WO1997005410A1 - Ratio selector mechanisms - Google Patents

Ratio selector mechanisms Download PDF

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Publication number
WO1997005410A1
WO1997005410A1 PCT/GB1996/001732 GB9601732W WO9705410A1 WO 1997005410 A1 WO1997005410 A1 WO 1997005410A1 GB 9601732 W GB9601732 W GB 9601732W WO 9705410 A1 WO9705410 A1 WO 9705410A1
Authority
WO
WIPO (PCT)
Prior art keywords
ratio
actuator
valve
pressure
mechanism according
Prior art date
Application number
PCT/GB1996/001732
Other languages
French (fr)
Inventor
John Spooner
Mark Stanley Willows
David Anthony Harries
Original Assignee
Ap Kongsberg Holdings Limited
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from GBGB9515333.4A external-priority patent/GB9515333D0/en
Priority claimed from GBGB9602734.7A external-priority patent/GB9602734D0/en
Application filed by Ap Kongsberg Holdings Limited filed Critical Ap Kongsberg Holdings Limited
Priority to US08/809,997 priority Critical patent/US5836207A/en
Priority to EP96924999A priority patent/EP0782675B1/en
Priority to JP9507313A priority patent/JPH10507256A/en
Priority to GB9705270A priority patent/GB2308413B/en
Priority to DE69616259T priority patent/DE69616259T2/en
Publication of WO1997005410A1 publication Critical patent/WO1997005410A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control 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
    • F16H61/26Generation or transmission of movements for final actuating mechanisms
    • F16H61/28Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control 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
    • F16H61/04Smoothing ratio shift
    • F16H61/0403Synchronisation before shifting
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control 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
    • F16H61/26Generation or transmission of movements for final actuating mechanisms
    • F16H61/28Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/2807Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted using electric control signals for shift actuators, e.g. electro-hydraulic control therefor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H59/00Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02Selector apparatus
    • F16H59/08Range selector apparatus
    • F16H2059/082Range selector apparatus with different modes
    • F16H2059/084Economy mode
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H59/00Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02Selector apparatus
    • F16H59/08Range selector apparatus
    • F16H2059/082Range selector apparatus with different modes
    • F16H2059/085Power mode
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H59/00Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02Selector apparatus
    • F16H59/08Range selector apparatus
    • F16H2059/082Range selector apparatus with different modes
    • F16H2059/087Winter mode, e.g. to start on snow or slippery surfaces
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H59/00Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/68Inputs being a function of gearing status
    • F16H2059/6807Status of gear-change operation, e.g. clutch fully engaged
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control 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
    • F16H61/26Generation or transmission of movements for final actuating mechanisms
    • F16H61/28Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H2061/2823Controlling actuator force way characteristic, i.e. controlling force or movement depending on the actuator position, e.g. for adapting force to synchronisation and engagement of gear clutch
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H59/00Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/36Inputs being a function of speed
    • F16H59/44Inputs being a function of speed dependent on machine speed of the machine, e.g. the vehicle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H59/00Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/68Inputs being a function of gearing status
    • F16H59/70Inputs being a function of gearing status dependent on the ratio established
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H59/00Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/68Inputs being a function of gearing status
    • F16H59/72Inputs being a function of gearing status dependent on oil characteristics, e.g. temperature, viscosity
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control 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
    • F16H61/26Generation or transmission of movements for final actuating mechanisms
    • F16H61/28Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30Hydraulic or pneumatic motors or related fluid control means therefor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H63/00Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/40Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms
    • F16H63/46Signals to a clutch outside the gearbox
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00Machine element or mechanism
    • Y10T74/19Gearing
    • Y10T74/19219Interchangeably locked
    • Y10T74/19251Control mechanism

