US20100075799A1 - Continuously variable transmission and control method thereof - Google Patents

Continuously variable transmission and control method thereof Download PDF

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Publication number
US20100075799A1
US20100075799A1 US12/558,139 US55813909A US2010075799A1 US 20100075799 A1 US20100075799 A1 US 20100075799A1 US 55813909 A US55813909 A US 55813909A US 2010075799 A1 US2010075799 A1 US 2010075799A1
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Prior art keywords
speed ratio
gear position
variator
subtransmission mechanism
speed
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Abandoned
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US12/558,139
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English (en)
Inventor
Hideaki Suzuki
Ryousuke Nonomura
Hiroyasu Tanaka
Takuichiro Inoue
Mamiko Inoue
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JATCO Ltd
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JATCO Ltd
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Assigned to JATCO LTD reassignment JATCO LTD ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: INOUE, MAMIKO, INOUE, TAKUICHIRO, NONOMURA, RYOUSUKE, SUZUKI, HIDEAKI, TANAKA, HIROYASU
Publication of US20100075799A1 publication Critical patent/US20100075799A1/en
Priority to US14/078,218 priority Critical patent/US8944956B2/en
Assigned to NISSAN MOTOR CO., LTD., JATCO LTD reassignment NISSAN MOTOR CO., LTD. ASSIGNOR ASSIGNS 50% INTEREST Assignors: JATCO LTD
Abandoned legal-status Critical Current

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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F16H61/0437—Smoothing ratio shift by using electrical signals
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F16H61/08—Timing control
    • 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
    • F16H61/10—Controlling shift hysteresis
    • 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
    • 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
    • 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
    • F16H2037/023—CVT's provided with at least two forward and one reverse ratio in a serial arranged sub-transmission
    • 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
    • F16H2037/025—CVT's in which the ratio coverage is used more than once to produce the overall transmission ratio coverage, e.g. by shift to end of range, then change ratio in sub-transmission and shift CVT through range once again
    • 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
    • F16H2061/6604—Special control features generally applicable to continuously variable gearings
    • F16H2061/6614—Control of ratio during dual or multiple pass shifting for enlarged ration coverage

Definitions

  • This invention relates to a continuously variable transmission having a continuously variable transmission mechanism and a subtransmission mechanism.
  • a belt type continuously variable transmission (to be referred to as a “CVT” hereafter) comprises a pair of pulleys having a variable groove width and a belt wrapped around the pulleys, and is capable of varying a speed ratio continuously by modifying the respective groove widths of the pulleys.
  • CVT continuously variable transmission
  • an engine can be used in a more efficient operating condition than in a vehicle having a conventional stepped transmission, and therefore improvements in a power performance and a fuel consumption performance of the vehicle can be expected.
  • a speed ratio range (to be referred to as a “ratio range” hereafter) of the CVT is preferably enlarged.
  • ratio range By enlarging the ratio range of the CVT, speed ratios on a large speed ratio side can be used during startup and acceleration, thereby further improving the power performance of the vehicle, and speed ratios on a small speed ratio side can be used during high-speed travel, thereby further improving the fuel consumption performance of the vehicle.
  • a pulley diameter may be increased, but with this method, the CVT increases in size and weight, which is undesirable.
  • JP60-37455A and JP61-241561A a two-forward speed subtransmission mechanism is provided in series with the CVT to the front or rear thereof, and by changing a gear position of the subtransmission mechanism in accordance with the operating conditions of the vehicle, a wide ratio range is realized without increasing the size of the CVT.
  • the gear position of the subtransmission mechanism is changed on the basis of a vehicle speed and a throttle opening in accordance with a predetermined shift pattern. Further, in JP61-241561A, the gear position of the subtransmission mechanism is changed when a condition for alleviating shift shock in the subtransmission mechanism is established.
  • An object of this invention is to suppress shift shock in a subtransmission mechanism while maintaining favorable power performance and fuel consumption performance.
