CN1950628B - Control device of driving device for vehicle - Google Patents
Control device of driving device for vehicle Download PDFInfo
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- CN1950628B CN1950628B CN2005800135243A CN200580013524A CN1950628B CN 1950628 B CN1950628 B CN 1950628B CN 2005800135243 A CN2005800135243 A CN 2005800135243A CN 200580013524 A CN200580013524 A CN 200580013524A CN 1950628 B CN1950628 B CN 1950628B
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H61/0437—Smoothing ratio shift by using electrical signals
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/44—Series-parallel type
- B60K6/445—Differential gearing distribution type
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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
- B60W10/02—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
- B60W20/00—Control systems specially adapted for hybrid vehicles
- B60W20/30—Control strategies involving selection of transmission gear ratio
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- General Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Control Of Transmission Device (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
Abstract
Disclosing a controller of a driving gear for a vehicle, wherein since the reduction gear ratio of a continuously variable transmission part (11) is changed so that the stepwise change of the reduction gear ratio can be suppressed by a hybrid control means (52) even if the reduction gear ratio of a stepped transmission part (20) is changed stepwise in the gear shift control of the stepped transmission part (20), the total reduction gear ratio gammaT of a transmission mechanism (10) formed based on the reduction gear ratio of the continuously variable transmission part (11) and the reduction gear ratio of the stepped transmission part (20) is continuously changed. As a result, the stepwise change of the rotating speed NE of an engine is suppressed before and after the gear shift control of the stepped transmission part (20) to suppress a shock caused by the gear shift operation. Also, the overall transmission mechanism (10) is allowed to function as the continuously variable transmission, fuel economy can be improved.
Description
Technical field
The present invention relates in general to the vehicle fitting of the modified roll mechanism that has comprised the transmission action with differential function.More specifically, relate to the technology that is used for controlling another speed ratio with respect to one of them speed ratio of modified roll mechanism and automatic transmission with hydraulic torque converter.
Background technology
Had known Vehicular drive system, it comprised the modified roll mechanism of transmission action with differential function and in the step change state exercisable automatic transmission with hydraulic torque converter, the output that this Vehicular drive system is set to the transmission of drive force source comes drive wheels.Generally speaking, the overall ratio of such driver for vehicle is confirmed by the speed ratio of these two speed-changing mechanisms.
Example as the modified roll mechanism that works transmission action with differential function; There is known drive system; It comprises the differential attachment that outputs to first electrical motor and output shaft that operationally distributes driving engine; And be arranged on second electrical motor between differential attachment and the drive wheel, and this drive system can be used as the operation of continuous control toric transmission.The example of such drive system comprises like the disclosed drive system that is used for motor vehicle driven by mixed power in patent documentation 1-6.In this drive system of hybrid power vehicle; Modified roll mechanism for example is made up of compound planet gear; And be delivered to drive wheel to the differential functional machinery of the main portion of the propulsive effort of driving engine through modified roll mechanism, and the remainder of propulsive effort electrically the circuit through therebetween be delivered to second electrical motor from first electrical motor, make modified roll mechanism play the electric controlling stepless variable speed device; The speed ratio of this electric steplessly variable transmission is electrically variable; Thus, can be under the control of control setup powered vehicle, and driving engine keeps best running state with improved fuel economy.
The overall ratio that comprises the driver for vehicle of two above-mentioned transmission mechanisms is confirmed by the speed ratio of the differential attachment with differential function and the speed ratio of automatic transmission with hydraulic torque converter.When modified roll mechanism places its stepless change state, be similar to the drive system that only comprises differential attachment, drive system is whole to play the electric controlling stepless variable speed device, and vehicle is by the engine drive that keeps optimal operational condition.
Patent documentation 1:JP-2003-301731A
Patent documentation 2:JP-2003-130203A
Patent documentation 3:JP-2003-127681A
Patent documentation 4:JP-2004-130202A
Patent documentation 5:JP-2003-127681A
Patent documentation 6:JP-11-198668A
Summary of the invention
In the gear shift course of action of the modified roll mechanism in the stepless change state; Or in the process that does not have the gear shift action; Automatic transmission with hydraulic torque converter is in the step change state during gear shift; Engine speed changes according to the variation step by step of the speed ratio of automatic transmission with hydraulic torque converter step by step, make the overall ratio that has drive system do as a whole before the gear shift action of automatic transmission with hydraulic torque converter with the possibility that does not have continuous variable afterwards.In other words, exist drive system to make the as a whole possibility that does not play toric transmission in the gear shift action of automatic transmission with hydraulic torque converter before and afterwards.Thereby drive system can suffer shifting shock, or suffers to think the influence that fuel economy that driving engine provides needed torque to cause worsens owing to failing to control engine speed along the highest fuel-economy linearity curve.
There is not to be provided with driving device at the driver for vehicle shown in the above-mentioned patent documentation 1 such as the fluid-actuated of tor-con; Make when change-speed box in the step change state during gear shift, engine speed is along with the variation of the speed ratio of change-speed box changes with the relation that becomes to be scheduled to the speed of a motor vehicle.For example, the engagement of change-speed box through controlling known fluid control friction coupling device with releasing action and gear shift with the situation that changes its speed ratio under, the delay that after the moment of gear shift action is carried out in judgement, exists the actual gear shift of change-speed box to move.At this timing period, engine speed possibly not change.Thereby change-speed box has the danger of the shift response of deterioration.For example, when change-speed box based on trampling accelerator pedal by order when carrying out shift-down action, engine speed may not produce the quick response to the tread-on quantity of accelerator pedal, causes existing the possibility of engine producing output delay (delay of increase begins).
In view of above-mentioned background technology is carried out the present invention.Thereby; First purpose of the present invention is to provide a kind of control setup that is used for driver for vehicle; This control setup is included in the modified roll mechanism that can work in the stepless change state; With the change-speed box that in the step change state, can work, and allow the minimizing that changes step by step of engine speed in the gear shift course of action of change-speed box in the step change state.Second purpose of the present invention provides the control setup of driver for vehicle; Comprise the modified roll mechanism of the speed-changing mechanism that plays a part to have differential function and the automatic transmission with hydraulic torque converter that in the step change state, can work; This control setup allows the quick variation of engine speed; With when automatic transmission with hydraulic torque converter in the step change state during gear shift, the improved shift response of automatic transmission with hydraulic torque converter.
According to first form of the present invention; Provide a kind of and be used for the control setup of (a) driver for vehicle; Comprise toric transmission partial sum change-speed box part; Toric transmission partly comprises modified roll mechanism, and modified roll mechanism has first element that is connected to driving engine, be connected to second element of first electrical motor and be connected to the element of drive disk assembly, and toric transmission partly comprises second electrical motor that further comprises in the drive path that is arranged between drive disk assembly and the driving wheel of vehicle; Toric transmission partly plays a part electric steplessly variable transmission; Change-speed box partly constitutes the part of drive path, and control setup is characterised in that and comprises: (b) stepless change control setup, but this stepless change control setup place of working in the variable speed control process of change-speed box part; Be used for synchronously carrying out the variable speed control of change-speed box part, make the speed ratio that is limited toric transmission partial sum change-speed box part change continuously with the variable speed control of change-speed box part.
In above-mentioned control setup; The stepless change control setup can be worked in the change-speed box that changes the step by step variable speed control process partly to speed ratio; Be used for synchronously carrying out the gear shift control of toric transmission part with the variable speed control of change-speed box part; The feasible speed ratio that is limited toric transmission partial sum change-speed box part (promptly; The overall ratio that limits the speed ratio of the speed ratio of toric transmission part and change-speed box part) changes continuously, that is, make owing to the speed ratio that causes variable quantity is step by step moved in change-speed box gear shift partly.Thereby reduce before change-speed box gear shift action partly and the variation step by step of engine speed afterwards, reduced the shifting shock of change-speed box part.Further, but drive system plays a part toric transmission in the place of working as a whole, the feasible fuel economy that improves vehicle.
According to second form of the present invention; Provide a kind of and be used for the control setup of (a) driver for vehicle; Comprise toric transmission partial sum change-speed box part; Toric transmission partly is arranged on and is used for driving engine output is delivered to the drive path of the drive wheel of vehicle, and plays a part toric transmission, and change-speed box partly constitutes the part of drive path and is connected to the toric transmission part; Control setup is characterised in that and comprises: (b) stepless change control setup; The stepless change control setup can be worked in the variable speed control process of change-speed box part, is used for synchronously carrying out with the said variable speed control of said change-speed box part the variable speed control of said toric transmission part, makes the speed ratio that is partly limited the said change-speed box of said toric transmission partial sum change continuously.
In above-mentioned control setup; The stepless change control setup can be worked in the change-speed box that changes the step by step variable speed control process partly to speed ratio; Be used for synchronously carrying out the variable speed control of toric transmission part with the variable speed control of change-speed box part; Make the speed ratio that is limited toric transmission partial sum change-speed box part change continuously, that is, make because the speed ratio that causes variable quantity is step by step moved in the gear shift of change-speed box part.Thereby reduce before change-speed box gear shift action partly and the variation step by step of engine speed afterwards, reduced the shifting shock of change-speed box part.Further, but drive system plays a part toric transmission in the place of working as a whole, the feasible fuel economy that improves vehicle.
According to of the present invention first or second form, change-speed box partly is that a grade automatic transmission with hydraulic torque converter is arranged.In this form of the present invention, when the gear shift of change-speed box part, change step by step the speed ratio and the overall ratio that change-speed box speed ratio partly limits of toric transmission part.In this case, overall ratio can be faster than when overall ratio changes continuously, changing.Thereby actuating device can operationally play a part toric transmission as a whole under the control of stepless change control setup, make the vehicular drive torque to change reposefully, and speed ratio can change at high speed step by step and change the vehicular drive torque.
In any one the 4th form of the present invention according to first to the 3rd form; But the variable speed control of stepless change control setup and change-speed box part synchronously changes the speed ratio of toric transmission part, the feasible variable quantity that reduces the speed ratio that is partly limited toric transmission partial sum change-speed box with the direction place of working that changes in the opposite direction with change-speed box speed ratio partly.In this form of the present invention, reduce before change-speed box gear shift action partly and the variable quantity of engine speed afterwards, further reduced shifting shock.
In any one the 5th form of the present invention according to first to the 4th form, but the variable speed control of toric transmission part is carried out in stepless change control setup place of working in the inertia phase that the input speed of the change-speed box part of the gear shift action of change-speed box part changes.In this form of the present invention, the variable speed control of toric transmission part is synchronously carried out by the variable speed control of stepless change control setup and change-speed box part.
In any one the 6th form of the present invention according to first to the 5th form; Control setup further comprises the torque minimizing control setup that is used to reduce change-speed box input torque partly, and torque reduces control setup and in the variable speed control process of change-speed box part, reduces input torque.In this form of the present invention; Torque reduces control setup and reduces change-speed box part input torque, makes to reduce corresponding to owing in the gear shift course of action, partly be the torque of the inertia torque that produces of the velocity variations of the change-speed box rotating element partly of form with step change transmission.Thereby reduced shifting shock.For example, torque reduces control setup and reduces input torque through the torque of minimizing driving engine or the torque of second electrical motor.
According to the 7th form of the present invention; Provide a kind of and be used for the control setup of (a) driver for vehicle; Comprise toric transmission partial sum step change transmission part; Toric transmission partly comprises modified roll mechanism; Modified roll mechanism has first element that is connected to driving engine, be connected to second element of first electrical motor and be connected to the element of drive disk assembly, and toric transmission partly comprises second electrical motor that further comprises in the drive path that is arranged between drive disk assembly and the driving wheel of vehicle, and toric transmission partly plays a part electric steplessly variable transmission; Step change transmission partly constitutes the part of drive path; And play a part to have a grade automatic transmission with hydraulic torque converter, control setup is characterised in that and comprises: (b) stepless change control setup, but stepless change control setup place of working in the variable speed control process of step change transmission part; Be used for synchronously carrying out the variable speed control of toric transmission part, make the speed ratio of toric transmission part change with the direction that changes in the opposite direction with change-speed box speed ratio partly with the variable speed control of step change transmission part.
In above-mentioned control setup; The stepless change control setup can be worked in the step change transmission that changes the step by step variable speed control process partly to speed ratio; Be used to change the speed ratio of toric transmission part, to reduce variable quantity step by step, the feasible overall ratio that is limited the speed ratio and the step change transmission speed ratio partly of toric transmission part changes continuously; That is, make because the speed ratio that causes variable quantity is step by step moved in the gear shift of change-speed box part.Thereby reduce before step change transmission gear shift action partly and the variation step by step of engine speed afterwards, reduced the shifting shock of step change transmission part.Further, but drive system plays a part toric transmission in the place of working as a whole, the feasible fuel economy that improves vehicle.
According to the 8th form of the present invention; Provide a kind of and be used for the control setup of (a) driver for vehicle; Comprise toric transmission partial sum step change transmission part; Toric transmission partly is arranged on the drive wheel drive path that is used for driving engine output is delivered to vehicle; And play a part toric transmission, step change transmission partly constitutes the part of drive path, plays a part to have grade automatic transmission with hydraulic torque converter and is connected to the toric transmission part; Control setup is characterised in that and comprises: (b) stepless change control setup; The stepless change control setup can be worked in the variable speed control process of step change transmission part, is used for synchronously carrying out with the variable speed control of step change transmission part the variable speed control of toric transmission part, makes the speed ratio of toric transmission part change with the direction that changes in the opposite direction with step change transmission speed ratio partly.
In above-mentioned control setup; The stepless change control setup can be worked in the step change transmission that changes the step by step variable speed control process partly to speed ratio; Be used to change the speed ratio of toric transmission part, to reduce variable quantity step by step, the feasible overall ratio that is limited the speed ratio and the step change transmission speed ratio partly of toric transmission part changes continuously; That is, make because the speed ratio that causes variable quantity is step by step moved in the gear shift of change-speed box part.Thereby reduce before step change transmission gear shift action partly and the variation step by step of engine speed afterwards, reduced the shifting shock of step change transmission part.Further, but drive system plays a part toric transmission in the place of working as a whole, the feasible fuel economy that improves vehicle.
The 9th form of the present invention of the 7th or the 8th form according to the present invention, but the variable speed control of toric transmission part is carried out in stepless change control setup place of working in the inertia phase of the input speed variation of the step change transmission part of the gear shift action of step change transmission part.The piston control of toric transmission part is synchronously carried out through the variable speed control of stepless change control setup and step change transmission part.
According to the present invention's the tenth form any in the 7th to the 9th form; Control setup further comprises the torque minimizing control setup that is used to reduce change-speed box input torque partly, and torque reduces control setup and in the variable speed control process of change-speed box part, reduces input torque.In this form of the present invention; Torque reduces control setup and reduces step change transmission part input torque; Make and the torque that reduces the inertia torque that produces corresponding to velocity variations reduce the torque of the inertia torque that produces corresponding to velocity variations owing to the rotating element partly of toric transmission in the gear shift course of action owing to the rotating element partly of step change transmission in the gear shift course of action.Thereby reduced shifting shock.For example, torque reduces control setup and reduces input torque through the torque of minimizing driving engine or the torque of second electrical motor.
The 11 form of the present invention of any one form in the 7th to the tenth form according to the present invention; But stepless change control setup place of working changes toric transmission speed ratio partly in the direction relative with the change direction of step change transmission speed ratio partly, to reduce the ratio change amount that is partly limited toric transmission partial sum step change transmission.In this form of the present invention, reduce before step change transmission gear shift action partly and the variable quantity of engine speed afterwards, further reduced shifting shock.
According to the 12 form of the present invention; A kind of control setup that is used for driver for vehicle is provided; Comprise toric transmission partial sum step change transmission part; Toric transmission partly is arranged on and is used for driving engine output is delivered to the drive wheel drive path of vehicle, and plays a part toric transmission, and step change transmission partly constitutes the part of drive path; Play a part to have grade automatic transmission with hydraulic torque converter and be connected to the toric transmission part; Control setup is characterised in that and comprises: (a) engine speed control setup, in the variable speed control of step change transmission part, can work, and be used for controlling the speed of driving engine through the electric stepless change action of control toric transmission part.
At the above-mentioned control setup that is used for drive system that comprises the toric transmission part that plays the electric steplessly variable transmission effect; The engine speed control setup is worked in the variable speed control process of step change transmission part; Come through utilizing the speed of toric transmission part as the function control driving engine of electric steplessly variable transmission, that is, and through utilizing the differential function of modified roll mechanism; Make that fast speed changes engine speed with improved response; And the zero hour no matter step change transmission gear shift is partly moved, because variable speed control and engine speed control are accomplished simultaneously, step change transmission variable speed control is partly accomplished fast.For example, as the partial response of level change-speed box and during change into lower gear in the trampling operation of accelerator pedal, engine speed accelerator pedal trample operation after improve apace, make driving engine export (power) and improve apace.Further, because change into lower gear control is accomplished with engine speed control simultaneously, the change into lower gear action of step change transmission part is accomplished fast.
The 13 form of the present invention according to the 12 form; The engine speed control setup is through utilizing the speed of motor control driving engine; Make the speed of driving engine equal, make that the speed of driving engine equals the target engine speed value when the gear shift action of step change transmission part is accomplished.In this form of the present invention, engine speed is with improved response controollable, and the no matter variation of engine speed in the gear shift course of action of step change transmission part.
According to the 14 form of the present invention of the 12 or the 13 form, based on the rate of change of the operational ton of accelerator pedal, the rate of change of the speed of engine speed control setup control driving engine.In this form of the present invention, the needs of vehicle operators are reflected on the engine speed fully, make the durability of vehicle be improved.
According to any one the 15 form of the present invention in the 12 to the 14 form; Modified roll mechanism comprises differential shifter, and differential shifter does not operationally switch the toric transmission part as the differential state and the toric transmission part of electric steplessly variable transmission work in the toric transmission part between the non-differential state as electric steplessly variable transmission work.In this form of the present invention; The toric transmission part not only can be operated the effect as electric steplessly variable transmission; But also switch to toric transmission part not as the non-differential state of electric steplessly variable transmission work through differential state switching device; That is, toric transmission is partly set up the state in mechanical drive path.
According to the 16 form of the present invention; A kind of control setup that is used for driver for vehicle is provided; Comprise toric transmission partial sum step change transmission part; Toric transmission partly comprises modified roll mechanism, and modified roll mechanism operationally is assigned to first electrical motor and drive disk assembly with the output of driving engine, and toric transmission partly comprises second electrical motor that further comprises in the drive path that is arranged between drive disk assembly and the driving wheel of vehicle; Toric transmission partly plays a part electric steplessly variable transmission; Step change transmission partly constitutes the part of drive path, plays a part to have a grade automatic transmission with hydraulic torque converter, and control setup is characterised in that and comprises: (a) differential state switching device; Differential shifter is arranged in the modified roll mechanism, and operationally the toric transmission part is not switched between the non-differential state as electric steplessly variable transmission work as the differential state and the toric transmission part of electric steplessly variable transmission work in the toric transmission part; (b) engine speed control setup; The engine speed control setup can be worked in the variable speed control of step change transmission part; Be used for controlling with a method in two engine speed control methods the speed of driving engine, when the variable speed control of step change transmission part begins, rely on power splitting mechanism whether to place differential state or non-differential state method for selecting in the variable speed control process of step change transmission part.
Above-mentioned control setup is provided for control-driven system, and wherein modified roll mechanism is not being switched the toric transmission part as the differential state and the toric transmission part of electric steplessly variable transmission work in the toric transmission part by differential state switching device between the non-differential state as electric steplessly variable transmission work.In this control setup; The engine speed control setup is worked in the variable speed control process of step change transmission part in the variable speed control process of step change transmission part with the speed of a method control driving engine in two engine speed control methods, when the variable speed control of step change transmission part begins, relies on power splitting mechanism whether to place differential state or selected this method of non-differential state.Thereby engine speed changes with improved response fast.For example; When modified roll mechanism places differential state; The engine speed control setup in the variable speed control process of step change transmission part through being used to through utilizing the toric transmission part (promptly as the speed of the function control driving engine of electric steplessly variable transmission; Through utilizing the differential function of modified roll mechanism), make that fast speed changes engine speed with improved response, and the zero hour no matter step change transmission gear shift is partly moved.
The 17 form of the present invention according to the 16 form; If modified roll mechanism is placed in differential state when the variable speed control of step change transmission part begins, then the engine speed control setup is controlled the speed of driving engine through the electric stepless gear shift action of control toric transmission part.In this form of the present invention, fast speed changes engine speed with improved response, and the zero hour no matter step change transmission gear shift is partly moved.Because variable speed control and engine speed control are accomplished simultaneously, the variable speed control of step change transmission part is accomplished fast.For example, as the partial response of level change-speed box and during change into lower gear in the trampling operation of accelerator pedal, engine speed accelerator pedal trample operation after improve apace, make driving engine export (power) and improve apace.Further, because change into lower gear control is accomplished with engine speed control simultaneously, the change into lower gear action of step change transmission part is accomplished fast.
In the 18 form of the present invention according to the 16 or the 17 form; If modified roll mechanism is placed in non-differential state when the variable speed control of step change transmission part begins; Then the engine speed control setup because the variation of the speed of the driving engine that the gear shift action of step change transmission part causes, is controlled the said speed of said driving engine through utilizing.In this form of the present invention, fast speed changes engine speed with improved response in the gear shift course of action of step change transmission part, and modified roll mechanism is not switched to differential state from non-differential state.