Definitions

  • This invention relates to ratio selector mechanisms and in particular to such mechanisms for the selection of the operative ratio in a vehicle transmission.
  • a selector mechanism of the type specified in which the operating pressure of the actuating means is varied during selection of a given ratio in the associated transmission or dependant on the ratio being selected in the associated transmission.
  • the operating pressure may be lowered when selecting the higher ratios of the associated transmission.
  • the actuating means comprises a first fluid pressure operated actuator which moves a selector member in a first direction to engage one of a number of ratio shift rails and a second fluid pressure operated actuator which moves the selector member in a second direction to longitudinally displace the engaged shift rail to engage an associated selected ratio.
  • the level of fluid pressure applied to the second actuator may be varied dependent on the position of the first actuator.
  • the pressure applied to the second actuator (which determines the force used in actually engaging the selected ratio) can be lowered when the first actuator is in engagement with the selector rail(s) associated with the higher ratios of the associated vehicle transmission.
  • This is particularly advantageous in synchromesh transmissions where the synchromesh units associated with the higher ratios are normally of a smaller diameter and therefore less powerful as they have a small speed differential to accommodate.
  • the level of pressure supplied to the second actuator may be controlled by a valve member which acts against a bias force which is varied in dependence on the position of the fir ⁇ t actuator.
  • the above arrangement can be provided by an abutment which moves with the first actuator and which bears on a spring which biases the valve member toward ⁇ a closed position, movement of the first actuator thus varying the effective bias force of the spring.
  • pressure is supplied to the actuating means via a master control valve which operates as a solenoid-operated proportional pressure regulating valve which outputs fluid at a pressure proportional to a signal (solenoid current) issued to an electronic control means in accordance with predetermined transmission or vehicle operating criteria.
  • the master control valve may be a solenoid-operated proportional flow valve and a pressure transducer is provided which sense ⁇ the pressure level supplied to the actuating means and whose output is fed to an electronic control means which issues signals to the solenoid of the master control valve to control the actuating means pressure in accordance with predetermined transmissin or vehicle operating criteria.
  • the shift load may be arranged to be lower up to the point at which the synchronising components come into contact and then higher to actually achieve synchronisation.
  • the pres ⁇ ure supplied to the actuators can easily be varied at any point in a shift cycle by varying the signal applied to the master control valve.
  • FIG. 1 diagrammatically illustrates a vehicle transmission ratio selector mechanism in accordance with the present invention
  • Figure 2 shows a ratio selection gate and associated shift rails used in the mechanism of figure 1;
  • Figure 3 diagrammatically illustrates a ball-type fluid pressure reducing valve which forms part of the selector mechanism
  • Figure 4 shows graphically the operating characteristic of the pressure reducing valve of figure 3;
  • Figure 5 shows graphically the operating characteristic of an alternative pressure limiting valve
  • Figure 6 shows diagrammatically a suitable form of pres ⁇ ure limiting valve
  • Figure 7 diagrammatically illustrates the basic constructional details of an alternative spool-type pressure control valve
  • Figure 8 diagrammatically illustrates an alternative vehicle transmission ratio selector mechanism in which actuator pressure is controlled by an electronically controlled proportional pressure regulating valve
  • Figure 9 diagrammatically illustrates a further vehicle transmission ratio selector mechanism in which actuator pressure is controlled by electronically controlled proportional flow valves and an associated pressure transducer, and
  • Figure 10 is a flow chart of the decision process used to control the mechanism of Figure 9.
  • FIG 1 this shows diagrammatically a gear selector mechanism in accordance with the present invention in which a selector member 10 is engageable with three shift rails 11,12 and 13 which engage ratios in an associated vehicle transmission using the shift gate shown in figure 2.
  • the shift rail 11 engages ratios 1 and 2
  • shift rail 12 engages ratios 3 and 4
  • shift rail 13 engages ratio 5 and reverse.
  • the selector member 10 is movable in a first direction X by a first fluid pressure operated actuator 14 and in a second direction Y by a second fluid pres ⁇ ure operated actuator 15. Thu ⁇ by a combination of the movements of the first and second actuators 14 and 15 the selector member 10 can be engaged with the required shift rail 11,12 or 13 and move in direction Y to engage the de ⁇ ired ratio associated with the currently engaged shift rail.
  • the actuators 14 and 15 each comprise a double-acting ram with an operating rod 14a and 15a respectively which is operatively connected with the selector member 10.
  • the presence of the operating rods 14a and 15a results in piston 16 of actuator 14 having a rod side effective area which is less than the effective area of the other head side of the piston.
  • piston 17 of actuator 15 has a smaller rod side area. Thus if both sides of the pistons are subjected to the same fluid pressure the piston ⁇ 16 and 17 will be di ⁇ placed along the actuators to extend the associated operating rods 14a and 15a.
  • Valve 20 is a master on/off valve which receives pressuri ⁇ ed fluid from a pump 23. Ma ⁇ ter valve 20, when in its on condition, supplies fluid to proportional flow valves 21 and 22 and also to the rod-end of each actuator 14 and 15.
  • a pressure regulating valve 24 is provided in the connection between master valve 20 and the rod end of actuator 15. The operation of pressure reducing valve 24 will be described in detail below.
  • Master valve 20 and proportional flow valves 21 and 22 are all controlled from an electronic control unit 25 which not only issues electrical control signal ⁇ to the solenoids 20a,21a and 22a of the valves but received signal inputs from potentiometers 26 and 27 which indicate the po ⁇ ition of a ⁇ sociated operating rods 14a and 15a and also a signal from a sensor 28 associated with a ratio selector lever 29 which is moved within the ratio selection gate ⁇ hown in figure 2 to ⁇ elect the desired ration of the associated transmission.
  • the sensor (or sensors) 28 outputs a signal to control unit 25 which is processed by control unit 25 and results in the emission of a signal to master valve 20 to move to the "on" position in.which pressuri ⁇ ed fluid i ⁇ ⁇ upplied to valve ⁇ 21 and 22 and al ⁇ o to the rod end of both actuator ⁇ 14 and 15.
  • valves 21 and 22 are operated by the control unit 25 in the appropriate sequence to give the appropriate movement of operating rods 14a and 15a in the appropriate sequence.
  • the fluid pres ⁇ ure ⁇ upplied to actuator 15, which moves the shift rail ⁇ 11,12 and 13 in direction Y to actually engage the ⁇ elected ratio, is varied dependent on which shift rail is engaged by the selector member 10.
  • Thi ⁇ variation in applied pressure is achieved by the previously referred to pressure reducing valve 24.
  • operating rod 14a has an abutment 30 connected therewith which moves with the operating rod.
  • This abutment provides the reaction surface against which a pressure level control spring 31 acts.
  • Pressure reducing valve 24 includes a movable piston member 32 which is acted upon by control spring 31 and within which a ball valve 33 is bia ⁇ ed again ⁇ t a seat 34 provided on the pi ⁇ ton member 32 by a ⁇ pring 35.
  • the end of bore 36 within which piston member 32 slides is provided with a projection 37 which extends through seat 34 to unseat ball valve 33 and piston 32 is held away from the end of bore 36 by spacers 32a on the piston.
  • valve 33 With the valve 24 in the position shown in figure 3, ball valve 33 is unseated and pres ⁇ ure i ⁇ free to flow from master valve 20 via inlet port 38 chamber 39 drilling 40 valve seats 34 and outlet port 41 to the rod end of actuator 15.
  • any further increase in the pressure supplied to the rod end of actuator is in accordance with the area ratio (al-a2)/al and is ⁇ hown as the gradient ⁇ in figure 4 which is a graphical representation of the pressure characteristics of valve 24.
  • valve 24 can be de ⁇ igned a ⁇ a pre ⁇ ure limiting valve in which after the initial closure of the valve there is no further increase in level of pressure ⁇ upplied to the rod end of actuator 15.
  • a valve operating characteristic is shown in figure 5 and can most easily be achieved by modifying the valve of figure 3 to the arrangement shown diagrammatically in figure 6 in which the effect of the pressure in chamber 39 is neutral on the displacement of piston 32 due to the balanced nature of the annular areas A exposed to the pressure in chamber 39.
  • a spool-valve arrangement as shown diagrammatically in figure 7, could be used in which spring 31 act ⁇ on one end of a spool member 50.