  • a continuously variable transmission installed in a vehicle comprises a continuously variable transmission mechanism (to be referred to hereafter as a “variator”) which modifies a speed ratio continuously, a subtransmission mechanism provided to the rear of and in series with the variator and including, as forward gear positions, a first gear position and a second gear position having a smaller speed ratio than the first gear position; and a shift control unit which modifies a through speed ratio, which is an overall speed ratio of the variator and the subtransmission mechanism, by modifying the speed ratio of the variator and changing the gear position of the subtransmission mechanism on a basis of an operating condition of the vehicle.
  • a continuously variable transmission mechanism to be referred to hereafter as a “variator”
  • a subtransmission mechanism provided to the rear of and in series with the variator and including, as forward gear positions, a first gear position and a second gear position having a smaller speed ratio than the first gear position
  • a shift control unit which modifies a through speed ratio, which is an overall speed ratio of the variator and
  • the through speed ratio when the speed ratio of the variator is a Highest speed ratio and the gear position of the subtransmission mechanism is the first gear position is set as a mode switch speed ratio.
  • the shift control unit changes the gear position of the subtransmission mechanism from the first gear position to the second gear position.
  • a control method for a continuously variable transmission installed in a vehicle and including a continuously variable transmission mechanism (to be referred to hereafter as a “variator”) which modifies a speed ratio continuously and a subtransmission mechanism provided to the rear of and in series with the variator and including, as forward gear positions, a first gear position and a second gear position having a smaller speed ratio than the first gear position is provided.
  • the control method comprises a shift control step for modifying a through speed ratio, which is an overall speed ratio of the variator and the subtransmission mechanism, by modifying the speed ratio of the variator and changing the gear position of the subtransmission mechanism on a basis of an operating condition of the vehicle.
  • the through speed ratio when the speed ratio of the variator is a Highest speed ratio and the gear position of the subtransmission mechanism is the first gear position is set as a mode switch speed ratio.
  • the shift control step changes the gear position of the subtransmission mechanism from the first gear position to the second gear position.
  • the gear position of the subtransmission mechanism is changed from the first gear position to the second gear position when the speed ratio of the variator is the Highest speed ratio.
  • the speed ratio of the variator is the Highest speed ratio
  • torque input into the subtransmission mechanism via the variator is at a minimum under the torque that is input into the variator at the time, and therefore shift shock in the subtransmission mechanism can be suppressed effectively.
  • FIG. 1 is a schematic constitutional diagram of a vehicle installed with a continuously variable transmission according to an embodiment of this invention.
  • FIG. 2 is a view showing the interior constitution of a transmission controller.
  • FIG. 3 is a view showing an example of a relationship between a speed ratio of a variator and an input torque input into a subtransmission mechanism.
  • FIG. 4 is a view showing an example of a shift map of the transmission.
  • FIG. 5 is a flowchart showing the content of a shift control program executed by the transmission controller.
  • FIG. 6 is a view showing the manner in which an operating point of the transmission moves during vehicle acceleration.
  • FIG. 7 is a timing chart showing the manner in which various parameters of the transmission vary during vehicle acceleration.
  • a “speed ratio” of a certain transmission mechanism is a value obtained by dividing an input rotation speed of the transmission mechanism by an output rotation speed of the transmission mechanism. Further, a “Lowest speed ratio” denotes a maximum speed ratio of the transmission mechanism, and a “Highest speed ratio” denotes a minimum speed ratio of the transmission mechanism.
  • FIG. 1 is a schematic constitutional diagram of a vehicle installed with a continuously variable transmission according to an embodiment of this invention.
  • the vehicle has an engine 1 as a power source. Output rotation of the engine 1 is transmitted to a drive wheel 7 via a torque converter having a lockup clutch 2 , a first gear train 3 , a continuously variable transmission (to be referred to simply as a “transmission 4 ” hereafter), a second gear train 5 , and a final reduction gear 6 .
  • the second gear train 5 is provided with a parking mechanism 8 which locks an output shaft of the transmission 4 mechanically so that the output shaft is incapable of rotation during parking.