In the 19 form of the present invention according to the 18 form; If modified roll mechanism is placed in non-differential state when the variable speed control of step change transmission part begins; Then through utilizing the speed of motor control driving engine, modified roll mechanism remains on non-differential state to the engine speed control setup simultaneously in the variable speed control process of step change transmission part.In this form of the present invention, fast speed changes engine speed with improved response in the gear shift course of action of step change transmission part, and modified roll mechanism is not switched to differential state from non-differential state.And through utilizing the motor control engine speed, make when the gear shift action of step change transmission part is accomplished, to equal target engine speed with further improved response.
According to the 20 form of the present invention; A kind of control setup that is used for driver for vehicle is provided; Comprise toric transmission partial sum step change transmission part; Toric transmission partly comprises modified roll mechanism, and modified roll mechanism operationally is assigned to first electrical motor and drive disk assembly with the output of driving engine, and toric transmission partly comprises second electrical motor that further comprises in the drive path that is arranged between drive disk assembly and the driving wheel of vehicle; Toric transmission partly plays a part electric steplessly variable transmission; Step change transmission partly constitutes the part of drive path, plays a part to have a grade automatic transmission with hydraulic torque converter, and control setup is characterised in that and comprises: (a) differential state switching device; Differential shifter is arranged in the modified roll mechanism, and operationally the toric transmission part is not switched between the non-differential state as electric steplessly variable transmission work as the differential state and the toric transmission part of electric steplessly variable transmission work in the toric transmission part; (b) engine speed control setup; The engine speed control setup can be worked in the variable speed control of step change transmission part; Be used for controlling with a method in two engine speed control methods the speed of driving engine, when the variable speed control of step change transmission part begins, rely on power splitting mechanism whether to place differential state or non-differential state method for selecting in the variable speed control process of step change transmission part.
Above-mentioned control setup is provided for control-driven system, and wherein modified roll mechanism is not being switched the toric transmission part as the differential state and the said toric transmission part of electric steplessly variable transmission work in the toric transmission part by differential state switching device between the non-differential state as electric steplessly variable transmission work.In this control setup; The engine speed control setup works the speed of the method control driving engine of the said variable speed control of in the variable speed control process of step change transmission part, passing through change step change transmission part in the variable speed control process of step change transmission part, whether the dependence modified roll mechanism places differential state or non-differential state to select this method when the variable speed control of step change transmission part begins.Thereby engine speed changes with improved response fast.For example; When modified roll mechanism places differential state; The engine speed control setup in the variable speed control process of step change transmission part through being used to through utilizing the toric transmission part (promptly as the speed of the function control driving engine of electric steplessly variable transmission; Through utilizing the differential function of modified roll mechanism), make that fast speed changes engine speed with improved response, and the zero hour no matter step change transmission gear shift is partly moved.
The present invention's the 21 form according to above the 20 form; If modified roll mechanism is placed in differential state when the variable speed control of step change transmission part begins; Then the engine speed control setup is controlled the speed of driving engine through the electric stepless gear shift action of control toric transmission part, and carries out the variable speed control of step change transmission part.In this form of the present invention, fast speed changes engine speed with improved response, and the zero hour no matter step change transmission gear shift is partly moved.Because variable speed control and engine speed control are accomplished simultaneously, the variable speed control of step change transmission part is accomplished fast.For example, as the partial response of level change-speed box and during change into lower gear in the trampling operation of accelerator pedal, engine speed accelerator pedal trample operation after improve apace, make driving engine export (power) and improve apace.Further, because change into lower gear control is accomplished with engine speed control simultaneously, the change into lower gear action of step change transmission part is accomplished fast.
The present invention's the 22 form according to the 20 or the 21 form; If modified roll mechanism is placed in non-differential state when the variable speed control of step change transmission part begins; Then the engine speed control setup is carried out the variable speed control of step change transmission part; Make the speed of driving engine through utilizing because the variation of the speed of the driving engine that the gear shift action of step change transmission part causes changes, step change transmission partly remains on non-differential state simultaneously.In this form of the present invention, fast speed changes engine speed with improved response in the gear shift course of action of step change transmission part, and modified roll mechanism is not switched to differential state from non-differential state.
Preferred the 23 form of the present invention according to arbitrary form in the 15 to the 22 form; Wherein, Modified roll mechanism has first element that is connected to driving engine, be connected to second element of first electrical motor and be connected to the element of drive disk assembly; But differential state switching device place of working allows first relative to each other to rotate to element; Be used to set up differential state, and allow first to element as one unit rotation or keep second element fixed, be used to set up non-differential state.In this form of the present invention, modified roll mechanism can switch between differential state and non-differential state.
The 24 form of the present invention according to the 23 form; Differential state switching device comprises power-transfer clutch and/or drg; Power-transfer clutch operationally is connected to each other first in the element any two; Be used to make first to rotate as one unit to element, drg operationally is fixed to second element and is used to process the fixed fixed parts of second element.In this form of the present invention, modified roll mechanism can easily switch between differential state and non-differential state.
Preferably, step change transmission partly comprises and operationally the output of driving engine is assigned to the modified roll mechanism of first electrical motor and drive disk assembly, and is arranged on second electrical motor in the drive path between said drive disk assembly and the driving wheel of vehicle.In this case, the speed ratio of drive system can change and comes powered vehicle, keeps driving engine at optimal operational condition simultaneously, makes fuel economy be improved.
Preferably, modified roll mechanism is provided with differential state switching device, operationally with modified roll mechanism at the differential state that can obtain differential function with can not obtain to switch between the lock-out state of differential function.In this case; Modified roll mechanism by differential state switching device at the differential state that can obtain differential function with can not obtain to switch between the non-differential state of differential function; Make drive system not only have because the advantage that the fuel economy of the variable function of the speed ratio of change-speed box electricity is improved; And, have owing to can mechanically transmit the advantage of high driving efficiency of function of the gear type driving device of vehicle drive force.For example, when the low or medium output of going of the low or moderate velocity for vehicle is gone, driving engine is when normal output area, and modified roll mechanism places infinite variable speed state, makes the fuel economy of vehicle be improved.On the other hand; When vehicle is in high-speed travel state; Modified roll mechanism places the output of driving engine mainly to be delivered to the lock-out state of drive wheel through the mechanical power bang path; Make fuel economy owing to the minimizing of the loss of the transformation of energy between machinery and the electric energy is improved, this degradation of energy can take place when the change-speed box work that changes with the mode of electricity as its speed ratio when modified roll mechanism.When vehicle is in high output motoring condition, the change-speed box work that modified roll mechanism changes with the mode of electricity as its speed ratio.Thereby; Have only when vehicle during at the low or medium output motoring condition of low or moderate velocity motoring condition; The change-speed box work that modified roll mechanism changes with the mode of electricity as its speed ratio; Make the electric energy maximum that produces by electrical motor (that is, the electric energy maximum that must transmit from electrical motor) can access minimizing, make needed size that can make electrical motor and the needed minimized in size that comprises the drive system of electrical motor.
Preferably; Toric transmission part at the differential state that can obtain differential function with can not obtain to switch between the lock-out state of differential function, makes that the toric transmission part is that feasible stepless change state and the action of electric stepless change are to switch between the feasible step change state in electric stepless change action by differential state switching device.In this way, the switching of toric transmission part between stepless change state and step change state.
Preferably, modified roll mechanism has first element that is connected to driving engine, is connected to second element of first electrical motor and is connected to the element of drive disk assembly.Differential state switching device is set to allow first relative to each other to rotate to element, setting up differential state, and allow first to element as the one unit rotation or keep second element fixed, to set up lock-out state.In this case, modified roll mechanism switches between differential state and lock-out state.
Preferably; Differential state switching device comprises power-transfer clutch and drg; But this power-transfer clutch place of working is connected to each other first in the element any two so that first rotate as one unit to element, and drg operationally is fixed to second element and is used to process the fixed fixed parts of second element.In this case, modified roll mechanism can easily switch between differential state and non-differential state.
Preferably; Releasing clutch and drg place differential state with modified roll mechanism; Wherein, first relative to each other rotates to element, and modified roll mechanism is worked as the electric controlled differential device; Engaging clutch is 1 change-speed box work with the tolerance actuation mechanism as having speed ratio, or engage brakes with the tolerance actuation mechanism as having the speedup change-speed box work that is lower than 1 speed ratio.In this case, modified roll mechanism switches between differential state and lock-out state, and as the change-speed box work with single gear, this change-speed box has single fixed speed ratio or a plurality of gear with each fixed speed ratio.
Preferably, modified roll mechanism is a compound planet gear, and first element is the planetary wheel carrier of compound planet gear, and second element is the sun wheel of compound planet gear, and element is the gear ring of compound planet gear.In this case, the axial dimension of modified roll mechanism can access minimizing, and modified roll mechanism simply is made up of a planetary gear apparatus.
Preferably, compound planet gear is a grade pinion type.In this case, the axial dimension of modified roll mechanism can access minimizing, and modified roll mechanism simply is made up of a planetary gear apparatus.
Preferably, the overall ratio of driver for vehicle is limited the speed ratio of above-mentioned toric transmission part and the speed ratio of above-mentioned change-speed box part.In this case, vehicle drive force can obtain on the scope of the broad of overall ratio through the speed ratio that utilizes change-speed box part, makes the efficient of electric stepless change control of toric transmission be further enhanced.
Preferably, the overall ratio of driver for vehicle is limited the speed ratio of above-mentioned toric transmission part and the speed ratio of above-mentioned step change transmission part.In this case, vehicle drive force can obtain on the scope of the broad of overall ratio through the speed ratio that utilizes step change transmission part, makes the efficient of electric stepless change control of toric transmission be further enhanced.
The toric transmission part places the toric transmission of stepless change state partly to constitute by the step change transmission partial sum, and the step change transmission part places the toric transmission that can not obtain electric stepless change action partly to constitute by the step change transmission partial sum.
Preferably, modified roll mechanism when engaging above-mentioned power-transfer clutch as have speed ratio be 1 change-speed box work and when engaging above-mentioned drg as the speed increasing mechanism work that is lower than 1 speed ratio.In this case, modified roll mechanism is as the change-speed box work with single gear, and this change-speed box has single fixed speed ratio or a plurality of gear with each fixed speed ratio.
Preferably, modified roll mechanism is a compound planet gear, and first element is the planetary wheel carrier of compound planet gear, and second element is the sun wheel of compound planet gear, and element is the gear ring of compound planet gear.In this case, the axial dimension of modified roll mechanism can access minimizing, and modified roll mechanism simply is made up of a planetary gear apparatus.
Preferably, compound planet gear is a grade pinion type.In this case, the axial dimension of modified roll mechanism can access minimizing, and modified roll mechanism simply is made up of a planetary gear apparatus.
Preferably, when the speed of a motor vehicle surpassed the higher limit that the high-speed travel state of confirming vehicle is provided, modified roll mechanism placed non-differential state.In this case; When actual vehicle speed has surpassed higher limit; The output of driving engine mainly is delivered to drive wheel through the mechanical power bang path; Make fuel economy owing to the minimizing of the loss of the transformation of energy between machinery and the electric energy is improved, this degradation of energy can take place when the change-speed box work that changes with the mode of electricity as its speed ratio when modified roll mechanism.The higher limit of the speed of a motor vehicle is to judge that vehicle is whether in the predetermined value of high-speed travel state.
Preferably, when the value of closing the vehicle propulsive effort surpassed the height output motoring condition higher limit that definite vehicle is provided, modified roll mechanism placed non-differential state.In this case; When actual vehicle speed has surpassed higher limit; The output of driving engine mainly is delivered to drive wheel through the mechanical power bang path; Make fuel economy owing to the minimizing of the loss of the transformation of energy between machinery and the electric energy is improved, this degradation of energy can take place when the change-speed box work that changes with the mode of electricity as its speed ratio when modified roll mechanism.The higher limit of the speed of a motor vehicle is to judge that vehicle is whether in the predetermined value of high-speed travel state.
Preferably, but when detecting the place of working stepless speed changing mechanism worsened as the fault of any electric-controlled parts such as electrical motor of electric steplessly variable transmission work or function modified roll mechanism place non-differential state.In this case, modified roll mechanism places transmit mode usually, and switches to non-transmit mode, in case above-mentioned fault or function deterioration, to allow going of vehicle.
Description of drawings
Fig. 1 is the scheme drawing of layout that the drive system of motor vehicle driven by mixed power according to an embodiment of the invention is shown;
Fig. 2 is the chart of gear shift action and the relation of the various combination of the serviceability of the fluid control friction coupling device that carries out each gear shift work of the drive system of hybrid power vehicle that can wherein work in one at selected stepless change state and step change state of the embodiment of presentation graphs 1;
Fig. 3 is illustrated in the different gears of drive system the alignment chart of the relative rotational of the drive system of hybrid power vehicle of in the step change state, working among Fig. 1 embodiment;
Fig. 4 is the view of input and output signal of electronic control package of the drive system of the expression embodiment that provides control chart 1;
Fig. 5 is the functional block diagram of major control function that the electronic control package of Fig. 4 is shown;
Fig. 6 is in the same two-dimensional coordinate system that controlled variable was limited that is form moving velocity and output torque with vehicle; The example of the speed change border line chart of being stored of the gear shift action that is used for definite step change transmission part is shown; Be used to switch the example of the handoff boundary line chart of being stored of the speed change state of speed-changing mechanism; And be used in the example of switching between engine drive pattern and the motor drive mode of the drive force source handoff boundary line chart of being stored of limited boundary line between engine drive zone and direct motor drive zone, make the view that these figure are relative to each other;
Fig. 7 illustrates and limits the highest fuel-economy linearity curve of driving engine, and explanation in the stepless change state driving engine operation (being represented by dotted lines) and in the step change state view of the example of the fuel oil consumption figure of the difference between the operation (with single-point line expression) of driving engine;
Fig. 8 illustrates the view that is limited to the relation of being stored of boundary line between stepless change zone and the step change zone, and its relation is used for shining upon qualification by the dotted line among Fig. 6 represented stepless change and the regional boundary line of step change;
Fig. 9 is the result of expression as the shift-up action of step change transmission part device, the view of the example that engine speed changes;
Figure 10 is that expression is provided with shifter bar and operates the view of the example of the transmission system of selecting a position in a plurality of shift position;
Figure 11 is the control operation of the electronic control package of presentation graphs 5, i.e. the diagram of circuit of the variable speed control operation of toric transmission part in the variable speed control process of step change transmission part;
Figure 12 is illustrated in the stepless change state of speed-changing mechanism when level change-speed box part upgrades third gear from second gear time diagram of the control operation of Figure 11;
Figure 13 is in another embodiment of the present invention corresponding to the functional block diagram of the functional block diagram of Fig. 5, shows the major control function of the electronic control package of Fig. 4;
Figure 14 is the diagram of circuit corresponding to the diagram of circuit of Figure 11, shows the control operation of the electronic control package of Figure 13, i.e. the variable speed control operation of toric transmission part in the variable speed control process of step change transmission part;
Figure 15 is the time diagram corresponding to the time diagram of Figure 12, is illustrated in the stepless change state of speed-changing mechanism when level change-speed box part upgrades third gear from second gear control operation shown in the diagram of circuit of Figure 14;
Figure 16 is the time diagram corresponding to the time diagram of Figure 12, is illustrated in the stepless change state of speed-changing mechanism when level change-speed box part lowers category second gear from third gear, in the control operation shown in the diagram of circuit of Figure 14;
Figure 17 is the time diagram corresponding to the time diagram of Figure 14, is illustrated in the stepless change state of speed-changing mechanism when level change-speed box part upgrades third gear from second gear control operation shown in the diagram of circuit of Figure 14;
Figure 18 is the time diagram corresponding to the time diagram of Figure 16, is illustrated in the stepless change state of speed-changing mechanism when level change-speed box part lowers category second gear from third gear the control operation shown in the diagram of circuit of Figure 14;
Figure 19 is the scheme drawing corresponding to the scheme drawing of Fig. 1, shows the layout of the drive system of motor vehicle driven by mixed power according to another embodiment of the present invention;
Figure 20 is the table corresponding to the table of Fig. 2, the gear shift action of exercisable drive system of hybrid power vehicle and the fluid control that carries out each gear shift action relation of various combination of serviceability of coupling device that rubs in the selected state in stepless change and step change process of expression Figure 19;
Figure 21 is the alignment chart corresponding to the alignment chart of Fig. 3, is illustrated in the different gears relative rotation speed of the rotating element of the drive system of hybrid power vehicle of the Figure 19 in the step change state;
Figure 22 is a transparent view, shows to be operated the example that the seesaw switch of selecting speed change state is the manual exercisable speed change state selecting arrangement of form by the user;
Figure 23 is a functional block diagram, and the major control function of the electronic control package of Fig. 4 according to another embodiment of the present invention is shown;
Figure 24 is a diagram of circuit, and the control operation of the electronic control package of Figure 23 is shown, that is, and and the control operation of engine speed in the variable speed control process of step change transmission part;
Figure 25 is a time diagram, expression when in the stepless change state in response to the operation of trampling of accelerator pedal, speed-changing mechanism is during from fourth speed potential drop shelves to second gear, the control operation shown in the diagram of circuit of Figure 24;
Figure 26 is a time diagram, expression when in the step change state in response to the operation of trampling of accelerator pedal, speed-changing mechanism is during from fourth speed potential drop shelves to second gear, the control operation shown in the diagram of circuit of Figure 24;
Figure 27 is a time diagram, and expression is worked as in the stepless change state to be increased in response to the speed of a motor vehicle, when speed-changing mechanism upgrades the fourth speed position from third gear, and the control operation shown in the diagram of circuit of Figure 24;
Figure 28 is a time diagram, and expression is worked as in the step change state to be increased in response to the speed of a motor vehicle, when speed-changing mechanism upgrades fourth speed from third gear, and the control operation shown in the diagram of circuit of Figure 24.
The specific embodiment
With reference to accompanying drawing, will describe the preferred embodiment of the invention in detail.
Fig. 1 is the scheme drawing of speed-changing mechanism 10 of the part of the explanation drive system that constitutes motor vehicle driven by mixed power, and wherein this drive system is controlled by control setup according to an embodiment of the invention.In Fig. 1, speed-changing mechanism 10 comprises: with input shaft 14 is that form is arranged on the input turning unit on the common axis of the change speed gear box that plays the fixed parts effect 12 that is attached to car body; Direct connection or absorb the toric transmission part 11 that damper (vibration damping device) is connected to input shaft 14 indirectly via unshowned pulsation; Be arranged between toric transmission part 11 and the driving wheel of vehicle 38 (shown in Fig. 5) and level or multi-step transmissions part 20 arranged via what drive disk assembly 18 (transmission shaft) was connected in series to toric transmission part 11 and drive wheel 38; And be the output turning unit that form is connected to step change transmission part 20 with output shaft 22.Input shaft 14, toric transmission part 11, step change transmission part 20 and output shaft 22 are connected in series mutually.As shown in Figure 5; This speed-changing mechanism 10 is applicable to horizontal FR vehicle (engine behind front wheel rear wheel drive vehicle); And being arranged on combustion engine 8 is that drive force source and the drive wheel of form is between 38, so that vehicle drive force is delivered to drive wheel to 38 from driving engine 8 through compensating gear 36 (final speed reduction gearing) and a pair of axle drive shaft.Driving engine 8 can be engine petrol or diesel motor, and plays direct connection or absorb the vehicle drive force source that damper is connected to input shaft 14 indirectly via pulsation.Notice that the latter half of speed-changing mechanism 10 constitutes with respect to its axis symmetry, it omits in Fig. 1.So same among the embodiment that is described below.In this speed-changing mechanism 10, driving engine 8 and toric transmission part 11 mutual direct connections.This direct connection means that driving engine 8 is connected mutually with change-speed box part 11, and does not arrange the hydraulic control driving device such as tor-con or fluid couplers betwixt, connects mutually but can absorb damper through above-mentioned pulsation.
The major part that power splitting mechanism 16 comprises has: have single pinion type first compound planet gear 24, the switch clutch C0 of for example about 0.418 transmitting ratio ρ 1 and switch drg B1.First compound planet gear 24 has the rotating element of being made up of following: the first sun wheel S1, the first planetary wheel P1; Support the first planetary wheel P1, make the planetary wheel P1 that wins around its axis and around the rotatable first planetary wheel carrier CA1 of the axis of the first sun wheel S 1; With through the first planetary wheel P1 and the first sun wheel S1 ingear, the first gear ring R1.The number of teeth of the first sun wheel S1 and the first gear ring R1 represented by ZS1 and ZR1 respectively, and above-mentioned transmitting ratio ρ 1 is represented by ZS1/ZR1.
In power splitting mechanism 16, the first planetary wheel carrier CA1 is connected to input shaft 14, promptly is connected to driving engine 8, the first sun wheel S1 and is connected to the first electrical motor M1, and the first gear ring R1 is connected to drive disk assembly 18 simultaneously.Switch drg B0 and be arranged between the first sun wheel S1 and the change speed gear box 12, switch clutch C0 is arranged between the first sun wheel S1 and the first planetary wheel carrier CA1.When switch clutch C0 and drg B0 discharge; Power splitting mechanism 16 places differential state; Three elements in first compound planet gear 24 that wherein is made up of the first sun wheel S1, the first planetary wheel carrier CA1 and the first gear ring R1 can relative to each other rotate; To carry out differential function, make the output of driving engine 8 be assigned to the first electrical motor M1 and drive disk assembly 18, thus; The part of the output of driving engine 8 is used to drive the first electrical motor M1 to produce electric energy, and this electric energy is stored or is used for driving the second electrical motor M2.Thereby power splitting mechanism 16 places stepless change state (the CVT state of electric foundation), and wherein the rotating speed of drive disk assembly 18 is continuous variables; And regardless of the rotating speed of driving engine 8; That is, place differential state, wherein the speed ratio γ 0 of power splitting mechanism 16 (rotating speed of the rotating speed/drive disk assembly 18 of input shaft 14) changes to maxim γ 0max from minimum value γ 0min continuously; Promptly; Place under the stepless change state, wherein power splitting mechanism 16 plays a part electric steplessly variable transmission, and its speed ratio γ 0 changes to maxim γ 0max from minimum value γ 0min continuously.
