WO1998046907A2 - Method and apparatus for operating a clutch in an automated mechanical transmission - Google Patents
Method and apparatus for operating a clutch in an automated mechanical transmission Download PDFInfo
- Publication number
- WO1998046907A2 WO1998046907A2 PCT/US1998/007606 US9807606W WO9846907A2 WO 1998046907 A2 WO1998046907 A2 WO 1998046907A2 US 9807606 W US9807606 W US 9807606W WO 9846907 A2 WO9846907 A2 WO 9846907A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- engine
- engagement
- signal
- engine speed
- Prior art date
Links
- 238000000034 method Methods 0.000 title abstract description 28
- 230000009347 mechanical transmission Effects 0.000 title abstract description 8
- 230000005540 biological transmission Effects 0.000 claims description 68
- 230000004044 response Effects 0.000 claims description 9
- 230000008569 process Effects 0.000 abstract description 20
- 230000007704 transition Effects 0.000 description 14
- 238000013459 approach Methods 0.000 description 8
- 230000007423 decrease Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 6
- 230000000994 depressogenic effect Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 4
- 230000007246 mechanism Effects 0.000 description 4
- 230000001133 acceleration Effects 0.000 description 3
- 230000000712 assembly Effects 0.000 description 3
- 238000000429 assembly Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 2
- 206010000210 abortion Diseases 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000000881 depressing effect Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000013022 venting Methods 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/02—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
- F16D48/066—Control of fluid pressure, e.g. using an accumulator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2510/00—Input parameters relating to a particular sub-units
- B60W2510/02—Clutches
- B60W2510/0208—Clutch engagement state, e.g. engaged or disengaged
- B60W2510/0216—Clutch engagement rate
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2510/00—Input parameters relating to a particular sub-units
- B60W2510/06—Combustion engines, Gas turbines
- B60W2510/0638—Engine speed
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2510/00—Input parameters relating to a particular sub-units
- B60W2510/06—Combustion engines, Gas turbines
- B60W2510/0657—Engine torque
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/02—Clutches
- B60W2710/021—Clutch engagement state
- B60W2710/023—Clutch engagement rate
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
- F16D2500/10406—Clutch position
- F16D2500/10412—Transmission line of a vehicle
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/108—Gear
- F16D2500/1081—Actuation type
- F16D2500/1083—Automated manual transmission
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/302—Signal inputs from the actuator
- F16D2500/3026—Stroke
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/304—Signal inputs from the clutch
- F16D2500/30401—On-off signal indicating the engage or disengaged position of the clutch
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/304—Signal inputs from the clutch
- F16D2500/3041—Signal inputs from the clutch from the input shaft
- F16D2500/30415—Speed of the input shaft
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/306—Signal inputs from the engine
- F16D2500/3065—Torque of the engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/306—Signal inputs from the engine
- F16D2500/3067—Speed of the engine
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/308—Signal inputs from the transmission
- F16D2500/3082—Signal inputs from the transmission from the output shaft
- F16D2500/30825—Speed of the output shaft
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/314—Signal inputs from the user
- F16D2500/31406—Signal inputs from the user input from pedals
- F16D2500/3144—Accelerator pedal position
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
- F16D2500/70402—Actuator parameters
- F16D2500/7041—Position
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
- F16D2500/70452—Engine parameters
- F16D2500/70454—Engine speed
Definitions
- This invention relates in general to vehicle transmissions and in particular to a method and apparatus for automatically controlling the operation of a clutch for use with an automated mechanical transmission in a vehicle drive train assembly.
- a transmission is provided in a drive train between a source of rotational power, such as an internal combustion or diesel engine, and the driven axle and wheels of the vehicle.
- a typical transmission includes a case containing an input shaft, an output shaft, and a plurality of meshing gears. Means are provided for connecting selected ones of the meshing gears between the input shaft and the output shaft to provide a desired speed reduction gear ratio therebetween.
- the meshing gears contained within the transmission case are of varying size so as to provide a plurality of such gear ratios.
- a typical structure for a vehicle clutch includes a cover which is connected to a flywheel secured to the end of the output shaft of the vehicle engine for rotation therewith.
- a pressure plate is disposed within the clutch between the cover and the flywheel. The pressure plate is connected for rotation with the flywheel and the cover, but is permitted to move axially relative thereto.
- the flywheel, the cover, and the pressure plate are all constantly rotatably driven by the vehicle engine.
- a driven disc assembly is disposed between the flywheel and the pressure plate.
- the driven disc assembly is supported on the input shaft of the transmission for rotation therewith, but is permitted to move axially relative thereto.
- the pressure plate is moved axially toward the flywheel to an engaged position, wherein the driven disc assembly is frictionally engaged between the flywheel and the pressure plate.
- the driven disc assembly (and the input shaft of the transmission upon which it is supported) are driven to rotate with the flywheel, the cover, and the pressure plate.
- the pressure plate is moved axially away from the flywheel to a disengaged position.
- the driven disc assembly is not frictionally engaged between the flywheel and the pressure plate.
- the driven disc assembly (and the input shaft of the transmission upon which it is supported) are not driven to rotate with the flywheel, the cover, and the pressure plate.
- a release assembly including a generally hollow cylindrical release sleeve which is disposed about the output shaft of the clutch.
- the forward end of the release sleeve extends within the clutch and is connected through a plurality of levers or other mechanical mechanism to the pressure plate.
- axial movement of the release sleeve causes corresponding axial movement of the pressure plate between the engaged and disengaged positions.
- one or more engagement springs are provided within the clutch to urge the pressure plate toward the engaged position. The engagement springs typically react between the release sleeve and the cover to normally maintain the clutch in the engaged condition.