  • the vehicle is further provided with an oil pump 10 which is driven using a part of the power of the engine 1 , a hydraulic control circuit 1 1 which regulates an oil pressure from the oil pump 10 and supplies the regulated oil pressure to various sites of the transmission 4 , and a transmission controller 12 which controls the hydraulic control circuit 11 .
  • the transmission 4 includes a belt type continuously variable transmission mechanism (to be referred to as a “variator 20 ” hereafter), and a subtransmission mechanism 30 provided to the rear of and in series with the variator 20 .
  • the term “provided to the rear of” means that the subtransmission mechanism 30 is provided further toward the drive wheel 7 side than the variator 20 on a power transmission path extending from the engine 1 to the drive wheel 7 .
  • the term “provided in series” means that the variator 20 and the subtransmission mechanism 30 are provided in series on this power transmission path.
  • the subtransmission mechanism 30 may be directly connected to an output shaft of the variator 20 , as in this example, or via another transmission mechanism or power transmission mechanism (for example, a gear train).
  • the variator 20 includes a primary pulley 21 , a secondary pulley 22 , and a V belt 23 wrapped around the pulleys 21 , 22 .
  • the pulleys 21 , 22 respectively include a fixed conical plate, a movable conical plate that is disposed relative to the fixed conical plate such that respective sheave surfaces thereof oppose each other and forms a V groove with the fixed conical plate, and a hydraulic cylinder 23 a , 23 b that is provided on a back surface of the movable conical plate and displaces the movable conical plate in an axial direction.
  • the subtransmission mechanism 30 is a two-forward speed, one-reverse speed transmission mechanism.
  • the subtransmission mechanism 30 includes a Ravigneaux planetary gear mechanism 31 coupling the carriers of two planetary gears, and a plurality of frictional engagement elements (a Low brake 32 , a High clutch 33 , and a Rev brake 34 ) connected to a plurality of rotary elements constituting the Ravigneaux planetary gear mechanism 31 to modify the rotation states thereof.
  • the gear position of the subtransmission mechanism 30 is changed by adjusting the oil pressure supplied to the respective frictional engagement elements 32 to 34 such that the engagement/disengagement states of the respective frictional engagement elements 32 to 34 are modified.
  • the gear position of the subtransmission mechanism 30 is set in a first speed.
  • the gear position of the subtransmission mechanism 30 is set in a second speed having a smaller speed ratio than the first speed.
  • the gear position of the subtransmission mechanism 30 is set in reverse.
  • the transmission controller 12 is constituted by a CPU 121 , a storage device 122 including a RAM and a ROM, an input interface 123 , an output interface 124 , and a bus 125 connecting these components to each other.
  • the storage device 122 stores a shift control program for the transmission 4 and a shift map ( FIG. 4 ) used by the shift control program.
  • the CPU 121 reads and executes the shift control program stored in the storage device 122 , generates a shift control signal by implementing various types of calculation processing on the various signals input via the input interface 123 , and outputs the generated shift control signal to the hydraulic control circuit 11 via the output interface 124 .
  • Various values used in the calculation processing executed by the CPU 121 and calculation results thereof are stored in the storage device 122 as appropriate.
  • the hydraulic control circuit 11 is constituted by a plurality of flow passages and a plurality of hydraulic control valves.
  • the hydraulic control circuit 11 controls the plurality of hydraulic control valves on the basis of the shift control signal from the transmission controller 12 to switch an oil pressure supply path, and prepares a required oil pressure from the oil pressure generated by the oil pump 10 , which is then supplied to various sites of the transmission 4 .
  • the speed ratio vRatio of the variator 20 is modified and the gear position of the subtransmission mechanism 30 is changed, whereby a shift is performed in the transmission 4 .
  • FIG. 3 is a table showing an example of a relationship between the speed ratio vRatio of the variator 20 and input torque input into the subtransmission mechanism 30 when the speed ratio vRatio of the variator 20 is varied, on the condition that an input torque input into the variator 20 is constant.