When switch clutch C0 or drg B0 engagement when power splitting mechanism 16 places the stepless change state simultaneously, mechanism 16 enters into the non-differential state that lock-out state maybe can not obtain differential function.Particularly; When switch clutch C0 meshes; The first sun wheel S1 and the first planetary wheel carrier CA1 link together; Three rotating elements of first compound planet gear 24 that makes power splitting mechanism 16 be placed in one to be made up of sun wheel S1, the first planetary wheel carrier CA1 and the first gear ring R1 can be used as the lock-out state that one unit rotates, and promptly place the non-differential state that can not obtain differential function, make toric transmission part 11 also place non-differential state.In this non-differential state; The rotating speed of the rotating speed of driving engine 8 and drive disk assembly 18 is equal to each other; Make toric transmission part 11 (power splitting mechanism 16) place fixed speed ratio speed change state or step change state, wherein the change-speed box that equals 1 fixed speed ratio γ 0 works to have in mechanism 16.
When switching drg B0 replacement switch clutch C0 joint; The first sun wheel S1 is fixed to change speed gear box 12; Make power splitting mechanism 16 place the non-rotary lock-out state of the first sun wheel S1; That is, place the second non-differential state that can not obtain differential function, make toric transmission part 11 also place non-differential state.Because the rotating speed of the first gear ring R1 is higher than the rotating speed of the first planetary wheel carrier CA1; Toric transmission part 11 places fixed speed ratio speed change state or step change state, and wherein toric transmission part 11 (power splitting mechanism 16) works to have the speed transmission that adds less than 1 for example about 0.7 fixed speed ratio γ 0.
Thereby; Friction coupling device with switch clutch C0 and drg B0 form plays differential shifter; It can be operated with at differential state (promptly; Unlock state) and non-differential state (promptly; Lock-out state) between, promptly (wherein toric transmission part 11 is as the electric steplessly variable transmission operation that can carry out the stepless change operation, and wherein the speed ratio of change-speed box part 11 keeps fixing at stepless change state (wherein toric transmission part 11 (power splitting mechanism 16) is operationally as the electric steplessly variable transmission of its speed ratio continuous variable) and lock-out state; Promptly; Fixed speed ratio speed change state (non-differential state), wherein change-speed box part 11 can operate with as the single gear with a speed ratio with have the change-speed box of a plurality of gears of corresponding speed ratio, promptly; The fixed speed ratio speed change state, wherein change-speed box part 11 as can operate with as single gear with a speed ratio and have the change-speed box of a plurality of gears of corresponding speed ratio) between optionally switch toric transmission part 11 change-speed box part change-speed box part change-speed box part change-speed box part change-speed box parts.
Step change transmission part 20 comprises single pinion type second compound planet gear 26, single pinion type the third line star gear cluster 28 and single pinion type fourth line star gear cluster 30.Second compound planet gear 26 comprises: the second sun wheel S2; The second planetary wheel P2; Support the second planetary wheel P2 and make that the second planetary wheel P2 can be around its axis and around the second planetary wheel carrier CA2 of the axis of second sun wheel S2 rotation; And with the second sun wheel S2 through the second planetary wheel P2 ingear, the second gear ring R2.Second compound planet gear 26 has for example about 0.562 transmitting ratio ρ 2.The third line star gear cluster 28 has: the 3rd sun gear S3; The third line star gear P3; Support the third line star gear P3 and make that the third line star can be around its axis and around the third line star wheel frame CA3 of the axis rotation of the 3rd sun wheel S3; And with the 3rd sun wheel S3 through the third line star gear P3 ingear the 3rd gear ring R3.For example, the third line star gear cluster 28 has about 0.425 transmitting ratio ρ 3.Fourth line star gear cluster 30 has: the 4th sun gear S4; Fourth line star gear P4; Support fourth line star gear P4 and make that the fourth line star can be around its axis and around the fourth line star wheel frame CA4 of the axis rotation of the 4th sun wheel S4; And with the 4th sun wheel S4 through fourth line star gear P4 ingear the 4th gear ring R4.For example, fourth line star gear cluster 30 has about 0.421 transmitting ratio ρ 4.The number of teeth of the second sun wheel S2, the second gear ring R2, the 3rd sun wheel S3, the 3rd gear ring R3, the 4th sun wheel S4 and the 4th gear ring R4 is expressed as ZS2, ZR2, ZS3, ZR3, ZS4 and ZR4 respectively, and above-mentioned transmitting ratio ρ 2, ρ 3 and ρ 4 are expressed as ZS2/ZR2, ZS3/ZR3 and ZS4/ZR4 respectively.
In step change transmission part 20, the second sun wheel S2 and the 3rd sun wheel S3 are fixed as a device each other integratedly, are connected to drive disk assembly 18 selectively through second clutch C2, and are fixed to change speed gear box 12 selectively through the first drg B1.The second planetary wheel carrier CA2 is fixed to change speed gear box 12 selectively through the second drg B2, and the 4th gear ring R4 is fixed to change speed gear box 12 selectively through the 3rd drg B3.The above-mentioned second gear ring R2, the third line star wheel frame CA3 and fourth line star wheel frame CA4 are fixed to one another and be fixed to output shaft 22 by integratedly.The 3rd gear ring R3 and the 4th sun wheel S4 are fixed to one another integratedly and be connected to drive disk assembly 18 selectively through first clutch C1.
Above-mentioned switch clutch C0, first clutch C1, second clutch C2, switching drg B0, the first drg B1, the second drg B2 and the 3rd drg B3 are the hydraulic operation friction coupling devices that is used in traditional automatic transmission for vehicles.Each of these friction coupling devices is made up of the wet multiple disc clutch that comprises a plurality of friction discs; These friction discs through hydraulic actuator or external contracting drum brake each other pressurized against; External contracting drum brake comprises going barrel, and the coiling going barrel outer peripheral face and at one end by hydraulic actuator fastening a band or two bands.Among power-transfer clutch C0-C2 and the drg B0-B3 each is all optionally meshed so that two parts are linked together, and each power-transfer clutch or drg insert between these two parts.
As shown in the table of Fig. 2; By in the transmission mechanism 10 of above-mentioned structure, the engagement action of the corresponding combination of first gear (first velocity location) in the 5th gear (the 5th velocity location), reverse gear (back transmission position) and the Neutral Position the friction coupling device through being selected from above-mentioned switch clutch C0, first clutch C1, second clutch C2, switching drg B0, the first drg B1, the second drg B2 and the 3rd drg B3 is optionally set up.These positions have into corresponding speed ratio γ (the drive shaft speed N that geometric series changes
IN/ output shaft speed N
OUT).Particularly; Note; Power splitting mechanism 16 is provided with switch clutch C0 and drg B0, makes as stated, and toric transmission part 11 can be selectively placed on the fixed speed ratio speed change state (wherein through the engagement of switch clutch C0 or switching drg B0; Change-speed box part 11 keeps fixing change-speed box to operate as its speed ratio) and stepless change state (wherein, change-speed box part 11 can be operated as toric transmission).Thereby in this speed-changing mechanism 10, step change transmission constitutes by change-speed box part 20 and through the toric transmission part 11 that the switch clutch C0 or the engagement of switching drg B0 are placed in the fixed speed ratio speed change state.In addition, electric steplessly variable transmission is by change-speed box part 20 and do not have switch clutch C0 or switch the engagement of drg B0 and the toric transmission part 11 that is placed in the electrodeless variable-speed state constitutes.In other words, speed-changing mechanism 10 wherein one switches to the step change state through engagement switch clutch C0 and switching drg B0, and switches to the stepless change state through discharging switch clutch C0 and drg B0.Toric transmission part 11 also is considered to be the change-speed box that between step change state and stepless change state, switches.
As it be shown in fig. 2; Under the situation of transmission mechanism 10 as step change transmission; For example; Have and for example be about 3.357 and set up through the engagement action of switch clutch C0, first clutch C1 and the 3rd drg B3 the most at a high speed, have second gear that for example is about 2.180 speed ratio γ 2 that is lower than speed ratio γ 1 and set up through the engagement action of switch clutch C0, first clutch C1 and the second drg B2 than first gear of γ 1.In addition, having the third gear that for example is about 1.424 speed ratio γ 3 that is lower than speed ratio γ 2 sets up through the engagement action of switch clutch C0, first clutch C1 and the first drg B1.Having the fourth speed position that for example is about 1.000 speed ratio γ 4 that is lower than speed ratio γ 3 sets up through the engagement action of switch clutch C0, first clutch C1 and second clutch C2.Having the 5th gear that for example is about 0.705 speed ratio γ 5 that is lower than speed ratio γ 4 sets up through the engagement action of switching first clutch C1, second clutch C2 and switching drg B0.In addition, having the reverse gear that for example is about 3.209 speed ratio γ R that is clipped between speed ratio γ 1 and the speed ratio γ 2 sets up through the engagement action of second clutch C2 and the 3rd drg B3.Neutral Position N sets up through only meshing switch clutch C0.
On the other hand; Under the situation of speed-changing mechanism 10 as toric transmission; The switch clutch C0 that in Fig. 2, representes with switch drg B0 and all be released, make toric transmission part 11 play toric transmission, and the change-speed box part 20 that is connected in series to toric transmission part 11 plays step change transmission; Thus; Being delivered to and placing first speed that rotatablely moves (that is, the rotating speed of drive disk assembly 18) to the change-speed box part 20 of a gear of fourth speed position is continuous variable, makes continuous variable in the scope that the speed ratio of the drive system when change-speed box part 20 places of these gears is being scheduled to.Thereby; The speed ratio γ T that confirms by toric transmission part 11 and step change transmission part 20 (that is the overall ratio γ T of the change-speed box part speed-changing mechanism of, confirming by the speed ratio γ of the speed ratio γ 0 of toric transmission part 11 and step change transmission part 20 10 (below be called " overall ratio ")) continuous variable on adjacent gear.
The alignment chart of Fig. 3 is illustrated in by the relation between the rotating speed of the rotating element in each gear of the toric transmission part 11 that plays the toric transmission part or the first change-speed box partial action and the speed-changing mechanism 10 of the step change transmission part that plays the step change transmission part (automatic transmission with hydraulic torque converter part) or the second change-speed box partial action 20 formations by straight line.The alignment chart of Fig. 3 is two-dimentional rectangular coordinate system, and wherein, the transmitting ratio ρ of compound planet gear 24,26,28,30 representes along horizontal shaft, and the relative rotation speed of rotating element is represented along vertical axis.Article three, the following horizon in the horizon, promptly horizon X1 representes 0 rotating speed, and the top horizon in three horizons, promptly horizon X2 representes 1.0 rotating speed, promptly is connected to the running velocity N of the driving engine 8 of input shaft 14
EHorizon XG representes the rotating speed of drive disk assembly 18.
The relative rotation speed of the 3rd rotating element (element) RE3 of first rotating element (first element) RE1 and the first gear ring R1 form of representing second rotating element (second element) RE2, the first planetary wheel carrier CA1 form of the first sun wheel S1 form corresponding to three perpendicular line Y1, Y2 and Y3 of the power splitting mechanism 16 of toric transmission part 11 respectively.Distance among perpendicular line Y1, Y2 and the Y3 between the adjacent perpendicular line is confirmed by the transmitting ratio ρ 1 of first compound planet gear 24.That is, the distance between perpendicular line Y1 and the Y2 corresponds to " 1 ", and the distance between perpendicular line Y2 and the Y3 is corresponding to transmitting ratio ρ 1.In addition, represent the 6th rotating element (the hexa-atomic) RE6 of the 5th rotating element (the 5th element) RE5, the 4th gear ring R4 form of the 4th rotating element (quaternary part) RE4, the second planetary wheel carrier CA2 form of the second and the 3rd fixing integratedly each other sun wheel S2, S3 form, the fixing integratedly second gear ring R2 and the 3rd and the 7th rotating element (the 7th element) RE7 of fourth line star wheel frame CA3, CA4 form and the relative rotation speed of the 8th rotating element (the 8th element) RE8 of fixing the 3rd gear ring R3 of one and the 4th sun wheel S4 form each other each other respectively corresponding to five perpendicular line Y4, Y5, Y6, Y7 and Y8 of change-speed box part 20.Distance between the adjacent perpendicular line is confirmed by second, third and fourth line star gear cluster 26,28 and 30 transmitting ratio ρ 2, ρ 3 and ρ 4.In the relation between the perpendicular line of alignment chart, the sun wheel and the distance between the planetary wheel carrier of each compound planet gear correspond to " 1 ", and the planetary wheel carrier of each compound planet gear and the distance between the gear ring correspond to transmitting ratio ρ.In toric transmission part 11, the distance between perpendicular line Y1 and the Y2 corresponds to " 1 ", and the distance between perpendicular line Y2 and the Y3 corresponds to transmitting ratio ρ.In step change transmission part 30; Each second, third and the sun wheel and the distance between the planetary wheel carrier of fourth line star gear cluster 26,28,30 correspond to " 1 ", and each compound planet gear 26,28,30 planetary wheel carrier and the distance between the gear ring correspond to transmitting ratio ρ.
Alignment chart with reference to Fig. 3; The power splitting mechanism 11 of speed-changing mechanism 10 (toric transmission part 11) is provided so that; The first rotating element RE1 of first compound planet gear 24 (the first planetary wheel carrier CA1) is fixed to input shaft 14 (driving engine 8) integratedly; And optionally be connected to the second rotating element RE2 (the first sun wheel S1) through switch clutch C0; And this second rotating element RE2 is fixed to the first electrical motor M1; And optionally be fixed to change speed gear box 12 through switching drg B0, and the 3rd rotating element RE3 (the first gear ring R1) is fixed to the drive disk assembly 18 and the second electrical motor M2, makes rotatablely moving of input shaft 14 transmit (input) to step change transmission part 20 through drive disk assembly 18.Relation between the rotating speed of the rotating speed of the first sun wheel S1 and the first gear ring R1 representes that by the bevelled straight line L0 representes, L0 is through the intersection point between line Y2 and the X2.
For example; When the releasing action of speed-changing mechanism 10 through switch clutch C0 and drg B0 places the stepless change state; Obtain raising or reducing by the antagonistic force that the operation of the first electrical motor M1 that produces electric energy produces through control by the rotating speed of the first represented sun wheel S1 of the intersection point between line L0 and the perpendicular line Y1, make rotating speed by the first represented sun wheel R1 of the intersection point between line L0 and the perpendicular line Y3 be lowered or raise.When switch clutch C0 is meshed; The first sun wheel S1 is connected mutually with the first planetary wheel carrier CA1; Power splitting mechanism 16 is placed in one above-mentioned three rotating elements as the first non-differential state that the one unit rotation is arranged; Make line L0 align, make drive disk assembly 18 to equal engine speed N with horizon X2
ESpeed rotation.On the other hand; When drg B0 is switched in engagement, stop the rotation of the first sun wheel S1, and power splitting mechanism 16 is placed in the second non-differential state; And play speed increasing mechanism; Make line L0 have a down dip at state shown in Figure 3, thus, the rotating speed of the first gear ring R1 (rotation of the drive disk assembly of promptly being represented by the intersection point between line L0 and the Y3 18) is higher than the speed N of driving engine
E, and be passed to change-speed box part 20.
In step change transmission part 20; The 4th rotating element RE4 optionally is connected to drive disk assembly 18 through second clutch C2; And optionally be fixed to change speed gear box 12 through the first drg B1; And the 5th rotating element RE5 optionally is fixed to change speed gear box 12 through the second drg B2, and the 6th rotating element RE6 optionally is fixed to change speed gear box 12 through the 3rd drg B3 simultaneously.The 7th rotating element RE7 is fixed to output shaft 22, and the 8th rotating element RE8 optionally is connected to drive disk assembly 18 through first clutch C1 simultaneously.
When first clutch C1 and the 3rd drg B3 were meshed, step change transmission part 20 placed first gear.The rotating speed of the output shaft 22 in first gear is fixed to perpendicular line Y7 and the intersection point between the angled straight lines L1 of rotating speed of the 7th rotating element RE7 of output shaft 22 to be represented by expression, the perpendicular line Y8 and the intersection point between the horizon X2 of the rotating speed of angled straight lines L1 through representing the 8th rotating element RE8 and perpendicular line Y6 and the intersection point between the horizon X1 of representing the rotating speed of the 6th rotating element RE6.Similarly, the intersection point between the perpendicular line Y7 of the angled straight lines L2 that confirmed by these engagement action of the rotating speed of the output shaft 22 in second gear set up of the engagement action through the first clutch C1 and the second drg B2 and the rotating speed of the 7th rotating element RE7 that representes to be fixed to output shaft 22 is represented.Intersection point between the perpendicular line Y7 of the angled straight lines L3 that the rotating speed of the output shaft 22 in the third gear that the engagement action through the first clutch C1 and the first drg B1 is set up is confirmed by these engagement action and the rotating speed of the 7th rotating element RE7 that representes to be fixed to output shaft 22 is represented.Intersection point between the perpendicular line Y7 of the horizontal linear L4 that the rotating speed of the output shaft 22 in the fourth speed position that the engagement action through the first clutch C1 and the second drg B2 is set up is confirmed by these engagement action and the rotating speed of the 7th rotating element RE7 that representes to be fixed to output shaft 22 is represented.Switch clutch C0 is placed in first to the 5th gear of engagement therein, the 8th rotating element RE8 utilize the propulsive effort that receives from toric transmission part 11 (that is, from power splitting mechanism 16) with engine speed N
EIdentical speed rotation.When switching drg B0 and replace switch clutch C0 to be meshed, the 8th rotating element RE8 utilizes the propulsive effort that receives from power splitting mechanism 16 to be higher than engine speed N
ESpeed rotation.Through first clutch C1, second clutch C2 and the intersection point between the perpendicular line Y7 of the horizontal linear L5 that confirms by these engagement action of the rotating speed that switches the output shaft 22 in the 5th gear that the engagement action of drg B0 sets up and the rotating speed of the 7th rotating element RE7 that representes to be fixed to output shaft 22 represent.
Fig. 4 illustrates signal that is received by the electronic control package that is provided for controlling speed-changing mechanism 10 40 and the signal that produces from electronic control package 40.This electronic control package 40 comprises the so-called microcomputer that comprises CPU, ROM, RAM and I/O interface; And be set to when utilizing the temporary transient data storage function of ROM, come processing signals according to the program that is stored among the ROM; Carrying out the hybrid power drive controlling of driving engine 8 with electrical motor M1 and M2, and execution is such as the drive controlling to the variable speed control of change-speed box part 20.
Electronic control package 40 is set to from receiving various signals at various sensors shown in Fig. 4 and switch, such as: the signal of expression engine cooling water temperature TEMPw; The selected control position P of expression shifter bar
SHSignal; The running velocity N of expression driving engine 8
ESignal; The signal of selected group the value that drives forwards the position of expression speed-changing mechanism 10; The signal of expression M pattern (motor drive mode); The signal of expression A/C mode of operation; Expression is corresponding to the rotational speed N of output shaft 22
OUTThe signal of speed V; The signal of the temperature of the work machine oil of expression step change transmission part 20; The signal of the mode of operation of expression side brake; The signal of the mode of operation of expression foot-operated brake; The signal of expression catalyst temperature; Operational ton (aperture) A of expression accelerator pedal
CCSignal; The signal of expression cam angle degree; The signal of snowfield drive pattern is selected in expression; The signal of expression longitudinal direction of car accekeration; The signal of the drive pattern of automatic cruising is selected in expression; The signal of expression vehicle weight; The signal of the speed of expression driving wheel of vehicle; Expression provides the signal of mode of operation that toric transmission part 11 (power splitting mechanism 16) is placed the step change switch of fixed speed ratio speed change state (non-differential state) (wherein, speed-changing mechanism 10 plays step change transmission); Expression provides the signal of mode of operation that toric transmission part 11 is placed the stepless change switch of stepless change state (differential state) (wherein, speed-changing mechanism 10 plays toric transmission); The rotational speed N of representing the first electrical motor M1
M1(below be called " the first electromotor velocity N
M1") signal; And the rotational speed N of representing the second electrical motor M2
M2(below be called " the second electromotor velocity N
M2") signal.
Electronic control package 40 also is configured to produce such as following various signals: drive electronic throttle actuator 94 and be used for the control throttle angle
THThe signal of aperture; Control is fed to the signal of the fuel supply amount of driving engine 8 by fuel injection system 96; Regulate the signal of supercharger pressure; The signal of operation electric air conditioner; Be used for signal by the timing of ignition of ignition device 98 control driving engines 8; The signal of operating motor M1 and M2; The signal of the operation that operation expression shifter bar is selected and the shift range indicating device of shift pattern; Operation is used to represent the signal of the transmitting ratio indicating device of transmitting ratio; Operation is used to represent the signal of the snowfield mode indicator of snowfield model selection, and operation A BS actuator is used for the signal of the ANTI LOCK of wheel; Operation is used to represent the signal to the M mode indicator of the selection of M pattern; Operation comprises the hydraulic actuator that the fluid control friction coupling device of controlling toric transmission part 11 and step change transmission part 20 is provided, the signal that is combined in the valve of the electromagnetic control in the hydraulic control unit 42 (shown in Fig. 5); Operation is with the signal of the electric oil pump of the hydraulic pressure source that acts on hydraulic control unit 42; Drive the signal of electric heater and the signal that is applied to the cruising control computing machine.