  • Edge 51 of an annular groove 52 in spool 50 cooperates with inlet port 38 to cut-off the flow of fluid along drilling 53 in spool 50 when the pressure applied to the outlet end 54 of spool 50 has risen to a level sufficient to displace spool 50 to the right against the action of spring 31.
  • the spool-valve arrangement shown in figure 7 operates as a pressure limiting valve in view of the balanced nature of the groove 52 of the spool.
  • the selector mechanism of the present invention has been described above in relation to a transmi ⁇ sion in which the ratio selection is done manually by the vehicle operator moving a ratio selector lever and, by implication, manually operating an associated drive line clutch, it will be appreciated that the present invention is also applicable to semi-automatic transmission of the type described, for example in the Applicant' ⁇ earlier European patents Nos. 0038113,0043660,0059035 and 0101220 in which the ratio ⁇ are manually ⁇ elected by the operator and the clutch i ⁇ operated by an electro-hydraulic control system.
  • the invention is also applicable to fully automated transmi ⁇ sions of the type described for example, in the Applicant's earlier co-pending UK patent application No. 95 02140.8.
  • Figure 8 shows diagrammatically a selector mechanism (for use with a fully automated transmi ⁇ ion) in which component ⁇ similar in function to the components of figure 1 have been similarly numbered.
  • the master valve 20 shown in Figure 8 is not a simple on/off valve, as in Figure 1, but a solenoid-operated proportional pressure regulating valve which outputs fluid at a pressure proportional to the applied solenoid current.
  • the pressure applied to the head ends of actuators 14 and 15 can be varied either in a manner dependant on the gear ratio being selected or at any point in the selection cycle to provide full control over the pressure exerted by the actuators.
  • the selector mechanism shown in Figure 8 is not only capable of reducing the pressure supplied to the actuator 15 when selecting a higher ratio of the transmi ⁇ sion (as described in the system shown in Figure 1) but is also capable of controlling the level of fluid pressure applied to both actuators in accordance with additional criteria such as : -
  • D) a requirement to vary shift load at different points in a given shifting cycle.
  • the shift load may be arranged to be lower up to the point at which the synchronising components come into contact and then higher to actually achieve synchronisation.
  • the system ⁇ hown in figure 8 also provides control over the vehicle clutch 60 to provide a fully automated transmis ⁇ ion.
  • Valve 63 is controlled by a solenoid 63a from electronic control unit 25 and has position 63a in which flow of fluid to and from the actuator 61 is cut off, position 63b in which the actuator is ⁇ upplied with pre ⁇ surised fluid from pump 23, position 63c in which the pressure in actuator 61 is vented back to sump, and position 63d in which the venting back to ⁇ ump is via a restriction to provide a slow engagement of the clutch. Position 63d is automatically assumed in the event of an electrical/electronic failure to ensure a slow engagement of the clutch which is the default condition of the system.
  • the control system also includes an accumulator 64, electric motor 65 which drives pump 23 and a pressure switch 66 which opens to turn off the pump when the accumulator pressure reaches a predeternined level.
  • the operating position of clutch actuator 61 is fed back as an input to the electronic control unit 25 from a sensor 67.
  • Figure 9 show ⁇ a ⁇ till further form of the present invention which again use ⁇ electronic monitoring of the control valve ⁇ to enable the actuator pre ⁇ ure to be varied at any point in the ratio ⁇ election cycle.
  • components of a similar function to those shown in Figure 1 have been similarly numbered.
  • valve 20 is a master proportional flow valve which receives pressuri ⁇ ed fluid from a circuit which includes pump 23 and an accumulator 75 which is charged via a one way valve 76, with a "blow off" valve 78 to protect from overcharging of accumulator pressure.
  • Master valve 20 supplies fluid to secondary proportional flow valves 21 and 22 and also to the rod-end of each actuator 14 and 15.
  • a pressure transducer 70 is provided in the connection between master valve 20 and the rod end of actuators 14 and 15.
  • Master valve 20 and proportional flow valves 21 and 22 are all controlled from electronic control unit 25 which not only is ⁇ ues electrical control signals to the solenoids 20a,21a and 22a of the valves but received signal inputs from potentiometers 26 and 27 which indicate the position of associated operating rods 14a and 15a and also a ⁇ ignal from a sensor 28 as ⁇ ociated with a ratio selector lever 29 which is moved within the ratio selection gate shown in figure 2 to select the desired ration of the as ⁇ ociated tran ⁇ mission. Addition inputs to control unit 25 are also described below.
  • the sensor (or sensors) 28 outputs a signal to control unit 25 which is processed by control unit 25 and results in the emission of a signal to the solenoid 20a of master valve 20 to supply pressurised fluid to valves 21 and 22 and also to the rod end of both actuators 14 and 15.
  • valves 21 and 22 are operated by the control unit 25 in the appropriate sequence to give the appropriate movement of operating rods 14a and 15a in the appropriate sequence.
  • the master valve 20 and valves 21 and 22 are solenoid-operated proportional flow control valves which output fluid at a flow rate proportional to the applied solenoid current.
  • pre ⁇ ure to the valve ⁇ 21 and 22 can be controlled. If pre ⁇ ure i ⁇ too high, fluid flow into the system is reduced, or vented, so that overall fluid volume in the gear selector mechanism is reduced, and vice versa.
  • the pres ⁇ ure applied to the head end ⁇ of actuators 14 and 15 can be varied either in a manner dependant on the gear ratio being selected or other pre-determined criteria at any point in the selection cycle to provide full control over the pressure exerted by the actuators.
  • the selector mechanism is not only capable of reducing the pres ⁇ ure supplied to the actuator 15 when selecting a higher ratio of the tran ⁇ mission but is also capable of controlling the level of fluid pres ⁇ ure applied to both actuator ⁇ in accordance with additional criteria A) to D) referred to above in relation to Figure 8.
  • Control unit 25 in addition to receiving inputs from sensors 71,72 and 73 also receives information as to the current gear engaged in the transmission from potentiometers 26 and 27 which are associated with shift rails 11,12 and 13 and has memory locations where other operating parameters [such as the loads to which each synchronizer in the transmission should be subjected at each point in it ⁇ operating cycle] are stored.
  • Signals from pressure transducer 70 which are fed back to control unit 25 are used to control the flow openings of valves 20,21 and 22 and hence the pressure applied to actuators 14 and 15 when the system determines that control of the pressure supplied to actuators is required (see deci ⁇ ion box A of Figure 3).
  • box B of Figure 3 a comparison is made between the feedback signal from pres ⁇ ure transducer 70 and the actuator pressure level which the control unit 25 has determined is currently appropriate from all the criteria under consideration.
  • box C and action boxes D and E the appropriate adjustment of fluid flow is made dependant on the result of the current versus appropriate pressure comparison. It is also pos ⁇ ible to use pre ⁇ sure transducer 70 to monitor the pres ⁇ ure currently held in accumulator 75. This removes the need to employ a seperate accumulator pressure monitor. Accumulator pressure can be monitored by transducer 70 when valves 21 and 22 are closed in the so-called "null" position in which no flow ia allowed into or out of actuators 14 and 15 and when the master valve 20 is also fully open.
  • the control unit 25 can be arranged to set-up the above accumulator pressure testing condition on a regular basis when the selector mechanism is not required for the execution of a ratio selection in the associated transmi ⁇ sion.
  • Figure 9 Although the selector mechanism of Figure 9 has been described above in relation to a transmission in which the ratio selection is done manually by the vehicle operator moving a ratio selector lever and, by implication, manually operating an associated drive line clutch, it will be appreciated that the Figure 9 construction is also applicable to semi-automatic transmission of the type described, for example in the Applicant's earlier European patents Nos. 0038113,0043660,0059035 and 0101220 in which the ratios are manually selected by the operator and the clutch is operated by an electro-hydraulic control system. The construction is also applicable to fully automated tran ⁇ mi ⁇ sions of the type described for example, in the Applicant's earlier co-pending UK patent application No. 95 02140.8. For example, the system shown in Figure 9 can also provide control over the associate vehicle clutch to provide a fully automated transmission in the manner described above in relation to Figure 8.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Gear-Shifting Mechanisms (AREA)