  • the input torque input into the subtransmission mechanism 30 decreases as the speed ratio vRatio of the variator 20 shifts further to the small speed ratio side, and reaches a minimum when the speed ratio vRatio of the variator 20 corresponds to the Highest speed ratio. This means that by changing the gear position of the subtransmission mechanism 30 when the speed ratio vRatio of the variator 20 is the Highest speed ratio, shift shock in the subtransmission mechanism 30 is suppressed.
  • the transmission controller 12 shifts the gear position of the subtransmission mechanism 30 from the first speed to the second speed when the speed ratio of the variator 20 is the Highest speed ratio.
  • the specific content of this shift control will be described below.
  • FIG. 4 shows an example of the shift map stored in the storage device 122 of the transmission controller 12 .
  • an operating point of the transmission 4 is determined on the basis of the vehicle speed VSP and the primary rotation speed Npri.
  • An incline of a line linking the operating point of the transmission 4 and a zero point in the lower left corner of the shift map indicates the speed ratio of the transmission 4 (an overall speed ratio obtained by multiplying the speed ratio of the subtransmission mechanism 30 with the speed ratio vRatio of the variator 20 , to be referred to hereafter as a “through speed ratio Ratio”).
  • a shift line is set at each throttle opening TVO, and a shift is performed in the transmission 4 according to a shift line selected in accordance with the throttle opening TVO.
  • the transmission 4 When the transmission 4 is in the low speed mode, the transmission 4 can be shifted between a low speed mode Lowest line, which is obtained by maximizing the speed ratio vRatio of the variator 20 , and a low speed mode Highest line, which is obtained by minimizing the speed ratio vRatio of the variator 20 .
  • the low speed mode the operating point of the transmission 4 moves within an A region and a B region.
  • the transmission 4 can be shifted between a high speed mode Lowest line, which is obtained by maximizing the speed ratio vRatio of the variator 20 , and a high speed mode Highest line, which is obtained by minimizing the speed ratio vRatio of the variator 20 .
  • the high speed mode the operating point of the transmission 4 moves within the B region and a C region.
  • the speed ratios of the respective gear positions of the subtransmission mechanism 30 are set such that a speed ratio corresponding to the low speed mode Highest line (low speed mode Highest speed ratio) is smaller than a speed ratio corresponding to the high speed mode Lowest line (high speed mode Lowest speed ratio).
  • a low speed mode ratio range which is the through speed ratio Ratio range of the transmission 4 in the low speed mode
  • a high speed mode ratio range which is the through speed ratio Ratio range of the transmission 4 in the high speed mode
  • a mode switch line on which a shift is performed in the subtransmission mechanism 30 (a 1-2 shift line of the subtransmission mechanism 30 ) is set to overlap the low speed mode Highest line.
  • a through speed ratio corresponding to the mode switch line (to be referred to hereafter as a “mode switch speed ratio mRatio”) is set at an equal value to the low speed mode Highest speed ratio.
  • the transmission controller 12 performs mode switch control. In the mode switch control, the transmission controller 12 performs a shift in the subtransmission mechanism 30 and modifies the speed ratio vRatio of the variator 20 in an opposite direction to the variation direction of the speed ratio of the subtransmission mechanism 30 .
  • the transmission controller 12 changes the gear position of the subtransmission mechanism 30 from the first speed to the second speed (subtransmission mechanism 1-2 shift) and modifies the speed ratio vRatio of the variator 20 to the large speed ratio side.
  • the transmission controller 12 changes the gear position of the subtransmission mechanism 30 from the second speed to the first speed (subtransmission mechanism 2-1 shift) and modifies the speed ratio vRatio of the variator 20 to the small speed ratio side.
  • the speed ratio vRatio of the variator 20 is varied in an opposite direction to the speed ratio variation of the subtransmission mechanism 30 in order to suppress an unpleasant feeling experienced by a driver due to input rotation variation generated by a sudden change in the through speed ratio Ratio of the transmission 4 .
  • FIG. 5 shows an example of the shift control program stored in the storage device 122 of the transmission controller 12 .