Fig. 5 is the functional block diagram of Fig. 4, is used to explain the major control function of electronic control package 40.Whether the gear shift action that is set to judge step change transmission part 20 at the step change control setup 54 shown in Fig. 5 should take place, and, judges the position that change-speed box part 20 should gear shift that is.Output torque T based on speed V and step change transmission part 20
OUTThe vehicle condition of form, and make above-mentioned judgement according to the speed change border line chart (variable speed control figure or relation) that is stored in the memory storage 56 and representes by the solid line among Fig. 5 and by the shift-down boundary line of the line of the single-point among Fig. 5 expression.Step change control setup 54 produces the order (shift command) that will be applied to hydraulic control unit 42; Come optionally to mesh and discharge fluid control friction coupling device (except switch clutch C0 and drg B0), be used for setting up determined gear according to the table of Fig. 2.
Hybrid power control setup 52 plays the stepless change control setup; And be set to control driving engine 8 in opereating specification work efficiently; Hybrid power control setup 52 is also controlled the first and second electrical motor M1, M2; Make and place the stepless change state (promptly at speed-changing mechanism 10; Place differential state in toric transmission part 11) in, optimize the propulsive effort that produces by driving engine 8 and the second electrical motor M2 and by the ratio of the first electrical motor M1, to be used for controlling speed ratio γ 0 change-speed box part thus as the toric transmission part 11 of electric steplessly variable transmission work at its antagonistic force that produces in as the electrical generator working process.For example, hybrid power control setup 52 is based on the operational ton A of the accelerator pedal of exporting as the required vehicle of operator
CCAnd Vehicle Speed calculates target (required) the vehicle output under current vehicle moving velocity V, and based on the target vehicle output of being calculated and need calculate vehicle target by the electric energy generated that the first electrical motor M1 produces and always export.Hybrid power control setup 52 is when considering transmission loss, acting on the load on each device of vehicle, the assist torque of the second electrical motor M2 etc., and the target output of calculation engine 8 is always exported with the vehicle target that obtains to be calculated.The speed N of hybrid power control setup 52 control driving engines 8
EWith torque T
E, make to obtain target engine output of being calculated and the electric energy generated that produces by the first electrical motor M1.
Hybrid power control setup 52 is set to carry out hybrid power control in the current selected gear of considering step change transmission part 20, the change-speed box part is thus with the drivability of raising vehicle and the fuel economy of driving engine 8.In hybrid power control, toric transmission part 11 has been controlled to the effect of electric controlling stepless variable speed device, optimizes the engine speed N of effective operation of coordinating driving engine 8
EThe rotating speed of the drive disk assembly of confirming with speed V and by the selected gears of change-speed box part 20 18.That is, hybrid power control setup 52 is confirmed the expected value of the overall ratio γ T of change-speed box part 10, makes driving engine 8 according to the highest fuel-economy linearity curve (fuel economy figure or the relation) work of being stored.The expected value of the overall ratio γ T of change-speed box part body 10 allows motor torque T
EWith speed N
EBe Controlled makes driving engine 8 provide and obtains the required output (vehicle target is always exported or required vehicle drive force) of target vehicle output.The experiment of the highest fuel economy curve negotiating obtains, and makes required work efficiency and the highest fuel economy that satisfies driving engine 8, and by engine speed N
EThe axle and motor torque T
EThe two-dimensional coordinate system of axis limit in be defined.The speed ratio γ 0 of hybrid power control setup 52 control toric transmission parts 11 makes overall ratio γ T can be controlled in the predetermined scope (for example, between 13 and 0.5).
In hybrid power control, hybrid power control setup 52 control inverters 58 make the electric energy that is produced by the first electrical motor M1 be fed to the electrical storage device 60 and the second electrical motor M2 through inverter 58.Promptly; The main portion of the propulsive effort that is produced by driving engine 8 mechanically is delivered to drive disk assembly 18; The remainder of propulsive effort is consumed to convert this part to electric energy by the first electrical motor M1 simultaneously; This electric energy is fed to the second electrical motor M2 through inverter 58, makes the second electrical motor M2 utilize the electric energy work of being supplied, and produces the mechanical energy that will be passed to drive disk assembly 18.Thereby drive system is provided with circuit, and through this circuit, the electric energy that a part produced of the propulsive effort through conversion engine 8 is converted into mechanical energy.
Especially, when the variable speed operation of level change-speed box part 20 was controlled by step change control setup 54, with afterwards, the overall ratio γ T of speed-changing mechanism 10 changed step by step before the speed ratio of step change transmission part 20 changes step by step.When overall ratio γ T step by step, when promptly noncontinuity changed, driving torque can be than changing when overall ratio γ T changes continuously more quickly, but have shifting shock or owing to fail the highest fuel economy curve controlled engine speed N in edge
EAnd the possibility that the fuel economy that causes worsens.
In view of above-mentioned possibility; Hybrid power control setup 52 is set to synchronously control with the variable speed operation of step change transmission part 20 variable speed operation of toric transmission part 11, makes the speed ratio of toric transmission part 11 change with the direction relative with the direction of step change transmission part 20 ratio change.In other words; The variable speed control of hybrid power control setup 52 and step change transmission part 20 is synchronously carried out the variable speed control of toric transmission part 11, makes the overall ratio γ T of change-speed box part 20 change continuously before with afterwards in the gear shift action of step change transmission part 20.For example; Hybrid power control setup 52 is set to synchronously carry out with step change transmission part 20 variable speed control of toric transmission part 11; Make change-speed box part 11 speed ratio with the direction that changes in the opposite direction step by step of the speed ratio of change-speed box part 20 on change the variable quantity step by step of the speed ratio of change-speed box part 20, the change-speed box part with the overall ratio γ T that stops speed-changing mechanism 10 before the gear shift action of step change transmission part 20 with transient changing afterwards.
Describe in another way; When driving engine 8 is operably connected to step change mechanism; Driving engine 8 operation that generally line is indicated like the single-point among Fig. 7; When driving engine 8 was operably connected to toric transmission, driving engine 8 was along the highest fuel-economy linearity curve of in Fig. 7, indicating or along the curve motion that compares near the highest fuel-economy linearity curve.Thereby, when driving engine 8 is connected to toric transmission, be used to obtain the motor torque T of required vehicular drive torque (propulsive effort)
ECan be than being connected to step change transmission when driving engine 8 more near the engine speed N of the highest fuel-economy linearity curve
EThe following execution.Thereby the fuel economy of toric transmission is improved with respect to step change transmission.Given this; Hybrid power control setup 52 is set to control the speed ratio γ 0 of toric transmission part 11; Make driving engine 8 along the highest fuel economy curve motion of representing by the dotted line among Fig. 7, to prevent the deterioration of the fuel economy when the speed ratio of level change-speed box part 20 changes step by step.
Like above description, the variable speed control of hybrid power control setup 52 and step change transmission part 20 is synchronously carried out the variable speed control of toric transmission part 11,, carries out the synchronous variable speed control of change-speed box part 11 that is.When process response time after the moment that take place is moved in the gear shift of step change control setup 54 definite step change transmission parts 20, the synchronous variable speed control of toric transmission part 11 starts.This response time is from the above-mentioned input speed that regularly is carved into change-speed box part 20 really (promptly; The rotating speed of drive disk assembly 18 (the second electrical motor M2)) owing to the engagement of the friction coupling device that is fit to or the moment that changes of releasing action; That is, got into the moment of so-called " inertia phase " that the rotating speed of drive disk assembly 18 wherein changes in the gear shift course of action of change-speed box part 20 to change-speed box part 20.Response time can obtain through experiment, and is stored in the memory device, or hybrid power control setup 52 starts the synchronous variable speed control of toric transmission part 11 can be set to the actual change when the speed that detects drive disk assembly 18 time.The synchronous variable speed control of toric transmission part 11 finished in the moment when the inertia phase in the process of moving in the gear shift of change-speed box part 20 finishes.The synchro control time up to this finish time can obtain through experiment; And be stored in the memory device; Or hybrid power control setup 52 can be set to when the actual change of the speed of drive disk assembly 18 has become zero, finish the synchronous variable speed control of change-speed box part 11.Thereby; When step change transmission part 20 is in the inertia phase in its gearshift procedure; Hybrid power control setup 52 is carried out the above-mentioned variable speed control of toric transmission part 11; Change-speed box partly makes synchronous variable speed control continue the predetermined amount of time that is obtained by experiment, or the actual change of the speed that is produced up to drive disk assembly 18 has become zero.
Hybrid power control setup 52 comprises the engine output controller that is used to control driving engine 8; To pass through separately or to combine ground control throttle actuator with opening and closing ETV Electronic Throttle Valve 94; And control gets into the fuel injection time and the emitted dose of the fuel injection system 96 of driving engine 8; And/or the firing unit point of ignition of ignition device 98, needed output is provided.For example, 52 basic setups of hybrid power control setup are the operational ton A based on accelerator pedal
CCAnd according to the operational ton A of flow regulating valve
CCWith angle
THBetween the (not shown) that concerns of predetermined storage come the control throttle actuator, make angle
THAlong with operational ton A
CCIncrease and increase.
Hybrid power control setup 52 can be set up motor drive mode, and wherein, vehicle is driven by electrical motor M2 through the electric CVT function of utilizing toric transmission part 11, and need not consider whether driving engine 8 is in non-operating state or idling mode.Solid line among Fig. 6 is represented to be defined for and between driving engine 8 and electrical motor (for example, the second electrical motor M2), is switched the engine drive zone and the regional boundary line of direct motor drive that is used to start with the vehicle drive force source of powered vehicle (below be called " drive force source ").In other words, vehicular drive pattern switching between " the engine drive pattern " in the engine drive zone that starts through driving engine 8 corresponding to vehicle wherein and drives and the what is called " motor drive mode " of coming the drive electric motor drive area corresponding to vehicle wherein through the second electrical motor M2 that is used as drive force source as drive force source.The predetermined storage relation that the boundary line of presentation graphs 6 (solid line A) is used between engine drive pattern and motor drive mode, switching is at controlled variable and output torque T by the speed V form
OUTDrive force source in the two-dimensional coordinate system that the drive-force-related value of form limits is switched the example of figure (drive force source figure).This drive force source is switched figure and together is stored in the memory storage 56 with the speed change border of in Fig. 6, being represented by solid line and single-point line line chart (speed change figure).Memory storage 56 plays speed change figure memory storage and drive force source figure memory storage.
Hybrid power control setup 52 is confirmed vehicle conditions whether in direct motor drive zone or engine drive zone, and sets up motor drive mode or engine drive pattern.Be somebody's turn to do based on the vehicle condition of representing by speed V and needed torque T, and carry out above-mentioned definite according to the drive force source switching figure of Fig. 6.As understanding, as output torque T from Fig. 6
OUTWhen being in the relatively low relatively low scope of engine efficiency wherein (, as motor torque T
EWhen being in relatively low scope), or when speed V is in relatively low scope (, when vehicle load is relatively low), generally set up motor drive mode through hybrid power control setup 52.Thereby vehicle starts in motor drive mode usually, rather than in the engine drive pattern, starts.Vehicle condition when starting vehicle is when being switched outside the direct motor drive zone of scheming to limit, because required output torque T the drive force source of Fig. 6
OUTWith motor torque T
EBecause of the operation of accelerator pedal increases, so vehicle can start in the engine drive pattern.
In order to reduce the sticking of brakes of driving engine 8 under non-operating state, and improve the fuel economy in the motor drive mode, because the differential function of toric transmission part 11, hybrid power control setup 52 is set to keep on demand engine speed N
EBe zero or be roughly zero, that is, for example carry out its electric CVT functions (differential function) the electrical motor Be Controlled of winning is rotated freely, so have negative velocity N through control change-speed box part 11
M1So-called " torque auxiliary " of auxiliary engine 8 is through will be from the supply of electrical energy of the first electrical motor M1 or electrical storage device 60 to the second electrical motor M2, and making the second electrical motor M2 can operate driving torque is delivered to drive wheel 38 becomes possibility.Thereby, in the engine drive pattern, except driving engine, can also use electrical motor.
Hybrid power control setup 52 is set to keep driving engine 8 to be in running state owing to the electric CVT function of toric transmission part 11, and no matter whether vehicle is static or with relatively low speed.When needs first electrical motor M1 work is static to be at vehicle during to electrical storage device 60 chargings; For the electrical storage device 60 that the electric weight SOS that is stored in the electrical storage device 60 is reduced charges; When although the running velocity that is in the second electrical motor M2 that is confirmed by speed V when static when vehicle is zero (being roughly zero); Because the differential function of power splitting mechanism 16, operation make the speed N of the driving engine 8 that the first electrical motor M1 turns round under fair speed
ECan keep enough height, pass through self-operating to allow driving engine 8.
Hybrid power control setup 52 also is set to the electric CVT function owing to toric transmission part 11, through controlling the operating speed N of the first electrical motor M1
M1And/or the operating speed N of the second electrical motor M2
M2, keep engine speed N
EConstant or control engine speed N on demand
E, and no matter whether vehicle is in static or under relatively low speed, goes.In other words, hybrid power control setup 52 is set to control the operating speed N of the first electrical motor M1 on demand
M1Or the operating speed N of the second electrical motor M2
M2, keep engine speed N simultaneously
EConstant or control engine speed N on demand
EObviously visible in the alignment chart from Fig. 3, for example in order to improve the engine speed N in the driving process of vehicle
E, hybrid power control setup 52 improves the operating speed N of the first electrical motor M1
M2While is by the operating speed N of the second definite electrical motor M2 of speed V (speed of drive wheel 38)
M2Keep constant.
High speed gear decision maker 62 be set to judge speed-changing mechanism 10 under vehicle condition and according to be stored in the memory storage 56 and in Fig. 6 the speed change border line chart through example shown should gear shift to gear whether be high gear, for example, the 5th gear.Make this and judge and judge and mesh among switch clutch C0 and the drg B0 which, speed-changing mechanism 10 is placed the step change state.
Particularly; When switching control 50 judges that vehicle condition is in the step change zone; Switching control 50 makes hybrid power control setup 52 can not carry out hybrid power control or stepless change control; Make step change apparatus 54 can carry out predetermined step change control, in this step change control, change-speed box 20 is according to being stored in speed change border line chart autoshift in the memory storage 56 and that in Fig. 6, pass through example shown.Fig. 2 representes the combination of the engagement action of fluid control friction coupling device C0, C1, C2, B0, B1, B2 and B3, and this figure is stored in the memory storage 56, and optionally is used for the autoshift of step change transmission part 20.In the step change state, the speed-changing mechanism 10 that is made up of toric transmission part 11 and step change transmission part 20 as a whole plays according to the table autoshift among Fig. 2 so-called a grade automatic transmission with hydraulic torque converter is arranged.
When high speed gear decision maker 62 has judged that speed-changing mechanism 10 should shift into the 5th gear; Switching control 50 order hydraulic control units 42 discharge switch clutch C0 and drg B0 is switched in engagement; So that toric transmission part 11 can work to have the auxiliary gear box of 0.7 fixed speed ratio γ 0; For example, make speed-changing mechanism 10 make the as a whole high gear that places with so-called " hypervelocity gear " of being lower than 1.0 speed ratio.When high speed gear decision maker 62 does not also judge that speed-changing mechanism 10 should shift into the 5th gear; Switching control 50 order hydraulic control units, 42 engagement switch clutch CO also discharge switching drg B0; So that toric transmission part 11 can work to have the auxiliary gear box of 1.0 fixed speed ratio γ 0; For example, make speed-changing mechanism 10 do as a whole placing and have the deceleration gear that is not less than 1.0 speed ratio.Thereby; When speed-changing mechanism 10 switches to the step change state by switching control 50; Under the control of switching control 50; Toric transmission part 11 as auxiliary gear box work is placed in selected gear in two gears, and the step change transmission part 20 that is connected in series to toric transmission part 11 simultaneously plays step change transmission, and making speed-changing mechanism 10 play what is called as a whole has a grade automatic transmission with hydraulic torque converter.
Judge vehicle condition when switching control 50 and be in stepless change when zone that speed-changing mechanism 10 is placed the stepless change state; Switching control 50 order hydraulic control units 42 discharge switch clutch C0 and drg B0, and toric transmission part 11 is placed the stepless change state.Simultaneously; Switching control 50 makes hybrid power control setup 52 can carry out hybrid power control; And order step change control setup 54 is selected and is kept one of them predetermined in gear gear, perhaps allow step change transmission part 20 will according to be stored in the memory storage 56 and in Fig. 6 the speed change border line chart autoshift through example shown.In the latter case, step change control setup 54 is carried out automatic control of transmission through the combination (except the ingear combination that comprises switch clutch C0 and drg B0) that option table compatibly is shown in the mode of operation of the friction coupling device in the table among Fig. 2.Thereby; The toric transmission part 11 that under the control of switching control 50, switches to the stepless change state plays toric transmission; And the step change transmission part 20 that is connected in series to toric transmission part youngster simultaneously plays step change transmission; Make speed-changing mechanism 10 that enough vehicle drive forces are provided; Make be delivered to place first to the fourth speed position speed that rotatablely moves (that is, the rotating speed of drive disk assembly 18) of the change-speed box part 20 of a gear changes continuously, make speed ratio continuous variable on the scope of being scheduled to of when change-speed box part 20 places gear of these gears speed-changing mechanism 10.Thereby the speed ratio of change-speed box part 20 is continuous variable on adjacent gear, thus, and the overall ratio γ T continuous variable of speed-changing mechanism 10.
Differential state determining apparatus 80 is set to judge whether power splitting mechanism 16 places differential state, that is, whether toric transmission part 11 places infinite variable speed state.This judgement be when judging that step change transmission part 20 should gear shift (for example, as level speed-change control device 54 based on vehicle condition and according to the speed change border line chart of Fig. 6 judged step change transmission part 20 should gear shift to gear the time) the change-speed box part of carrying out.For example, based on switching control 50 according to the handoff boundary line chart through example shown in Fig. 6 to by speed V and output torque T
OUTWhether the vehicle condition of expression is in the step change zone that is used for speed-changing mechanism 10 is placed the step change state; Or be in the judgement that is used for speed-changing mechanism 10 is placed the stepless gear shift zone of stepless change state, whether 80 pairs of toric transmission parts of differential state determining apparatus 11 are in the stepless change state is judged.
Differential state determining apparatus 80 is set to judge that toric transmission part 11 places differential state; Make the variable speed control of toric transmission part 11 and the variable speed control of step change transmission part 20 carry out synchronously; To reduce since step change transmission part 20 cause the variable quantity step by step of overall ratio γ T of speed-changing mechanism 10, toric transmission part 11 is placed in differential state simultaneously.
Torque reduces control setup 82 and is set to reduce the torque that will be delivered to drive wheel 38.For example, through by the aperture that reduces electrical throttle valve 94 or the fuel supply amount of fuel injection system 96, or the point of ignition of 98 pairs of driving engines 8 of lated sparking device is carried out and is reduced motor torque T
EMotor torque reduce control, torque reduces the input torque T that control setup 82 reduces step change transmission parts 20
INReduce the torque that will be delivered to drive wheel 38.Torque minimizing control setup 82 also is set to control or be additional to the motor torque minimizing through the minimizing of replacement motor torque and controls operating motor torque minimizing to control operating motor torque minimizing to control with minimizing input torque T
INReduce in the control at motor torque, control the second electrical motor M2, make electrical storage device 60 is being carried out the electrically-charged while, temporarily produce reverse vehicular drive torque through inverter 58, or regenerative brake torque.
Step change transmission part 20 upgrades under the control of step change control setup 54; Speed-changing mechanism 10 is done as a whole placing under the control of switching control under the situation of step change state simultaneously; There is following possibility; Be that change-speed box part 20 stands shifting shock owing to so-called " inertia torque ", this inertia torque increases input torque T
INAnd increase output torque T subsequently
OUT, and this inertia torque is because the engine speed N of the inertia phase in the process of the shift-up action of the step change transmission part 20 of the variation of the speed of input speed that relates to change-speed box part 20 or drive disk assembly 18
EDecline produce by the energy that temporarily produces by driving engine 8.
If do as a whole step change transmission part 20 gear shift under the control of step change control setup 54 in the infinite variable speed state that under the control of switching control 50, places at speed-changing mechanism 10; Then under the control of hybrid power control setup 52, carry out the variable speed control of toric transmission part 11; To prevent before the gear shift action of change-speed box part 20 and the variation of the overall ratio γ T of speed-changing mechanism 10 afterwards; Or guarantee the lasting variation of overall ratio γ T with the variable quantity that reduces overall ratio γ T, prevent thus or reduce engine speed N in the process of the gear shift action of change-speed box part 20
EChange.Yet the gear shift of this step change transmission part 20 action also has so-called inertia phase, and this stage relates to the variation of speed of input speed or the drive disk assembly 18 of change-speed box part 20, and relates to inertia torque, and this inertia torque increases output torque T
OUT, and owing to the speed decline of at least one among the 4th to the 8th rotating element RE4-RE8 of step change transmission part 20 produces.In this case, because inertia torque has change-speed box part 20 to stand the possibility of shifting shock.
Be similar to step change transmission part 20, owing to increase output torque T
OUT, and in the inertia phase of the process of the gear shift of change-speed box part 20 action because of the descend reason of the inertia torque that produced of the speed of the second and/or the 3rd rotating element RE2 of change-speed box part 11, RE3, toric transmission part 11 also can stand shifting shock.