Abstract

A ratio selector mechanism for the selection of the operative ratio in an associated synchromesh vehicle transmission in which a fluid pressure operated actuating means (14, 15) operates synchromesh units. The operating pressure of the actuating means is varied either mechanically or electronically during selection of a given ratio in the associated transmission or dependant on the ratio being selected in the associated transmission.

Description

RATIO SELECTOR MECHANISMS
This invention relates to ratio selector mechanisms and in particular to such mechanisms for the selection of the operative ratio in a vehicle transmission.
Selector mechanisms, hereinafter referred to as bearing "of the type specified", are known in which a fluid pressure operated actuating means operates synchromesh units in an associated synchromesh vehicle transmission.
It is an object of the present invention to provide an improved from of selector mechanism of the type specified.
Thus according to the present invention there is provided a selector mechanism of the type specified in which the operating pressure of the actuating means is varied during selection of a given ratio in the associated transmission or dependant on the ratio being selected in the associated transmission.
For example, the operating pressure may be lowered when selecting the higher ratios of the associated transmission.
In one form of the invention the actuating means comprises a first fluid pressure operated actuator which moves a selector member in a first direction to engage one of a number of ratio shift rails and a second fluid pressure operated actuator which moves the selector member in a second direction to longitudinally displace the engaged shift rail to engage an associated selected ratio.
The level of fluid pressure applied to the second actuator may be varied dependent on the position of the first actuator.
Using such an arrangement the pressure applied to the second actuator (which determines the force used in actually engaging the selected ratio) can be lowered when the first actuator is in engagement with the selector rail(s) associated with the higher ratios of the associated vehicle transmission. This is particularly advantageous in synchromesh transmissions where the synchromesh units associated with the higher ratios are normally of a smaller diameter and therefore less powerful as they have a small speed differential to accommodate.
In a preferred arrangement the level of pressure supplied to the second actuator may be controlled by a valve member which acts against a bias force which is varied in dependence on the position of the firεt actuator.
Conveniently the above arrangement can be provided by an abutment which moves with the first actuator and which bears on a spring which biases the valve member towardε a closed position, movement of the first actuator thus varying the effective bias force of the spring.
In an alternative arrangement pressure is supplied to the actuating means via a master control valve which operates as a solenoid-operated proportional pressure regulating valve which outputs fluid at a pressure proportional to a signal (solenoid current) issued to an electronic control means in accordance with predetermined transmission or vehicle operating criteria.
In a still further alternative arrangement the master control valve may be a solenoid-operated proportional flow valve and a pressure transducer is provided which senseε the pressure level supplied to the actuating means and whose output is fed to an electronic control means which issues signals to the solenoid of the master control valve to control the actuating means pressure in accordance with predetermined transmissin or vehicle operating criteria.
The advantage of such electronically controlled arrangements are that the pressure supplied to the εelector actuators can be controlled by the master control valve not only in dependence on the ratio to be engaged but also in accordance with additional criteria such as:-
A) a requirement to use a different shift loads on one or more synchroε in a given tranεmiεεion which are of a different design to other synchroε used in the same transmission;
B) a requirement to have a higher shift load when changing down. This load could be arranged to be higher than the transmiεsion member sustain permanently but which might be required during kickdown in a fully automated transmission which used synchromesh units;
C) a requirement to have a shift load which is sensitive to a selected mode of operation of the associated transmission. For example, if the transmission is operating in "sport" mode quicker and noisier shifts are acceptable than when operating in for example, an "economy" or "winter" mode, and
D) a requirement to vary shift load at different points in a given shifting cycle. For example, the shift load may be arranged to be lower up to the point at which the synchronising components come into contact and then higher to actually achieve synchronisation. Alternatively, there may be a requirement to pull out of engagement with a lower shift load than is used for engagement or vice versa.
As indicated above, the presεure supplied to the actuators can easily be varied at any point in a shift cycle by varying the signal applied to the master control valve.
The present invention will now be described, by way of example only, with reference to the accompanying drawings in which:-
Figure 1 diagrammatically illustrates a vehicle transmission ratio selector mechanism in accordance with the present invention;
Figure 2 shows a ratio selection gate and associated shift rails used in the mechanism of figure 1;
Figure 3 diagrammatically illustrates a ball-type fluid pressure reducing valve which forms part of the selector mechanism;
Figure 4 shows graphically the operating characteristic of the pressure reducing valve of figure 3;
Figure 5 shows graphically the operating characteristic of an alternative pressure limiting valve;
Figure 6 shows diagrammatically a suitable form of presεure limiting valve;
Figure 7 diagrammatically illustrates the basic constructional details of an alternative spool-type pressure control valve;
Figure 8 diagrammatically illustrates an alternative vehicle transmission ratio selector mechanism in which actuator pressure is controlled by an electronically controlled proportional pressure regulating valve;
Figure 9 diagrammatically illustrates a further vehicle transmission ratio selector mechanism in which actuator pressure is controlled by electronically controlled proportional flow valves and an associated pressure transducer, and
Figure 10 is a flow chart of the decision process used to control the mechanism of Figure 9.
Referring to figure 1 this shows diagrammatically a gear selector mechanism in accordance with the present invention in which a selector member 10 is engageable with three shift rails 11,12 and 13 which engage ratios in an associated vehicle transmission using the shift gate shown in figure 2. The shift rail 11 engages ratios 1 and 2, shift rail 12 engages ratios 3 and 4, and shift rail 13 engages ratio 5 and reverse.
The selector member 10 is movable in a first direction X by a first fluid pressure operated actuator 14 and in a second direction Y by a second fluid presεure operated actuator 15. Thuε by a combination of the movements of the first and second actuators 14 and 15 the selector member 10 can be engaged with the required shift rail 11,12 or 13 and move in direction Y to engage the deεired ratio associated with the currently engaged shift rail. The actuators 14 and 15 each comprise a double-acting ram with an operating rod 14a and 15a respectively which is operatively connected with the selector member 10. As will be appreciated, the presence of the operating rods 14a and 15a results in piston 16 of actuator 14 having a rod side effective area which is less than the effective area of the other head side of the piston. Similarly piston 17 of actuator 15 has a smaller rod side area. Thus if both sides of the pistons are subjected to the same fluid pressure the pistonε 16 and 17 will be diεplaced along the actuators to extend the associated operating rods 14a and 15a.
The supply of pressure to the rod and head ends of the actuators 14 and 15 is controlled by three solenoid-operated valves 20,21 and 22. Valve 20 is a master on/off valve which receives pressuriεed fluid from a pump 23. Maεter valve 20, when in its on condition, supplies fluid to proportional flow valves 21 and 22 and also to the rod-end of each actuator 14 and 15. A pressure regulating valve 24 is provided in the connection between master valve 20 and the rod end of actuator 15. The operation of pressure reducing valve 24 will be described in detail below.
Master valve 20 and proportional flow valves 21 and 22 are all controlled from an electronic control unit 25 which not only issues electrical control signalε to the solenoids 20a,21a and 22a of the valves but received signal inputs from potentiometers 26 and 27 which indicate the poεition of aεsociated operating rods 14a and 15a and also a signal from a sensor 28 associated with a ratio selector lever 29 which is moved within the ratio selection gate εhown in figure 2 to εelect the desired ration of the associated transmission. Thus, in response to the movement of selector lever 29 to select a desired ratio in the associated transmission, the sensor (or sensors) 28 outputs a signal to control unit 25 which is processed by control unit 25 and results in the emission of a signal to master valve 20 to move to the "on" position in.which pressuriεed fluid iε εupplied to valveε 21 and 22 and alεo to the rod end of both actuatorε 14 and 15.
Dependent on the required movement of εelector member 10 and the associated operating rods 14a and 15a, valves 21 and 22 are operated by the control unit 25 in the appropriate sequence to give the appropriate movement of operating rods 14a and 15a in the appropriate sequence.
Initially operating rod 14a is moved in direction X to engage the appropriate shift rail followed by movement of operating rod 15a to displace the shift rail currently engaged by the selector member 10 in direction Y to engage the selected ratio.
In accordance with the present invention the fluid presεure εupplied to actuator 15, which moves the shift railε 11,12 and 13 in direction Y to actually engage the εelected ratio, is varied dependent on which shift rail is engaged by the selector member 10. Thiε variation in applied pressure is achieved by the previously referred to pressure reducing valve 24.
As can be seen more clearly from figure 3, operating rod 14a has an abutment 30 connected therewith which moves with the operating rod. This abutment provides the reaction surface against which a pressure level control spring 31 acts. Pressure reducing valve 24 includes a movable piston member 32 which is acted upon by control spring 31 and within which a ball valve 33 is biaεed againεt a seat 34 provided on the piεton member 32 by a εpring 35. The end of bore 36 within which piston member 32 slides is provided with a projection 37 which extends through seat 34 to unseat ball valve 33 and piston 32 is held away from the end of bore 36 by spacers 32a on the piston.
With the valve 24 in the position shown in figure 3, ball valve 33 is unseated and presεure iε free to flow from master valve 20 via inlet port 38 chamber 39 drilling 40 valve seats 34 and outlet port 41 to the rod end of actuator 15.
As the pressure entering valve 24 via inlet port 38 rises, because of the differential area of piston 32 (which is equal to the larger area al minus the smaller area a2) there is a net hydraulic force acting on piston 32 to the right, as viewed in figure 3, against the action of spring 31. When the pressure level within bore 36 acting on area al-a2 results in a force greater than the force applied to piston 32 by spring 31 the piston 32 is moved to the right so that ball-valve 33 engages seat 34 to close-off the flow of fluid through the valve to the rod end of actuator 15 thus controlling the level of pressure supplied to the rod end of actuator 15 and hence the force applied by actuator 15 to the associated synchromesh units.
Any further increase in the fluid pressure entering the chamber 39 of reducing valve 24 will tend to produce a hydraulic force on piston 32 acting to the left, as viewed in figure 3, which will produce periodic opening of ball valve 33 and a consequent rise in the level of pressure supplied to the rod end of actuator 15.
After the initial seating of ball valve 33, any further increase in the pressure supplied to the rod end of actuator is in accordance with the area ratio (al-a2)/al and is εhown as the gradient Θ in figure 4 which is a graphical representation of the pressure characteristics of valve 24.
