable speed ratio ⁇ 1 by the continuously variable transmission unit 7.
- the electronic control unit detects the change state of the groove width of the primary pulley 30 to detect the change rate of the variable speed ratio ⁇ 1 by the continuously variable transmission unit 7, and according to the change rate of the variable speed ratio ⁇ 1.
- an electronic control device when the thrust-imparting mechanism 33 includes an electric actuator, an electronic control device outputs an instruction signal to the thrust-imparting mechanism 33 based on the variable gear ratio gamma 1 rate of change, rate of change of the overall speed ratio gamma 4 it may be configured to control so as to change the second pressure P C2 of the clutch mechanism C 2 to become equal.
- an electronic control device may be configured to output an indication signal to the hydraulic circuit based on the variable gear ratio gamma 1 rate of change.
- the overall speed ratio gamma 4 is variable gear ratio gamma 1, including geared transmission unit 20
- the change rate of the total transmission ratio ⁇ 4 and the change rate of the variable transmission ratio ⁇ 1 are controlled to be equal, a smooth transmission is performed. It can be carried out.
- the stepless control is started before the clutch changeover control is started. Since the shift control in the transmission unit is started, it is possible to prevent a change in the transmission ratio by the continuously variable transmission unit from being delayed with respect to the target transmission ratio. Therefore, the shift response can be improved when the transmission path is switched. In addition, since the clutch change-over time is not increased while reducing the shift shock, the load acting on the friction material in the friction clutch can be suppressed. That is, the durability of the friction clutch can be improved.
- clutch change-over control can be performed in a state where the change in the gear ratio by the continuously variable transmission is relatively small. That is, at the beginning of the shift control in the continuously variable transmission unit, the clutch re-holding control is not started, so the clutch is detected while detecting the change in the rotational speed of the secondary pulley due to the shift of the continuously variable transmission unit. There is no need for a control structure such as having to carry out re-holding control, and complexity can be prevented.
- the speed change operation of the continuously variable transmission unit is controlled to stop, so the change in the rotation speed of the secondary pulley due to the shift of the continuously variable transmission unit Therefore, it is possible to prevent the control from becoming complicated, for example, it is necessary to perform clutch re-holding control while detecting the state of the change in the rotational speed. That is, according to the control device of the present invention, the shift control in the continuously variable transmission unit can be performed while the transmission path re-holding control is being performed with a simple control structure.
- the total speed ratio ⁇ 4 in this case is a speed ratio obtained by multiplying the fixed speed ratio ⁇ 2 by the stepped speed change unit 20 and the speed ratio ⁇ 3 by the planetary gear mechanism constituting the forward / reverse switching mechanism 5.
- the output shaft 8 and the second clutch mechanism C 2 is not released because it is shut off from the continuously variable transmission unit 7, via the continuously variable transmission unit 7 between the input shaft 4 and the output shaft 8 Torque is not transmitted, and a so-called interlock state is not obtained.
- the forward / reverse switching mechanism according to the present invention can be configured by a single pinion type planetary gear mechanism instead of the above-described double pinion type planetary gear mechanism.
- a single pinion type planetary gear mechanism is used as the forward / reverse switching mechanism 5
- a sun gear 5s provided so as to be relatively rotatable with respect to the input shaft 4 is used as an output element, and a carrier 5c is used as a reaction force element.
- the ring gear 5r can be used as an input element. Therefore, the carrier 5c is connected to the brake mechanism B, and the drive gear 21 is connected to the sun gear 5s.
- the first clutch mechanism C 1 is provided for connecting so as to integrally rotate with the sun gear 5s and the ring gear 5r.
- the first clutch mechanism is for integrating the entire forward / reverse switching mechanism for performing the differential action. Therefore, as shown in the above-described specific examples, the two rotating elements of the sun gear and the carrier are used. In addition to the configuration in which the two gears are coupled to each other, the three rotational elements of the sun gear, the carrier, and the ring gear may be coupled.
- the third clutch mechanism in the present invention may be constituted by a key type synchromesh mechanism or a cone type synchromesh mechanism. That is, the third clutch mechanism may be a meshing clutch, and may be constituted by a single cone type synchromesh mechanism or a multi cone type synchromesh mechanism.
- the stepped transmission unit according to the present invention is not limited to a gear mechanism having a single transmission ratio (gear ratio, reduction ratio) as a fixed transmission ratio, and two or more fixed transmission ratios (gear ratio, reduction ratio). And a gear mechanism that can select and set the fixed gear ratio thereof.
- the stepped transmission unit is configured by a gear mechanism capable of transmitting torque from the input shaft to the output shaft.