  • the specific content of the shift control executed by the transmission controller 12 will now be described with reference to FIG. 5 .
  • a step S 1 the transmission controller 12 reads the primary rotation speed Npri, vehicle speed VSP, and throttle opening TVO.
  • a step S 2 the transmission controller 12 calculates the through speed ratio Ratio (current value) of the transmission 4 on the basis of the primary rotation speed Npri, the vehicle speed VSP, and a reduction ratio fRatio of the final reduction gear 6 .
  • the transmission controller 12 refers to the shift map ( FIG. 4 ) stored in the storage device 122 on the basis of the primary rotation speed Npri and vehicle speed VSP to calculate a target through speed ratio DRatio (target value), or in other words the speed ratio to be attained by the transmission 4 next, on the basis of the current primary rotation speed Npri, vehicle speed VSP, and throttle opening TVO.
  • target value target value
  • the transmission controller 12 determines whether or not the through speed ratio Ratio has crossed the mode switch speed ratio mRatio. This determination is made by comparing the through speed ratio Ratio and a previous value thereof (a value calculated in the step S 2 during the previous execution of the processing shown in FIG. 5 ) with the mode switch speed ratio mRatio.
  • the processing advances from the step S 4 to a step S 6 , and when the through speed ratio Ratio has crossed the mode switch speed ratio mRatio from the small speed ratio side to the large speed ratio side, the processing advances from the step S 5 to a step S 9 . Further, when the through speed ratio Ratio has not crossed the mode switch speed ratio mRatio, the processing advances from the step S 5 to a step S 12 .
  • the transmission controller 12 changes the gear position of the subtransmission mechanism 30 from the first speed to the second speed and modifies the speed ratio vRatio of the variator 20 to the large speed ratio side (subtransmission mechanism 1-2 shift and variator return shift).
  • the transmission controller 12 calculates a target variator speed ratio vDRatio (target value), or in other words the speed ratio to be attained by the variator 20 following completion of the mode switch, on the basis of the target through speed ratio DRatio calculated in the step S 3 and the second-speed speed ratio (post-shift speed ratio) of the subtransmission mechanism 30 .
  • target value the target variator speed ratio
  • second-speed speed ratio post-shift speed ratio
  • the transmission controller 12 sets shift characteristics (shift speed, increase/decrease tendency of shift speed, and so on) of the variator 20 during the mode switch on the basis of a target shift time t 12 for a gear position shift in the subtransmission mechanism 30 from the first speed to the second speed and a deviation between the speed ratio vRatio (current value) and the target variator speed ratio vDRatio of the variator 20 such that when the shift in the subtransmission mechanism 30 is complete, the speed ratio vRatio of the variator 20 corresponds to the target variator speed ratio vDRatio.
  • the target shift time t 12 of the subtransmission mechanism 30 may take a fixed value or may be modified in accordance with the vehicle speed VSP, an engine torque, and an input torque input into the subtransmission mechanism 30 .
  • the speed ratio vRatio of the variator 20 is calculated on the basis of the through speed ratio Ratio calculated in the step S 1 and the speed ratio of the current gear position (first speed) of the subtransmission mechanism 30 .
  • the transmission controller 12 begins the 1-2 shift in the subtransmission mechanism 30 and the return shift in the variator 20 .
  • the gear position of the subtransmission mechanism 30 is changed from the first speed to the second speed and the speed ratio vRatio of the variator 20 is modified to the large speed ratio side.
  • the shift in the variator 20 is completed at substantially the same time as the shift in the subtransmission mechanism 30 .
  • the transmission controller 12 changes the gear position of the subtransmission mechanism 30 from the second speed to the first speed and modifies the speed ratio vRatio of the variator 20 to the small speed ratio side (subtransmission mechanism 2-1 shift and variator return shift).
  • the transmission controller 12 calculates the target variator speed ratio vDRatio (target value), or in other words the speed ratio to be attained by the variator 20 following completion of the mode switch, on the basis of the target through speed ratio DRatio calculated in the step S 3 and the first-speed speed ratio (post-shift speed ratio) of the subtransmission mechanism 30 .