As will be appreciated, due to the higher εpring force applied by spring 31 in the lower ratios 1 and 2 the initial seating of ball valve 33 occurs at a higher pressure level P (see figure 4) than the pressures Q and R at in which the ball valve 33 initially seatε when shift rails 12 and 13 respectively are in operation.
As an alternative, valve 24 can be deεigned aε a preεεure limiting valve in which after the initial closure of the valve there is no further increase in level of pressure εupplied to the rod end of actuator 15. Such a valve operating characteristic is shown in figure 5 and can most easily be achieved by modifying the valve of figure 3 to the arrangement shown diagrammatically in figure 6 in which the effect of the pressure in chamber 39 is neutral on the displacement of piston 32 due to the balanced nature of the annular areas A exposed to the pressure in chamber 39.
It will also be appreciated that instead of the ball-valve arrangement shown in figureε 3 and 6 a spool-valve arrangement, as shown diagrammatically in figure 7, could be used in which spring 31 actε on one end of a spool member 50. Edge 51 of an annular groove 52 in spool 50 cooperates with inlet port 38 to cut-off the flow of fluid along drilling 53 in spool 50 when the pressure applied to the outlet end 54 of spool 50 has risen to a level sufficient to displace spool 50 to the right against the action of spring 31. As will be appreciated the spool-valve arrangement shown in figure 7 operates as a pressure limiting valve in view of the balanced nature of the groove 52 of the spool.
Although the selector mechanism of the present invention has been described above in relation to a transmiεsion in which the ratio selection is done manually by the vehicle operator moving a ratio selector lever and, by implication, manually operating an associated drive line clutch, it will be appreciated that the present invention is also applicable to semi-automatic transmission of the type described, for example in the Applicant'ε earlier European patents Nos. 0038113,0043660,0059035 and 0101220 in which the ratioε are manually εelected by the operator and the clutch iε operated by an electro-hydraulic control system. The invention is also applicable to fully automated transmiεsions of the type described for example, in the Applicant's earlier co-pending UK patent application No. 95 02140.8.
Figure 8 shows diagrammatically a selector mechanism (for use with a fully automated transmiεεion) in which componentε similar in function to the components of figure 1 have been similarly numbered.
The master valve 20 shown in Figure 8 is not a simple on/off valve, as in Figure 1, but a solenoid-operated proportional pressure regulating valve which outputs fluid at a pressure proportional to the applied solenoid current. Thus, as will be appreciated, the pressure applied to the head ends of actuators 14 and 15 can be varied either in a manner dependant on the gear ratio being selected or at any point in the selection cycle to provide full control over the pressure exerted by the actuators.
Thus the selector mechanism shown in Figure 8 is not only capable of reducing the pressure supplied to the actuator 15 when selecting a higher ratio of the transmiεsion (as described in the system shown in Figure 1) but is also capable of controlling the level of fluid pressure applied to both actuators in accordance with additional criteria such as : -
A) a requirement to use a different shift loadε on one or more synchros in a given transmiεsion which are of a different deεign to other εynchros used in the same transmission;
B) a requirement to have a higher shift load when changing down. This load could be arranged to be higher than the transmission member sustain permanently but which might be required during kickdown in a fully automated transmission which used synchromesh units;
C) a requirement to have a shift load which is sensitive to a selected mode of operation of the associated transmission. For example, if the transmission is operating in "sport" mode quicker and noisier shiftε are acceptable than when operating in for example, an "economy" or "winter" mode, and
D) a requirement to vary shift load at different points in a given shifting cycle. For example, the shift load may be arranged to be lower up to the point at which the synchronising components come into contact and then higher to actually achieve synchronisation. Alternatively, there may be a requirement to pull out of engagement with a lower shift load than is uεed for engagement or vice verεa. The system εhown in figure 8 also provides control over the vehicle clutch 60 to provide a fully automated transmisεion.
Clutch 60 iε diεengaged by pressurisation of chamber 62 of a clutch hydraulic actuator 61 which is supplied with pressurised fluid via a control valve 63. Valve 63 is controlled by a solenoid 63a from electronic control unit 25 and has position 63a in which flow of fluid to and from the actuator 61 is cut off, position 63b in which the actuator is εupplied with preεsurised fluid from pump 23, position 63c in which the pressure in actuator 61 is vented back to sump, and position 63d in which the venting back to εump is via a restriction to provide a slow engagement of the clutch. Position 63d is automatically assumed in the event of an electrical/electronic failure to ensure a slow engagement of the clutch which is the default condition of the system.
The control system also includes an accumulator 64, electric motor 65 which drives pump 23 and a pressure switch 66 which opens to turn off the pump when the accumulator pressure reaches a predeternined level.
The operating position of clutch actuator 61 is fed back as an input to the electronic control unit 25 from a sensor 67.
Since the control of clutch 60 via valve 63 does not form part of the present invention it will not be further described in this application. The reader is directed to the Applicant'ε previously referred to patents and pending application if further details of the control of clutch 60 are required.
Figure 9 showε a εtill further form of the present invention which again useε electronic monitoring of the control valveε to enable the actuator preεεure to be varied at any point in the ratio εelection cycle. In Figure 9 components of a similar function to those shown in Figure 1 have been similarly numbered.
In Figure 9 valve 20 is a master proportional flow valve which receives pressuriεed fluid from a circuit which includes pump 23 and an accumulator 75 which is charged via a one way valve 76, with a "blow off" valve 78 to protect from overcharging of accumulator pressure.
Master valve 20 supplies fluid to secondary proportional flow valves 21 and 22 and also to the rod-end of each actuator 14 and 15. A pressure transducer 70 is provided in the connection between master valve 20 and the rod end of actuators 14 and 15.
Master valve 20 and proportional flow valves 21 and 22 are all controlled from electronic control unit 25 which not only isεues electrical control signals to the solenoids 20a,21a and 22a of the valves but received signal inputs from potentiometers 26 and 27 which indicate the position of associated operating rods 14a and 15a and also a εignal from a sensor 28 asεociated with a ratio selector lever 29 which is moved within the ratio selection gate shown in figure 2 to select the desired ration of the asεociated tranεmission. Addition inputs to control unit 25 are also described below. Thus, in response to the movement of selector lever 29 to select a desired ratio in the associated transmiεsion, the sensor (or sensors) 28 outputs a signal to control unit 25 which is processed by control unit 25 and results in the emission of a signal to the solenoid 20a of master valve 20 to supply pressurised fluid to valves 21 and 22 and also to the rod end of both actuators 14 and 15.
Dependent on the required movement of selector member 10 and the associated operating rods 14a and 15a, valves 21 and 22 are operated by the control unit 25 in the appropriate sequence to give the appropriate movement of operating rods 14a and 15a in the appropriate sequence.
Initially operating rod 14a is moved in direction X to engage the appropriate shift rail followed by movement of operating rod 15a to displace the shift rail currently engaged by the selector member 10 in direction Y to engage the selected ratio.
In accordance with the present invention the master valve 20 and valves 21 and 22 are solenoid-operated proportional flow control valves which output fluid at a flow rate proportional to the applied solenoid current. By controlling the flow rate (very accurately and quickly) through the aεter valve 20, preεεure to the valveε 21 and 22 can be controlled. If preεεure iε too high, fluid flow into the system is reduced, or vented, so that overall fluid volume in the gear selector mechanism is reduced, and vice versa.
Thus, as will be appreciated, by controlling the flow rate through these valves the presεure applied to the head endε of actuators 14 and 15 can be varied either in a manner dependant on the gear ratio being selected or other pre-determined criteria at any point in the selection cycle to provide full control over the pressure exerted by the actuators.
Thus the selector mechanism is not only capable of reducing the presεure supplied to the actuator 15 when selecting a higher ratio of the tranεmission but is also capable of controlling the level of fluid presεure applied to both actuatorε in accordance with additional criteria A) to D) referred to above in relation to Figure 8.
Additionally as can be seen from Figure 10 (which is a largely self explanatory flow-chart of the decision procesε used in the control of the presεure applied to actuatorε 14 and 15) other criteria εuch aε tranεmission oil temperature and road and engine speed can be used as determining factors in the presεure level applied to actuators 14 and 15. Oil temperature is sensed by εensor 71, road speed by sensor 72 and engine speed by sensor 73 or can be obtained by other means, such as a CAN (controller area network) on the vehicle.
Control unit 25 in addition to receiving inputs from sensors 71,72 and 73 also receives information as to the current gear engaged in the transmission from potentiometers 26 and 27 which are associated with shift rails 11,12 and 13 and has memory locations where other operating parameters [such as the loads to which each synchronizer in the transmission should be subjected at each point in itε operating cycle] are stored.
Signals from pressure transducer 70 which are fed back to control unit 25 are used to control the flow openings of valves 20,21 and 22 and hence the pressure applied to actuators 14 and 15 when the system determines that control of the pressure supplied to actuators is required (see deciεion box A of Figure 3).
In box B of Figure 3 a comparison is made between the feedback signal from presεure transducer 70 and the actuator pressure level which the control unit 25 has determined is currently appropriate from all the criteria under consideration. In box C and action boxes D and E the appropriate adjustment of fluid flow is made dependant on the result of the current versus appropriate pressure comparison. It is also posεible to use preεsure transducer 70 to monitor the presεure currently held in accumulator 75. This removes the need to employ a seperate accumulator pressure monitor. Accumulator pressure can be monitored by transducer 70 when valves 21 and 22 are closed in the so-called "null" position in which no flow ia allowed into or out of actuators 14 and 15 and when the master valve 20 is also fully open. The control unit 25 can be arranged to set-up the above accumulator pressure testing condition on a regular basis when the selector mechanism is not required for the execution of a ratio selection in the associated transmiεsion.
Although the selector mechanism of Figure 9 has been described above in relation to a transmission in which the ratio selection is done manually by the vehicle operator moving a ratio selector lever and, by implication, manually operating an associated drive line clutch, it will be appreciated that the Figure 9 construction is also applicable to semi-automatic transmission of the type described, for example in the Applicant's earlier European patents Nos. 0038113,0043660,0059035 and 0101220 in which the ratios are manually selected by the operator and the clutch is operated by an electro-hydraulic control system. The construction is also applicable to fully automated tranεmiεsions of the type described for example, in the Applicant's earlier co-pending UK patent application No. 95 02140.8. For example, the system shown in Figure 9 can also provide control over the associate vehicle clutch to provide a fully automated transmission in the manner described above in relation to Figure 8.
Also, although in the arrangement of Figure 9 the secondary valves 21 and 22 are proportional flow valveε these valves could be of the cheaper on/off type with the volume flow rate of the system being controlled by master valve 20.

Claims

1. A ratio selector mechanism for the selection of the operative ratio in an associated synchromesh vehicle transmission in which a fluid pressure operated actuating means operates synchromesh units, the mechanism being characterised in that the operating presεure of the actuating means is varied during selection of a given ratio in the associated transmission or dependant on the ratio being selected in the associated transmission.
2. A mechanism according to claim 1 characterised in that the operating pressure is lowered when selecting the higher ratios of the asεociated tranεmiεsion.
3. A mechanism according to claim 1 or 2 characterised in that the actuating means comprises a first fluid pressure operated actuator which moves a selector member in a first direction to engage one of a number of ratio shift rails and a second fluid pressure operated actuator which moves the selector member in a second direction to longitudinally displace the engaged shift rail to engage an associated selected ratio, the level of fluid pressure applied to the second actuator being varied dependent on the position of the first actuator.
4. A mechaniεm according to claim 3 characteriεed in that the pressure applied to the second actuator, which determines the force used in actually engaging the selected ratio, is lowered when the first actuator is in engagement.with a shift rail associated with the higher ratios of the associated vehicle transmission.
5. A mechanism according to claim 3 or 4 characterised in that the level of preεεure εupplied to the εecond actuator may be controlled by a valve member which actε against a bias force which is varied in dependence on the position of the firεt actuator.
6. A mechanism according to claim 5 characterised in that an abutment which moves with the first actuator bears on a spring which biases the valve member towards a closed position, movement of the first actuator thus varying the effective bias force of the spring.
7. A mechanism according to claim 5 or 6 characterised in that the valve member is deεigned to operate aε a pressure reducing valve.
8. A mechanism according to claim 5 or 6 characterised in that the valve member is designed to operate aε a pressure limiting valve.
9. A mechanism according to claim 1 characterised in that fluid pressure is supplied to the actuating means via a solenoid-operated master control valve which operates as a proportional presεure regulating valve which outputε fluid at a preεεure proportional to a signal from an electronic control means in accordance with predetermined transmission or vehicle operating criteria.
10. A mechanism according to claim 1 characterised in that fluid pressure is supplied to the actuating means via a solenoid-operating master control valve which operates as a proportional flow valve and in that a pressure transducer is provided which senεes the pressure level supplied to the actuating means and whose output is fed to an electronic control means which issues signals to the solenoid of the master control valve to control actuating means pressure in accordance with predetermined transmiεεion or vehicle operating criteria.
11. A mechanism according to claim 10 characterised in that the source of pressuriεed fluid comprises a pump which charges an accumulator which is connected with the master control valve and in that the pressure transducer is sited on the actuating means side of the master control valve but iε connectable via the maεter control valve with accumulator preεεure on the supply side of the master control valve, when the mechanism is not effecting a ratio selection, to monitor accumulator preεsure .
12. A mechaniεm according to any one of claims 1 and 9 to 11 characteriεed in that the preεsure supplied to the actuating means is controlled in response to one or more of the following criteria:-
a) shift load required for the currently operative synchro;
b) operative mode of the associated transmission;
c) current point in the current ratio selection cycle;
d) transmiεsion oil temperature, and
e) road or engine speed of associated vehicle.
13. A ratio selector mechanism according to any one of claims 1 to 12 characterised in that the selection of the operative ratio is made manually by the movement of a ratio selector member by a vehicle operator.
14. A ratio selector mechanism according to any one of claims 1 to 12 characterised in that the selection of the operative ratio is made automatically by electronic control means in accordance with predetermined vehicle operating criteria.
15. A transmission control system characterised by the inclusion of a ratio selector mechanism according to any one of claims 1 to 14 and a clutch control system in which a main drive line clutch is disengaged and engaged by a clutch actuator under the control of electronic control means in accordance with predetermined vehicle operating parameters.
16. A ratio selector mechanism constructed and arranged substantially as hereinbefore described with reference to and as shown in Figures 1 to 5 or 6 or 7 or 8 or 9 and 10 of the accompanying drawings.
PCT/GB1996/001732 1995-07-26 1996-07-19 Ratio selector mechanisms WO1997005410A1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US08/809,997 US5836207A (en) 1995-07-26 1996-07-19 Ratio selector mechanisms
EP96924999A EP0782675B1 (en) 1995-07-26 1996-07-19 Ratio selector mechanisms
JP9507313A JPH10507256A (en) 1995-07-26 1996-07-19 Ratio selection mechanism
GB9705270A GB2308413B (en) 1995-07-26 1996-07-19 Ratio selector mechanisms
DE69616259T DE69616259T2 (en) 1995-07-26 1996-07-19 SPEED CONTROL DEVICE

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GBGB9515333.4A GB9515333D0 (en) 1995-07-26 1995-07-26 Ratio selector mechanisms
GBGB9602734.7A GB9602734D0 (en) 1996-02-10 1996-02-10 Ratio selector mechanisms
GB9602734.7 1996-02-10
GB9515333.4 1996-02-10

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WO1997005410A1 true WO1997005410A1 (en) 1997-02-13

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US (1) US5836207A (en)
EP (2) EP0782675B1 (en)
JP (1) JPH10507256A (en)
KR (1) KR100436278B1 (en)
DE (2) DE69616259T2 (en)
ES (1) ES2166898T3 (en)
GB (1) GB2308413B (en)
WO (1) WO1997005410A1 (en)

Cited By (50)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999032809A2 (en) * 1997-12-19 1999-07-01 Zf Friedrichshafen Ag Gear shifting device
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EP1046341A1 (en) 1999-04-19 2000-10-25 GE.FIN. S.A. Società Finanziaria Fiduciaria Food composition with a high polyunsaturated fatty acid content, its preparations and use in a proper alimentary diet
EP1055546A2 (en) 1999-05-24 2000-11-29 AISIN AI Co., Ltd. Shift control apparatus and shift control method of automatic transmission
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US6446522B1 (en) 1999-09-11 2002-09-10 Luk Lamellen Und Kupplungsbau Gmbh Automated transmission systems
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US7275455B2 (en) 2001-09-12 2007-10-02 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Automatic gear system
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US8733521B2 (en) 2010-12-06 2014-05-27 Gm Global Technology Operations Apparatus for and method of controlling a dual clutch transmission
US8738257B2 (en) 2010-12-08 2014-05-27 Gm Global Technology Operations, Llc Electro-hydraulic control system and method for a dual clutch transmission
US8839928B2 (en) 2010-12-02 2014-09-23 Gm Global Technology Operations, Llc Electro-hydraulic control system for a dual clutch transmission
US8844392B2 (en) 2010-06-09 2014-09-30 Gm Global Technology Operations, Llc Electro-hydraulic and electro-mechanical control system for a dual clutch transmission
US8915076B2 (en) 2011-01-12 2014-12-23 Gm Global Technology Operations, Llc Transmission hydraulic control system having flow augmentation
US8942901B2 (en) 2010-12-09 2015-01-27 Gm Global Technology Operations, Llc Method of controlling a hydraulic control system for a dual clutch transmission
US8967351B2 (en) 2012-08-14 2015-03-03 Gm Global Technology Operations, Llc Transmission clutch piston compensator feed circuit
US9080666B2 (en) 2012-05-29 2015-07-14 Gm Global Technology Operations, Inc. Discrete mechanism for electronic transmission range selection
DE10037547B4 (en) * 1999-09-16 2016-11-24 Schaeffler Technologies AG & Co. KG Automated transmission system
US10167948B2 (en) 2016-03-17 2019-01-01 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission

Families Citing this family (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2645110B1 (en) 1989-03-30 1994-08-26 Brunet Jacques DEVICE FOR ASSURING THE RECTIFICATION OF A BOAT
WO1997010456A2 (en) * 1995-09-12 1997-03-20 Luk Getriebe-Systeme Gmbh Motor vehicle with a device for actuating the torque-transmission system and the gearbox
DE19713423C5 (en) * 1996-04-03 2015-11-26 Schaeffler Technologies AG & Co. KG Device and method for actuating a transmission
GB9608256D0 (en) * 1996-04-20 1996-06-26 Ap Kongsberg Holdings Ltd Actuation systems
US6145398A (en) * 1998-02-20 2000-11-14 New Venture Gear, Inc. Electronically controlled shift system for a manual transmission
DE19931973A1 (en) * 1999-07-09 2001-01-11 Wabco Gmbh & Co Ohg Device for controlling an actuator for a transmission
FR2801355B1 (en) 1999-11-20 2006-09-15 Luk Lamellen & Kupplungsbau CLUTCH CONTROL SYSTEM
WO2001073321A1 (en) * 2000-03-24 2001-10-04 Siemens Aktiengesellschaft Control for an automatic transmission
DE10142147A1 (en) * 2000-09-15 2002-03-28 Luk Lamellen & Kupplungsbau Supply of hydraulic fluid to e.g. automatic gears at controlled maximum pressure between nominal and system pressures, has greater control magnitude for higher pressures
JP4776764B2 (en) * 2000-10-03 2011-09-21 アイシン・エーアイ株式会社 Control device for synchronous mesh transmission
KR100869184B1 (en) * 2000-10-20 2008-11-18 루크 라멜렌 운트 쿠플룽스바우 베타일리궁스 카게 Motor vehicle with a gearbox and method for operating a motor vehicle
GB0025848D0 (en) * 2000-10-21 2000-12-06 Luk Lamellen & Kupplungsbau Hydraulic actuation systems
GB0025847D0 (en) * 2000-10-21 2000-12-06 Luk Lamellen & Kupplungsbau Hydraulic actuation systems
JP2002147590A (en) 2000-11-09 2002-05-22 Isuzu Motors Ltd Shift control device for transmission
GB2369657A (en) * 2000-12-02 2002-06-05 Luk Lamellen & Kupplungsbau Automatic transmission hydraulic actuation system with separate gear engagement control valves
DE60207311T2 (en) * 2001-01-22 2006-07-20 Isuzu Motors Ltd. Shift actuator for transmission
JP2002243028A (en) * 2001-02-15 2002-08-28 Hitachi Ltd Device and method for control of automatic transmission
ITTO20020131A1 (en) * 2002-02-15 2003-08-18 Magneti Marelli Powertrain Spa METHOD OF CONTROL OF AN ELECTRIC PUMP SUITABLE FOR PROVIDING PRESSURIZED WORKING FLUID FOR AN AUTOMATED TRANSMISSION.
JP4502103B2 (en) * 2002-03-27 2010-07-14 スズキ株式会社 Automatic transmission
US6647816B1 (en) 2002-04-25 2003-11-18 Borgwarner Inc. Electrically actuated synchronizer for a vehicle transmission
GB0226934D0 (en) * 2002-11-19 2002-12-24 Luk Lamellen & Kupplungsbau Gear engagement mechanism
DE10304588B3 (en) * 2003-02-05 2004-04-15 Daimlerchrysler Ag Automobile gearbox operating method has control signal for gearbox setting element varied in dependence on comparison between measured parameter and stored values
GB0307118D0 (en) * 2003-03-27 2003-04-30 Ricardo Uk Linmited Method for controlling a transmission of a vehicle
GB0307119D0 (en) * 2003-03-27 2003-04-30 Ricardo Uk Linmited Method for controlling the transmission of a vehicle
JP2005147302A (en) * 2003-11-18 2005-06-09 Aisin Ai Co Ltd Synchronous controller in automatic transmission
DE102004001753A1 (en) * 2004-01-12 2005-08-04 Volkswagen Ag Valve system or method for controlling a clutch or a gear selector of a motor vehicle
DE102004055030B4 (en) 2004-11-15 2009-09-10 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Device for pressurizing a piston actuator
DE102004056609A1 (en) * 2004-11-24 2006-06-01 Zf Friedrichshafen Ag Shift assistance device for a manual shiftable manual transmission
DE102006016780A1 (en) * 2006-04-10 2007-10-11 Ford Global Technologies, LLC, Dearborn Method and device for selecting driving programs in automatic transmissions
DE102007044431A1 (en) * 2007-09-18 2009-03-19 Zf Friedrichshafen Ag Electrohydraulic control device
EP2065624B1 (en) * 2007-11-28 2010-03-03 Magneti Marelli S.p.A. A method of driving an hydraulic actuator by means of a pressure-controlled proportioning solenoid valve
DE102008054662A1 (en) 2008-12-15 2010-06-17 Zf Friedrichshafen Ag Method for monitoring a hydraulic or pneumatic transmission control
US8904893B2 (en) * 2010-12-06 2014-12-09 Gm Global Technology Operations, Llc Method of controlling a dual clutch transmission
DE102011007107B4 (en) 2011-04-11 2023-11-02 Zf Friedrichshafen Ag Method for controlling an automated manual transmission
DE102011007105A1 (en) 2011-04-11 2012-10-11 Zf Friedrichshafen Ag Method for controlling an automated manual transmission
US9651138B2 (en) 2011-09-30 2017-05-16 Mtd Products Inc. Speed control assembly for a self-propelled walk-behind lawn mower
FR2992384B1 (en) * 2012-06-26 2014-07-04 Borgwarner Inc DOUBLE OIL CLUTCH TRANSMISSION
CN104481959B (en) * 2014-12-26 2017-02-22 中国北方车辆研究所 Hydraulic system capable of lowering hydraulic oil source startup frequency of AMT (Automated Mechanical Transmission)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0059853A2 (en) * 1981-03-07 1982-09-15 WABCO Westinghouse Fahrzeugbremsen GmbH Servo-control for a transmission
GB2214248A (en) * 1987-12-08 1989-08-31 Automotive Products Plc Ratio selector system using fluid actuators and ectrohydraulic control in a vehicle transmission
EP0378218A1 (en) * 1989-01-13 1990-07-18 IVECO FIAT S.p.A. Motor vehicle drive control system
EP0477564A2 (en) * 1990-08-31 1992-04-01 Isuzu Motors Limited Electronically controlled transmission

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU548876B2 (en) 1980-02-18 1986-01-09 Automotive Products Ltd. Standing-start clutch control
AU543540B2 (en) 1980-07-08 1985-04-26 Automotive Products Ltd. Clutch control system
AU552105B2 (en) 1981-02-24 1986-05-22 Automotive Products Ltd. Clutch control system
AU1725283A (en) 1982-08-11 1984-02-16 Automotive Products Plc Clutch control system
US5224392A (en) * 1992-01-23 1993-07-06 Eaton Corporation Variable pressure range section actuator piston
US5231895A (en) * 1992-01-23 1993-08-03 Eaton Corporation Auxiliary section actuator air control system
GB9512838D0 (en) * 1995-06-23 1995-08-23 Massey Ferguson Sa Synchromesh control apparatus and method

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0059853A2 (en) * 1981-03-07 1982-09-15 WABCO Westinghouse Fahrzeugbremsen GmbH Servo-control for a transmission
GB2214248A (en) * 1987-12-08 1989-08-31 Automotive Products Plc Ratio selector system using fluid actuators and ectrohydraulic control in a vehicle transmission
EP0378218A1 (en) * 1989-01-13 1990-07-18 IVECO FIAT S.p.A. Motor vehicle drive control system
EP0477564A2 (en) * 1990-08-31 1992-04-01 Isuzu Motors Limited Electronically controlled transmission

Cited By (67)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6301984B1 (en) 1997-12-19 2001-10-16 Zf Friedrichshafen Ag Gear shifting device
WO1999032809A3 (en) * 1997-12-19 1999-10-07 Zahnradfabrik Friedrichshafen Gear shifting device
WO1999032809A2 (en) * 1997-12-19 1999-07-01 Zf Friedrichshafen Ag Gear shifting device
EP0947743A2 (en) 1998-04-01 1999-10-06 AISIN AI Co., Ltd. Gear ratio selecting apparatus for transmissions
EP0947743A3 (en) * 1998-04-01 2000-06-28 AISIN AI Co., Ltd. Gear ratio selecting apparatus for transmissions
US6131476A (en) * 1998-04-01 2000-10-17 Aisin Ai Co., Ltd. Gear ratio selecting and shifting apparatus in a transmission
WO2000061399A1 (en) 1999-04-14 2000-10-19 Luk Lamellen Und Kupplungsbau Gmbh Transmission system
EP1046341A1 (en) 1999-04-19 2000-10-25 GE.FIN. S.A. Società Finanziaria Fiduciaria Food composition with a high polyunsaturated fatty acid content, its preparations and use in a proper alimentary diet
EP1055546A2 (en) 1999-05-24 2000-11-29 AISIN AI Co., Ltd. Shift control apparatus and shift control method of automatic transmission
EP1055546A3 (en) * 1999-05-24 2002-08-21 AISIN AI Co., Ltd. Shift control apparatus and shift control method of automatic transmission
US6394929B1 (en) 1999-05-24 2002-05-28 Aisin Ai Co., Ltd. Shift control apparatus and shift control method of automatic transmission
US6276224B1 (en) 1999-05-25 2001-08-21 Aisin Ai Co., Ltd Shift control apparatus for transmission
EP1055847A2 (en) 1999-05-25 2000-11-29 AISIN AI Co., Ltd. Shift control apparatus for transmission
FR2798173A1 (en) 1999-09-04 2001-03-09 Luk Lamellen & Kupplungsbau AUTOMATIC TRANSMISSION SYSTEM
DE10037551B4 (en) * 1999-09-11 2012-10-25 Schaeffler Technologies AG & Co. KG transmission system
US6446522B1 (en) 1999-09-11 2002-09-10 Luk Lamellen Und Kupplungsbau Gmbh Automated transmission systems
DE10037547B4 (en) * 1999-09-16 2016-11-24 Schaeffler Technologies AG & Co. KG Automated transmission system
FR2804192A1 (en) 2000-01-24 2001-07-27 Luk Lamellen & Kupplungsbau HYDRAULIC DEVICE
FR2804194A1 (en) 2000-01-24 2001-07-27 Luk Lamellen & Kupplungsbau REPORT LOCKING MECHANISM
DE10102031B4 (en) * 2000-03-04 2017-02-09 Schaeffler Technologies AG & Co. KG transmission
FR2805877A1 (en) 2000-03-04 2001-09-07 Luk Lamellen & Kupplungsbau GEARBOXES
FR2805876A1 (en) 2000-03-04 2001-09-07 Luk Lamellen & Kupplungsbau HYDRAULIC MANEUVER SYSTEM
DE10148083B4 (en) * 2000-10-12 2014-02-13 Schaeffler Technologies AG & Co. KG Hydraulic actuation systems
US6553857B2 (en) 2000-10-12 2003-04-29 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic actuation systems
US6637282B2 (en) 2000-11-13 2003-10-28 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic actuation systems
FR2816894A1 (en) 2000-11-21 2002-05-24 Luk Lamellen & Kupplungsbau HYDRAULIC ACTUATION SYSTEM
US6568515B2 (en) 2000-11-21 2003-05-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic actuation systems
FR2818722A1 (en) 2000-12-27 2002-06-28 Luk Lamellen & Kupplungsbau Compliant link for use in hydraulic actuation system, has springs preloaded in components to prevent relative movement of connecting rod between components, when axial load of specific range is applied to any component
US6810768B2 (en) 2000-12-27 2004-11-02 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Compliant link
US6658951B2 (en) 2001-02-12 2003-12-09 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic actuation systems
FR2820694A1 (en) 2001-02-12 2002-08-16 Luk Lamellen & Kupplungsbau HYDRAULIC ACTUATION SYSTEM
FR2822513A1 (en) 2001-03-21 2002-09-27 Luk Lamellen & Kupplungsbau AUTOMATED TRANSMISSION SYSTEMS
GB2378489A (en) * 2001-07-31 2003-02-12 Luk Lamellen & Kupplungsbau Method of gear selection using current pulses in a hydraulic transmission system with actuators and valves
US7275455B2 (en) 2001-09-12 2007-10-02 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Automatic gear system
DE10251031B4 (en) * 2001-11-10 2014-02-27 Schaeffler Technologies AG & Co. KG Calibrating a vehicle system
WO2004085886A1 (en) * 2003-03-27 2004-10-07 Ricardo Uk Limited Method for controlling a transmission of a vehicle
US8475336B2 (en) 2009-07-30 2013-07-02 GM Global Technology Operations LLC Hydraulic control system for a dual clutch transmission
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US8844392B2 (en) 2010-06-09 2014-09-30 Gm Global Technology Operations, Llc Electro-hydraulic and electro-mechanical control system for a dual clutch transmission
US8839928B2 (en) 2010-12-02 2014-09-23 Gm Global Technology Operations, Llc Electro-hydraulic control system for a dual clutch transmission
US8733521B2 (en) 2010-12-06 2014-05-27 Gm Global Technology Operations Apparatus for and method of controlling a dual clutch transmission
US8738257B2 (en) 2010-12-08 2014-05-27 Gm Global Technology Operations, Llc Electro-hydraulic control system and method for a dual clutch transmission
US8942901B2 (en) 2010-12-09 2015-01-27 Gm Global Technology Operations, Llc Method of controlling a hydraulic control system for a dual clutch transmission
US9765885B2 (en) 2010-12-09 2017-09-19 GM Global Technology Operations LLC Method of controlling a hydraulic control system for a dual clutch transmission
US8500600B2 (en) 2011-01-10 2013-08-06 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having a manual valve with a two gear default strategy
US8915076B2 (en) 2011-01-12 2014-12-23 Gm Global Technology Operations, Llc Transmission hydraulic control system having flow augmentation
US8702548B2 (en) 2011-11-03 2014-04-22 Gm Global Technology Operations Hydraulic control system for an automatic transmission
WO2013068175A1 (en) * 2011-11-11 2013-05-16 Zf Friedrichshafen Ag Method for controlling shift processes of a transmission
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US9574576B2 (en) 2012-02-22 2017-02-21 MAGNETI MARELLI S.p.A. Hydraulic servo-control of a servo-controlled gearbox
EP2631493A1 (en) * 2012-02-22 2013-08-28 Magneti Marelli S.p.A. Hydraulic servo-control of a servo-controlled gearbox
US9080666B2 (en) 2012-05-29 2015-07-14 Gm Global Technology Operations, Inc. Discrete mechanism for electronic transmission range selection
US8967351B2 (en) 2012-08-14 2015-03-03 Gm Global Technology Operations, Llc Transmission clutch piston compensator feed circuit
US10167948B2 (en) 2016-03-17 2019-01-01 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission

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GB2308413B (en) 1999-09-01
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US5836207A (en) 1998-11-17
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EP0933564B1 (en) 2003-01-22
EP0782675B1 (en) 2001-10-24
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EP0782675A1 (en) 1997-07-09
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EP0933564A2 (en) 1999-08-04
JPH10507256A (en) 1998-07-14

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