- the stepped gear ratio cannot be set by the continuously variable transmission unit as the fixed gear ratio. Therefore, the gear mechanism is configured by a combination of gear pairs in which a plurality of gears are engaged. That is, it is only necessary that the gear ratio (ratio of the number of teeth) be greater than the maximum speed ratio that can be set by the continuously variable transmission.
- Secondary pulley 41 ... Fixed sheave, 42 ... Movable sheave, 43 ... Thrust applying mechanism, 44 ... secondary shaft, B ... brake mechanism, C 1 ... first clutch mechanism (friction clutch , C 2 ... second clutch mechanism (friction clutch), C 3 ... third clutch mechanism (dog clutch).
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Abstract
Description
Claims (16)
- 動力源が出力したトルクが入力される入力軸とトルクを出力する出力軸との間に、変速比を連続的に変化させる無段変速部と、前記無段変速部で設定できない変速比を設定できる有段変速部とが並列に設けられ、前記有段変速部を含む伝達経路を経由してトルクを伝達する走行状態では係合し、かつ前記無段変速部を含む伝達経路を経由してトルクを伝達する走行状態では解放する第1摩擦クラッチと、前記無段変速部を含む伝達経路を経由してトルクを伝達する走行状態では係合し、かつ前記有段変速部を含む伝達経路を経由してトルクを伝達する走行状態では解放する第2摩擦クラッチとを備えた車両の制御装置おいて、
前記有段変速部を含む伝達経路から前記無段変速部を含む伝達経路にトルクを伝達する経路を切り替える際、前記摩擦クラッチによる掴み替え動作を開始させる前に、前記無段変速部における変速動作を開始させるように構成されていることを特徴とする車両の制御装置。 - 前記伝達経路を切り替える際、前記第1摩擦クラッチを解放させ始める前、あるいは前記第2摩擦クラッチを係合させ始める前に、前記無段変速部における変速動作を開始させるように構成されていることを特徴とする請求項1に記載の車両の制御装置。
- 前記摩擦クラッチによる掴み替え動作は、前記無段変速部による変速比が変化している最中に前記摩擦クラッチによる掴み替え動作がおこなわれるように構成されていることを特徴とする請求項1または2に記載の車両の制御装置。
- 前記摩擦クラッチによる掴み替え動作により発生するイナーシャ相が開始する際に、前記無段変速部の変速動作を停止させるように構成されていることを特徴とする請求項1から3のいずれかに記載の車両の制御装置。
- 前記摩擦クラッチによる掴み替え動作が完了する前に、前記無段変速部の変速動作を再開させるように構成されていることを特徴とする請求項4に記載の車両の制御装置。
- 前記第2摩擦クラッチにおける伝達トルク容量が所定値以上であると判断した場合に、前記無段変速部における変速動作を再開させるように構成されていることを特徴とする請求項5に記載の車両の制御装置。
- 前記無段変速部は、一対のプーリを含み、
前記出力軸の回転数と前記無段変速部における従動側プーリの回転数との差が所定値以内であると判断した場合に、前記無段変速部における変速動作を再開させるように構成されていることを特徴とする請求項5に記載の車両の制御装置。 - 前記第1摩擦クラッチおよび前記第2摩擦クラッチは、それぞれに油圧アクチュエータを備え、
前記第2摩擦クラッチの油圧が所定値以上になったと判断した場合に、前記無段変速部における変速動作を再開させるように構成されていることを特徴とする請求項5に記載の車両の制御装置。 - 動力源が出力したトルクが入力される入力軸とトルクを出力する出力軸との間に、変速比を連続的に変化させる無段変速部と、前記無段変速部で設定できない変速比を設定できる有段変速部とが並列に設けられ、前記有段変速部を含む伝達経路を経由してトルクを伝達する走行状態では係合し、かつ前記無段変速部を含む伝達経路を経由してトルクを伝達する走行状態では解放する第1摩擦クラッチと、前記無段変速部を含む伝達経路を経由してトルクを伝達する走行状態では係合し、かつ前記有段変速部を含む伝達経路を経由してトルクを伝達する走行状態では解放する第2摩擦クラッチとを備えた車両の制御方法おいて、
前記有段変速部を含む伝達経路から前記無段変速部を含む伝達経路にトルクを伝達する経路を切り替える際、、前記無段変速部における変速動作を開始させ、その後に前記摩擦クラッチによる掴み替え動作を開始させることを特徴とする車両の制御方法。 - 前記伝達経路を切り替える際、前記第1摩擦クラッチを解放させ始める前、あるいは前記第2摩擦クラッチを係合させ始める前に、前記無段変速部における変速動作を開始させることを特徴とする請求項9に記載の車両の制御方法。
- 前記摩擦クラッチによる掴み替え動作は、前記無段変速部による変速比が変化している最中に前記摩擦クラッチによる掴み替え動作がおこなわれることを特徴とする請求項9または10に記載の車両の制御方法。
- 前記摩擦クラッチによる掴み替え動作により発生するイナーシャ相が開始する際に、前記無段変速部の変速動作を停止させることを特徴とする請求項9から11のいずれかに記載の車両の制御方法。
- 前記摩擦クラッチによる掴み替え動作が完了する前に、前記無段変速部の変速動作を再開させることを特徴とする請求項12に記載の車両の制御方法。