In view of above-mentioned possibility, under the control of step change control setup 54 in its gear shift course of action, torque reduces the input torque T that control setup 82 is set to reduce step change transmission part 20
INParticularly, reduce control and motor torque and reduce one in the control or both through carrying out above-mentioned motor torque, torque reduces the input torque T that control setup 82 is set to reduce step change transmission part 20
INCorresponding to the amount of above-mentioned inertia torque, to reduce the shifting shock that causes owing to inertia torque.Be similar to the synchronous variable speed control of 52 pairs of toric transmission parts 11 of hybrid power control setup, torque reduces 82 couples of input torque T of control setup
INMinimizing carry out in the inertia phase of the gear shift of step change transmission part 20 action.Perhaps, torque reduces the input torque T that control setup 82 is set to reduce step change transmission part 20
IN, the torque pulsation variable quantity when feasible minimizing engagement under the control of step change control setup 54 comes the engagement action completion of the suitable friction coupling device of change-speed box part 20 gear shift, the mesh impact of the coupling device of reducing friction thus.
With the figure that describes in detail among Fig. 6.Mode through example is shown in Fig. 6 and be stored in speed change border line chart (variable speed control figure or relation) in the memory storage 56 and be used to judge that step change transmission part 20 whether should gear shift, and by speed V and required output torque T
OUTThe controlled variable that the drive-force-related value of form is formed limits.In Fig. 6, solid line is represented shift-up boundary line, and single-point line expression shift-down boundary line.
Dotted line among Fig. 6 is represented speed of a motor vehicle upper limit V1 and output torque upper limit T1, and both are used to switching control 50 to judge whether vehicle condition is in step change zone or stepless change zone.In other words, dotted line is represented the boundary line of running at high speed of speed of a motor vehicle upper limit V1, and just judges that above it motor vehicle driven by mixed power is in the state of running at high speed, and height is exported the output torque T that step change transmission part 20 is represented in the boundary line of going
OUTOutput torque upper limit T1, just judge that above it motor vehicle driven by mixed power is in high output motoring condition.Output torque T
OUTBe the example of drive-force-related value, it relates to the propulsive effort of motor vehicle driven by mixed power.Fig. 6 also illustrates with respect to the amount that is fit to of dotted line skew control hysteresis and judges whether the step change state changes to stepless change state or opposite long and two-short dash line.Thereby the dotted line of Fig. 6 and long and two-short dash line constitute the handoff boundary line chart (switching controls figure or relation) of storage, and it is utilized with based on speed V and output torque T by switching control 50
OUTWhether the controlled variable of form is higher than preset upper limit value V, and T1 judges whether vehicle condition is in step change zone or stepless change zone.This handoff boundary line chart can be stored in the memory storage 56 together with speed change boundary line figure.The handoff boundary line chart can use among speed of a motor vehicle upper limit V1 and the output torque upper limit T1 at least one, or speed V and output torque T
OUTIn at least one as at least one parameter.
Above-mentioned speed change border line chart, handoff boundary line and drive force source switching figure can use the actual vehicle speed V that stored and comparison and the real output torque T of limits value V1
OUTReplace with the comparison formula of limits value T1.In this case, when actual vehicle speed V surpasses upper limit V1, or the output torque T of step change transmission part 20
OUTWhen surpassing upper limit T1, switching control 50 switches speed-changing mechanism 10 to step change state.
More than the drive-force-related value of expression is the parameter corresponding to vehicle drive force, and it can be the output torque T of step change transmission part 20
OUT, engine output torque T
EOr the accekeration G of vehicle, and the driving torque of wheel 38 or propulsive effort.Parameter can be: based on the operational ton A of accelerator pedal
CCOr the aperture of flow regulating valve (or suction quantity, empty so than or fuel injection amount) and engine speed N
EThe actual value of being calculated; Or required (target) motor torque T
E, change-speed box part 20 required (target) output torque T
OUT, and the estimated valve of required vehicle drive force (based on the operational ton A of accelerator pedal
CCOr the operating angle of flow regulating valve and calculate) in any one.Above-mentioned vehicular drive torque not only can be based on output torque T
OUTDeng calculating, also can obtain based on the speed ratio of compensating gear 36 and the radius calculation of drive wheel 38, perhaps can obtain by direct detections such as torque sensors.
For example, judge speed of a motor vehicle upper limit V1, make that speed-changing mechanism 10 places the step change state when vehicle is in high-speed travel state.If speed-changing mechanism 10 places the stepless change state when vehicle is in high-speed travel state, then this judgement can reduce the possibility of the fuel economy deterioration of vehicle effectively.Judge output torque upper limit T1 according to the operating characteristic of the first electrical motor M1; This first electrical motor is undersized; And its maximum electric energy output is less relatively; Make and to export in the motoring condition when higher relatively at the height of vehicle that the reactive torque of the first electrical motor M1 can be not excessive when driving engine output.
With reference to Fig. 8, handoff boundary line chart (switching controls figure or relation) is shown, this figure is stored in the memory storage 56, and limits as judged the driving engine output line that whether vehicle condition is in has level or stepless change zone by the boundary line of switching control 50 uses.These driving engine output lines are by engine speed N
ELimit with the controlled variable of motor torque NT form.Switching control 50 can use the handoff boundary line chart of Fig. 8 to replace the handoff boundary line chart of Fig. 6, with based on engine speed N
EWith motor torque T
EJudge vehicle condition whether be in stepless or step change regional in.The handoff boundary line chart of Fig. 6 can be based on the handoff boundary line chart of Fig. 8.In other words, the dotted line among Fig. 6 can be based on Fig. 8 by speed V and output torque T
OUTRelation (figure) in the two-dimensional coordinate system that the controlled variable of form limits is confirmed.
The step change zone that is limited the handoff boundary line chart of Fig. 6 is restricted to output torque T
OUTBe not less than the high torque (HT) drive area of predetermined upper limit T1, or speed V is not less than the high-speed driving zone of predetermined upper limit V1.Thereby, higher relatively or when speed V is higher relatively when the torque of driving engine 8, carry out step change control; Relatively low or when speed V is relatively low when the torque of driving engine 8 simultaneously; That is, when driving engine 8 is in normal output state, carry out stepless change control.
Similarly, the step change area limiting that is limited the handoff boundary line chart of Fig. 8 is motor torque T
EBe not less than the high torque (HT) drive area of predetermined upper limit TE1, or engine speed N
EBe not less than the high-speed driving zone of predetermined upper limit NE1, perhaps be defined as wherein based on motor torque N
TWith speed N
EAnd the output of the driving engine 8 that calculates is not less than the height output drive area of predetermined limit value.Thereby, as torque T
E, speed N
EOr the output of driving engine 8 carries out step change control when higher relatively, and as torque T
E, speed N
EOr stepless change control is carried out in the output of driving engine 8 when relatively low (, when driving engine 8 is in normal output state).The boundary line of the handoff boundary switching figure of Fig. 8 can be considered to be the high speed threshold line or the high-engine output threshold line of the upper limit that limits speed V or driving engine output.
In above-mentioned present embodiment, speed-changing mechanism 10 is placed in low speed or the medium velocity motoring condition of vehicle or in the low output of vehicle or middle output motoring condition, is placed in the stepless change state, guarantees the fuel economy of vehicle higher degree.Be higher than at vehicle in the running at high speed under the speed V of upper limit V1; Speed-changing mechanism 10 places the step change state; Wherein the output of driving engine 8 mainly is delivered to drive wheel 38 through the mechanical energy bang path, makes to improve fuel economy because mechanical energy converts conversion loss (doing the time spent when 11 electric controlling stepless variable speed devices of toric transmission part can the take place) minimizing of electric energy into.
At output torque T
OUTThe height that is higher than the vehicle of upper limit T1 is exported in the motoring condition, and speed-changing mechanism 10 places the step change state.Thereby; Only when speed V is relatively low or medium or when driving engine output is relatively low or medium; Just speed-changing mechanism 10 is placed the stepless change state; Make the required electric weight that produces by the first electrical motor M1 (the maximum electric weight that must transmit from the first electrical motor M1) to reduce; The required electric antagonistic force of the first electrical motor M1 can reduce thus, can make the required size of the first electrical motor M1 and the second electrical motor M2 thus and comprise that the required size of the drive system of these electrical motors minimizes.
That is, confirm upper limit TE1, make as driving engine output T
EWhen not being higher than upper limit TE1, the first electrical motor M1 can resist reactive torque, when vehicle is in wherein motor torque T
EWhen being higher than the height output motoring condition of upper limit TE1, toric transmission part 11 places the step change state.Therefore, in the step change state of change-speed box part 11, the first electrical motor M1 do not need as in the stepless change state of change-speed box part 11 with respect to motor torque T
EThe opposing reactive torque, the feasible deterioration that can reduce the durability of the first electrical motor M1 prevents the increase of its required size simultaneously.In other words, in the present embodiment, the required peak output of the first electrical motor M1 can be less than exporting T corresponding to driving engine
EPeaked reactive torque load-carrying capacity.That is, the required peak output of the first electrical motor M1 can be determined, and makes the reactive torque load-carrying capacity less than corresponding to the motor torque T that surpasses upper limit TE1
EValue, make the size of the electrical motor M1 that wins can be less.
The peak output of the first electrical motor M1 is in electrical motor nominal rating value by this definite electrical motor of experiment in the environment of work.Above-mentioned motor torque T
EThe upper limit confirm through experiment, make that the upper limit is to be equal to or less than motor torque T
EPeaked value, below the value, the first electrical motor M1 can resist reactive torque at this, the durability of the electrical motor M1 that wins is worsened can access minimizing.
As shown in figure 8 wherein; More need improve the durability of vehicle rather than improve in the high output of the vehicle motoring condition of economy of fuel oil in vehicle operators; Speed-changing mechanism 10 places step change state (fixed speed ratio speed change state), rather than places the stepless change state, makes engine speed N
EChange along with the shift-up action of step change transmission part 20, thereby guarantee engine speed N when change-speed box part 20 upgrades
EComfortable rhythmic the variation.
Figure 10 illustrates an example of the hand shift device of one gearshift 90 forms can manually selecting in a plurality of gears.Gearshift 90 comprises shifter bar 92; Shifter bar 92 is near the seat horizontally set of vehicle operators; And operated to select: stop position P by one in the following shift position of forming; Be used for speed-changing mechanism 10 (that is, the step change transmission part 20) drive path that is placed in one and the Neutral Position state that places the switch clutch C0 of release position and drg B0 all breaks off and the output shaft 22 of while change-speed box part 20 is in the lock state; Reverse drive position R is used for powered vehicle rearward; Neutral Position N is used for the speed-changing mechanism 10 Neutral Position state that drive path in the speed-changing mechanism 10 are disconnected that is placed in one; Automatic forerunner's shift pattern D; And manual forerunner's shift pattern M.
For example; Shifter bar 92 is mechanically connected to the hand control valve (HCV) that is included in the hydraulic control unit 42; Make hand control valve (HCV) in response to a selected shift position of manually being operated into of shifter bar 92; Make that hydraulic control unit 42 is mechanically worked to set up corresponding rear-guard position R, Neutral Position N or forerunner position D according to the engagement table of friction coupling device.At forerunner's shift position D or M, first gear " 1
St" to the 5th gear " 5
Th" set up through the automatically controlled automatically controlled solenoid electric valve that is included in the hydraulic control unit 42.
Parking position P and Neutral Position N are when vehicle selected non-driven state when driving not; In this non-driven state; As shown in the table among Fig. 2, the drive path in step change transmission part 20 is in and first clutch C1 and second clutch C2 (all remaining in the release position) power interruption state.Reverse drive position R and automatic and manual forerunner's shift pattern D, M are when vehicle selected activation point when driving; In this activation point; As shown in the table of Fig. 2, the power transfer path in change-speed box part 20 is in the power delivery status that at least one power-transfer clutch among wherein the first clutch C1 and second clutch C2 is in engagement.
Detailed description, when shifter bar 92 from Parking position P or Neutral Position N M/C to the reverse drive position during R, engagement second clutch C2 switches to power delivery status with the drive path in the change-speed box part 20 from power interruption state.When shifter bar 92 during from Neutral Position N M/C to automatic forerunner's shift pattern D, meshing at least, first clutch C1 switches to power delivery status with the drive path in the change-speed box part 20 from power interruption state.Automatically forerunner's shift pattern D provides the most high-revolving position, and selectable position " 4 " to " L " is the Jake brake position that wherein applies Jake brake to vehicle in manual forerunner's shift pattern M.
Manual forerunner's shift pattern M is located at vertically going up with automatic forerunner's shift pattern D of vehicle and is in identical position, and spaced apart or adjacent with automatic before driving shift pattern D on the side direction of vehicle.Shifter bar 92 is operable to manual before driving shift pattern M and comes manually that chosen position " D " arrives a position in " L ".Detailed description, shifter bar 92 can from manual forerunner's shift pattern M move to upgrade position "+" and downshift position "-" (each other vehicle vertically on spaced apart).Each shifter bar 92 moves to when upgrading position "+" or downshift position "-" position of the position change of current selected.Five positions " D " to " L " have wherein each different lower limit of the scope of the overall ratio γ T automated variable of speed-changing mechanism 10, that is, and and corresponding to the minimum of each different overall ratio γ T of the highest output speed of speed-changing mechanism 10.That is, the velocity location of step change transmission part 20 or each different quantity (they can be selected automatically) of gear are selected in five positions " D " to " L ", make the minimum overall ratio γ T that is obtained confirmed by the quantity of selected selectable gear.Shifter bar 48 is made shifter bar 92 automatically be back to manual forerunner's shift pattern M from upgrade position "+" and downshift position "-" by the bias unit biasing such as spring.Gearshift 90 is provided with can be operated to detect the shift pattern sensor of selected shifter bar 92 current locations, makes and representes selected shifter bar 98 work at present position P
SHAnd the signal provision of the quantity of the variable speed operation of shifter bar 92 arrives electronic control package 40 in manual forerunner's shift pattern M.
For example; When shifter bar 92 is operated automatic forerunner's shift pattern D; Switching control 50 according to stored at the handoff boundary line chart shown in Fig. 6; Carry out the automatic switchover control of speed-changing mechanism 10, hybrid power control setup 52 is carried out the stepless change control of power splitting mechanism 16, and step change control setup 54 is carried out the automatic control of transmission of step change transmission part 20 simultaneously.For example, when speed-changing mechanism 10 placed the step change state, the gear shift of speed-changing mechanism 10 action was selected suitable gear in first gear to the, five gears (in Fig. 2, representing) by control automatically.When speed-changing mechanism 10 places the stepless change state; The speed ratio of power splitting mechanism 16 changes continuously; The gear shift of step change transmission part 20 action is simultaneously selected first gear suitable gear in the fourth speed position by control automatically, makes the overall ratio γ T of speed-changing mechanism 10 be controlled to continuous variable in predetermined scope.Automatically forerunner position D is selected the position of setting up automatic shift mode (automatic mode), speed-changing mechanism 10 gear shift automatically in this pattern.
On the other hand; When shifter bar 92 is operated manual forerunner's shift pattern M; The gear shift action of speed-changing mechanism 10 is automatically controlled by switching control 50, hybrid power control setup 52 and step change control setup 54; Make overall ratio γ T variable in predetermined scope, the lower limit of this scope is confirmed that by the gear with dead slow ratio this gear is confirmed by the manually selected gear in the gear " D " to " L ".For example, when speed-changing mechanism 10 placed the step change state, the gear shift of speed-changing mechanism 10 action is control automatically in the preset range of above-mentioned overall ratio γ T.When speed-changing mechanism 10 places the stepless change state; The speed ratio of power splitting mechanism 16 changes continuously; The gear shift of step change transmission part 20 action is simultaneously selected the suitable gear (quantity of this gear is confirmed by manually selected in the gear " D " to " L " gear) in the gear by control automatically, makes the overall ratio γ T of speed-changing mechanism 10 be controlled to continuous variable in predetermined scope.Manually before driving position M is the position that is selected to set up manual shift mode (manual mode), and in this manual mode, the selectable gear of speed-changing mechanism 10 is selected by manually.
The major control operation that the flowcharting of Figure 11 is carried out by electronic control package 40 promptly, is used for controlling in the variable speed control process of step change transmission part 20 the variable speed control program of the variable speed operation of toric transmission part 11.This variable speed control program arrives the execution of shorter repetition cycle time of tens of microseconds with for example approximate number microsecond.When the time diagram of Figure 12 is illustrated in speed-changing mechanism 10 and places the stepless change state as level change-speed box part 20 from the upgrade control operation of third gear of second gear.
The variable speed control program confirms with step S1 (omitting below " the step ") beginning corresponding to step change control setup 54 whether the gear shift action of step change transmission part 20 should take place.This judgement through the gear confirming change-speed box part 20 and should gear shift arrive one of them whether based on output torque T by speed V and change-speed box part 20
OUTThe vehicle condition of expression and basis are determined to carry out through the speed change border line chart of example shown in Fig. 6.In the example depicted in fig. 12, make the judgement that the shift-up action of change-speed box portion 20 from second gear to third gear should take place at time point T1.
When in S1, obtaining sure judgement, control flow proceeds to the S2 corresponding to differential state determining apparatus 80, judges whether power splitting mechanism 16 places differential state, that is, whether toric transmission part 11 places the stepless change state.Whether this judgement relies on vehicle condition to be in through carrying out in the stepless change zone that the speed change border line chart shown in the example limits in Fig. 6, and in this stepless change zone, speed-changing mechanism 10 should place the stepless change state.
If in S2, obtain negative judgement, then control flow proceeds to the S6 corresponding to step change control setup 54, carries out the variable speed control of the gear shift action of in S1, judging of carrying out step change transmission part 20.If in S2, obtain sure judgement; Then control flow proceeds to the S3 corresponding to step change control setup 54; Carry out the variable speed control of the gear shift action of in S1, confirming of carrying out change-speed box part 20; Then proceed to S4 corresponding to hybrid power control setup 52; Carry out the variable speed control with the synchronous toric transmission part 11 of the variable speed control of step change transmission part 20 in S3, make the speed ratio of change-speed box part 11 change (during the time period of in Figure 12, representing) from time point t1 to time point t3 in the direction that changes in the opposite direction with the speed ratio of change-speed box part 20.For example; The variable speed control of the speed ratio of toric transmission part 11 and change-speed box part in S3 has synchronously changed the amount corresponding to the variable quantity step by step of the speed ratio of change-speed box part 20 in the direction that changes in the opposite direction step by step with the speed ratio of step change transmission part 20 step by step, prevents before the gear shift action of change-speed box part 20 and the overall ratio γ T transient changing of speed-changing mechanism 10 afterwards.
Variable speed control in S3 and S4 or in the variable speed control process of S6, the torque of in the step S5 that reduces control setup 82 corresponding to torque, carrying out the input torque TIN that reduces step change transmission part 20 reduces control (during the time period of in Figure 12, representing from time point t2 to time point t3).For example; In the variable speed control process of S3 and S4; The speed NE of driving engine does not change as illustrated in fig. 12; But because the result that the speed of the rotating element of step change transmission part 20 descends and the speed of the rotating element of toric transmission part 11 descends, and produced the inertia torque that increases output torque TOUT.In the variable speed control process of S6, because the result that engine speed NE reduces has produced the inertia torque that increases output torque TOUT.Generation in view of above-mentioned inertia torque; Reduce motor torque TE or use second electrical motor M2 operating motor torque minimizing control to come minimizing input torque TIN in S5 through carrying out motor torque minimizing control, reduce the amount of the output torque TOUT that increases owing to the inertia torque that produces.
If in S1, obtained the judgement negating; Then the control flow various control setups that proceed to S7 cause electric controller 40 are carried out various controls; Rather than the variable speed control of step change transmission part 20, carry out circulation for one that perhaps finishes current variable speed control program.For example, when speed-changing mechanism 10 places the stepless change state, hybrid power control setup 52 is carried out the variable speed control of toric transmission part 11 based on vehicle condition.
As stated; Present embodiment is set to; The speed ratio of toric transmission part 11 changes the variable quantity step by step that reduces step change transmission part 20 speed ratio in the variable speed control process under the control of hybrid power control setup 52 (stepless change control setup), make that overall ratio (whole speed ratio) the γ T by the definite speed-changing mechanism 10 (drive system) of the speed ratio of the speed ratio of change-speed box part 11 and change-speed box part 20 is a continually varying.This gear shift action that is arranged on step change transmission part 20 has reduced the variable quantity step by step of engine speed NE before with afterwards, has reduced shifting shock thus.In addition, this is provided with and allows speed-changing mechanism 10 to make the as a whole toric transmission that plays a part, and has improved fuel economy thus.
In addition, in the variable speed control of in the inertia phase that the gear shift of step change transmission part 20 is moved, carrying out toric transmission part 11 under the control of hybrid power control setup 52.That is the synchronous execution of variable speed control of the variable speed control of toric transmission part 11 and change-speed box part 20.In addition; Carry out the variable speed control of toric transmission part 11 and come on the direction that the speed ratio with change-speed box part 20 changes in the opposite direction step by step, to change the amount of the speed ratio of change-speed box part 11, reduced the variable quantity of the overall ratio γ T of speed-changing mechanism 10 thus corresponding to the variable quantity step by step of the speed ratio of step change transmission part 20.Therefore, reduced before the gear shift action of change-speed box part 20 and the variable quantity of engine speed NE afterwards, made and further reduce shifting shock.
The control that present embodiment also is set to reduce control setup 82 in torque is the amount of the inertia torque that produces corresponding to the result owing to the velocity variations of the rotating element of step change transmission part 20 of minimizing input torque TIN and the inertia torque that produces owing to the result of the velocity variations of the rotating element of toric transmission part 11 down, and these inertia torques produce in the gear shift course of action of change-speed box part 20.Thereby, reduced shifting shock.
Other embodiment of the present invention will be described.In being described below, will be used for representing corresponding element with the identical reference symbol of using in the above-described embodiments of symbol.