  • the transmission controller 12 sets the shift characteristics (shift speed, increase/decrease tendency of shift speed, and so on) of the variator 20 during the mode switch on the basis of a target shift time t 21 for a gear position shift in the subtransmission mechanism 30 from the second speed to the first speed and the deviation between the speed ratio vRatio (current value) and the target variator speed ratio vDRatio of the variator 20 such that when the shift in the subtransmission mechanism 30 is complete, the speed ratio vRatio of the variator 20 corresponds to the target variator speed ratio vDRatio.
  • the target shift time t 21 of the subtransmission mechanism 30 may take a fixed value or may be modified in accordance with the vehicle speed VSP, the engine torque, and the input torque input into the subtransmission mechanism 30 .
  • the speed ratio vRatio of the variator 20 is calculated on the basis of the through speed ratio Ratio calculated in the step S 1 and the speed ratio of the current gear position (second speed) of the subtransmission mechanism 30 .
  • the transmission controller 12 begins the 2-1 shift in the subtransmission mechanism 30 and the return shift in the variator 20 .
  • the gear position of the subtransmission mechanism 30 is changed from the second speed to the first speed and the speed ratio vRatio of the variator 20 is modified to the small speed ratio side.
  • the shift in the variator 20 is completed at substantially the same time as the shift in the subtransmission mechanism 30 .
  • steps S 12 to S 13 the transmission controller 12 performs a shift (normal shift) in the variator 20 alone without changing the gear position of the subtransmission mechanism 30 .
  • the transmission controller 12 calculates the target variator speed ratio vDRatio (target value) on the basis of the target through speed ratio DRatio calculated in the step S 3 and the speed ratio of the current gear position of the subtransmission mechanism 30 .
  • the transmission controller 12 performs a shift in the variator 20 such that the speed ratio vRatio of the variator 20 (current value) varies to the target variator speed ratio vDRatio with a desired shift characteristic (for example, a first order lag response).
  • a desired shift characteristic for example, a first order lag response
  • FIG. 7 is a timing chart showing the manner in which the through speed ratio Ratio, the subtransmission mechanism speed ratio, the speed ratio vRatio of the variator 20 , the primary rotation speed Npri, and the vehicle speed VSP vary during this acceleration.
  • the vehicle begins to accelerate.
  • the transmission 4 is in the low speed mode
  • the speed ratio vRatio of the variator 20 is the Lowest speed ratio
  • the gear position of the subtransmission mechanism 30 is the first speed.
  • the operating point of the transmission 4 moves along the shift lines set in advance on the shift map for each throttle opening TVO.
  • the throttle opening TVO is set at 4/8, and therefore the operating point of the transmission 4 moves along the partial line, as shown by the thick arrow in FIG. 6 .
  • mode switch control for switching the mode of the transmission 4 from the low speed mode to the high speed mode is begun.
  • the mode switch control is performed from the time t 2 to a time t 3 .
  • the gear position of the subtransmission mechanism 30 is changed from the first speed to the second speed and the speed ratio vRatio of the variator 20 is modified to the large speed ratio side.
  • the mode switch control is completed and the gear position of the subtransmission mechanism 30 reaches the second speed. Subsequent shifts in the transmission 4 are performed by modifying the speed ratio vRatio of the variator 20 to the small speed ratio side.
  • the speed ratio vRatio of the variator 20 Focusing on the speed ratio vRatio of the variator 20 , at the time t 2 , the speed ratio vRatio of the variator 20 is the Highest speed ratio, and the torque input into the subtransmission mechanism 30 via the variator 20 is at a minimum under the torque input into the variator 20 at the time. In this embodiment, change of the gear position of the subtransmission mechanism 30 from the first speed to the second speed begins in this state, and therefore shift shock during a subtransmission mechanism 1-2 shift can be suppressed effectively.