- 前記第2摩擦クラッチにおける伝達トルク容量が所定値以上であると判断した場合に、前記無段変速部における変速動作を再開させることを特徴とする請求項13に記載の車両の制御方法。
- 前記無段変速部は、一対のプーリを含み、
前記出力軸の回転数と前記無段変速部における従動側プーリの回転数との差が所定値以内であると判断した場合に、前記無段変速部における変速動作を再開させることを特徴とする請求項13に記載の車両の制御方法。 - 前記第1摩擦クラッチおよび前記第2摩擦クラッチは、それぞれに油圧アクチュエータを備え、前記第2摩擦クラッチの油圧が所定値以上になったと判断した場合に、前記無段変速部における変速動作を再開させることを特徴とする請求項13に記載の車両の制御方法。
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CN201380075721.2A CN105121917B (zh) | 2013-04-16 | 2013-04-16 | 车辆的控制装置以及方法 |
US14/785,260 US9540012B2 (en) | 2013-04-16 | 2013-04-16 | Vehicle control system and vehicle control method |
JP2015512224A JP6015852B2 (ja) | 2013-04-16 | 2013-04-16 | 車両の制御装置および方法 |
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US10683933B2 (en) | 2017-11-24 | 2020-06-16 | Toyota Jidosha Kabushiki Kaisha | Control apparatus for vehicle drive-force transmitting apparatus |
US10753463B2 (en) | 2017-12-27 | 2020-08-25 | Toyota Jidosha Kabushiki Kaisha | Control apparatus for vehicle drive-force transmitting apparatus |
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KR20160035328A (ko) * | 2014-09-23 | 2016-03-31 | 현대자동차주식회사 | 차량용 무단 변속기 |
US9551131B2 (en) * | 2014-12-10 | 2017-01-24 | Caterpillar Inc. | Power system having clutch-based fuel control modes |
CN108138927B (zh) * | 2015-10-30 | 2020-10-23 | 爱信艾达株式会社 | 自动变速器 |
JP7120035B2 (ja) * | 2019-01-15 | 2022-08-17 | トヨタ自動車株式会社 | 車両の変速制御装置 |
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JP2748511B2 (ja) | 1989-03-08 | 1998-05-06 | 日産自動車株式会社 | 変速機の制御装置 |
JP2847780B2 (ja) * | 1989-07-27 | 1999-01-20 | 日産自動車株式会社 | 変速機の制御装置 |
JPH03234960A (ja) * | 1990-02-13 | 1991-10-18 | Nissan Motor Co Ltd | 複合変速機の制御装置 |
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JP2001330140A (ja) * | 2000-05-22 | 2001-11-30 | Toyota Motor Corp | 車両用クラッチの制御装置 |
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JPH0356762A (ja) * | 1989-07-24 | 1991-03-12 | Nissan Motor Co Ltd | 無段変速機 |
JP2002266979A (ja) * | 2001-03-08 | 2002-09-18 | Toyota Motor Corp | 無段変速機およびその変速制御装置 |
JP2010138961A (ja) * | 2008-12-10 | 2010-06-24 | Jatco Ltd | 複数の伝達経路を有する変速機及びその制御方法 |
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US10683933B2 (en) | 2017-11-24 | 2020-06-16 | Toyota Jidosha Kabushiki Kaisha | Control apparatus for vehicle drive-force transmitting apparatus |
US10753463B2 (en) | 2017-12-27 | 2020-08-25 | Toyota Jidosha Kabushiki Kaisha | Control apparatus for vehicle drive-force transmitting apparatus |
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CN105121917A (zh) | 2015-12-02 |
US20160121896A1 (en) | 2016-05-05 |
JPWO2014170960A1 (ja) | 2017-02-16 |
CN105121917B (zh) | 2017-06-09 |
JP6015852B2 (ja) | 2016-10-26 |
US9540012B2 (en) | 2017-01-10 |
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