Second embodiment
In the aforementioned embodiment; Hybrid power control setup 52 be set to the variable speed control of step change transmission part 20 synchronously (promptly; Do in the inertia phase in the process at moving of change-speed box part 20) variable speed control of the toric transmission part 11 carried out, make the overall ratio γ T of speed-changing mechanism 10 before the gear shift action of step change transmission part 20 with change continuously afterwards.And present embodiment provides some examples; Be illustrated in the variable speed control of the toric transmission part 11 that takes place in the inertia phase in the process of gear shifting operation of step change transmission part 20, be used to guarantee before the gear shift action of change-speed box part 20 to change continuously with the overall ratio of speed-changing mechanism 10 afterwards.
In the foregoing embodiments; Carry out the variable speed control of toric transmission part 11 by hybrid power control setup 52; Make the speed ratio of change-speed box part 11 change, make the overall ratio γ T of speed-changing mechanism 10 change continuously before with afterwards in the gear shift action of change-speed box part 20 with the ratio change of step change transmission part 20 direction in the opposite direction.In order to prevent that speed-changing mechanism 10 from moving before and overall ratio γ T transient changing afterwards in the gear shift of change-speed box part 20, the ratio change direction of change-speed box part 11 is asked to the ratio change of change-speed box part 20 in the opposite direction.In order only to guarantee before change-speed box part 20 and the continuous variation of the overall ratio γ T of speed-changing mechanism 10 afterwards, the above-mentioned requirements relevant with the ratio change direction is dispensable.
Promptly; Can carry out the variable speed control that was used for before the gear shift of step change transmission part 20 action with the toric transmission part 11 of the speed ratio of the overall ratio γ T that continuously changes speed-changing mechanism 10 afterwards, make the speed ratio of change-speed box part 11 on the ratio change direction of change-speed box part 20, change.In concrete examples more of the present invention, the speed ratio of change-speed box part 11 changes in the ratio change direction of change-speed box part 20.
Corresponding to the functional block diagram among Figure 13 of the block diagram among Figure 15 the major control function according to the electronic control package 40 of present embodiment is shown, the embodiment of Figure 13 is different from the inertia phase that embodiment that Fig. 5 mainly is Figure 13 comprises further whether the gear shift action that is used to judge step change transmission part 20 has got into inertia phase and gets into decision maker 84.
Inertia phase entering decision maker 84 is set to be based on and will discharges after the coupling device releasing action of carrying out the gear shift action; The velocity variations of drive disk assembly 18 (the second electrical motor M2) whether owing to begin to produce will the ingear coupling device the engagement torque gear shift action that is used to carry out the change-speed box part 20 judged by step change control setup 54 begin, carry out whether having got into the judgement of inertia phase about the variable speed control of step change transmission part 20.
For example; By inertia phase get into that decision maker 84 makes about the variation of the second electromotor velocity NM2 whether owing to begin to produce and wait to mesh the judgement whether the engagement torque of carrying out the gear shift action of step change transmission part 20 under the control of step change control setup 54 begun and carry out in the following manner: whether the speed (i.e. the second electromotor velocity NM2) of judging drive disk assembly 18 has changed more than through testing the amount of being scheduled to of acquisition; Perhaps whether surpassed through experiment and obtained and the preset time in above-mentioned moment of beginning corresponding to the engagement generation of torque, perhaps whether be increased to the transient pressure value PC that is scheduled to that obtains and produce the above-mentioned moment of beginning through experiment corresponding to the engagement torque through the engagement hydraulic pressure of confirming to want the ingear coupling device through the time span of confirming when step change control setup 54 carries out the judgement of gear shift action of step change transmission part 20, to be carved into engagement generation of torque zero hour of treating the ingear coupling device.
The diagram of circuit of Figure 14 shows the major control operation of being carried out by electronic control package 40, promptly is used for being controlled at the variable speed control program of variable speed operation of the variable speed control process toric transmission part 11 of step change transmission part 20.This variable speed control program repeats in the short cycle time of tens of microseconds in for example approximate number microsecond.The diagram of circuit of Figure 14 is corresponding to the diagram of circuit of Figure 11, and the diagram of circuit that is different from Figure 11 mainly is in the diagram of circuit of Figure 14, to have increased the S3 ' of the judgement that the inertia phase of the gear shift action that is used for confirming change-speed box part 20 gets into.
The time diagram of Figure 15 shows in the control operation shown in the diagram of circuit of Figure 14, places the stepless change state at speed-changing mechanism 10, when level change-speed box part 20 upgrades third gear from second gear, carries out this operation.The time diagram of Figure 15 is corresponding to the time diagram of Figure 12, and the time diagram that is different from Figure 12 mainly is in Figure 15, to have increased hydraulic pressure signal output (hydraulic pressure).
The time diagram of Figure 16 shows the control operation shown in the diagram of circuit of Figure 14, places the stepless change state at speed-changing mechanism 10, when step change transmission part 20 in the coast process at vehicle is carried out this control operation when third gear lowers category second gear.The time diagram of Figure 16 is corresponding to the time diagram of Figure 12.
The time diagram of Figure 17 shows in the control operation shown in the diagram of circuit of Figure 14, places the stepless change state at speed-changing mechanism 10, when second gear upgrades third gear, carries out this control operation as level change-speed box part 20.The time diagram of Figure 17 is corresponding to the time diagram of Figure 15, and the time diagram that is different from Figure 15 is that mainly the speed ratio of toric transmission part 11 changes in the time diagram of Figure 17 on the ratio change direction of step change transmission part 20.
The time diagram of Figure 18 shows in the control operation shown in the diagram of circuit of Figure 14, places the stepless change state at speed-changing mechanism 10, when step change transmission part in the coast process at vehicle is carried out this control operation when third gear lowers category second gear.The time diagram of Figure 18 is corresponding to the time diagram of Figure 16, and is different from Figure 16 time diagram is that mainly the speed ratio of toric transmission part 11 changes in the time diagram of Figure 18 on the ratio change direction of step change transmission part 20.
To Figure 18, with only describing the aspect that the present invention is different from the previous embodiment of Figure 11 and Figure 12, other aspects will not described with reference to Figure 14.
The variable speed control program begins with the S1 corresponding to step change control setup 54, judges whether the gear shift action of step change transmission part 20 should take place.This judgement is through based on by the represented vehicle condition of the output torque TOUT of speed V and change-speed box part 20 and according to judging that through the exemplary speed change border line chart that illustrates in Fig. 6 the gear that change-speed box part 20 whether should gear shift carries out.
In Figure 15 and example shown in Figure 17, carry out the judgement whether shift-up action of change-speed box part 20 from second gear to third gear should take place at time point t1.In Figure 16 and example shown in Figure 180, carry out the judgement that lowers category of change-speed box part 20 at time point t1 from third gear to second gear.
When in S1, having obtained sure judgement, control flow proceeds to the S2 corresponding to differential state determining apparatus 80, judges whether power splitting mechanism 16 places differential state, that is, whether toric transmission part 11 places the stepless change state.Whether this judgement is being carried out in the stepless change zone that limits through the speed change border line chart shown in the example in Fig. 6 based on vehicle condition, and speed-changing mechanism 10 should place the stepless change state in this stepless change zone.
If in S2, obtained the judgement negating, then control flow proceeds to the S6 corresponding to step change control setup 54, carries out to be used for carrying out the variable speed control in the gear shift action of the definite step change transmission part 20 of S1.
If in S2, obtained sure judgement, then control flow proceeds to the S3 corresponding to step change control setup 54, carries out to be used for carrying out the variable speed control in the gear shift action of the definite change-speed box part 20 of S1.In the example of Figure 15 and Figure 17, produce the upgrade gear-shift command of third gear of step change transmission part 20 at time point T1, at this time point t1, the hold-off pressure PB2 of the second drg B2 (coupling device to be discharged) begins to reduce.In the example of Figure 16 and Figure 18, produce at time point t1 and to make the lower category gear-shift command of second gear of change-speed box part 20, at this time point t1, the hold-off pressure PB1 of the first drg B1 (coupling device to be discharged) begins to reduce.
Then, control flow proceeds to the S3 ' that gets into decision maker 84 corresponding to inertia phase, judges whether the gear shift action of step change transmission part 20 has got into inertia phase.For example; The judgement that whether got into inertia phase about gear shift action is based on following carrying out: the judgement that whether has begun about the variation of the second electromotor velocity NM2; Whether this judgement changes more than the scheduled volume that obtains through experiment based on the second electromotor velocity NM2 is carried out; Whether perhaps surpassed by experiment up to the time span of generation zero hour of the engagement torque of coupling device to be joined and obtain and corresponding to the preset time of the above-mentioned zero hour, whether the engagement hydraulic pressure of perhaps treating the ingear coupling device has been increased to the predetermined transient pressure value PC that obtains and produce corresponding to the engagement torque of treating the ingear coupling device zero hour through experiment.
In the example of Figure 15, Figure 16, Figure 17 and Figure 18; Judge the entering of inertia phase at time point T1, this be since the second electromotor velocity NM2 changed the scheduled volume that obtains through experiment with detection got into inertia phase judgement, or obtain through experiment and corresponding to the schedule time of engagement generation of torque zero hour of treating the ingear coupling device over and done with the engagement hydraulic pressure of judgement or coupling device be increased to the result of judgement of the predetermined transient pressure value PC of the above-mentioned zero hour that obtains through experiment and produce corresponding to engagement torque.In the example of Figure 15 and Figure 17, treat that the ingear coupling device is the first drg B1 with engagement hydraulic pressure PB1.In the example of Figure 16 and Figure 18, treat that the ingear coupling device is the second drg B2 with engagement hydraulic pressure PB2.
When in S3 ', having obtained the judgement negating, repeat this step S3 '.When in S3 ', having obtained sure judgement; Control flow proceeds to the S4 corresponding to hybrid power control setup 52; Come synchronously to carry out the variable speed control of toric transmission part 11, make the overall ratio γ T of speed-changing mechanism 10 change continuously before with afterwards in the gear shift action of change-speed box part 20 with the variable speed control of step change transmission part 20 in S3.
In the example of Figure 15 and Figure 16; In the inertia phase that the gear shift of change-speed box part 20 is moved; From time point t2 to time point t3 (Figure 15) or during the time period of time t4 (Figure 16); The speed ratio of toric transmission part 11 is changing corresponding to the speed ratio of change-speed box part 20 amount of variable quantity step by step with the ratio change of step change transmission part 20 direction in the opposite direction step by step; Prevent before the gear shift of change-speed box part 20 is moved and the variation of the overall ratio γ T of speed-changing mechanism 10 afterwards, that is, prevent before the gear shift action of change-speed box 20 and the variation of engine speed NE afterwards.
In the example of Figure 17 and Figure 18; In the inertia phase that the gear shift of change-speed box part 20 is moved; From time point T2 to time point T3 (Figure 17) or during time period of time point T4 (Figure 18); The speed ratio of toric transmission part 11 changes on the direction of the ratio change direction of step change transmission part 20, makes the overall ratio γ T of speed-changing mechanism change continuously before with afterwards in the gear shift action of change-speed box part 20.Thereby engine speed NE is owing to the variation of the overall ratio γ T of speed-changing mechanism 10 changes, and this is opposite with the engine speed NE in the example of Figure 15 and Figure 16.
In the variable speed control or the variable speed control process at S6 of S3 and S4, the torque minimizing that reduces the input torque TIN of step change transmission part 20 is controlled at corresponding to carrying out among the torque minimizing control setup 82 step S5.For example, in the variable speed control process, owing to descend speed with the rotating element of step change transmission part 11 of the speed of the rotating element of step change transmission part 20 descends and caused the inertia torque of increase output torque TOUT.Perhaps because in the shift-up action process, the speed of engine speed NE descends and has caused increasing the inertia torque of output torque TOUT.Inertia torque in view of above-mentioned generation; Input torque TIN for example reduces motor torque TE through carrying out motor torque minimizing control; Perhaps, reduce because the recruitment of the output torque TOUT that inertia torque produced through using the second electrical motor M2 operating motor torque to reduce control.Perhaps, reduce the pulsatile change that output torque TIN reduces the output torque TOUT when accomplishing friction and carry out the joint action of friction coupling device of gear shift action of step change transmission part 20, reduced the joint impact of coupling device thus.Do not operate at car retardation that the gear shift action is a shift-down action in the process of accelerator pedal; Promptly; Under the shift-down action situation in the process that the coast of vehicle is gone, need not carry out torque and reduce the amount that reduces owing to the output torque TOUT that inertia torque increased of controlling.
In the example of Figure 15; Because the speed of the rotating element of step change and toric transmission part 20,22 descends; Engine speed NE keeps constant result simultaneously; During time period, reduce output torque TIN, reduce because the amount of the output torque TOUT that inertia torque increased from time point t2 to time point t3.
In the example of Figure 16; During time period, reduce input torque TIN from time point t3 to time point t5; Reduce the engagement action completion of carrying out the gear shift action of step change transmission part 20 when the friction coupling device; When simultaneously engine speed NE kept constant, the pulsatile change of output torque TOUT had lowered the mesh impact of coupling device thus.In the example of the Figure 16 that in the coast driving process of change-speed box part 20, lowers category, there is not to carry out the torque minimizing control that reduces the recruitment of output torque TOUT owing to inertia torque at vehicle.Yet, operate simultaneously under the situation that change-speed box part 20 lowers category in the process of accelerator pedal in vehicle ', as in the example of Figure 15, carry out torque and reduce that control reduces because the output torque amount that inertia torque increased.
In the example of Figure 17; During time period, reduce input torque TIN from time point t2 to time point t3; Reduce because the amount of the output torque TOUT that inertia torque increased, this is because the variation of engine speed NE and the causing of speed decline of the rotating element of level and toric transmission part 20,11 arranged.
In the example of Figure 18 that change-speed box part 20 lowers category in the coast driving process of vehicle, do not carry out torque minimizing control and reduce because the output torque recruitment of inertia torque.Yet, as in the example of Figure 17, to operate simultaneously under the situation that change-speed box part 20 lowers category in the process of accelerator pedal in vehicle ', torque reduces control and carries out and reduce because the output torque recruitment of inertia torque.
If in S1, obtained the judgement negating, control flow proceeds to the various controls that S7 carries out the various control setups of electronic control package 40, rather than the variable speed control of step change transmission part 20, carries out circulation for one that perhaps finishes this variable speed control program.For example, when speed-changing mechanism 10 places the stepless change state, hybrid power control setup 52 is carried out the variable speed control of toric transmission part 11 based on vehicle condition.
As stated, present embodiment has the advantage identical with previous embodiment.For example; Under the control of hybrid power control setup 52 (stepless change control setup), carry out (promptly synchronously with the gear shift action of step change transmission part 20; In the gear shift of change-speed box part 20 action inertia phase) variable speed control of toric transmission part 11; Guarantee the continuous variation of overall ratio (general speed ratio) the γ T (confirming) of speed-changing mechanism 10 drive systems, promptly reduced the variable quantity step by step of overall ratio γ T in the gear shift action of step change transmission part 20 by the speed ratio of change-speed box part 11 and the speed ratio of change-speed box part 20.Move before and speed NE afterwards in the gear shift of step change transmission part 20, reduced its shifting shock thus.In addition, this is provided with and allows speed-changing mechanism 10 to make the as a whole stepless speed changing mechanism that plays a part, and has improved fuel economy thus.
The 3rd embodiment
Scheme drawing with reference to Figure 19; Show the setting of the speed-changing mechanism 70 in the another embodiment of the present invention; Figure 20 is the rub table of the relation between the engagement various combination of coupling device of gear and the fluid control that is used for setting up respectively those gears of expression speed-changing mechanism 70, and Figure 21 is the alignment chart that is used to explain the variable speed operation of speed-changing mechanism 70.
As in the aforementioned embodiment, speed-changing mechanism 70 comprises toric transmission part 11, and this toric transmission part 11 has the first electrical motor M1, power splitting mechanism 16 and the second electrical motor M2.Speed-changing mechanism 70 further comprises the step change transmission part 72 with three forerunner positions.Change-speed box part 72 is arranged between toric transmission part 11 and the output shaft 22, and is connected in series to toric transmission part 11 and output shaft 22 through drive disk assembly 18.Power splitting mechanism 16 comprises single pinion type first compound planet gear 24 and switch clutch C0 and switching drg B0 with for example about 0.418 transmitting ratio ρ 1.Step change transmission part 72 comprises single pinion type second compound planet gear 26 with transmitting ratio ρ 2 of for example about 0.532 and the single pinion type the third line star gear cluster 28 with for example about 0.418 transmitting ratio ρ 3.The second sun wheel S2 of second compound planet gear 26 and the 3rd sun wheel S3 of the third line star gear cluster 28 be fixed to one another integratedly to become one unit; And optionally be connected to drive disk assembly 18 through second clutch C2, be fixed to change speed gear box 12 through the first drg B1 selectivity.Second planetary wheel carrier CA2 of second compound planet gear 26 and the 3rd gear ring R3 of the third line star gear cluster 28 are fixed to one another integratedly, and are fixed to output shaft 22.The second gear ring R2 optionally is connected to drive disk assembly 18 through first clutch C1, and the third line star wheel frame CA3 optionally is fixed to change speed gear box 12 through the second drg B2.
By in the speed-changing mechanism 70 of above-mentioned structure, the gear of first gear (first velocity location) in fourth speed position (the 4th speed stage), reverse gear (rear-guard position) and the neutral gear is through from as optionally setting up in the engagement action of the friction coupling device respective combination that is selected from above-mentioned switch clutch C0, first clutch C1, second clutch C2, switching drg B0, the first drg B1 and the second drg B2 shown in the table of Figure 20.These gears have into the corresponding speed ratio γ (drive shaft speed NIN/ output shaft speed NOUT) that geometric series changes.Concrete; Note; The power splitting mechanism 16 that is provided with switch clutch C0 and drg B0 optionally places mechanism 16 to can be used as the fixed speed ratio speed change state of the transmission operating with fixed speed ratio through the engagement of switch clutch C0 or switching drg B0, and places mechanism 16 to can be used as the stepless change state of above-mentioned toric transmission work.Thereby in this speed-changing mechanism 70, step change transmission places the toric transmission part 11 of fixed speed ratio speed change state to form by change-speed box part 20 and by the engagement of switch clutch C0 or switching drg B0.Further, toric transmission constitutes by change-speed box part 20 with because of switch clutch C0 and drg B0 all do not mesh the toric transmission part 11 that places the stepless change state.In other words, speed-changing mechanism 70 switches to the step change state through engagement switch clutch C0 with one that switches among the drg B0, and switches to the stepless change state through discharging switch clutch C0 and switching drg B0.
For example; Play a part under the step change transmission situation at speed-changing mechanism 70; As shown in Figure 20; Through the engagement action of switch clutch C0, first clutch C1 and the second drg B2 set up have for example be about 2.804 the most at a high speed than first gear of γ 1, set up through the engagement action of switch clutch C0, first clutch C1 and the first drg B1 and to have second gear that is about 1.531 speed ratio γ 2 that for example is lower than speed ratio γ 1.In addition; Set up through the engagement action of switch clutch C0, first clutch C1 and second clutch C2 and to have the third gear that for example is about 1.000 speed ratio γ 3 that is lower than speed ratio γ 2, set up to have through first clutch C1, second clutch C2 and the engagement action of switching drg B0 and be lower than the fourth speed position that speed ratio γ 3 for example is about 0.705 speed ratio γ 4.In addition, set up the reverse gear that for example is about 2.393 speed ratio γ R that has between speed ratio γ 1 and γ 2 through the engagement action of the second clutch C2 and the second drg B2.Set up neutral gear N through only meshing switch clutch C0.
On the other hand; Play the time spent of doing of toric transmission when speed-changing mechanism 70; Discharge switch clutch C0 and switch drg B0; Make toric transmission part 11 play a part toric transmission, the step change transmission part 72 that is connected in series to toric transmission part 11 simultaneously plays a part step change transmission, is delivered to thus to place first gear to the speed that rotatablely moves of the change-speed box portion 72 of a gear of third gear (promptly; The rotative speed of drive disk assembly 18) continuous variable, the speed ratio of feasible speed-changing mechanism 10 when change-speed box part 72 places gear of those gears is continuous variable on predetermined scope.Thereby the overall ratio of change-speed box part 72 is continuous variable on adjacent gear, thus, is continuous variables as the overall ratio γ T of a single-piece speed-changing mechanism 70.
The alignment chart of Figure 21 is illustrated in the relation between the rotating speed of the rotating element in each gear of speed-changing mechanism 70 by straight line, speed-changing mechanism 70 is made up of toric transmission part 11 that plays the toric transmission part or the first change-speed box partial action and the change-speed box part 72 that plays the step change transmission part or the second change-speed box partial action.The alignment chart of Figure 21 is represented the rotating speed of the discrete-component of toric transmission part 11 when discharging switch clutch C0 and drg B0; With the rotative speed of those elements when engaging switch clutch C0 or drg B0 engagement, as in the foregoing embodiments.
In Figure 21; Represent the second and the 3rd fixing sun wheel S2 of one each other, the 4th rotating element (quaternary part) RE4 of S3 form respectively corresponding to automatic transmission with hydraulic torque converter 72 and four perpendicular line Y4, Y5, Y6 and Y7 being set to vertical direction, the relative rotation speed of the 7th rotating element (the 7th element) RE7 of the second planetary wheel carrier CA2 that the 5th rotating element (the 5th element) RE5 of the third line star wheel frame CA3 form, one are fixed to one another and the 6th rotating element (the hexa-atomic) RE6 of the 3rd gear ring R3 form and the second gear ring R2 form.In automatic transmission with hydraulic torque converter 72; The 4th rotating element RE4 optionally is connected to drive disk assembly 18 through second clutch C2; And optionally be fixed to change speed gear box 12, the five rotating element RE5 through the first drg B1 and optionally be fixed to change speed gear box 12 through the second drg B2.Output shaft 22, the seven rotating element RE7 that the 6th rotating element RE6 is fixed to automatic transmission with hydraulic torque converter 72 optionally are connected to drive disk assembly 18 through first clutch C1.