  • the gear position of the subtransmission mechanism 30 is changed when the through speed ratio varies across the mode switch speed ratio mRatio, and therefore change of the gear position of the subtransmission mechanism 30 is not limited excessively. As a result, the favorable operating performance and fuel consumption performance that are obtained by providing the subtransmission mechanism 30 can be enjoyed.
  • the speed ratio vRatio of the variator 20 is modified in the opposite direction to the variation direction of the speed ratio of the subtransmission mechanism 30 during the mode switch (time t 2 to t 3 ), and it is therefore possible to suppress not only shift shock in the subtransmission mechanism 30 , but also an unpleasant feeling experienced by the driver due to input rotation variation generated by a sudden change in the through speed ratio Ratio.
  • the subtransmission mechanism 30 is a transmission mechanism having two positions, i.e. the first speed and the second speed, as forward gear positions, but the subtransmission mechanism 30 may have three or more positions as forward gear positions.
  • similar actions and effects to those of the above embodiment can be achieved by applying the invention to control for changing the gear position of the subtransmission mechanism between the first speed and second speed and control for changing the gear position between the second speed and third speed.
  • the variator 20 may use a chain instead of a V belt 23 .
  • the variator 20 may be other types of continuously transmission, for example, toroidal type continuously transmission.
  • the subtransmission mechanism 30 uses a Ravigneaux planetary gear mechanism, but the invention is not limited to this constitution.
  • the subtransmission mechanism 30 may be formed from a combination of a normal planetary gear mechanism and frictional engagement elements or from a plurality of power transmission paths constituted by a plurality of gear trains having different gear ratios and frictional engagement elements for switching the power transmission paths.
  • hydraulic cylinders 23 a , 23 b are provided as actuators for displacing the movable conical plates of the pulleys 21 , 22 in the axial direction, but the actuator is not limited to a hydraulically driven actuator, and may be driven electrically.
  • the mode switch speed ratio is set at an equal value to the low speed mode Highest speed ratio, but here, the term “equal to” includes a case in which the mode switch speed ratio is substantially equal to the low speed mode Highest speed ratio, and such a case is included in the technical scope of the invention.
US12/558,139 2008-09-25 2009-09-11 Continuously variable transmission and control method thereof Abandoned US20100075799A1 (en)

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US8142330B2 (en) * 2008-09-25 2012-03-27 Jatco Ltd Continuously variable transmission and control method thereof
US8944956B2 (en) 2008-09-25 2015-02-03 Jatco Ltd Continuously variable transmission and control method thereof
US20100075800A1 (en) * 2008-09-25 2010-03-25 Jatco Ltd Continuously variable transmission and control method thereof
US20140342876A1 (en) * 2011-12-12 2014-11-20 Jatco Ltd Continuously variable transmission and method of controlling the same
EP2792913A4 (en) * 2011-12-12 2016-06-01 Jatco Ltd CONTINUOUS GEARBOX AND METHOD FOR ITS CONTROL
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US10107394B2 (en) * 2013-10-08 2018-10-23 Jatco Ltd Control device for continuously variable transmission equipped with auxiliary transmission
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CN112594375A (zh) * 2020-12-18 2021-04-02 陕西法士特齿轮有限责任公司 一种用于拖拉机的机械液压无级变速器的速比变化率控制方法

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JP4660584B2 (ja) 2011-03-30
KR20130141405A (ko) 2013-12-26
CN101684856A (zh) 2010-03-31
KR20150122608A (ko) 2015-11-02
DE602009000567D1 (de) 2011-02-24
CN103557320B (zh) 2016-02-24
US8944956B2 (en) 2015-02-03
CN103498895B (zh) 2016-10-05
CN103498895A (zh) 2014-01-08
JP2010078029A (ja) 2010-04-08
KR20100035116A (ko) 2010-04-02
EP2169278A1 (en) 2010-03-31
US20140073469A1 (en) 2014-03-13
ATE495396T1 (de) 2011-01-15
CN103557320A (zh) 2014-02-05

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Effective date: 20131224

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION