CN1950628A - Control device of driving device for vehicle - Google Patents
Control device of driving device for vehicle Download PDFInfo
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- CN1950628A CN1950628A CNA2005800135243A CN200580013524A CN1950628A CN 1950628 A CN1950628 A CN 1950628A CN A2005800135243 A CNA2005800135243 A CN A2005800135243A CN 200580013524 A CN200580013524 A CN 200580013524A CN 1950628 A CN1950628 A CN 1950628A
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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
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 differential attachment 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 differential attachment and automatic transmission.
Background technique
Had known Vehicular drive system, it comprised the differential attachment of transmission action with differential function and in the step change state exercisable automatic transmission, the output that this Vehicular drive system is set to the transmission of drive force source comes driving wheel.Generally speaking, the overall ratio of such driver for vehicle is determined by the speed ratio of these two gears.
Example as the differential attachment that works transmission action with differential function, there is known drive system, it comprises the differential motion that outputs to first motor and output shaft that operationally distributes motor, and be arranged on second motor between differential motion and the driving wheel, and this drive system can be used as the operation of continuous control stepless speed variator.The example of such drive system comprises as 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, differential attachment for example is made of planetary gear set, and be delivered to the differential functional machinery of the major component of the driving force of motor by differential attachment driving wheel, and the remaining part of driving force electrically the circuit by therebetween be delivered to second motor from first motor, make differential attachment 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 gear powered vehicle, and motor keeps best running state with improved fuel economy.
The overall ratio that comprises the driver for vehicle of two above-mentioned transmission mechanisms is determined by the speed ratio of the differential motion with differential function and the speed ratio of automatic transmission.When differential attachment places its stepless change state, be similar to the drive system that only comprises differential motion, drive system is whole to play the electric controlling stepless variable speed device, and vehicle is by the engine-driving 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 differential attachment in the stepless change state, or in the process that does not have the gear shift action, automatic transmission is in the step change state during gear shift, engine speed changes step by step according to the variation step by step of the speed ratio of automatic transmission, and it is as a whole before the gear shift action of automatic transmission and do not have the possibility of continuous variable afterwards to make the overall ratio that has drive system do.In other words, exist drive system to do before the as a whole gear shift action in automatic transmission and do not play the possibility of stepless speed variator afterwards.Thereby drive system can suffer shifting shock, or suffers to think the influence that fuel economy that motor provides needed torque to cause worsens owing to failing to control engine speed along the highest fuel-economy linearity curve.
The transmission device that does not have the fluid-actuated of setting such as torque-converters at the driver for vehicle shown in the above-mentioned patent documentation 1, make when speed changer in the step change state during gear shift, engine speed is along with the variation of the speed ratio of speed changer changes with the relation that becomes to be scheduled to the speed of a motor vehicle.For example, speed changer by controlling known hydraulic control friction coupling device engagement and release movement 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 speed changer to move.At this timing period, engine speed may not change.Thereby speed changer has the danger of the gear shift response of deterioration.For example, when speed changer 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 motor to produce the possibility of output delay (delay of increase begins).
In view of above-mentioned background technique is carried out the present invention.Thereby, first purpose of the present invention is to provide a kind of control gear that is used for driver for vehicle, this control gear is included in the differential attachment that can work in the stepless change state, with the speed changer 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 speed changer in the step change state.Second purpose of the present invention provides the control gear of driver for vehicle, comprise the differential attachment of the gear that plays a part to have differential function and the automatic transmission that in the step change state, can work, this control gear allows the quick variation of engine speed, with when automatic transmission in the step change state during gear shift, the improved gear shift response of automatic transmission.
According to first form of the present invention, provide a kind of and be used for the control gear of (a) driver for vehicle, comprise stepless speed variator part and speed changer part, stepless speed variator partly comprises differential attachment, differential attachment has first element that is connected to motor, be connected to second element and the three element that is connected to transmission part of first motor, and stepless speed variator partly comprises second motor that further comprises in the drive path that is arranged between transmission part and the driving wheel of vehicle, stepless speed variator partly plays a part electric steplessly variable transmission, speed changer partly constitutes the part of drive path, control gear is characterised in that and comprises: (b) stepless change control gear, but this stepless change control gear is the place of working in the speed Control process of speed changer part, be used for synchronously carrying out the speed Control of speed changer part, make the speed ratio that is limited by stepless speed variator part and speed changer part change continuously with the speed Control of speed changer part.
In above-mentioned control gear, the stepless change control gear can be worked in the speed changer that changes the step by step speed Control process partly at speed ratio, be used for synchronously carrying out the gear shift control of stepless speed variator part with the speed Control of speed changer part, the feasible speed ratio that is limited by stepless speed variator part and speed changer part (promptly, the overall ratio that limits by the speed ratio of the speed ratio of stepless speed variator part and speed changer part) variation continuously, that is, make because the speed ratio that causes variable quantity is step by step moved in the gear shift of speed changer part.Thereby reduce before speed changer gear shift action partly and the variation step by step of engine speed afterwards, reduced the shifting shock of speed changer part.Further, but drive system plays a part stepless speed variator 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 gear of (a) driver for vehicle, comprise stepless speed variator part and speed changer part, stepless speed variator partly is arranged on the drive path that is used for motor output is delivered to the driving wheel of vehicle, and play a part stepless speed variator, speed changer partly constitutes the part of drive path and is connected to the stepless speed variator part, control gear is characterised in that and comprises: (b) stepless change control gear, the stepless change control gear can be worked in the speed Control process of speed changer part, be used for synchronously carrying out the speed Control of described stepless speed variator part, make the speed ratio that partly limits by described stepless speed variator part and described speed changer change continuously with the described speed Control of described speed changer part.
In above-mentioned control gear, the stepless change control gear can be worked in the speed changer that changes the step by step speed Control process partly at speed ratio, be used for synchronously carrying out the speed Control of stepless speed variator part with the speed Control of speed changer part, make the speed ratio that is limited by stepless speed variator part and speed changer part change continuously, that is, make because the speed ratio that causes variable quantity is step by step moved in the gear shift of speed changer part.Thereby reduce before speed changer gear shift action partly and the variation step by step of engine speed afterwards, reduced the shifting shock of speed changer part.Further, but drive system plays a part stepless speed variator 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, speed changer partly is that a grade automatic transmission is arranged.In this form of the present invention, when the gear shift of speed changer part, the overall ratio that is limited by the speed ratio of the speed ratio of stepless speed variator part and speed changer part changes step by step.In this case, overall ratio can be faster than changing when overall ratio changes continuously.Thereby drive unit can operationally play a part stepless speed variator as a whole under the control of stepless change control gear, make the vehicle traction torque to change reposefully, and speed ratio can change step by step with the torque of quick change vehicle traction.
In any one the 4th form of the present invention according to first to the 3rd form, but the speed Control of stepless change control gear and speed changer part synchronously changes the speed ratio of stepless speed variator part with the direction place of working that changes in the opposite direction with the speed ratio of speed changer part, makes the variable quantity that reduces the speed ratio that is partly limited by stepless speed variator part and speed changer.In this form of the present invention, reduce before speed changer 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 speed Control of stepless speed variator part is carried out in stepless change control gear place of working in the inertia phase that the input speed of the speed changer part of the gear shift action of speed changer part changes.In this form of the present invention, the speed Control of stepless speed variator part is synchronously carried out by the speed Control of stepless change control gear and speed changer part.
In any one the 6th form of the present invention according to first to the 5th form, control gear further comprises the torque minimizing control gear that is used to reduce speed changer input torque partly, and torque reduces control gear and reduce input torque in the speed Control process of speed changer part.In this form of the present invention, torque reduces control gear and reduces speed changer part input torque, makes to reduce corresponding to owing to partly be the torque of the inertia torque that produces of the velocity variations of the speed changer rotatable member partly of form with step change transmission in the gear shift course of action.Thereby reduced shifting shock.For example, torque reduces control gear and reduces input torque by the torque of minimizing motor or the torque of second motor.