When the engagement first clutch C1 and the second drg B2, step change transmission part 72 places first gear.As shown in Figure 21; The rotating speed of the output shaft 22 in first gear is fixed to perpendicular line Y6 and the intersection point between the bevelled straight line L1 of the 6th rotating element RE6 rotating speed of output shaft 22 to be represented by expression, and angled straight lines L1 is through at the intersection point between the perpendicular line Y7 of the rotative speed of expression the 7th rotating element RE7 (R2) and the horizon X2 and at the perpendicular line Y5 of the rotative speed of representing the 5th rotating element RE5 (CA3) and the intersection point between the horizon X1.Similarly; The rotation rotating speed of the output shaft 22 in second gear of setting up through the engagement action of the first clutch C1 and the first drg B1, be fixed to by determined angled straight lines L2 of those engagement action and expression output shaft 22 the 6th rotating element RE6 (CA2, R3) rotating speed perpendicular line Y6 between intersection point represent.The rotating speed of the output shaft 22 in the third gear of setting up through the engagement action of first clutch C1 and second clutch C2 is represented by determined angled straight lines L3 of those engagement action and the intersection point that is fixed between the perpendicular line Y6 of rotating speed of the 6th rotating element RE6 of output shaft 22.Switch clutch C0 place engagement first to third gear, the 7th rotating element RE7 utilizes the propulsive effort that receives from toric transmission part 11 with the speed rotation identical with the speed NE of driving engine.When switching drg B0 replaced switch clutch C0 engagement, the 6th rotating element RE6 utilized the propulsive effort that receives from toric transmission part 11 to rotate to be higher than engine speed NE.Through first clutch C1, second clutch C2 and the rotative speed that switches the output shaft 22 in the fourth speed position that the engagement action of drg B0 sets up represent by the intersection point between the perpendicular line Y6 of the determined horizontal line L 4 of those engagement action and the rotating speed of the 6th rotating element RE6 that representes to be fixed to output shaft 22.
Also constitute according to speed-changing mechanism 70 of the present invention, make this speed-changing mechanism 70 have the advantage that is similar to first embodiment by toric transmission part that plays the toric transmission partial sum first change-speed box partial action 11 and the step change transmission part that plays level (automatically) change-speed box part or the second change-speed box partial action 72.
The 4th embodiment
But Figure 22 has shown the seesaw switch 44 (below be called " switch 44 ") of speed change state selecting arrangement effect that M/C is selected differential state (unlock state) and/or the non-differential state (lock-out state) (promptly selecting the stepless change state or the step change state of speed-changing mechanism 10) of power splitting mechanism 16.This switch 44 allows the user in the driving process of vehicle, to select required speed change state.As shown in Figure 22, seesaw switch 44 have be used for vehicle the sign that the stepless change state goes have the stepless change of " step change " go button be used for vehicle and the step change of " stepless change " button that goes arranged in the sign that the step change state goes.When the user pressed stepless change and goes button, switch 44 placed the stepless change position, with the stepless change state of selecting speed-changing mechanism 10 to work as electric steplessly variable transmission.When the user pressed step change and goes button, switch 44 placed the step change state to select the step change state of speed-changing mechanism as step change transmission work.
In aforementioned exemplary, the speed change state of speed-changing mechanism 10 is based on vehicle condition, and according to automatically switching through the handoff boundary line chart shown in the example in Fig. 6.Yet the speed change state of speed-changing mechanism 10,70 can be switched through the M/C that replaces automatically switching operation or the seesaw switch 44 except automatically switching operation.That is, switching control 50 can be set to optionally speed-changing mechanism 10 placed stepless change state or step change state, and this depends on whether switch 44 places stepless change state or step change state.For example; When the user hopes that speed-changing mechanism 10 is worked as toric transmission, perhaps wanting to improve the fuel economy of driving engine; User's manual operation switch 44 places the stepless change state with speed-changing mechanism 10; Perhaps hope because during the tempo variation of the engine speed as a result of the gear shift of step change transmission action, user's manual operation switch 44 places the step change state with speed-changing mechanism 10 as the user.
Switch 44 can have does not have stepless change and step change state to be chosen Neutral Position.Under this situation, when the user did not select required speed change state or do not hope that speed-changing mechanism 10 automatically places state of stepless change and step change state, switch 44 can place Neutral Position.
Speed change state at speed-changing mechanism 10 is automatically not selected; But by under the manually selected situation of the M/C of switch 44; Step S2 in the diagram of circuit of Figure 11 or Figure 14 is stated as makes whether place differential state about power splitting mechanism 16; That is, the judgement whether toric transmission part 11 places the stepless change state, whether based on operating switch 44 selects the differential state of power splitting mechanism 16 or the speed change state of speed-changing mechanism 10 to judge.
The 5th embodiment
Figure 23 is the major control functional block diagram that electronic control package 40 is shown.In Figure 23, accelerator operation amount rate of change computer device 100 is set to based on the operational ton of expression accelerator pedal 46 and is applied to the operating speed of accelerator pedal 46 of rate of change ACC ' form of operational ton of the operational ton signal ACC computation accelerator pedal of electronic control package 40.This rate of change ACC ' expression is by the speed of the increase or the minimizing of the needed vehicle drive force of vehicle operators.For the starting fast or suddenly or quicken of vehicle, the climbing that perhaps is used for vehicle is gone, when accelerator pedal 46 operation suddenly, promptly when required vehicle drive force is relatively large, rate of change ACC ' be higher relatively on the occasion of.For the vehicle that under constant speed, goes, when the rate of change of required vehicle drive force is relatively low, that is, when the operational ton of accelerator pedal 46 keeps constant, rate of change ACC ' is almost nil or be relatively low value.
Differential state determining apparatus 102 is set to judge whether power splitting mechanism 16 places differential state, that is, whether toric transmission part 11 places the stepless change state.When definite step change transmission part 20 should gear shift, for example, when having confirmed gear that step change transmission part 20 should gear shift, carry out this judgement based on vehicle condition with according to the speed change border line chart step change control setup 54 of Fig. 6.For example; Based on switching control 50 about being used for placing the step change of step change state regional or be in the judgement that is used for speed-changing mechanism 10 is placed the stepless change zone of stepless change state speed-changing mechanism 10 by whether being in according to speed V through the handoff boundary line chart shown in the example in Fig. 6 and vehicle condition that output torque TOUT representes, differential state determining apparatus 80 carries out whether being in about toric transmission part 11 judgement of stepless change state.
Provide differential state determining apparatus 80 to confirm whether toric transmission part 11 places differential state; Make when the gear shift action of confirming step change transmission part 20 whether be in differential state or be in non-differential state based on toric transmission part 11 and control engine speed.
Engine speed control setup 104 comprises stepless variable engine control setup 106 and step change engine control unit 108; And be set in perhaps to utilize the speed NE of gear shift action (having caused the variation step by step of engine speed NE) the control driving engine of step change transmission part 20 through the stepless change action of control toric transmission part 11 by the variable speed control process of the step change transmission part 20 of step change control setup 54 control.
When power splitting mechanism 16 is in differential state when under the control of step change control setup 54, beginning the gear shift action in step change transmission part 20, operating slepless transmission engine control unit 106.The first electrical motor M1 that stepless variable engine control setup 106 is set to order hybrid power control setup 52 control toric transmission parts 11 carries out the stepless change action, makes the velocity variations of the sun wheel S1 that wins make the speed NE of driving engine when the gear shift action of step change transmission part 20 is accomplished and target engine speed value NE
*Consistent.Stepless variable engine speed device 106 further is set to order step change control setup and controls the variable speed control of carrying out step change transmission part 20 with above-mentioned engine speed.Above-mentioned target engine speed NE
*Be the engine speed NE that the driving engine output of required vehicle drive force is satisfied in acquisition when the gear shift action of level change-speed box part 20 is accomplished; Mixed power control unit 52 controls of engine speed NE make driving engine 8 along the best curve that controlled variable the limited operation engine speed NE and motor torque TE form of being stored.
Generally speaking; After the moment that the gear shift action of being confirmed step change transmission part 20 by step change control setup 54 should take place, operating lag is arranged; Up to the moment that engine speed NE changes beginning, this is to move because of the actual gear shift of the engagement of the coupling device that rubs along with suitable fluid control and releasing action to begin to cause.In order to reduce this operating lag; And the output of acquisition required driving engine after accomplishing the gear shift action fast; Stepless variable engine control setup 106 is set to after being judged by the gear shift action of step change control setup 54; Through speed by the hybrid power control setup 52 control first electrical motor M1, rather than through utilizing since the engine speed NE of the gear shift action of step change transmission part 20 change the speed NE that changes driving engine apace step by step.
For example; When level speed-change control device 54 judges that the shift-down action of change-speed box part 20 should take place; Stepless variable engine control setup 106 order hybrid power control setups 52 improve the speed of the first electrical motor M1; Thus, improved the speed NE of driving engine, rather than allowed to improve the speed NE of driving engine owing to shift-down action.At this moment, the speed of the stepless variable engine control setup 106 order hybrid power control setups 52 controls first electrical motor M1 is so that engine speed NE and above-mentioned target engine speed NE
*Consistent.Simultaneously, consider the speed and the gear of change-speed box part 20 of drive disk assembly 18, this speed is come definite through the input speed (being speed V) of the step change transmission part 20 that risen by shift-down action.
Stepless variable engine control setup 106 is based on the rate of change ACC ' of accelerator pedal operation amount and the rate of change of control engine speed NE.As stated, the rate of change ACC ' of accelerator pedal operation amount expression is by the increase of the required vehicle drive force of vehicle operators or the speed of minimizing.The needed vehicle drive force of vehicle operators satisfies the rate of change of the driving engine output of required propulsive effort corresponding to needs.In this respect, rate of change ACC ' is regarded as the rate of change of expression engine speed.For example; The speed of the stepless variable engine control setup 106 order hybrid power control setups 52 controls first electrical motor M1 increases the ascending velocity of engine speed, make when variable Rate ACC ' be higher relatively on the occasion of the time required vehicle drive force increment rate than as variable Rate ACC ' be relatively low on the occasion of the time relative high.
When power splitting mechanism 16 is in non-differential state when the variable speed control of step change transmission part 20 under the control of step change control setup 54 begins, 108 work of step change engine control unit.The device 108 of step change engine control is set to the variable speed control that order step change control setup 54 is carried out step change transmission part 20; Make the speed NE of driving engine change step by step, make when the gear shift action of accomplishing change-speed box part 20 and step change target engine speed value NE owing to the result of the gear shift action of change-speed box part 20
*Consistent.Step change target engine speed value NE
*Be the engine speed NE that is confirmed by the speed of drive disk assembly 18, the speed of drive disk assembly 18 is confirmed by the fixed speed ratio of speed V and toric transmission part 11.
Step change engine control unit 108 further is set to the speed of the order hybrid power control setup 52 control first electrical motor M1 and/or the second electrical motor M2; Power splitting mechanism 16 remains on non-differential state by switching control 50 simultaneously, makes engine speed NE equal step change target engine speed value NE as far as possible
*For example; When power splitting mechanism 16 is in non-differential state; And switch clutch C0 remains on rotating element that engagement state is used for mechanism 16 when rotating as one unit; The speed of the step change engine control unit 108 order hybrid power control setup 52 control first electrical motor M1 and/or the second electrical motor M2; Simultaneously power splitting mechanism 16 remains on non-differential state under the control of switching control 50, make engine speed NE as far as possible with step change target engine speed value NE
*Consistent.
When power splitting mechanism 16 is in non-differential state in step change transmission part 20 when the gear shift action begins under the control of step change control setup 54; Engine speed control setup 104 is controlled the speed of driving engine through starting step change engine control unit 108 rather than stepless variable engine control setup 106; Keep power splitting mechanism 16 to be in non-differential state simultaneously; Rather than mechanism 16 switched to differential state, to prevent because mechanism 16 switches to the operating lag of differential state.Be that engine speed control setup 104 is when being set to when the variable speed control at step change control setup 54 begins power splitting mechanism 16 and being in non-differential state; By the speed control of step change control setup 54 execution driving engines, to improve the shift response of step change transmission part 20.
Thereby; In the variable speed control process of step change transmission part 20; Whether utilization places a method of two selected engine speed control methods of differential state or non-differential state, engine speed control setup 104 optionally to start the speed that stepless variable engine control setup 106 or step change engine control unit 108 are controlled driving engine when the variable speed control by step change control setup 54 begins based on power splitting mechanism 16.
In other words; Engine speed control setup 104 is set to when the variable speed control of the change-speed box part of being controlled by step change control setup 54 20 begins, whether place differential state or non-differential state based on power splitting mechanism 16; Through selecting by the engine speed control of stepless variable engine control setup 106 with by a control in the engine speed control of step change engine speed control setup 108; In the variable speed control process of step change transmission part 20, change the shifting control method of step change transmission part 20.
The diagram of circuit of Figure 24 shows the major control operation of being carried out by electronic control package 40, the i.e. control of the engine speed in the variable speed control process of step change transmission part 20.Repeat the short cycle time that this engine speed control program is done microsecond to tens of microseconds at for example approximate number.
The engine speed control program judges with step S11 (omitting below " the step ") beginning corresponding to step change control setup 54 whether the gear shift action of step change transmission part 20 should take place.This judgement through confirm change-speed box part 20 should gear shift to a gear in based on determining whether and gear shift carry out through the speed change border line chart shown in the example in Fig. 6 by the output torque TOUT of speed V and change-speed box part 20 represented vehicle condition and basis.When in S11, obtaining the judgement negating, control flow proceeds to the current driving state that S18 keeps vehicle, and finishes an execution circulation of current control program.When in S11, obtaining sure judgement; Control flow proceeds to the S12 corresponding to accelerator operation amount rate of change computer device 100, and wherein accelerator operation amount rate of change ACC ' is based on the operational ton of expression accelerator pedal 46 and be applied to the operational ton signal ACC of electronic control package 40 and calculate.
Subsequently, the S13 that carries out corresponding to differential state determining apparatus 102 judges whether power splitting mechanism 16 places differential state, that is, whether toric transmission part 11 places the stepless change state.Whether this judgement dependence vehicle condition is in the stepless change zone that limits through the speed change border line chart shown in the example in Fig. 6 is judged that speed-changing mechanism 10 should place the stepless change state in the stepless change zone.
When in S13, obtaining the judgement negating; Control flow proceeds to the S14 corresponding to engine speed control setup 104, and the variable speed control of the step change transmission part 20 that the gear shift of wherein carrying out among S11s judging through utilization owing to the execution of variation step by step of the result's of gear shift action engine speed NE by step change control setup 54 is moved is controlled the speed NE of driving engine.Simultaneously; Execution is corresponding to the S15 of engine speed control setup 104; Wherein, The speed of the first electrical motor M1 and/or the second electrical motor M2 is through 2 controls of hybrid power control setup, and power splitting mechanism 16 remains on non-differential state by switching control 50 simultaneously, makes engine speed NE when step change transmission part 20 is accomplished the gear shift action, equal target engine speed value NE as far as possible
*
When in S13, obtaining sure judgement; Control flow proceeds to the S16 corresponding to engine speed control setup 104; Wherein, control the speed that the first electrical motor M1 controls the first sun wheel S1, control the speed NE of driving engine thus by hybrid power control setup 52.Simultaneously, carry out S17, wherein, carry out the variable speed control of step change transmission part 20 by step change control setup 54 corresponding to engine speed control setup 104.Thereby, come when the completion step change moves than 20 gear shift and target engine speed value NE through the speed NE that uses first electrical motor in S16 and S17, to control driving engine
*Be consistent.
The time diagram of Figure 25 to Figure 28 shows each example in the control operation shown in the diagram of circuit of Figure 24.
Figure 25 shows as the result who tramples operation of accelerator pedal when speed-changing mechanism 10 places the stepless change state, and change-speed box part 20 is as in the example from fourth speed potential drop shelves to second gear shown in the solid line A among Fig. 6.In the example of Figure 25, control operation is made up of S11, S12, S13, S16 and S17 (carrying out smoothly by this) in the diagram of circuit of Figure 24.That is, confirm the shift-down action from the fourth speed position to second gear at the time point t1 of Fig. 2, at this moment, accelerator pedal is trampled.Judge that in response to this first electrical motor M1 is controlled to the speed that improves the first sun wheel S1, improves engine speed NE thus, the variable speed control of step change transmission part 20 has begun.Because the operating lag of the gear shift of change-speed box part 20 action, the speed of change-speed box part 20 keep not becoming, up to time point t2.Yet, the no matter gear shift of change-speed box part 20 action, engine speed NE obtains fast speed and improves (during the time period from time point t1 to time point t2), and this is because toric transmission part 11 remains in the stepless change state.Promptly; Up to the engine speed control of time point t3 (this moment, step change transmission part 20 variable speed control was accomplished) through since the engine speed that the gear shift action of change-speed box part 20 causes change and do not carry out; But carried out through controlling the first electrical motor M1; Make and reduced the delay of trampling of engine speed NE rising with respect to the tread-on quantity of accelerator pedal, that is, the response of engine speed NE is improved.Thereby in the gear shift course of action of change-speed box part 20, the speed of driving engine increases with respect to Traditional engine speed control (by the line of the single-point in Figure 25 expression).In addition, the output of driving engine also obtains fast speed increases.Under the relatively low situation of the rate of change ACC ' of accelerator pedal operation amount; Promptly under the relatively low situation of the operating speed of accelerator pedal, the speed of driving engine can be like indicated the controlling of dotted line (during the time period from time point t1 to time point t4).
Figure 26 shows the operation of trampling owing to accelerator pedal, and speed-changing mechanism 10 places the example of the portion of change-speed box as a result 20 from fourth speed potential drop shelves to second gear of step change state simultaneously.In the example of Figure 26, control operation is made up of S11, S12, S13, S14 and the S15 (carrying out in this order) of the diagram of circuit of Figure 24.That is, confirm shift-down action from the fourth speed position to second gear at the time point t1 of Figure 26, at this moment between point, accelerator pedal is trampled.Judge the variable speed control of beginning step change transmission part 20 in response to this.Because the operating lag of the switching speed of change-speed box part 20, the input speed of change-speed box part 20 remains unchanged, up to time point t2.In this case, power splitting mechanism 16 is not once to switch to differential state, but remains on non-differential state, to prevent owing to the operating lag that switches to differential state action.Among this non-differential state, change-speed box part 20 lowers category to change speed ratio step by step, has improved the speed (during the time period from time point t2 to time point t3) of driving engine thus.Thereby the variable speed control of change-speed box part 20 is accomplished fast.In order to reduce the time period from time point t2 to time point t3, the speed NE of driving engine can control through controlling the first electrical motor M1 and/or the second electrical motor M2.Further, engine speed NE fine adjustment can after toric transmission part 11 is switched to the stepless change state, use the first electrical motor M1 to carry out through during the time period from time point t3 to time point t4.This switches among the S15 that switches in diagram 24 diagram of circuit of stepless change state and can carry out.Under the relatively low situation of the rate of change ACC ' of accelerator pedal operation amount; Promptly; Under the low relatively situation of the operating speed of accelerator pedal, the speed of driving engine can controlling shown in dotted line (during the time period from time point t2 to time point t5).
Figure 27 shows because the speed of a motor vehicle increases, and speed-changing mechanism 10 places the result of stepless change state simultaneously, change-speed box part 20 shown in solid line B among Fig. 6 from the upgrade example of fourth speed position of third gear.In the example of Figure 27, control operation is made up of S11, S12, S13, S16 and the S17 (carrying out in proper order with this) of the diagram of circuit of Figure 24.Promptly confirm that at the time point t1 of Figure 27 at this time point, the speed of a motor vehicle obtains increasing from the upgrade shift-up action of fourth speed position of third gear.Judge that in response to this first electrical motor M1 is controlled to the speed that reduces by the first sun wheel S1, has reduced engine speed NE thus, the variable speed control of beginning step change transmission part 20.Because the operating lag of the gear shift of change-speed box part 20 action, the input speed of change-speed box part 20 keep not changing, up to time point t2.Yet, the no matter gear shift of change-speed box part 20 action, engine speed NE reduces (during the time period from time point t1 to time point t2) apace, and this is because toric transmission part 11 remains on infinite variable speed state.Promptly; Up to time point t3 (at this moment; The variable speed control of step change transmission part 20 is accomplished) change of the speed control of the driving engine engine speed that not have to move owing to the gear shift of change-speed box part 20 carries out; But carry out through controlling the first electrical motor M1, make variable speed control to accomplish fast.During the time period from time point t1 to time point t2, the speed that engine speed reduces can reduce the shifting shock of change-speed box part 20 than lower during from time point t2 to time point t3.Under the relatively low situation of the variable Rate ACC ' of accelerator pedal operation amount; Promptly under the relatively low situation of the operating speed of accelerator pedal, the speed of driving engine can be controlled (during the time period from time point t1 to time point t4) shown in dotted line.
Figure 28 shows because the increase of the speed of a motor vehicle, and speed-changing mechanism 10 places the result of step change state simultaneously, and change-speed box part 20 is from the upgrade example of change-speed box part of fourth speed position of third gear.In the example of Figure 28, control operation is made up of the S11 in the diagram of circuit of Figure 24, S12, S13, S14 and S16 (carrying out in proper order with this).That is, confirm shift-up action, obtain increasing in this time point speed of a motor vehicle from third gear to the fourth speed position at the time point t1 of Figure 27.Judge the variable speed control of beginning step change transmission part 20 in response to this.Because the operating lag of the gear shift of change-speed box part 20 action, the remaining unchanged of input speed of change-speed box part 20 is up to time point t2.In this case, power splitting mechanism 16 does not once switch to differential state, but remains on non-differential state, to prevent owing to the operating lag that switches to the change action of differential state.In this non-differential state, change-speed box partly upgrades and changes its speed ratio step by step, has reduced the speed (during the time period from time point t2 to time point t3) of driving engine thus.Thereby the variable speed control fast speed of change-speed box part 20 is accomplished.In order to reduce the time period from time point t2 to t3, the speed N8 of driving engine can be through controlling the first electrical motor M1 and/or the second dynamo-electric machine M2 controls.Further, engine speed NE fine adjustment can use the first electrical motor M1 to carry out after toric transmission part 11 is switched to the stepless change state during the time period from time point t3 to time point t4.This switching that switches to the stepless change state can be carried out in the step in the diagram of circuit S15 of Figure 24 or after S15.
As stated, speed-changing mechanism 10 according to the present invention comprises the switch clutch C0 and switching drg B0 that can operate so that power splitting mechanism 16 is switched between the non-differential state that toric transmission part 11 is not partly worked as toric transmission as the differential state and the change-speed box part 11 of electric steplessly variable transmission work.In this speed-changing mechanism 10; Through utilizing the function of toric transmission part 11 as electric steplessly variable transmission; Promptly through utilizing the differential function of power splitting mechanism 16, the speed NE of the driving engine in the variable speed control process of step change transmission part 20 is by 104 controls of engine speed control setup.Thereby; The speed NE of driving engine changes along with improved response fast; And zero hour of the gear shift of step change transmission part 20 action no matter, and because variable speed control and engine speed control execution simultaneously, the variable speed control of change-speed box part 20 is accomplished fast.For example, when change-speed box part 20 in response to the trampling operation of accelerator pedal when lowering category, engine speed NE accelerator pedal trample operation after improve fast, make driving engine output (power) the at high speed increase.In addition, because the control that lowers category is carried out with the control of engine speed simultaneously, the shift-down action of change-speed box part 20 is accomplished fast.
The device 104 that engine speed control in the present invention is set further is set to through utilizing the speed NE of first electrical motor M1 control driving engine, the target engine speed value NE when making the gear shift action completion of speed and step change transmission part 20 of the driving engine when the gear shift action of step change transmission part 20 is accomplished
*Unanimity makes that the response to the speed NE of the driving engine of gear shift action is improved, and no matter because the variation of the engine speed NE of the gear shift action of change-speed box part 20.
Present embodiment further is arranged so that the rate of change ACC of the speed control unit 104 of driving engine based on accelerator pedal operation amount
*And the rate of change of control engine speed makes the demand of vehicle operators fully be reflected on the engine speed NE, and the drivability of vehicle is improved thus.
Present embodiment further is arranged so that the control method of engine speed NE of the control setup 104 of engine speed; When the variable speed control of step change transmission part 20 begins, whether be in differential state or non-differential state based on power splitting mechanism 16 and change; Make the speed NE fast speed of driving engine change, the response of the engine speed of gear shift action is improved.
For example; Be in differential state in power splitting mechanism 16; The speed NE of the speed control unit 104 of driving engine differential function control driving engine through utilizing power splitting mechanism 16 in the variable speed control process of step change transmission part 20; Make the speed NE fast speed of driving engine change, and zero hour of the gear shift action of change-speed box part 20 no matter, this makes the response of engine speed NE improve; And because variable speed control and engine speed control completion simultaneously, the variable speed control fast speed of change-speed box part 20 is accomplished.
Be in power splitting mechanism 16 under the situation of non-differential state; The speed control unit 106 of driving engine in the variable speed control process of step change transmission part 20 through utilizing because the speed NE of the variation control driving engine of the engine speed that the gear shift of change-speed box part 20 action causes; Make that the speed NE of driving engine changes with improved response fast in the gear shift working process of change-speed box part 20, and power splitting mechanism 16 is not switched to differential state from non-differential state.
Be under the non-differential state status in power splitting mechanism 16; The control setup 106 of engine speed in the variable speed control process of step change transmission part 20 through utilize the first electrical motor M1 and/or the second electrical motor M2 control driving engine speed; Keep power splitting mechanism 16 to be in non-differential state simultaneously; Make the speed NE of driving engine in the gear shift course of action of step change transmission part 20, change fast, and power splitting mechanism 16 is not switched to differential state from non-differential state.Further, the speed NE of driving engine controls through utilizing electrical motor M1, M2, makes the speed NE of driving engine and target engine speed value NE when the gear shift of change-speed box part 20 action is accomplished
*Unanimity makes the response of gear shift action be further enhanced.
The variable speed control mode of step change transmission part 20 that further is arranged so that present embodiment depends on whether power splitting mechanism 16 is in differential state or non-differential state when the variable speed control of step change transmission part 20 begins; Make engine speed NE fast speed change, the speed of driving engine is improved to the response of gear shift action.
For example; Be in power splitting mechanism 16 under the situation of differential state; The speed NE of the speed control unit 104 of driving engine differential function control driving engine through utilizing power splitting mechanism 16 in the gear shift working process of change-speed box part 20; Variable speed control when allowing change-speed box part 20 simultaneously makes the speed NE of driving engine change fast, and zero hour of the gear shift action of change-speed box part 20 no matter; This makes the raising of response of engine speed NE, and because the variable speed control fast speed completion of change-speed box part 20 is carried out in variable speed control and engine speed control simultaneously.
Be in power splitting mechanism 16 under the situation of non-differential state; Engine speed control setup 104 in the variable speed control process of step change transmission part 20 through utilizing because the speed NE of the variation control driving engine of the engine speed that the gear shift of change-speed box part 20 action causes; Keep power splitting mechanism 16 to be in non-differential state simultaneously; Make that fast speed changes with improved response for the speed NE of in the gear shift working process of change-speed box part 20 driving engine, and power splitting mechanism 16 is not switched to differential state from non-differential state.
Although embodiments of the invention through describing with reference to accompanying drawing, it will be understood that the present invention can embody with other mode in detail in the above.
In shown embodiment; Power splitting mechanism 16 was switched before differential state and non-differential state, made speed-changing mechanism 10,70 play a part to switch between the stepless change state of electric controlling stepless variable speed mechanism and the step change state that speed-changing mechanism 10 plays the step change transmission effect at stepless speed changing mechanism 10.Yet; Principle of the present invention can be applied to the speed-changing mechanism 10,70 that can not place the step change state; Be that toric transmission part (differential portion) 11 is not provided with switch clutch C0 and drg B0, and can operate with as electric steplessly variable transmission (electric controlled differential device) and acting speed-changing mechanism.In this case; At the switching control shown in Fig. 5 50, high gear decision maker 62 and differential state determining apparatus 80 not necessarily; Judge in the diagram of circuit in Figure 11 and Figure 14 speed-changing mechanism 16 differential state step S2 not necessarily, make that step S6 neither be necessary.The present invention can also be applied to the change-speed box that toric transmission part 11 is known toric transmission (CVT).
In an illustrated embodiment, speed-changing mechanism 10,70 is through switching as the differential state of electric steplessly variable transmission work and change-speed box part 11 toric transmission part 11 (power splitting mechanism 16) between not as the non-differential state (lock-out state) of electric steplessly variable transmission work and between stepless change state and step change state, switch in change-speed box part 11.Yet speed-changing mechanism 10,70 can play a part step change transmission, and the speed ratio of toric transmission part 11 changes step by step, rather than changes continuously, and this change-speed box part 11 is keeping differential state simultaneously.In other words, the differential and non-differential state of toric transmission part 11 need not correspond respectively to the stepless and step change state of speed-changing mechanism 10,70, and toric transmission part 11 needn't be switched between stepless and step change state.Principle of the present invention is applied to can switch any speed-changing mechanism (its toric transmission part 11 or power splitting mechanism 16) between differential state and non-differential state.
In the foregoing embodiments, the variable speed control of carrying out toric transmission part 11 prevents the variation of engine speed NE from promptly, to prevent the variation of the overall ratio of speed-changing mechanism 10, and is represented like the time diagram in Figure 12, Figure 15 and Figure 16.Yet, reducing the variation step by step of engine speed NE as long as carry out variable speed control, and guarantee the continuous variation of engine speed, the variable speed control that just needn't carry out change-speed box part 11 prevents the variation of engine speed NE.
In the foregoing embodiments, differential state determining apparatus 80 (at the step S2 of Figure 11 and Figure 14) is set to judge whether vehicle condition is in the stepless change zone, judges whether power splitting mechanism 16 places differential state.Yet,, can rely on speed-changing mechanism 10 under the control of switching control 30, whether to place level or stepless change state to carry out about the judgement whether power splitting mechanism 16 places differential state.
In the power splitting mechanism 16 in an illustrated embodiment, the first planetary wheel carrier CA1 is fixed to driving engine 8, the first sun wheel S1 and is fixed to the first electrical motor M1, and the first sun wheel R1 is fixed to drive disk assembly 18.Yet this layout is optional.Driving engine 8, the first electrical motor M1 and drive disk assembly 18 can be fixed to any other element of three element CA1, S1 and R1 being selected from first compound planet gear 24.
Although driving engine 8 directly is fixed to input shaft 14 in shown embodiment, driving engine 8 can be operably connected to input shaft 14 through any suitable parts such as gear and band, and not need with input shaft 14 coaxial settings.
In shown embodiment, the first electrical motor M1 and the second electrical motor M2 and input shaft 14 coaxial settings, and be respectively fixed to the first sun wheel S1 and drive disk assembly S8.Yet this layout is dispensable.For example, the first and second electrical motor M1, M2 can be operably connected to the first sun wheel S1 and drive disk assembly 18 respectively through gear or band.
Although 16 being provided with switch clutch C0 and switching drg B0 in shown embodiment, power splitting mechanism 16 needn't be provided with power-transfer clutch C0 and drg B0.Although switch clutch C0 provides optionally the first sun wheel S1 and the first planetary wheel carrier CA1 is connected to each other; But switch clutch C0 can provide selectivity that the first sun wheel S1 is connected with the first gear ring R1, perhaps optionally the first planetary wheel carrier C1 is connected with the first gear ring R1.That is, switch clutch C0 can be set to connect any two elements in three elements of first compound planet gear 24.
Although in the transmission device 10,70 of shown embodiment, switch clutch C0 meshes and sets up neutral gear N, and switch clutch C0 needn't mesh and set up neutral gear.
As the fluid control friction coupling device of switch clutch C0, switching drg B0 etc., can replace in an illustrated embodiment by magnetic type, electromagnetic type or mechanical type coupling device such as magnetic-powder clutch (electromagnetism powder power-transfer clutch), magnetic clutch and engagement type canine tooth power-transfer clutch.
In shown embodiment, the second electrical motor M2 is fixed to drive disk assembly 18.Yet the second electrical motor M2 can be fixed to output shaft 22 and the turning unit that is fixed to transfer part 20,72.
In an illustrated embodiment, step change transmission part 20,72 is arranged on drive wheel 38 and is in the drive path between the power transmission member 18 of output block of toric transmission part 11 or power splitting mechanism 16.Yet; Change- speed box part 20,72 can be used such as toric transmission (CVT) (a kind of automatic transmission with hydraulic torque converter), as hand-operated transmission and the parallel biaxial type change-speed box of known a kind of permanent engagement, and the torque transfer of any other type through selecting the automatic transmission with hydraulic torque converter that gear air cylinder and gear shifting cylinder automatically switch replaces.Under the situation that toric transmission (CVT) is provided, when power splitting mechanism 16 placed the fixed speed ratio speed change state, speed-changing mechanism placed the step change state as a whole.The fixed speed ratio speed change state is restricted to power and mainly transmits through the mechanical power bang path, and does not carry out the state of transmission of power through circuit.Toric transmission can be set to the storage data according to the expression predetermined speed ratios, sets up the predetermined fixed speed ratio of the speed ratio of a plurality of gears corresponding to step change transmission.
Although change-speed box part in the aforementioned embodiment 20,27 is connected in series to toric transmission part 11 through drive disk assembly 18, change- speed box part 20,72 can be installed to the tween drive shaft parallel with input shaft 44 and with the coaxial setting of tween drive shaft.In this case, toric transmission part 11 comes operationally to be connected to each other with change- speed box part 20,72 one group of two torque transfer through the combination of suitable torque transfer or for example a pair of transmission gear and sprocket wheel and chain.
Provide power splitting mechanism 16 to replace in previous embodiment with the compensating gear that comprises miniature gears that rotates by driving engine 8 and the bevel-gear sett that is operably connected to the first and second electrical motor M1, M2 respectively as modified roll mechanism.
Although transmission system in the aforementioned embodiment 90 is provided with the shifter bar 92 of operationally selecting a plurality of shift patterns; Shifter bar 92 can be used the operationally shifter such as button push or sliding-type switch of selective speed gear shift position, perhaps selects the shifter of a plurality of shift patterns to replace by the pin operation of sound that vehicle operators produced or vehicle operators rather than by hand.Although the required scope of selected shift range when shifter bar 92 places manual forerunner position M1, required gear (being the top-gear position of each shift range) can place the shifter bar 92 of manual forerunner position M to select through operation.20,70 gear shift of step change transmission part are to selected gear in this case; For example; Each shifter bar 92 is operated downshift position "-" or the position "+" that upgrades from manual forerunner position M, step change transmission part 20,70 first the required gear in the fourth speed position that lowers category or upgrade.
Although switch 44 is seesaw switches in the aforementioned embodiment; But seesaw switch 44 can be used single button push switch, and two button push switches (optionally being pushed into operated position), bar type switch, sliding-type switch are perhaps operationally selected the switch or the shifter of any other type of required state in stepless change state (differential state) and the step change state (non-differential state).Mutual switch 44 can not have neutral gear.Do not have at interactive switch 44 under the situation of neutral gear, can provide extra switch to make interactive switch 44 effective or invalid.The function of this additional switch is corresponding to the function of the Neutral Position of interactive switch 44.Mutual switch 44 can use the shifter of being operated by the pin of the sound of vehicle operators generation or vehicle operators to replace, rather than hand is selected a state in stepless change state (differential state) and the step change state (non-differential state).
In the embodiment shown in the diagram of circuit of Figure 24; Step S1 is set to through judging whether the gear that step change transmission part 20 should gear shift arrives is confirmed based on vehicle condition and according to the speed change border line chart shown in Fig. 6, carries out about whether carrying out the judgement of the variable speed control of step change transmission part 20.Under required shift range or the required gear situation manually selected through known gearshift in the prior art, can be in the judgement of carrying out the variable speed control execution of change-speed box part 20 when change-speed box part 20 according to the M/C of gearshift during gear shift.Thereby the present invention can be applied in the speed-changing mechanism of wherein step change transmission part 20 gear shift in response to the hand gear operation.
In the embodiment of diagram of circuit shown in Figure 24, step S16 and S17 carry out simultaneously.Yet, execution in step S16 at first, execution in step S17 also is feasible then.
In the shown embodiment of the diagram of circuit of Figure 24, step S15 and S12 are optional, can be omitted according to the present invention.
Be appreciated that, embodiments of the invention only be to illustrative purpose and describe, the present invention can embody with variations and modifications, this modification and variation are that the those skilled in the art in present technique field can expect.
Claims (4)
1. control setup that is used for driver for vehicle; Comprise toric transmission partial sum step change transmission part; Said toric transmission partly comprises modified roll mechanism; This modified roll mechanism can be operated with the output with driving engine and be assigned to first electrical motor and drive disk assembly; Said toric transmission part also comprises second electrical motor in the drive path between the drive wheel that is arranged in said drive disk assembly and vehicle, and said toric transmission partly plays the electric controlling stepless variable speed device, and said step change transmission partly constitutes the part of said drive path; Work to have grade automatic transmission with hydraulic torque converter and be connected to said toric transmission part, said control setup is characterised in that and comprises:
Exercisable engine speed control setup in the variable speed control of said step change transmission part is used for moving the speed of controlling said driving engine through the electric stepless gear shift of controlling said toric transmission part,
Wherein, said engine speed control setup makes that through utilizing the said speed of the said driving engine of said motor control the said speed of said driving engine equals the target engine speed value when the gear shift action of said step change transmission part is accomplished.
2. control setup according to claim 1, wherein, based on the rate of change of the operational ton of accelerator pedal, said engine speed control setup is controlled the rate of change of the said speed of said driving engine.
3. control setup according to claim 1; Wherein, Said modified roll mechanism comprises differential state switching device, and said differential state switching device can be operated partly not can be used as between the non-differential state of said electric steplessly variable transmission work with the differential state that said toric transmission part partly can be used as said electric steplessly variable transmission work at said toric transmission and said toric transmission and switch.
4. control setup according to claim 3, wherein, said modified roll mechanism has first element that is connected to said driving engine, be connected to second element of said first electrical motor and be connected to the element of said drive disk assembly,
And wherein; Said differential state switching device can be operated allowing said first relative to each other to rotate setting up said differential state to element, and allow said first to element as the one unit rotation or keep said second element static to set up said non-differential state.
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP132029/2004 | 2004-04-27 | ||
| JP2004132029 | 2004-04-27 | ||
| JP2004165807A JP4151614B2 (en) | 2004-06-03 | 2004-06-03 | Control device for vehicle drive device |
| JP165807/2004 | 2004-06-03 | ||
| JP040653/2005 | 2005-02-17 | ||
| JP2005040653A JP4389806B2 (en) | 2004-04-27 | 2005-02-17 | Control device for vehicle drive device |
| PCT/JP2005/006688 WO2005106290A1 (en) | 2004-04-27 | 2005-03-28 | Controller of driving gear for vehicle |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101727484A Division CN101451608B (en) | 2004-04-27 | 2005-03-28 | Control device for vehicular drive system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1950628A CN1950628A (en) | 2007-04-18 |
| CN1950628B true CN1950628B (en) | 2012-08-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101727484A Expired - Fee Related CN101451608B (en) | 2004-04-27 | 2005-03-28 | Control device for vehicular drive system |
| CN2005800135243A Expired - Fee Related CN1950628B (en) | 2004-04-27 | 2005-03-28 | Control device of driving device for vehicle |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101727484A Expired - Fee Related CN101451608B (en) | 2004-04-27 | 2005-03-28 | Control device for vehicular drive system |
Country Status (2)
| Country | Link |
|---|---|
| KR (1) | KR100954716B1 (en) |
| CN (2) | CN101451608B (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5298539B2 (en) * | 2007-02-09 | 2013-09-25 | トヨタ自動車株式会社 | Control device for vehicle drive device |
| JP4229205B1 (en) * | 2007-09-18 | 2009-02-25 | トヨタ自動車株式会社 | Control device for hybrid drive |
| JP4970480B2 (en) * | 2009-03-06 | 2012-07-04 | 日産自動車株式会社 | Control device for automatic transmission |
| JP5402901B2 (en) * | 2010-09-30 | 2014-01-29 | 株式会社デンソー | Engine control device |
| WO2012117518A1 (en) * | 2011-03-01 | 2012-09-07 | スズキ株式会社 | Hybrid vehicle drive control device |
| CN104245458A (en) * | 2012-03-26 | 2014-12-24 | 丰田自动车株式会社 | Hybrid vehicle drive control device |
| JP5513570B2 (en) * | 2012-09-04 | 2014-06-04 | 本田技研工業株式会社 | Vehicle control device |
| DE102013219276A1 (en) * | 2013-09-25 | 2015-03-26 | Robert Bosch Gmbh | Method and device for controlling an internal combustion engine of a motor vehicle |
| KR101846894B1 (en) * | 2016-03-18 | 2018-04-09 | 현대자동차 주식회사 | Planetary gear train of automatic transmission for vehicles |
| DE102016223066A1 (en) * | 2016-11-23 | 2018-05-24 | Robert Bosch Gmbh | A method for traction control of drive wheels of a motor vehicle and traction control device for traction control of drive wheels of a motor vehicle |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1413855A (en) * | 2001-10-22 | 2003-04-30 | 丰田自动车株式会社 | Mixed power vehicle drive system with speed changing box and operating method |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000346169A (en) * | 1999-06-07 | 2000-12-12 | Toyota Motor Corp | Control device of vehicle continuously variable transmission |
| JP3650089B2 (en) * | 2002-08-02 | 2005-05-18 | トヨタ自動車株式会社 | Hybrid drive device and automobile equipped with the same |
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- 2005-03-28 CN CN2008101727484A patent/CN101451608B/en not_active Expired - Fee Related
- 2005-03-28 KR KR1020097010780A patent/KR100954716B1/en active IP Right Grant
- 2005-03-28 CN CN2005800135243A patent/CN1950628B/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1413855A (en) * | 2001-10-22 | 2003-04-30 | 丰田自动车株式会社 | Mixed power vehicle drive system with speed changing box and operating method |
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| JP平2-256957A 1990.10.17 |
| JP平5-164205A 1993.06.29 |
| JP平7-336810A 1995.12.22 |
| JP昭50-30223A 1975.03.26 |
Also Published As
| Publication number | Publication date |
|---|---|
| KR100954716B1 (en) | 2010-04-23 |
| CN101451608B (en) | 2013-07-10 |
| CN1950628A (en) | 2007-04-18 |
| CN101451608A (en) | 2009-06-10 |
| KR20090103996A (en) | 2009-10-05 |
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