- the rearward end of the release sleeve extends outwardly from the clutch through a central opening formed through the cover. Because the release sleeve is connected to the cover and the pressure plate of the clutch, it is also constantly driven to rotate whenever the vehicle engine is operating. Thus, an annular release bearing is usually mounted on the rearward end of the release sleeve.
- the release bearing is axially fixed on the release sleeve and includes an inner race which rotates with release sleeve, an outer race which is restrained from rotation, and a plurality of bearings disposed between the inner race and the outer race to accommodate such relative rotation.
- the non-rotating outer race of the release bearing is typically engaged by an actuating mechanism for moving the release sleeve (and, therefore, the pressure plate) between the engaged and disengaged positions to operate the clutch.
- both the operation of the clutch and the gear shifting operation in the transmission are performed manually by an operator of the vehicle.
- the clutch can be disengaged by depressing a clutch pedal located in the driver compartment of the vehicle.
- the clutch pedal is connected through a mechanical linkage to the outer race of the release bearing of the clutch such that when the clutch pedal is depressed, the pressure plate of the clutch is moved from the engaged position to the disengaged position.
- the gear shifting operation in the transmission can be performed when the clutch is disengaged by manually moving a shift lever which extends from the transmission into the driver compartment of the vehicle.
- Manually operated clutch/transmission assemblies of this general type are well known in the art and are relatively simple, inexpensive, and lightweight in structure and operation. Because of this, the majority of medium and heavy duty truck clutch/transmission assemblies in common use today are manually operated.
- the driver-manipulated clutch pedal may be replaced by an automatic clutch actuator, such as a hydraulic or pneumatic actuator.
- the operation of the automatic clutch actuator can be controlled by an electronic controller or other control mechanism to selectively engage and disengage the clutch without manual effort by the driver.
- the driver-manipulated shift lever may also be replaced by an automatic transmission actuator, such as a hydraulic or pneumatic actuator which is controlled by an electronic controller or other control mechanism to select and engage desired gear ratios for use.
- the control of the movement of the release bearing from the disengaged position to the engaged position has been found to be less critical when sMfting among such higher gear ratios because a much lesser force is required to overcome the inertia of the vehicle when the vehicle is already moving.
- the total movement of the release bearing from the disengaged position to the engaged position can be divided into three ranges of movement.
- the first range of movement is from the disengaged position to a first intermediate position (referred to as the transition point).
- the transition point is selected to be relatively near, but spaced apart from, the position of the release bearing at which the driven disc assembly of the clutch is initially engaged by the flywheel and the pressure plate.
- the transition movement the clutch is completely disengaged, and no torque is transmitted through the clutch to the transmission.
- the second range of movement is from the transition point to a second intermediate position (referred to as the kiss point).
- the kiss point is the position of the release bearing at which the driven disc assembly is initially engaged by the flywheel and the pressure plate.
- the clutch is disengaged until the release bearing reaches the kiss point, at which point the first measurable amount of torque is transmitted through the clutch to the transmission.
- the third range of movement of the release bearing is from the kiss point to the engaged position.
- the engaged position is the position of the release bearing at which the driven disc assembly is completely engaged by the flywheel and the pressure plate.
- the clutch is gradually engaged so as to increase the amount of torque which is transmitted through the clutch to the transmission from the first measurable amount at the kiss point to the full capacity of the clutch at the engaged position.
- the clutch is gradually engaged so as to increase the amount of torque which is transmitted through the clutch to the transmission from the first measurable amount at the kiss point to the full capacity of the clutch at the engaged position.
- this engagement movement of the release bearing is still important to engage the clutch smoothly to prevent the engine from stalling and to avoid undesirable sudden jerking movement of the vehicle.
- the rate of engagement movement of the release bearing (referred to as the engagement rate) has been determined as a function of the difference between the rotational speeds of the input member and the output member of the clutch.
- This invention relates to an apparatus and method for controlling the operation of a clutch in a partially or fully automated mechanical transmission which is responsive to the actual load on the vehicle engine for varying the engagement rate of release bearing during re-engagement of the clutch.
- the apparatus includes an electronic controller which initially sets a desired speed for the vehicle engine during the sl ⁇ fting process, determines a rate of engagement movement of a release bearing of the clutch, and actuates appropriate valves to initiate the gradual engagement of the clutch.
- the electronic controller sets a first lower engine speed threshold and a second lower engine speed threshold. In a first embodiment, the magnitude of the first lower engine speed threshold varies with the actual load on the engine.
- the engagement process is continued without interruption. If the actual speed of the engine drops below the first lower engine speed threshold but remains above the second lower engine speed threshold, the release bearing is held in its current position until the actual speed of the engine recovers above the first lower engine speed threshold. If the actual speed of the engine drops below both the first lower engine speed threshold and the second lower engine speed threshold, the engagement process is aborted, and the release bearing is returned to the disengaged position until the actual speed of the engine recovers above an engagement re-start speed threshold.
- the magnitude of the first lower engine speed threshold varies with both the actual load on the engine and the amount of depression of an accelerator pedal of the vehicle.
- Fig. 1 is a block diagram of a vehicle drive train assembly including an electronic controller in accordance with this invention.
- Fig. 2 is sectional elevational view of the clutch actuator and portions of the clutch and transmission illustrated in Fig. 1 showing the clutch actuator and the clutch in a disengaged position, together with a block diagram of the valves and related control circuitry for operating the clutch actuator and the clutch.
- Fig. 3 is a flow chart of a first embodiment of an algorithm for controlling the movement of the release bearing of the clutch in its engagement movement from the kiss point to the engaged position.
- Fig. 4 is a flow chart of a second embodiment of an algorithm for controlling the movement of the release bearing of the clutch in its engagement movement from the kiss point to the engaged position.
- Fig. 1 a block diagram of a vehicle drive train assembly, indicated generally at 10.
- the drive train assembly 10 includes a conventional engine 11 or other source of rotational power.
- the engine 11 is connected through an output shaft 11a, such as a crankshaft of the engine 11, to a clutch 12.
- the clutch 12 is also conventional in the art and functions to selectively connect the output shaft 1 la of the engine 11 to an input shaft 13a of a transmission 13.
- the transmission 13 contains a plurality of meshing gears (not shown) which are selectively connected between the input shaft 13a and an output shaft 13b.
- the meshing gears contained within the transmission 13 are of varying size so as to provide a plurality of such gear ratios. By appropriately shifting among these various gear ratios, a desired speed reduction gear ratio can be provided between the input shaft 13a and the output shaft 13b. Consequently, acceleration and deceleration of the vehicle can be accomplished in a smooth and efficient manner.
- the output shaft 13b is connected to a conventional axle assembly 14.
- the axle assembly 14 includes one or more wheels which are rotatably driven by the engine 11 whenever the clutch 12 and the transmission 13 are engaged. This general structure for the drive train assembly 10 is well known in the art.
- the illustrated transmission 13 may be either a partially or fully automated mechanical transmission.
- a driver-manipulated shift lever (not shown) engages and moves certain ones of a plurality of shift rails contained within the transmission to engage a first set of gear ratios for use.
- an automatically shifting transmission actuator 15 is provided on the transmission 13 to engage and move the remaining shift rails to engage a second set of gear ratios for use.
- it is known to provide a partially automated manual transmission wherein the lower gear ratios are manually selected and engaged by the vehicle driver using the shift lever, while the higher gear ratios are automatically selected and engaged by the transmission actuator 15.
- the clutch 12 is provided with a clutch actuator 16.
- the structure and operation of the clutch actuator 16 will be discussed further below. Briefly, however, the clutch actuator 16 is provided to replace a driver-manipulated clutch pedal so as to partially or fully automate the operation of the clutch 12.
- the clutch actuator 16 is effective to operate the clutch 12 in either an engaged or disengaged mode.
- the clutch 12 is engaged, the transmission 13 is driven by the vehicle engine 11 to operate the vehicle at a selected gear ratio.
- the clutch 12 is initially disengaged such that power is not transmitted from the vehicle engine 11 to the transmission 13.
- the transmission actuator 15 allows the transmission actuator 15 to effect a gear shifting operation within the transmission 13 under a non-torque loading condition to prevent undesirable clashing of the meshing gear teeth. Thereafter, the clutch 12 is re-engaged such that power is transmitted from the vehicle engine 11 to the fransmission 13 to operate the vehicle at the second gear ratio.
- the operation of the clutch actuator 16 and the transmission actuator 15 are controlled by an electronic controller 20.
- the electronic controller 20 can be embodied as any conventional microprocessor or similar computing apparatus which can be programmed to operate the clutch actuator 16 (to effect automatic disengagement and engagement of the clutch 12) and the transmission actuator 15 (to effect automatic shifting of the transmission 13 when the clutch 12 is disengaged) as described above. The operation of the electronic controller 20 will be described in detail below.
- a fransmission output shaft speed sensor 21 provides an input signal to the electronic controller 20.
- the transmission output shaft speed sensor 21 is conventional in the art and is adapted to generate an electrical signal which is representative of the actual rotational speed of the output shaft 13b of the fransmission 13.
- a clutch position sensor 22 also provides an input signal to the electronic controller 20. The structure and operation of the clutch position sensor 22 will be described below.
- An engine controller 23 is provided to control the operation of the vehicle engine 11.
- the engine controller 23 can also be embodied as any conventional microprocessor or similar computing apparatus which can be programmed to operate the engine 11 in a desired manner.
- the engine controller 23 controls the operation of the engine 11 in response to an input signal generated by an accelerator pedal position sensor 24.
- the accelerator pedal position sensor 24 is conventional in the art and is adapted to generate an electrical signal which is representative of the actual position of the accelerator pedal (not shown) of the vehicle.
- the accelerator pedal is physically manipulated by the foot of the driver of the vehicle to control the operation thereof.
- the accelerator pedal is depressed by the driver when it is desired to increase the speed of the engine 11 and move the vehicle.
- the accelerator pedal is released when it is desired to decrease the speed of the engine 11 to slow or stop such movement of the vehicle.
- the engine controller 23 controls the speed of the engine 11 in response to the signal from the accelerator pedal position sensor 24 so as to operate the vehicle as desired by the driver.
- the engine controller 23 accomplishes this by issuing engine torque commands to the engine 11.
- the accelerator pedal position sensor 24 may, if desired, be replaced by a throttle position sensor (not shown) or other driver-responsive sensor which generates a signal which is representative of the desired speed or mode of operation of the vehicle.
- a second input to the engine controller 23 is an engine output shaft speed sensor 25.
- the engine output shaft speed sensor 25 is conventional in the art and is adapted to generate an electrical signal which is representative of the actual rotational speed of the output shaft 1 la of the engine 11.
- the electronic controller 20 and the engine controller 23 communicate with one another over a data bus line 26 extending therebetween.
- the electronic controller 20 and the engine controller 23 are programmed to communicate and cooperate with one another to so as to control the operation of the vehicle in a manner desired by the driver of the vehicle.
- the electronic controller 20 and the engine controller 23 are effective to control the operation of the engine 11, the clutch 12, and the transmission 13 in such a manner that the vehicle can be started and stopped solely by physical manipulation of the accelerator and brake pedals, similar to a conventional automatic transmission in a passenger car.
- the signals from the accelerator pedal position sensor 24 and the engine output shaft speed sensor 25 are available to the electronic controller 20 over the data bus line 26.
- the signals from the accelerator pedal position sensor 24 and the engine output shaft speed sensor 25 can be fed directly to the electronic controller 20.
- the engine torque commands issued by the engine controller 23 to the engine 11 are also available to the electronic controller 20 over the data bus line 26.
- the clutch actuator 16 and portions of the clutch 12 and the transmission 13 are illusfrated in detail.
- the structure and operation of the clutch actuator 16 are disclosed and illustrated in detail in co-pending application Serial No. 08/775,460, filed December 30, 1996 (owned by the assigned of this invention), the disclosure of which is incorporated herein by reference.
- the clutch actuator 16 includes an outer cylinder housing 30, a hollow cylindrical piston 31, and an inner cylinder housing 32.
- the piston 31 has at least one, and preferably a plurality, of axially forwardly projecting protrusions 3 la, each of which has a circumferentially extending groove 3 lb formed therein.
- the piston 31 is initially disposed concentrically within the outer cylinder housing 30, and the inner cylinder housing 32 is disposed concentrically within the piston 31. Then, the outer cylinder housing 30 is secured to a forwardly facing surface of a case of the transmission 13 by threaded fasteners (not illusfrated) or other means. When this is done, a forwardly facing surface 32a of the inner cylinder housing 32 abuts a complementary shaped, rearwardly facing annular surface 30a formed within the outer cylinder housing 30. At the same time, a rearwardly facing surface 30b of the outer cylinder housing 30 abuts portions of the case of the transmission 13.
- the inner cylinder housing 32 is captured between the case of the fransmission 13 and the outer cylinder housing 30 so as to be fixed in position relative thereto.
- a circumferential rim portion 3 lc of the piston 31 is received in an undercut 30c formed in the interior of the outer cylinder housing 30.
- the piston 31 is capable of limited axial movement relative to the outer cylinder housing 30 and the inner cylinder housing 32.
- the clutch 12 is a conventional pull-to-release type clutch and includes a cover 12a which is connected to a flywheel (not illustrated) which, in turn, is connected to the output shaft 1 la of the engine 11.
- the flywheel and the cover 12a are thus rotatably driven by the engine 11 of the vehicle for rotation about an axis.
- the cover 12a has a central opening formed therethrough which receives a hollow, generally cylindrical release sleeve 12b.
- the release sleeve 12b is disposed concentrically about the transmission input shaft 13 a.
- a driven disc assembly (not shown) is mounted within the clutch 12 on the forward end of the transmission input shaft 13 a for rotation therewith and for axial movement relative thereto.
- a forward end of the release sleeve 12b has an annular groove formed thereabout which receives the radially innermost ends of a plurality of clutch operating levers 12c therein.
- axial movement of the release sleeve 12b causes pivoting movement of the clutch operating levers 12c which, in turn, causes engagement and disengagement of the clutch 12 in a known manner.
- a plurality of clutch engagement springs 12d (only one of which is illustrated) reacts between the cover 12a and the forward end of the release sleeve 12b.
- the ends of the clutch engagement springs 12d are preferably supported on respective seats provided on the release sleeve 12b and the cover 12a.
- the springs 12d urge the release sleeve 12b axially forwardly (toward the left when viewing Fig. 2) toward an engaged position, wherein the components of the clutch 12 are frictionally engaged so as to cause the transmission input shaft 13a to be rotatably driven by the engine 11.
- the release sleeve 12b is moved axially rearwardly (toward the right when viewing Fig. 2) against the urging of the engagement springs 12d toward a disengaged position, the components of the clutch 12 are frictionally disengaged so as to prevent the fransmission input shaft 13a from being rotatably driven by the engine 11.
- the rearward end of the release sleeve 12b extends axially rearwardly through the central opening in the cover 12a.
- An annular release bearing 33 is disposed about the rearward end of the release sleeve 12b and is retained on one side by a snap ring 34 disposed within an annular groove.
- a retaining ring 35 is also disposed about the rearward end of the release sleeve 12b adjacent to the forward side of the release bearing 33.
- a snap ring 36 is disposed in an annular groove in the release sleeve 12b to retain the retaining ring 35 on the release sleeve 12b.
- a snap ring 37 is disposed within the groove formed in the outer surface of the retaining ring 35.
- the snap ring 37 connects the piston 31 with the retaining ring 35 such that axial movement of the piston 31 causes corresponding axial movement of the retaining ring 35, the release bearing 33, and the release sleeve 12b.
- An annular chamber 38 is defined between the outer surface of the body of the piston 31, the enlarged rim portion 31c formed at the rearward end of the piston 31, and the undercut 30c formed in the inner surface of the outer cylinder housing 30.
- the chamber 38 is sealed to form a fluid-tight chamber by sealing elements, such as 0-rings.
- a radially extending port 39 is formed through the outer cylinder housing 30. As will be explained in detail below, pressurized fluid (hydraulic or pneumatic, as desired) is supplied through the port 39 used to effect axial movement of the piston 31 in one direction relative to the outer cylinder housing 30 and the inner cylinder housing 31.
- the clutch position sensor 22 is mounted on the outer cylinder housing 30 for generating an electrical signal which is representative of the axial position of the piston 31 relative to the outer and inner cylinder housings 30 and 32. Such an electrical position signal is used by an electronic controller 20 for automatically operating the clutch actuator 16 in a manner described in detail below.
- the clutch position sensor 22 is conventional in the art.
- the port 39 communicates through a conduit 40 with an engage valve 41 and a disengage valve 42.
- the engage valve 41 communicates with a reservoir (in hydraulic systems) or the atmosphere (in pneumatic systems), while the disengage valve 42 communicates with a source of pressurized fluid 43, either hydraulic or pneumatic as desired.
- the operation of the engage valve 41 is controlled by an engage solenoid 44, while the operation of the disengage valve 42 is controlled by a disengage solenoid 45.
- the engage solenoid 44 and the disengage solenoid 45 are, in turn, connected to the electronic controller 23 so as to be selectively operated thereby.
- the clutch 12 is normally maintained in the engaged position under the influence of the engagement springs 12d.
- the engage solenoid 44 is actuated by the electronic confroller 20 to close the engage valve 41
- the disengage solenoid 45 is actuated by the electronic confroller 20 to open the disengage valve 42.
- pressurized fluid from the source 43 is supplied to the chamber 38, causing the piston 31 to move rearwardly (toward the right when viewing Fig. 2) against the urging of the engagement springs 12d.
- rearward movement of the piston 31 causes the clutch 12 to be disengaged.
- the disengage valve 42 is operated by the elecfronic confroller 20 in an on-off manner, i.e., either wide open or completely closed.
- the engage solenoid When it is desired to subsequently re-engage the clutch 12, the engage solenoid
- the engage valve 44 is actuated by the elecfronic confroller 20 to open the engage valve 41, and the disengage solenoid 45 is actuated by the elecfronic controller 20 to close the disengage valve 42.
- the chamber 38 is vented to the reservoir, causing the piston 31 to move forwardly (toward the left when viewing Fig. 2) under the influence of the engagement springs 12d.
- the engage valve 44 is operated using pulse width modulation techniques to control the engagement of the clutch 12.
- the elecfronic controller 20 varies the duty cycle of the pulse width modulation of the engage valve 41 so as to adjust the rate at which the pressurized fluid in the chamber 38 is vented to the reservoir.
- the rate of venting of the chamber 38 By adjusting the rate of venting of the chamber 38 in this manner, the speed at which the release bearing 33 is moved from the disengaged position to the engaged position can be precisely controlled. Precise control of the speed of movement of the release bearing from the disengaged position to the engaged position is important to engage the clutch 12 smoothly and avoid undesirable sudden jerking movement of the vehicle.
- the first range of movement of the release bearing 33 is from the disengaged position to a first intermediate position (referred to as the transition point).
- the transition point is selected to be relatively near, but spaced apart from, the position of the release bearing 33 at which the driven disc assembly of the clutch 12 is initially engaged by the flywheel and the pressure plate.
- the second range of movement of the release bearing 33 is from the fransition point to a second intermediate position (referred to as the kiss point).
- the kiss point is the position of the release bearing 33 at which the driven disc assembly is initially engaged by the flywheel and the pressure plate.
- the clutch 12 is disengaged until the release bearing 33 reaches the kiss point, at which point the first measurable amount of torque is fransmitted through the clutch 12 to the fransmission 13.
- the third range of movement of the release bearing 33 is from the kiss point to the engaged position.
- the engaged position is the position of the release bearing 33 at which the driven disc assembly is completely engaged by the flywheel and the pressure plate.
- the clutch 12 is gradually engaged so as to increase the amount of torque which is fransmitted through the clutch 12 to the fransmission 13 from the first measurable amount at the kiss point to the full capacity of the clutch 12 at the engaged position.
- Movement of the release bearing 33 through the first and second ranges of movement can be accomplished in any known manner.
- the initial movement of the release bearing 33 from the disengaged position to the transition point can be accomplished by pulse width modulating the engage valve 41 at a predetermined duty cycle so as to cause rapid movement of the release bearing 33 from the disengaged position to the transition point.
- the engage valve 41 may be pulse width modulated at a constant rate throughout the fransition movement of the release bearing 33.
- the engage valve 41 may be pulse width modulated at a rate which varies with the current position of the release bearing 33 relative to the fransition point so as to decelerate the release bearing 33 somewhat as it approaches the fransition point.
- the elecfronic controller 20 can be programmed to monitor the clutch position signal from the clutch position sensor 22 to deterrnine when the release bearing 33 has reached the fransition point. Regardless of the specific transition rate which is used, it is desirable that the initial transition movement of the release bearing 33 be performed as rapidly as possible because the clutch 12 is completely disengaged throughout. Therefore, no sudden and undesirable engagement of the clutch 12 will occur during this initial fransition movement of the release bearing 33.
- the approach movement of the release bearing 33 from the transition point to the kiss point can be accomplished by pulse width modulation of the engage valve 41 at a duty cycle which is initially relatively long (to initially maintain the rapid movement of the release bearing 33), but subsequently is shortened to decelerate the release bearing 33 as it approaches the kiss point.
- the clutch 12 By slowing the movement of the release bearing 33 as it approaches the kiss point, the clutch 12 will be engaged smoothly so as to prevent the engine from stalling and avoid undesirable sudden jerking movement of the vehicle.
- the elecfronic confroller 20 can be programmed to automatically alter the duty cycle of the engage valve during this approach movement of the release bearing 33 in response to sensed operating conditions.
- the elecfronic confroller 20 can be responsive to the amount of depression of the accelerator pedal from the pedal position sensor 24 for adjusting the duty cycle of the engage valve.
- any known algorithms may be used to confrol the movement of the release bearing 33 in its initial fransition movement from the disengaged position to the transition point, and in its subsequent approach movement from the fransition point to the kiss point.
- the algorithm of this invention relates to the confrol of the movement of the release bearing 33 in its engagement movement from the kiss point to the engaged position.
- the clutch 12 is gradually engaged so as to increase the amount of torque which is transmitted through the clutch 12 to the fransmission 13 from the first measurable amount at the kiss point to the full capacity of the clutch 12 at the engaged position.
- this engagement movement of the release bearing 33 it is still important to engage the clutch 12 smoothly to prevent the engine from stalling and avoid undesirable sudden jerking movement of the vehicle.
- Fig. 3 there is illusfrated a flow chart of a first embodiment of an algorithm, indicated generally at 50, for controlling the movement of the release bearing 33 in its engagement movement from the kiss point to the engaged position.
- the elecfronic controller 20 issues a command to the engine controller 23 setting a desired engine speed signal V E NG-
- the desired engine speed signal V ENG is selected to be sufficiently high such that the engine 11 is capable of overcoming the inertia of the vehicle as the clutch 12 is engaged and thereby avoid stalling during the engagement process.
- the desired engine speed signal VE NG can, therefore, vary with the specific structure of the engine 11, the fransmission 13 used in conjunction with the engine 11, and other factors.
- the second step 52 of the algorithm 50 is to determine the engagement rate of the release bearing 33 of the clutch 12.
- the engagement rate can be determined in any conventional manner in response to a number of operating conditions of the vehicle.
- the engagement rate can be selected to be a constant rate or may vary with the movement of the release bearing 33 from the kiss point to the engaged position in the manner discussed above.
- the algorithm 50 of this invention monitors the status of clutch engagement and alters the predeterrnined engagement rate under certain circumstances.
- the engage valve 41 and the disengage valve 42 are actuated (by means of the respective solenoids 44 and 45) to effect movement of the release bearing 33 of the clutch 12 according to the selected engagement rate.
- the clutch engagement process is initiated.
- the fourth step 54 of the algorithm 50 causes the elecfronic controller 20 to read the actual engine speed signal V ACT from the engine controller 23.
- the engine output shaft speed sensor 25 generates the actual engine speed signal V A c ⁇ to the engine confroller 23 which is representative of the actual rotational speed of the output shaft 1 la of the engine 11. That information is available to the electronic controller 20 from the engine controller 23 over the data bus line 26.
- the electronic confroller 20 reads the engine torque signal generated by the engine controller 23 to the engine 11. As discussed above, that information is also available to the elecfronic confroller 20 from the engine confroller 23 over the data bus line 26.
- the algorithm 60 next enters a sixth step 56 wherein a first lower engine speed threshold signal Vt is generated by the elecfronic confroller 20.
- the first lower engine speed threshold signal Vi represents an engine speed below which it is undesirable to have the engine 11 operate to avoid even approaching a stalling condition.
- the first lower engine speed threshold signal Vj is set somewhat above an engine speed at which stalling of the engine 11 is likely to occur. For example, if the desired engine speed signal V ENG is initially set at approximately 850 r.p.m., the first lower engine speed threshold signal Vt can be set at approximately 600 r.p.m. In this instance, the allowable r.p.m.
- the magnitude of the first lower engine speed threshold signal Vi varies in response to the engine torque signal generated by the engine controller 23 to the engine 11.
- the first lower engine speed threshold signal Vj may be increased somewhat in accordance with an increase in the engine torque signal. Such an increase in the engine torque signal would indicate that the engine 11 is under an increased load. It is known that the likelihood of an undesirable engine stalling condition increases with the amount of load placed on the engine 11.
- the electronic confroller 20 may increase the value of first lower engine speed threshold signal Vt and, therefore, decrease the allowable r.p.m. error in response to an increase in the actual load on the engine 11. For example, if the engine load increases, the electronic confroller 20 may increase the first lower engine speed threshold signal Vj from 600 r.p.m. to 620 r.p.m. Such an adjustment would accommodate engagement of the clutch 12, while preventing the likelihood of a stalling condition. Similarly, if the engine load decreases, the electronic confroller 20 may decrease the first lower engine speed threshold signal Vi.
- the algorithm 50 After deterrnining the magnitude of the first lower engine speed threshold signal Vi, the algorithm 50 next enters a first decision point 57 wherein the actual engine speed signal V ACT is compared with the first lower engine speed threshold signal Vi. If the actual engine speed signal V A c ⁇ is greater than the first lower engine speed threshold signal V ls then the actual speed of the engine 11 is being maintained at a normal level during the engagement process of the clutch 12. Thus, the algorithm 50 branches from the first decision point 57 to a second decision point 58 wherein it is determined whether the clutch 12 is fully engaged.
- This determination can be made by any known method, such as by comparing the rotational speed of the input shaft of the clutch 12 (the output shaft 1 la of the engine 11) with the rotational speed of the output shaft of the clutch 12 (the input shaft 13a of the fransmission 13). If the rotational speeds of the input and output shafts of the clutch 12 are substantially equal, then it can be inferred that the engagement process is substantially completed. Thus, the algorithm 50 branches from the second decision point 58 to a step 59 wherein the engage valve 41 is actuated to interrupt the gradual engagement process and immediately move the release bearing 33 from its current position to the fully engaged position. If the rotational speeds of the input and output shafts of the clutch 12 are not substantially equal, then it can be inferred that the engagement process is not yet completed. Thus, the gradual engagement process is continued, and the algorithm 50 branches from the second decision point 58 back to the second step 52. This loop of the algorithm 50 is repeated until the rotational speeds of the input and output shafts of the clutch 12 are substantially equal.
- the algorithm 50 branches from the first decision point 57 to a third decision point 60 wherein the actual engine speed signal V A c ⁇ s compared with a second lower engine speed threshold signal V 2 .
- the second lower engine speed threshold signal V 2 represents an engine speed below which the engine 11 is likely to stall.
- the second lower engine speed threshold signal V 2 is set somewhat below the first engine speed threshold signal V l5 but still above an engine speed at which stalling of the engine 11 is likely to occur.
- the second lower engine speed threshold signal V 2 can be set at approximately 500 r.p.m.
- the second lower engine speed threshold signal V is fixed at a predetermined value according to the specifications of the engine 11 and other factors, but may vary with the accelerator pedal position or other factors as desired.
- the algorithm 50 branches from the third decision 60 to a step 61 wherein the electronic confroller 20 interrupts the engagement process and holds the release bearing 33 of the clutch 12 in its current position. Then, the algorithm 50 branches back to the fourth step 54.
- the actual engine speed signal V ACT falls below the first lower engine speed threshold signal Vi but remains greater than the second lower engine speed threshold signal V 2 , further movement of the clutch release bearing 33 is prevented until the actual engine speed signal V A c ⁇ recovers to be greater than the first lower engine speed threshold signal Vi .
- the algorithm 50 branches from the third decision 60 to a step 62 wherein the engage valve 41 and the disengage valve 42 are actuated by the electronic controller 20 to immediately disengage the clutch 12.
- the algorithm 50 not only interrupts the engagement process, but further aborts the engagement of the clutch 12 and returns the release bearing 33 to the disengaged position.
- the algorithm 50 may return from the step 62 back to the fourth step 54 to attempt to re-start the engagement process by reading the actual engine speed signal V A c ⁇ and proceeding forward from that point. However, it has been found to be desirable to introduce a measure of hysteresis into the re-engagement process. To accomplish this, the algorithm 50 may next enter a step 63 wherein the actual engine speed signal V A c ⁇ is again read from the speed sensor 25. Then, the actual engine speed signal V ACT is compared with an engagement re-start speed threshold signal V 3 , as shown in a fourth decision point 64.
- the engagement re-start speed threshold signal V 3 is set to be somewhat above the first lower threshold signal Vj.
- the engagement re-start speed threshold signal V 3 can be set at approximately 750 r.p.m. This higher threshold is desirable to insure a full recovery of the actual engine speed signal V ACT following an imminent stalling condition. If the actual engine speed signal V ACT is less than or equal to the engagement re-start speed threshold signal V 3 , then the algorithm 50 branches from the fourth decision point 64 back to the step 63. This loop of the algorithm 50 continues until the actual engine speed signal V ACT is greater than the engagement re-start speed threshold signal V 3 .
- the algorithm 50 branches from the fourth decision point 64 to a step 65 wherein the magnitude of the first lower threshold signal Vj is incremented.
- the first lower threshold signal Vj is incremented to minimize the likelihood that an imminent stalling condition will occur during the re-engagement process.
- the release bearing 33 of the clutch 12 is held in its current position when the actual engine speed signal V A c ⁇ falls below the first lower engine speed threshold signal Vi but remains greater than the second lower engine speed threshold signal V 2 .
- the algorithm 50 enters the step 63 wherein the actual engine speed signal V ACT is again read from the speed sensor 25.
- the actual engine speed signal V ACT is compared with the engagement re-start speed threshold signal V 3 , as shown in a fourth decision point 64, to introduce a measure of hysteresis into the re-engagement process. If the actual engine speed signal V A c ⁇ is less than or equal to the engagement re-start speed threshold signal V 3 , then the algorithm 50 branches from the fourth decision point 64 back to the step 63. This loop of the algorithm 50 continues until the actual engine speed signal V ACT is greater than the engagement re-start speed threshold signal V 3 . When this occurs, the algorithm 50 branches from the fourth decision point 64 to a step 65 wherein the magnitude of the first lower threshold signal Vj is incremented. This step 65, which is usually desirable when re-starting the engagement process after an aborted attempt, may be omitted when re-starting the engagement process after merely holding the release bearing 33 of the clutch 12 in its current position for a period of time.
- Fig. 4 there is illustrated a flow chart of a second embodiment of an algorithm, indicated generally at 50', for controlling the movement of the release bearing 33 in its engagement movement from the kiss point to the engaged position.
- the second embodiment of the algorithm 50' is generally similar to the first embodiment of the algorithm 50 described above, and like reference numbers have been used to indicate similar steps therein.
- the electronic controller 20 reads not only the engine torque signal generated by the engine confroller 23 to the engine 11, but also the accelerator pedal position signal from the engine controller 23.
- the accelerator pedal position sensor 24 generates the accelerator pedal position signal to the engine confroller 23 which is representative of the actual position of the accelerator pedal of the vehicle.
- the magnitude of the first lower engine speed threshold signal Vi varies in response to both the engine load signal and the accelerator pedal position signal. As discussed above, the magnitude of the first lower engine speed threshold signal Vi increases with increases in the engine torque signal generated by the engine confroller 23 to the engine 11 and decreases with decreases in the engine torque signal. Additionally, the first lower engine speed threshold signal Vi may be lowered somewhat in accordance with an increase in the accelerator pedal position signal, indicating further depression of the accelerator pedal.
- the electronic confroller 20 may lower the value of first lower engine speed threshold signal Vi and, therefore, increase the allowable r.p.m. error.
- the elecfronic confroller 20 may adjust the first lower engine speed threshold signal Vi from 600 r.p.m. to 580 r.p.m. Such an adjustment would accommodate a more aggressive engagement of the clutch 12, while still preventing the likelihood of a stalling condition.
- the elecfronic confroller 20 is responsive to both the engine torque signal generated by the engine controller 23 to the engine 11 and the accelerator pedal position signal from the engine controller 23 for determining the first lower engine speed threshold signal Vi.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Automation & Control Theory (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
BR9808910-2A BR9808910A (en) | 1997-04-16 | 1998-04-15 | Method and apparatus for operating clutch on automatic mechanical transmission |
EP98918260A EP0975886A4 (en) | 1997-04-16 | 1998-04-15 | Method and apparatus for operating a clutch in an automated mechanical transmission |
AU71222/98A AU7122298A (en) | 1997-04-16 | 1998-04-15 | Method and apparatus for operating a clutch in an automated mechanical transmis sion |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US84344397A | 1997-04-16 | 1997-04-16 | |
US08/843,443 | 1997-04-16 |
Publications (3)
Publication Number | Publication Date |
---|---|
WO1998046907A2 true WO1998046907A2 (en) | 1998-10-22 |
WO1998046907A3 WO1998046907A3 (en) | 1999-02-25 |
WO1998046907A8 WO1998046907A8 (en) | 1999-04-15 |
Family
ID=25289994
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US1998/007606 WO1998046907A2 (en) | 1997-04-16 | 1998-04-15 | Method and apparatus for operating a clutch in an automated mechanical transmission |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0975886A4 (en) |
AU (1) | AU7122298A (en) |
BR (1) | BR9808910A (en) |
WO (1) | WO1998046907A2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2001017815A1 (en) * | 1999-09-03 | 2001-03-15 | Volvo Lastvagnar Ab | Drive unit for a motor vehicle and method of identifying the engagement position of an automatic clutch being part of the drive unit |
US6206803B1 (en) * | 1997-04-16 | 2001-03-27 | Tranmissiones Tsp, S.A. De C.V. | Method and apparatus for operating a clutch in an automated mechanical transmission |
EP1177932A3 (en) * | 2000-08-02 | 2006-12-06 | Toyota Jidosha Kabushiki Kaisha | Automatic start controlling apparatus of internal combustion engine and detector for detecting engagement of clutch |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4497397A (en) * | 1981-02-24 | 1985-02-05 | Automotive Products Limited | Clutch control system |
US5679099A (en) * | 1994-10-21 | 1997-10-21 | Toyota Jidosha Kabushiki Kaisha | Apparatus for controlling slip amount of motor vehicle clutch during vehicle starting |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61211536A (en) * | 1985-03-14 | 1986-09-19 | Toyota Motor Corp | Controlling method for magnetic powder type electromagnetic clutch for vehicle |
EP0352277B1 (en) * | 1987-03-26 | 1990-10-31 | ZF FRIEDRICHSHAFEN Aktiengesellschaft | Device for controlling an automatic motor vehicle clutch |
JPH0742998B2 (en) * | 1988-12-15 | 1995-05-15 | 株式会社ゼクセル | Vehicle start control device and method |
JP2576240B2 (en) * | 1989-10-19 | 1997-01-29 | トヨタ自動車株式会社 | Control device for semi-automatic transmission |
JP3572623B2 (en) * | 1992-08-31 | 2004-10-06 | 本田技研工業株式会社 | Control device for vehicle clutch |
-
1998
- 1998-04-15 WO PCT/US1998/007606 patent/WO1998046907A2/en not_active Application Discontinuation
- 1998-04-15 EP EP98918260A patent/EP0975886A4/en not_active Withdrawn
- 1998-04-15 AU AU71222/98A patent/AU7122298A/en not_active Withdrawn
- 1998-04-15 BR BR9808910-2A patent/BR9808910A/en not_active Application Discontinuation
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4497397A (en) * | 1981-02-24 | 1985-02-05 | Automotive Products Limited | Clutch control system |
US5679099A (en) * | 1994-10-21 | 1997-10-21 | Toyota Jidosha Kabushiki Kaisha | Apparatus for controlling slip amount of motor vehicle clutch during vehicle starting |
Non-Patent Citations (1)
Title |
---|
See also references of EP0975886A2 * |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6206803B1 (en) * | 1997-04-16 | 2001-03-27 | Tranmissiones Tsp, S.A. De C.V. | Method and apparatus for operating a clutch in an automated mechanical transmission |
WO2001017815A1 (en) * | 1999-09-03 | 2001-03-15 | Volvo Lastvagnar Ab | Drive unit for a motor vehicle and method of identifying the engagement position of an automatic clutch being part of the drive unit |
US6711486B1 (en) | 1999-09-03 | 2004-03-23 | Volvo Lastvagnar Ab | Drive unit for a motor vehicle and method of identifying the engagement position of an automatic clutch being part of the drive unit |
EP1177932A3 (en) * | 2000-08-02 | 2006-12-06 | Toyota Jidosha Kabushiki Kaisha | Automatic start controlling apparatus of internal combustion engine and detector for detecting engagement of clutch |
Also Published As
Publication number | Publication date |
---|---|
BR9808910A (en) | 2002-03-26 |
WO1998046907A8 (en) | 1999-04-15 |
AU7122298A (en) | 1998-11-11 |
EP0975886A2 (en) | 2000-02-02 |
WO1998046907A3 (en) | 1999-02-25 |
EP0975886A4 (en) | 2000-04-26 |
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