According to the 7th form of the present invention, provide a kind of and be used for the control gear of (a) driver for vehicle, comprise stepless speed variator part and step change transmission part, stepless speed variator partly comprises differential attachment, differential attachment has first element that is connected to motor, be connected to second element and the three element that is connected to transmission part of first motor, and stepless speed variator partly comprises second motor that further comprises in the drive path that is arranged between transmission part and the driving wheel of vehicle, stepless speed variator 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, control gear is characterised in that and comprises: (b) stepless change control gear, but the stepless change control gear is the place of working in the speed Control process of step change transmission part, be used for synchronously carrying out the speed Control of stepless speed variator part, make the speed ratio of stepless speed variator part change with the direction that changes in the opposite direction with speed changer speed ratio partly with the speed Control of step change transmission part.
In above-mentioned control gear, the stepless change control gear can be worked in the step change transmission that changes the step by step speed Control process partly at speed ratio, be used to change the speed ratio of stepless speed variator part, to reduce variable quantity step by step, the feasible overall ratio that is limited by the speed ratio and the step change transmission speed ratio partly of stepless speed variator part changes continuously, that is, make because the speed ratio that causes variable quantity is step by step moved in the gear shift of speed changer 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 stepless speed variator 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 gear of (a) driver for vehicle, comprise stepless speed variator part and step change transmission part, stepless speed variator partly is arranged on the driving wheel drive path that is used for motor output is delivered to vehicle, and play a part stepless speed variator, step change transmission partly constitutes the part of drive path, play a part to have grade automatic transmission and be connected to the stepless speed variator part, control gear is characterised in that and comprises: (b) stepless change control gear, the stepless change control gear can be worked in the speed Control process of step change transmission part, be used for synchronously carrying out the speed Control of stepless speed variator part, make the speed ratio of stepless speed variator part change with the direction that changes in the opposite direction with step change transmission speed ratio partly with the speed Control of step change transmission part.
In above-mentioned control gear, the stepless change control gear can be worked in the step change transmission that changes the step by step speed Control process partly at speed ratio, be used to change the speed ratio of stepless speed variator part, to reduce variable quantity step by step, the feasible overall ratio that is limited by the speed ratio and the step change transmission speed ratio partly of stepless speed variator part changes continuously, that is, make because the speed ratio that causes variable quantity is step by step moved in the gear shift of speed changer 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 stepless speed variator 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 speed Control of stepless speed variator part is carried out in stepless change control gear 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 stepless speed variator part is synchronously carried out by the speed Control of stepless change control gear and step change transmission part.
According to the present invention's the tenth form any in the 7th to the 9th form, control gear further comprises the torque minimizing control gear that is used to reduce speed changer input torque partly, and torque reduces control gear and reduce input torque in the speed Control process of speed changer part.In this form of the present invention, torque reduces control gear 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 rotatable member partly of stepless speed variator in the gear shift course of action owing to the rotatable member partly of step change transmission in the gear shift course of action.Thereby reduced shifting shock.For example, torque reduces control gear and reduces input torque by the torque of minimizing motor or the torque of second 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 gear place of working changes stepless speed variator speed ratio partly in the direction relative with the change direction of step change transmission speed ratio partly, to reduce the speed ratio variable quantity that is partly limited by stepless speed variator part and 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 gear that is used for driver for vehicle is provided, comprise stepless speed variator part and step change transmission part, stepless speed variator partly is arranged on the driving wheel drive path that is used for motor output is delivered to vehicle, and play a part stepless speed variator, step change transmission partly constitutes the part of drive path, play a part to have grade automatic transmission and be connected to the stepless speed variator part, control gear is characterised in that and comprises: (a) engine speed control gear, in the speed Control of step change transmission part, can work, be used for controlling the speed of motor by the electric stepless change action of control stepless speed variator part.
At the above-mentioned control gear that is used for drive system that comprises the stepless speed variator part that plays the electric steplessly variable transmission effect, the engine speed control gear is worked in the speed Control process of step change transmission part, come by utilizing the speed of stepless speed variator part as the function control motor of electric steplessly variable transmission, promptly, by utilizing the differential function of differential attachment, make engine speed change fast with improved response, and the zero hour no matter step change transmission gear shift is partly moved, because speed Control and engine speed control are finished simultaneously, the speed Control of step change transmission part is finished fast.For example, as the partial response of level speed changer and during change into lower gear in the trampling operation of accelerator pedal, engine speed accelerator pedal trample operation after improve apace, make motor export (power) and improve apace.Further, because change into lower gear control is finished simultaneously with engine speed control, the change into lower gear action of step change transmission part is finished fast.
The 13 form of the present invention according to the 12 form, the engine speed control gear is by utilizing the speed of motor control motor, make the speed of motor equal, make that the speed of motor equals the target engine speed value when the gear shift action of step change transmission part is finished.In this form of the present invention, engine speed is controllable with improved response, 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 variance ratio of the operation amount of accelerator pedal, the variance ratio of the speed of engine speed control gear control motor.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, differential attachment comprises differential COMM communication, and differential COMM communication is not operationally switched the stepless speed variator part as the differential state and the stepless speed variator part of electric steplessly variable transmission work in the stepless speed variator part between the non-differential state as electric steplessly variable transmission work.In this form of the present invention, the stepless speed variator part not only can be operated the effect as electric steplessly variable transmission, but also switch to stepless speed variator part not as the non-differential state of electric steplessly variable transmission work by differential state switching device, that is, stepless speed variator is partly set up the state in mechanical transmission path.
According to the 16 form of the present invention, a kind of control gear that is used for driver for vehicle is provided, comprise stepless speed variator part and step change transmission part, stepless speed variator partly comprises differential attachment, differential attachment operationally is assigned to first motor and transmission part with the output of motor, stepless speed variator partly comprises second motor that further comprises in the drive path that is arranged between transmission part and the driving wheel of vehicle, stepless speed variator partly plays a part electric steplessly variable transmission, step change transmission partly constitutes the part of drive path, play a part to have a grade automatic transmission, control gear is characterised in that and comprises: (a) differential state switching device, differential COMM communication is arranged in the differential attachment, and operationally the stepless speed variator part is not switched between the non-differential state as electric steplessly variable transmission work as the differential state and the stepless speed variator part of electric steplessly variable transmission work in the stepless speed variator part; (b) engine speed control gear, the engine speed control gear can be worked in the speed Control of step change transmission part, be used for controlling with a method in two engine speed controlling methods the speed of motor, when the 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 speed Control process of step change transmission part.
Above-mentioned control gear is provided for control-driven system, and wherein differential attachment is not being switched the stepless speed variator part as the differential state and the stepless speed variator part of electric steplessly variable transmission work in the stepless speed variator part by differential state switching device between the non-differential state as electric steplessly variable transmission work.In this control gear, the engine speed control gear works the speed of controlling motor in the speed Control process of step change transmission part with a method in two engine speed controlling methods in the speed Control process of step change transmission part, rely on power splitting mechanism whether to place differential state or selected this method of non-differential state when the speed Control of step change transmission part begins.Thereby engine speed changes fast with improved response.For example, when differential attachment places differential state, the engine speed control gear in the speed Control process of step change transmission part by being used to by utilizing the stepless speed variator part (promptly as the speed of the function control motor of electric steplessly variable transmission, by utilizing the differential function of differential attachment), make engine speed change fast 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 differential attachment is placed in differential state when the speed Control of step change transmission part begins, then the engine speed control gear is controlled the speed of motor by the electric stepless gear shift action of control stepless speed variator part.In this form of the present invention, engine speed changes fast with improved response, and the zero hour no matter step change transmission gear shift is partly moved.Because speed Control and engine speed control are finished simultaneously, the speed Control of step change transmission part is finished fast.For example, as the partial response of level speed changer and during change into lower gear in the trampling operation of accelerator pedal, engine speed accelerator pedal trample operation after improve apace, make motor export (power) and improve apace.Further, because change into lower gear control is finished simultaneously with engine speed control, the change into lower gear action of step change transmission part is finished fast.
In the 18 form of the present invention according to the 16 or the 17 form, if differential attachment is placed in non-differential state when the speed Control of step change transmission part begins, then the engine speed control gear because the variation of the speed of the motor that the gear shift action of step change transmission part causes, is controlled the described speed of described motor by utilizing.In this form of the present invention, engine speed changes fast with improved response in the gear shift course of action of step change transmission part, and differential attachment is not switched to differential state from non-differential state.
In the 19 form of the present invention according to the 18 form, if differential attachment is placed in non-differential state when the speed Control of step change transmission part begins, then by utilizing the speed of motor control motor, differential attachment remains on non-differential state to the engine speed control gear simultaneously in the speed Control process of step change transmission part.In this form of the present invention, engine speed changes fast with improved response in the gear shift course of action of step change transmission part, and differential attachment is not switched to differential state from non-differential state.And by utilizing the motor control engine speed, make to equal target engine speed when finishing in step change transmission gear shift action partly with further improved response.
According to the 20 form of the present invention, a kind of control gear that is used for driver for vehicle is provided, comprise stepless speed variator part and step change transmission part, stepless speed variator partly comprises differential attachment, differential attachment operationally is assigned to first motor and transmission part with the output of motor, stepless speed variator partly comprises second motor that further comprises in the drive path that is arranged between transmission part and the driving wheel of vehicle, stepless speed variator partly plays a part electric steplessly variable transmission, step change transmission partly constitutes the part of drive path, play a part to have a grade automatic transmission, control gear is characterised in that and comprises: (a) differential state switching device, differential COMM communication is arranged in the differential attachment, and operationally the stepless speed variator part is not switched between the non-differential state as electric steplessly variable transmission work as the differential state and the stepless speed variator part of electric steplessly variable transmission work in the stepless speed variator part; (b) engine speed control gear, the engine speed control gear can be worked in the speed Control of step change transmission part, be used for controlling with a method in two engine speed controlling methods the speed of motor, when the 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 speed Control process of step change transmission part.
Above-mentioned control gear is provided for control-driven system, and wherein differential attachment is not being switched the stepless speed variator part as the differential state and the described stepless speed variator part of electric steplessly variable transmission work in the stepless speed variator part by differential state switching device between the non-differential state as electric steplessly variable transmission work.In this control gear, the engine speed control gear works the speed of the method control motor of the described speed Control of passing through change step change transmission part in the speed Control process of step change transmission part in the speed Control process of step change transmission part, whether the dependence differential attachment places differential state or non-differential state to select this method when the speed Control of step change transmission part begins.Thereby engine speed changes fast with improved response.For example, when differential attachment places differential state, the engine speed control gear in the speed Control process of step change transmission part by being used to by utilizing the stepless speed variator part (promptly as the speed of the function control motor of electric steplessly variable transmission, by utilizing the differential function of differential attachment), make engine speed change fast 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 differential attachment is placed in differential state when the speed Control of step change transmission part begins, then the engine speed control gear is controlled the speed of motor by the electric stepless gear shift action of control stepless speed variator part, and carries out the speed Control of step change transmission part.In this form of the present invention, engine speed changes fast with improved response, and the zero hour no matter step change transmission gear shift is partly moved.Because speed Control and engine speed control are finished simultaneously, the speed Control of step change transmission part is finished fast.For example, as the partial response of level speed changer and during change into lower gear in the trampling operation of accelerator pedal, engine speed accelerator pedal trample operation after improve apace, make motor export (power) and improve apace.Further, because change into lower gear control is finished simultaneously with engine speed control, the change into lower gear action of step change transmission part is finished fast.
The present invention's the 22 form according to the 20 or the 21 form, if differential attachment is placed in non-differential state when the speed Control of step change transmission part begins, then the engine speed control gear is carried out the speed Control of step change transmission part, make the speed of motor by utilizing because the variation of the speed of the motor 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, engine speed changes fast with improved response in the gear shift course of action of step change transmission part, and differential attachment 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, differential attachment has first element that is connected to motor, be connected to second element of first motor and be connected to the three element of transmission part, but differential state switching device place of working allows first relative to each other to rotate to three element, be used to set up differential state, and allow first to three element as the rotation of unit or keep second element to maintain static, be used to set up non-differential state.In this form of the present invention, differential attachment 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 clutch and/or break, clutch operationally is connected to each other first in the three element any two, be used to make first to rotate as a unit to three element, break operationally is fixed to second element and is used to process the fixed fixed component of second element.In this form of the present invention, differential attachment can easily switch between differential state and non-differential state.
Preferably, step change transmission partly comprises the differential attachment that operationally output of motor is assigned to first motor and transmission part, and is arranged on second motor in the drive path between described transmission part and the driving wheel of vehicle.In this case, the speed ratio of drive system can change and comes powered vehicle, keeps motor at optimal operational condition simultaneously, makes fuel economy be improved.
Preferably, differential attachment is provided with differential state switching device, operationally with differential attachment at the differential state that can obtain differential function with can not obtain to switch between the lock state of differential function.In this case, differential attachment 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 speed changer electricity is improved, and, have owing to can mechanically transmit the advantage of high transmission efficiency of function of the gear type transmission device of vehicle drive force.For example, when the low or medium output of travelling of the low or medium speed for vehicle is travelled, motor is when normal output area, and differential attachment 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, differential attachment places the output of motor mainly to be delivered to the lock state of driving wheel by the machine 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 energy loss can take place when the speed changer work that changes in the mode of electricity as its speed ratio when differential attachment.When vehicle is in high output travelling state, the speed changer work that differential attachment changes in the mode of electricity as its speed ratio.Thereby, have only when vehicle during at the low or medium output travelling state of low or medium speed's travelling state, the speed changer work that differential attachment changes in the mode of electricity as its speed ratio, the feasible electric energy maximum flow that is produced by motor (promptly, the electric energy maximum flow that must transmit from motor) minimizing be can access, needed size that can make motor and the needed minimized in size that comprises the drive system of motor made.
Preferably, stepless speed variator part at the differential state that can obtain differential function with can not obtain to switch between the lock state of differential function, makes that the stepless speed variator part is that feasible stepless change state and electric stepless change action 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 stepless speed variator part between stepless change state and step change state.
Preferably, differential attachment has first element that is connected to motor, is connected to second element of first motor and is connected to the three element of transmission part.Differential state switching device is set to allow first relative to each other to rotate to three element, setting up differential state, and allow first to three element as a unit rotation or keep second element to maintain static, to set up lock state.In this case, differential attachment switches between differential state and lock state.
Preferably, differential state switching device comprises clutch and break, but this clutch place of working is connected to each other first in the three element any two so that first rotate as a unit to three element, and break operationally is fixed to second element and is used to process the fixed fixed component of second element.In this case, differential attachment can easily switch between differential state and non-differential state.
Preferably, releasing clutch and break place differential state with differential attachment, wherein, first relative to each other rotates to three element, differential attachment is worked as the electric controlled differential device, engaging clutch is 1 speed changer work with the tolerance actuation mechanism as having speed ratio, or engage brake with the tolerance actuation mechanism as having the speedup speed changer work that is lower than 1 speed ratio.In this case, differential attachment switches between differential state and lock state, and as the speed changer work with single gear, this speed changer has single fixed speed ratio or a plurality of gear with each fixed speed ratio.
Preferably, differential attachment is a planetary gear set, and first element is the planetary wheel carrier of planetary gear set, and second element is the sun gear of planetary gear set, and three element is the gear ring of planetary gear set.In this case, the axial dimension of differential attachment can access minimizing, and differential attachment simply is made of a planetary gear system.
Preferably, planetary gear set is a grade pinion type.In this case, the axial dimension of differential attachment can access minimizing, and differential attachment simply is made of a planetary gear system.
Preferably, the overall ratio of driver for vehicle is limited by the speed ratio of above-mentioned stepless speed variator part and the speed ratio of above-mentioned speed changer part.In this case, vehicle drive force can obtain on the scope of the broad of overall ratio by the speed ratio that utilizes speed changer part, makes the efficient of electric stepless change control of stepless speed variator be further enhanced.
Preferably, the overall ratio of driver for vehicle is limited by the speed ratio of above-mentioned stepless speed variator 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 by the speed ratio that utilizes step change transmission part, makes the efficient of electric stepless change control of stepless speed variator be further enhanced.
Stepless speed variator part is by the step change transmission part and place the stepless speed variator of stepless change state partly to constitute, and the step change transmission part is by the step change transmission part with place the stepless speed variator that can not obtain electric stepless change action partly to constitute.
Preferably, differential attachment when engaging above-mentioned clutch as have speed ratio be 1 speed changer work and when engaging above-mentioned break as the speed increasing mechanism work that is lower than 1 speed ratio.In this case, differential attachment is as the speed changer work with single gear, and this speed changer has single fixed speed ratio or a plurality of gear with each fixed speed ratio.
Preferably, differential attachment is a planetary gear set, and first element is the planetary wheel carrier of planetary gear set, and second element is the sun gear of planetary gear set, and three element is the gear ring of planetary gear set.In this case, the axial dimension of differential attachment can access minimizing, and differential attachment simply is made of a planetary gear system.
Preferably, planetary gear set is a grade pinion type.In this case, the axial dimension of differential attachment can access minimizing, and differential attachment simply is made of a planetary gear system.
Preferably, when the speed of a motor vehicle surpassed the CLV ceiling limit value that the high-speed travel state of determining vehicle is provided, differential attachment placed non-differential state.In this case, when actual vehicle speed has surpassed CLV ceiling limit value, the output of motor mainly is delivered to driving wheel by the machine 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 energy loss can take place when the speed changer work that changes in the mode of electricity as its speed ratio when differential attachment.The CLV ceiling limit value 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 driving force surpassed the height output travelling state CLV ceiling limit value that definite vehicle is provided, differential attachment placed non-differential state.In this case, when actual vehicle speed has surpassed CLV ceiling limit value, the output of motor mainly is delivered to driving wheel by the machine 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 energy loss can take place when the speed changer work that changes in the mode of electricity as its speed ratio when differential attachment.The CLV ceiling limit value 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 motor of electric steplessly variable transmission work or function differential attachment place non-differential state.In this case, differential attachment places transmit mode usually, and switches to non-transmit mode, in case above-mentioned fault or function deterioration, to allow travelling of vehicle.
Description of drawings
Fig. 1 is the schematic representation 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 embodiment's of presentation graphs 1 the chart of gear shift action and the relation of the various combination of the serviceability of the hydraulic 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;
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 working among Fig. 1 embodiment in the step change state;
Fig. 4 is the view of input and output signal of electric control device of the expression embodiment's that provides control graph 1 drive system;
Fig. 5 is the functional block diagram of major control function that the electric control device of Fig. 4 is shown;
Fig. 6 is to be in the same two-dimensional coordinate system that Control Parameter was limited of form by travelling speed 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 gear, and be used in the example of switching between engine-driving pattern and the motor drive mode of the actuating force source handoff boundary line chart of being stored of limited boundary line between engine-driving zone and motoring zone, make the view that these figure are relative to each other;
Fig. 7 illustrates and limits the highest fuel-economy linearity curve of motor, and explanation in the stepless change state motor operation (being represented by dotted lines) and in the step change state view of the example of the fuel consume figure of the difference between the operation (with single-point line expression) of motor;
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 represented stepless change of the dotted line among Fig. 6 and the boundary line in step change zone;
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 speed change lever and operates the view of the example of the speed change gear of selecting a position in a plurality of shift position;
Figure 11 is the control operation of the electric control device of presentation graphs 5, i.e. the flow chart of the speed Control operation of stepless speed variator part in the speed Control process of step change transmission part;
Figure 12 is illustrated in the stepless change state of gear when level speed changer 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 electric control device of Fig. 4;
Figure 14 is the flow chart corresponding to the flow chart of Figure 11, shows the control operation of the electric control device of Figure 13, i.e. the speed Control operation of stepless speed variator part in the 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 gear when level speed changer part upgrades third gear from second gear control operation shown in the flow chart 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 gear when level speed changer part lowers category second gear from third gear, in the control operation shown in the flow chart 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 gear when level speed changer part upgrades third gear from second gear control operation shown in the flow chart 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 gear when level speed changer part lowers category second gear from third gear the control operation shown in the flow chart of Figure 14;
Figure 19 is the schematic representation corresponding to the schematic representation 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 relation of the gear shift action of exercisable drive system of hybrid power vehicle and the various combination of the serviceability of the hydraulic control friction coupling device that carries out each gear shift action 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 rotatable member of the drive system of hybrid power vehicle of the Figure 19 in the step change state;
Figure 22 is a perspective view, shows to be operated the example that the seesaw switch of selecting speed change state is the manual exercisable speed change state selection device of form by the user;
Figure 23 is a functional block diagram, and the major control function of the electric control device of Fig. 4 according to another embodiment of the present invention is shown;
Figure 24 is a flow chart, and the control operation of the electric control device of Figure 23 is shown, that is, and and the control operation of engine speed in the 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, gear is during from fourth speed potential drop shelves to second gear, the control operation shown in the flow chart 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, gear is during from fourth speed potential drop shelves to second gear, the control operation shown in the flow chart 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 gear upgrades the fourth speed position from third gear, and the control operation shown in the flow chart 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 gear upgrades fourth speed from third gear, and the control operation shown in the flow chart of Figure 24.
Embodiment
With reference to accompanying drawing, will describe the preferred embodiment of the invention in detail.
Fig. 1 is the schematic representation of gear 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 gear according to an embodiment of the invention.In Fig. 1, gear 10 comprises: with input shaft 14 is that form is arranged on the input rotary component on the common shaft of the gearbox that plays the fixed component effect 12 that is attached to car body; Directly connect or be connected to indirectly the stepless speed variator part 11 of input shaft 14 via unshowned pulsation absorption damper (vibration damping device); Be arranged between stepless speed variator part 11 and the driving wheel of vehicle 38 (shown in Figure 5) and level or multiple-speed gear-box part 20 arranged via what transmission part 18 (transmission shaft) was connected in series to stepless speed variator part 11 and driving wheel 38; And be the output rotary component that form is connected to step change transmission part 20 with output shaft 22.Input shaft 14, stepless speed variator part 11, step change transmission part 20 and output shaft 22 are connected in series mutually.As shown in Figure 5, this gear 10 is applicable to horizontal FR vehicle (engine behind front wheel rear wheel drive vehicle), and being arranged on internal-combustion engine 8 is the actuating force source of form and driving wheel between 38, so that vehicle drive force is delivered to driving wheel to 38 from motor 8 by differential gearing 36 (final speed reducer) and a pair of live axle.Motor 8 can be petrol engine or diesel engine, and plays a part directly to connect or absorb the vehicle drive force source that damper is connected to input shaft 14 indirectly via pulsation.Notice that lower half portion of gear 10 constitutes with respect to its axis symmetry, it omits in Fig. 1.So same among the embodiment who is described below.In this gear 10, motor 8 directly is connected mutually with stepless speed variator part 11.Should directly connect and mean that motor 8 and speed changer part 11 were connected to each other, and not arrange hydraulic control transmission device betwixt, be connected to each other but can absorb damper by above-mentioned pulsation such as torque-converters or fluid couplers.
Stepless speed variator part 11 comprises: the first motor M1; Play and to operate the power splitting mechanism 16 of mechanically distributing to the differential attachment effect of the first motor M1 and transmission part 18 with the output of the motor 8 that will receive by input shaft 14; With and the second motor M2 that together rotates of output shaft and transmission part 18.The second motor M2 can be arranged on any position of the drive path between transmission part 18 and the driving wheel 38.With in the present embodiment the first and second motor M1 and each among the M2 all is so-called dynamoelectric machine with motor function and generator function.Yet the first motor M1 should play to operate the generator with generation electric energy and reaction force at least, and the second motor M2 should play a part to operate to produce the actuating force source of vehicle drive force at least.
The critical piece that power splitting mechanism 16 comprises has: have single pinion type first planetary gear set 24, the switch clutch C0 of for example about 0.418 velocity ratio ρ 1 and switch break B1.First planetary gear set 24 has the rotatable member of being made up of following: the first sun gear S1, the first planetary pinion P1; Support the first planetary pinion P1, make the planetary pinion P1 that wins around its axis and around the rotatable first planetary wheel carrier CA1 of the axis of the first sun gear S1; With the first gear ring R1 by the first planetary pinion P1 and first sun gear S1 engagement.The number of teeth of the first sun gear S1 and the first gear ring R1 represented by ZS1 and ZR1 respectively, and above-mentioned velocity 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 motor 8, the first sun gear S1 and is connected to the first motor M1, and the first gear ring R1 is connected to transmission part 18 simultaneously.Switch break B0 and be arranged between the first sun gear S1 and the gearbox 12, switch clutch C0 is arranged between the first sun gear S 1 and the first planetary wheel carrier CA1.When switch clutch C0 and break B0 discharge, power splitting mechanism 16 places differential state, wherein three elements in first planetary gear set 24 that is made of the first sun gear 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 motor 8 be assigned to the first motor M1 and transmission part 18, thus, the part of the output of motor 8 is used to drive the first motor M1 to produce electric energy, and this electric energy is stored or is used for driving the second motor M2.Thereby, power splitting mechanism 16 places stepless change state (the CVT state of electric foundation), wherein the rotating speed of transmission part 18 is continuous variables, and regardless of the rotating speed of motor 8, promptly, place differential state, wherein the speed ratio γ 0 of power splitting mechanism 16 (rotating speed of the rotating speed/transmission part 18 of input shaft 14) changes to maximum value γ 0max continuously from minimum value γ 0min, 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 maximum value γ 0max continuously from minimum value γ 0min.
When switch clutch C0 or break B0 engagement when power splitting mechanism 16 places the stepless change state simultaneously, mechanism 16 enters into the non-differential state that lock state maybe can not obtain differential function.Particularly, when switch clutch C0 meshes, the first sun gear S1 and the first planetary wheel carrier CA1 link together, three rotatable members of first planetary gear set 24 that makes power splitting mechanism 16 be placed in one to be made of sun gear S1, the first planetary wheel carrier CA1 and the first gear ring R1 can be used as the lock state of a unit rotational, promptly place the non-differential state that can not obtain differential function, make stepless speed variator part 11 also place non-differential state.In this non-differential state, the rotating speed of the rotating speed of motor 8 and transmission part 18 is equal to each other, make stepless speed variator part 11 (power splitting mechanism 16) place fixed speed ratio speed change state or step change state, wherein the speed changer that equals 1 fixed speed ratio γ 0 works to have in mechanism 16.
When switching break B0 replacement switch clutch C0 joint, the first sun gear S1 is fixed to gearbox 12, make power splitting mechanism 16 place the non-rotary lock state of the first sun gear S1, promptly, place the second non-differential state that can not obtain differential function, make stepless speed variator 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, stepless speed variator part 11 places fixed speed ratio speed change state or step change state, and wherein stepless speed variator 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 break B0 form plays differential COMM communication, it can be operated with at differential state (promptly, unlock state) and non-differential state (promptly, lock state) between, promptly (wherein stepless speed variator part 11 is as the electric steplessly variable transmission operation that can carry out the stepless change operation with lock state at stepless change state (wherein stepless speed variator part 11 (power splitting mechanism 16) is operationally as the electric steplessly variable transmission of its speed ratio continuous variable), and wherein the speed ratio of speed changer part 11 is maintained fixed, promptly, fixed speed ratio speed change state (non-differential state), wherein speed changer part 11 can be operated with as the single gear with a speed ratio with have the speed changer of a plurality of gears of corresponding speed ratio, promptly, the fixed speed ratio speed change state, wherein speed changer part 11 as can operate with as single gear with a speed ratio and have the speed changer of a plurality of gears of corresponding speed ratio) between optionally switch stepless speed variator part 11 speed changer part speed changer part speed changer part speed changer part speed changer parts.
Step change transmission part 20 comprises single pinion type second planetary gear set 26, single pinion type the third line star gear train 28 and single pinion type fourth line star gear train 30.Second planetary gear set 26 comprises: the second sun gear S2; The second planetary pinion P2; Support the second planetary pinion P2 and make that the second planetary pinion P2 can be around its axis and around the second planetary wheel carrier CA2 of the axis of second sun gear S2 rotation; And with the second gear ring R2 of the second sun gear S2 by second planetary pinion P2 engagement.Second planetary gear set 26 has for example about 0.562 velocity ratio ρ 2.The third line star gear train 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 gear S3; And with the three gear ring R3 of the 3rd sun gear S3 by the third line star gear P3 engagement.For example, the third line star gear train 28 has about 0.425 velocity ratio ρ 3.Fourth line star gear train 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 gear S4; And with the four gear ring R4 of the 4th sun gear S4 by fourth line star gear P4 engagement.For example, fourth line star gear train 30 has about 0.421 velocity ratio ρ 4.The number of teeth of the second sun gear S2, the second gear ring R2, the 3rd sun gear S3, the 3rd gear ring R3, the 4th sun gear S4 and the 4th gear ring R4 is expressed as ZS2, ZR2, ZS3, ZR3, ZS4 and ZR4 respectively, and above-mentioned velocity 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 gear S2 and the 3rd sun gear S3 are fixed as a device each other integratedly, are connected to transmission part 18 selectively by second clutch C2, and are fixed to gearbox 12 selectively by the first break B1.The second planetary wheel carrier CA2 is fixed to gearbox 12 selectively by the second break B2, and the 4th gear ring R4 is fixed to gearbox 12 selectively by the 3rd break B3.The above-mentioned second gear ring R2, the third line star wheel frame CA3 and fourth line star wheel frame CA4 are by fixed to one another and be fixed to output shaft 22 integratedly.The 3rd gear ring R3 and the 4th sun gear S4 are fixed to one another integratedly and be connected to transmission part 18 selectively by first clutch C1.
Above-mentioned switch clutch C0, first clutch C1, second clutch C2, switching break B0, the first break B1, the second break B2 and the 3rd break 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 of the wet multiple disc clutch that comprises a plurality of friction disks, these friction disks by hydraulic actuator or band brake each other pressurized against, band brake comprises going barrel, and the coiling going barrel outer circumferential face and at one end by hydraulic actuator fastening a band or two bands.Among clutch C0-C2 and the break B0-B3 each is all optionally meshed so that two parts are linked together, and each clutch or break 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 by being selected from above-mentioned switch clutch C0, first clutch C1, second clutch C2, switching break B0, the first break B1, the second break B2 and the 3rd break B3 is optionally set up.These positions have into corresponding speed ratio γ (the input shaft speed N that geometrical progression changes
IN/ output shaft speed N
OUT).Particularly, note, power splitting mechanism 16 is provided with switch clutch C0 and break B0, make as mentioned above, stepless speed variator part 11 can be selectively placed on the fixed speed ratio speed change state (wherein by the engagement of switch clutch C0 or switching break B0, speed changer part 11 can be operated as the speed changer that its speed ratio is maintained fixed) and stepless change state (wherein, speed changer part 11 can be operated as stepless speed variator).Thereby in this gear 10, step change transmission constitutes by speed changer part 20 and by the stepless speed variator part 11 that the switch clutch C0 or the engagement of switching break B0 are placed in the fixed speed ratio speed change state.In addition, electric steplessly variable transmission is by speed changer part 20 and do not have switch clutch C0 or switch the engagement of break B0 and the stepless speed variator part 11 that is placed in the electrodeless variable-speed state constitutes.In other words, gear 10 wherein one switches to the step change state by engagement switch clutch C0 and switching break B0, and switches to the stepless change state by discharging switch clutch C0 and break B0.Stepless speed variator part 11 also is considered to be the speed changer that switches between step change state and stepless change state.
As 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 by the engagement action of switch clutch C0, first clutch C1 and the 3rd break 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 by the engagement action of switch clutch C0, first clutch C1 and the second break 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 by the engagement action of switch clutch C0, first clutch C1 and the first break 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 by 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 by the engagement action of switching first clutch C1, second clutch C2 and switching break 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 by the engagement action of second clutch C2 and the 3rd break B3.Neutral position N sets up by only meshing switch clutch C0.
On the other hand, under the situation of gear 10 as stepless speed variator, switch clutch C0 that represents in Fig. 2 and switching break B0 are released, make stepless speed variator part 11 play stepless speed variator, and the speed changer part 20 that is connected in series to stepless speed variator part 11 plays step change transmission, thus, be delivered to and place first (promptly to the speed that rotatablely moves of the speed changer part 20 of a gear of fourth speed position, the rotating speed of transmission part 18) is continuous variable, makes continuous variable in the scope that the speed ratio of the drive system when speed changer part 20 places of these gears is being scheduled to.Thereby, the speed ratio γ T that determines by stepless speed variator part 11 and step change transmission part 20 (that is the overall ratio γ T (hereinafter referred to as " overall ratio ") of the speed changer part gear of determining by the speed ratio γ of the speed ratio γ 0 of stepless speed variator part 11 and step change transmission part 20 10) continuous variable on adjacent gear.
The alignment chart of Fig. 3 is illustrated in by the stepless speed variator part 11 that plays the stepless speed variator part or the first speed changer partial action by straight line and plays relation between the rotating speed of the rotatable member in each gear of gear 10 of step change transmission part 20 formations of the step change transmission part (automatic transmission part) or the second speed changer partial action.The alignment chart of Fig. 3 is two-dimentional rectangular coordinate system, and wherein, the velocity ratio ρ of planetary gear set 24,26,28,30 represents along horizontal axis, and the relative rotation speed of rotatable member is represented along vertical shaft.Article three, the following horizontal line in the horizontal line, promptly horizontal line X1 represents 0 rotating speed, and the top horizontal line in three horizontal lines, promptly horizontal line X2 represents 1.0 rotating speed, promptly is connected to the motion speed N of the motor 8 of input shaft 14
EHorizontal line XG represents the rotating speed of transmission part 18.
The relative rotation speed of the 3rd rotatable member (three element) RE3 of second rotatable member (second element) RE2 that represents the first sun gear S1 form respectively corresponding to three vertical line Y1, Y2 and the Y3 of the power splitting mechanism 16 of stepless speed variator part 11, first rotatable member (first element) RE1 of the first planetary wheel carrier CA1 form and the first gear ring R1 form.Distance among vertical line Y1, Y2 and the Y3 between the adjacent vertical line is determined by the velocity ratio ρ 1 of first planetary gear set 24.That is, the distance between vertical line Y1 and the Y2 corresponds to " 1 ", and the distance between vertical line Y2 and the Y3 is corresponding to velocity ratio ρ 1.In addition, corresponding to five vertical line Y4 of speed changer part 20, Y5, Y6, Y7 and Y8 represent the second and the 3rd fixing integratedly each other sun gear S2 respectively, the 4th rotatable member (quaternary part) RE4 of S3 form, the 5th rotatable member of the second planetary wheel carrier CA2 form (the 5th element) RE5, the 6th rotatable member (the hexa-atomic) RE6 of the 4th gear ring R4 form, the second fixing integratedly each other gear ring R2 and the 3rd and fourth line star wheel frame CA3, the 7th rotatable member of CA4 form (the 7th element) RE7, and the relative rotation speed of the 8th rotatable member (the 8th element) RE8 of fixing the 3rd gear ring R3 of one and the 4th sun gear S4 form each other.Distance between the adjacent vertical line is determined by velocity ratio ρ 2, ρ 3 and the ρ 4 of second, third and fourth line star gear train 26,28 and 30.In the relation between the vertical line of alignment chart, the sun gear and the distance between the planetary wheel carrier of each planetary gear set correspond to " 1 ", and the planetary wheel carrier of each planetary gear set and the distance between the gear ring correspond to velocity ratio ρ.In stepless speed variator part 11, the distance between vertical line Y1 and the Y2 corresponds to " 1 ", and the distance between vertical line Y2 and the Y3 corresponds to velocity ratio ρ.In step change transmission part 30, each second, third and the sun gear and the distance between the planetary wheel carrier of fourth line star gear train 26,28,30 correspond to " 1 ", and each planetary gear set 26,28,30 planetary wheel carrier and the distance between the gear ring correspond to velocity ratio ρ.
Alignment chart with reference to Fig. 3, the power splitting mechanism 11 of gear 10 (stepless speed variator part 11) is provided so that, the first rotatable member RE1 of first planetary gear set 24 (the first planetary wheel carrier CA1) is fixed to input shaft 14 (motor 8) integratedly, and optionally be connected to the second rotatable member RE2 (the first sun gear S1) by switch clutch C0, and this second rotatable member RE2 is fixed to the first motor M1, and optionally be fixed to gearbox 12 by switching break B0, and the 3rd rotatable member RE3 (the first gear ring R1) is fixed to the transmission part 18 and the second motor M2, makes rotatablely moving of input shaft 14 transmit (input) to step change transmission part 20 by transmission part 18.Relation between the rotating speed of the rotating speed of the first sun gear S1 and the first gear ring R1 represents that by the straight line that tilts L0 represents, L0 is by the intersection point between line Y2 and the X2.
For example, when the release movement of gear 10 by switch clutch C0 and break B0 places the stepless change state, obtain raising or reducing by the reaction force that the operation of the first motor M1 that produces electric energy produces by control by the rotating speed of the first represented sun gear S1 of the intersection point between line L0 and the vertical line Y1, make rotating speed by the first represented sun gear R1 of the intersection point between line L0 and the vertical line Y3 be lowered or raise.When switch clutch C0 is engaged, the first sun gear S1 and the first planetary wheel carrier CA1 are connected to each other, power splitting mechanism 16 is placed in one above-mentioned three rotatable members as the first non-differential state that a unit rotation is arranged, make line L0 align, make transmission part 18 to equal engine speed N with horizontal line X2
ESpeed rotation.On the other hand, when break B0 is switched in engagement, stop the rotation of the first sun gear 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 (i.e. the rotation of the transmission part of being represented by the intersection point between line L0 and the Y3 18) is higher than the speed N of motor
E, and be passed to speed changer part 20.
In step change transmission part 20, the 4th rotatable member RE4 optionally is connected to transmission part 18 by second clutch C2, and optionally be fixed to gearbox 12 by the first break B1, and the 5th rotatable member RE5 optionally is fixed to gearbox 12 by the second break B2, and the 6th rotatable member RE6 optionally is fixed to gearbox 12 by the 3rd break B3 simultaneously.The 7th rotatable member RE7 is fixed to output shaft 22, and the 8th rotatable member RE8 optionally is connected to transmission part 18 by first clutch C1 simultaneously.
When first clutch C1 and the 3rd break B3 were engaged, step change transmission part 20 placed first gear.The rotating speed of the output shaft 22 in first gear is fixed to the vertical line Y7 of rotating speed of the 7th rotatable member RE7 of output shaft 22 by expression and the intersection point between the angled straight lines L1 is represented, the vertical line Y8 and the intersection point between the horizontal line X2 of the rotating speed of angled straight lines L1 by representing the 8th rotatable member RE8 and represent the vertical line Y6 of rotating speed of the 6th rotatable member RE6 and the intersection point between the horizontal line X1.Similarly, the intersection point between the vertical line Y7 of the angled straight lines L2 that determined by these engagement action of the rotating speed of the output shaft 22 in second gear set up of the engagement action by the first clutch C1 and the second break B2 and the rotating speed of the 7th rotatable member RE7 that represents to be fixed to output shaft 22 is represented.Intersection point between the vertical 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 by the first clutch C1 and the first break B1 is set up is determined by these engagement action and the rotating speed of the 7th rotatable member RE7 that represents to be fixed to output shaft 22 is represented.Intersection point between the vertical 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 by the first clutch C1 and the second break B2 is set up is determined by these engagement action and the rotating speed of the 7th rotatable member RE7 that represents 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 rotatable member RE8 utilize the driving force that receives from stepless speed variator part 11 (that is, from power splitting mechanism 16) with engine speed N
EIdentical speed rotation.When switching break B0 and replace switch clutch C0 to be engaged, the 8th rotatable member RE8 utilizes the driving force that receives from power splitting mechanism 16 to be higher than engine speed N
ESpeed rotation.By first clutch C1, second clutch C2 and the intersection point between the vertical line Y7 of the horizontal linear L5 that determines by these engagement action of the rotating speed that switches the output shaft 22 in the 5th gear that the engagement action of break B0 sets up and the rotating speed of the 7th rotatable member RE7 that represents to be fixed to output shaft 22 represent.
Fig. 4 illustrates signal that is received by the electric control device 40 that is provided for controlling gear 10 and the signal that produces from electric control device 40.This electric control device 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 mixed power drive controlling, and carry out such as drive controlling to the speed Control of speed changer part 20 to motor 8 and motor M1 and M2.
Electric control device 40 is set to receive various signals from various sensors shown in Figure 4 and switch, such as: the signal of expression engine cooling water temperature TEMPw; The selected working position P of expression speed change lever
SHSignal; The motion speed N of expression motor 8
ESignal; The signal of selected group the value that drives forwards the position of expression gear 10; The signal of expression M pattern (motor drive mode); The signal of expression air conditioner working state; Expression is corresponding to the rotational speed N of output shaft 22
OUTThe signal of vehicle velocity V; The signal of the temperature of the work machine oil of expression step change transmission part 20; The signal of the working state of expression side brake; The signal of the working state of expression pedal brake; The signal of expression catalyst temperature; Operation amount (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 working state that stepless speed variator part 11 (power splitting mechanism 16) is placed the step change switch of fixed speed ratio speed change state (non-differential state) (wherein, gear 10 plays step change transmission); Expression provides the signal of working state that stepless speed variator part 11 is placed the stepless change switch of stepless change state (differential state) (wherein, gear 10 plays stepless speed variator); The rotational speed N of representing the first motor M1
M1(hereinafter referred to as " the first electromotor velocity N
M1") signal; And the rotational speed N of representing the second motor M2
M2(hereinafter referred to as " the second electromotor velocity N
M2") signal.
Electric control device 40 also is configured to produce such as following various signals: drive electronic throttle actuator 94 and be used to control throttle valve opening θ
THThe signal of aperture; Control is fed to the signal of the supplying fuel amount of motor 8 by fuel injection apparatus 96; Regulate the signal of supercharger pressure; The signal of operation electric air conditioner; Be used for signal by the ignition timing of ignition mechanism 98 control motors 8; The signal of operating motor M1 and M2; The signal of the operation that operation expression speed change lever is selected and the shift range indicator of shift pattern; Operation is used to represent the signal of the velocity ratio indicator of velocity 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 ABS (Anti-lock Braking System) 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 hydraulic control friction coupling device of controlling stepless speed variator 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 Figure 5); The operation 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 Ruiss Controll computer.
Fig. 5 is the functional block diagram of Fig. 4, is used to illustrate the major control function of electric control device 40.Whether the gear shift action that is set to judge step change transmission part 20 at the step change control gear 54 shown in Fig. 5 should take place, and, judges the position that speed changer part 20 should gear shift that is.Output torque T based on vehicle velocity 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 (speed Control figure or relation) that is stored in the storage device 56 and represents 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 gear 54 produces the order (shift command) that will be applied to hydraulic control unit 42, optionally mesh and discharge hydraulic control friction coupling device (except switching clutch C0 and break B0), be used for setting up determined gear according to the table of Fig. 2.
Mixed power control gear 52 plays the stepless change control gear, and be set to control motor 8 in operating range work efficiently, mixed power control gear 52 is also controlled the first and second motor M1, M2, make and place the stepless change state (promptly at gear 10, place differential state in stepless speed variator part 11) in, the driving force that optimization is produced by motor 8 and the second motor M2 with by the ratio of the first motor M1, to be used for controlling thus speed ratio γ 0 speed changer part as the stepless speed variator part 11 of electric steplessly variable transmission work at its reaction force that produces in as the generator working procedure.For example, mixed power control gear 52 is based on the operation amount 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 Speed V, and based on the target vehicle output of being calculated and need calculate vehicle target by the generated energy that the first motor M1 produces and always export.Mixed power control gear 52 is when considering transmission loss, acting on the load on each device of vehicle, the assist torque of the second 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 mixed power control gear 52 control motors 8
EWith torque T
E, make to obtain target engine output of being calculated and the generated energy that produces by the first motor M1.
Mixed power control gear 52 is set to carry out mixed power control in the current selected gear of considering step change transmission part 20, the speed changer part is thus with the drivability of raising vehicle and the fuel economy of motor 8.In mixed power control, stepless speed variator 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 motor 8
EThe rotating speed of the transmission part of determining with vehicle velocity V and by the selected gears of speed changer part 20 18.That is, mixed power control gear 52 is determined the desired value of the overall ratio γ T of speed changer part 10, makes motor 8 according to the highest fuel-economy linearity curve (fuel economy figure or the relation) work of being stored.The desired value of the overall ratio γ T of speed changer part body 10 allows engine torque T
EWith speed N
EControlled, make motor 8 provide and obtain 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 working efficiency and the highest fuel economy that satisfies motor 8, and by engine speed N
EThe axle and engine torque T
EThe two-dimensional coordinate system of axis limit in be defined.The speed ratio γ 0 of mixed power control gear 52 control stepless speed variator parts 11 makes overall ratio γ T can be controlled in the predetermined scope (for example, between 13 and 0.5).
In mixed power control, mixed power control gear 52 control inverters 58 make the electric energy that is produced by the first motor M1 be fed to the electric accumulator 60 and the second motor M2 by inverter 58.Promptly, the major component of the driving force that is produced by motor 8 mechanically is delivered to transmission part 18, the remaining part of driving force is consumed to convert this part to electric energy by the first motor M1 simultaneously, this electric energy is fed to the second motor M2 by inverter 58, make the second motor M2 utilize the electric energy work of being supplied, produce the mechanical energy that will be passed to transmission part 18.Thereby drive system is provided with circuit, and by this circuit, the electric energy that a part produced of the driving force by conversion engine 8 is converted into mechanical energy.
Especially, as the variable speed operation of level speed changer part 20 during by 54 controls of step change control gear, before the speed ratio of step change transmission part 20 changes step by step and afterwards, the overall ratio γ T of gear 10 changes step by step.When overall ratio γ T step by step, when promptly discontinuity 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, mixed power control gear 52 is set to synchronously control with the variable speed operation of step change transmission part 20 variable speed operation of stepless speed variator part 11, makes the speed ratio of stepless speed variator part 11 change with the direction relative with the direction of step change transmission part 20 speed ratios variation.In other words, mixed power control gear 52 and the speed Control of step change transmission part 20 are synchronously carried out the speed Control of stepless speed variator part 11, make the overall ratio γ T of speed changer part 20 before the gear shift action of step change transmission part 20 and change continuously afterwards.For example, mixed power control gear 52 is set to synchronously carry out with step change transmission part 20 speed Control of stepless speed variator part 11, make speed changer part 11 speed ratio with the direction that changes in the opposite direction step by step of the speed ratio of speed changer part 20 on change the variable quantity step by step of the speed ratio of speed changer part 20, the speed changer part is with the overall ratio γ T that stops gear 10 transient changing before the gear shift action of step change transmission part 20 and afterwards.
Describe in another way, when motor 8 is operably connected to step change mechanism, motor 8 operation that generally line is indicated as the single-point among Fig. 7, when motor 8 was operably connected to stepless speed variator, motor 8 was along the curve motion of the highest fuel-economy linearity curve of indicating in Fig. 7 or edge the highest relatively more close fuel-economy linearity curve.Thereby, when motor 8 is connected to stepless speed variator, be used to obtain the engine torque T of required vehicle traction torque (driving force)
ECan be than be connected to the engine speed N of step change transmission the highest more close fuel-economy linearity curve when motor 8
EThe following execution.Thereby the fuel economy of stepless speed variator is improved with respect to step change transmission.Given this, mixed power control gear 52 is set to control the speed ratio γ 0 of stepless speed variator part 11, make motor 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 speed changer part 20 changes step by step.
As described above, the speed Control of mixed power control gear 52 and step change transmission part 20 is synchronously carried out the speed Control of stepless speed variator part 11,, carries out the synchronous speed Control of speed changer part 11 that is.When process response time after the moment that take place is moved in the gear shift of step change control gear 54 definite step change transmission parts 20, the synchronous speed Control of stepless speed variator part 11 starts.This response time is from the above-mentioned input speed that regularly is carved into speed changer part 20 really (promptly, the rotating speed of transmission part 18 (the second motor M2)) owing to the engagement of the friction coupling device that is fit to or the moment that changes of release movement, that is, entered the moment of so-called " inertia phase " that the rotating speed of transmission part 18 wherein changes in the gear shift course of action of speed changer part 20 to speed changer part 20.Response time can obtain by experiment, and is stored in the storage, or mixed power control gear 52 starts the synchronous speed Control of stepless speed variator part 11 can be set to actual change when the speed that detects transmission part 18 time.The synchronous speed Control of stepless speed variator part 11 finished in the moment when the inertia phase in the process of moving in the gear shift of speed changer part 20 finishes.The synchronization control time up to this finish time can obtain by experiment, and be stored in the storage, or mixed power control gear 52 can be set to finish the synchronous speed Control of speed changer part 11 when the actual change of the speed of transmission part 18 has become zero.Thereby, when step change transmission part 20 is in inertia phase in its gearshift procedure, mixed power control gear 52 is carried out the above-mentioned speed Control of stepless speed variator part 11, speed changer partly makes synchronous 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 transmission part 18 has become zero.
Mixed power control gear 52 comprises the engine output controller that is used to control motor 8, with by controlling the throttle valve actuator separately or in combination with opening and closing electronic throttle 94, and control enters the fuel injection time and the emitted dose of the fuel injection apparatus 96 of motor 8, and/or the igniter firing time of ignition mechanism 98, needed output is provided.For example, 52 basic setups of mixed power control gear are the operation amount A based on accelerator pedal
CCAnd according to the operation amount A of throttle valve
CCWith aperture θ
THBetween the (not shown) that concerns of predetermined storage control the throttle valve actuator, make aperture θ
THAlong with operation amount A
CCIncrease and increase.
Mixed power control gear 52 can be set up motor drive mode, and wherein, vehicle is driven by motor M2 by the electric CVT function of utilizing stepless speed variator part 11, and need not consider whether motor 8 is in non-operating state or idling mode.Solid line among Fig. 6 is represented to be defined for to switch between motor 8 and motor (for example, the second motor M2) and is used to start and the engine-driving zone in the vehicle drive force source (hereinafter referred to as " actuating force source ") of powered vehicle and the boundary line in motoring zone.In other words, vehicle traction pattern switching between " the engine-driving pattern " in the engine-driving zone that starts by motor 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 by the second motor M2 that is used as actuating force source as actuating force source.The boundary line of presentation graphs 6 (solid line A) is used for switching between engine-driving pattern and motor drive mode predetermined storage relation is at Control Parameter and output torque T by the vehicle velocity V form
OUTActuating force source in the two-dimensional coordinate system that the drive-force-related value of form limits is switched the example of figure (actuating force source figure).This actuating force source is switched figure and together is stored in the storage device 56 with the speed change border of being represented by solid line and single-point line in Fig. 6 line chart (speed change figure).Storage device 56 plays speed change figure storage device and actuating force source figure storage device.
Mixed power control gear 52 is determined vehicle conditions whether in motoring zone or engine-driving zone, and sets up motor drive mode or engine-driving pattern.Be somebody's turn to do based on the vehicle condition of representing by vehicle velocity V and needed torque T, and carry out above-mentioned definite according to the actuating 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 engine torque T
EWhen being in relatively low scope), or when vehicle velocity V is in relatively low scope (, when vehicle load is relatively low), generally set up motor drive mode by mixed power control gear 52.Thereby vehicle starts in motor drive mode usually, rather than starts in the engine-driving pattern.Vehicle condition when starting vehicle is when being switched outside the motoring zone of scheming to limit, because required output torque T by the actuating force source of Fig. 6
OUTWith engine torque T
EBecause of the operation of accelerator pedal increases, so vehicle can start in the engine-driving pattern.
In order to reduce the braking drag of motor 8 under non-operating state, and improve fuel economy in the motor drive mode, because the differential function of stepless speed variator part 11, mixed power control gear 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) and make that the motor of winning is controlled to rotate freely, so have negative velocity N by control speed changer part 11
M1So-called " torque auxiliary " of auxiliary engine 8 is by will be from the supply of electrical energy of the first motor M1 or electric accumulator 60 to the second motor M2, and making the second motor M2 can operate driving torque is delivered to driving wheel 38 becomes possibility.Thereby, in the engine-driving pattern, except motor, can also use motor.
Mixed power control gear 52 is set to keep motor 8 to be in running state owing to the electric CVT function of stepless speed variator part 11, and no matter whether vehicle is static or travel with relatively low speed.When needs first motor M1 work is static to be at vehicle during to electric accumulator 60 chargings, for the electric accumulator 60 that the electric weight SOS that is stored in the electric accumulator 60 is reduced charges, when although the motion speed that is in the second motor M2 that is determined by vehicle velocity 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 motor 8 that the first motor M1 turns round under fair speed
ECan keep enough height, pass through self-operating to allow motor 8.
Mixed power control gear 52 also is set to the electric CVT function owing to stepless speed variator part 11, by controlling the running speed N of the first motor M1
M1And/or the running speed N of the second 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 travels under relatively low speed.In other words, mixed power control gear 52 is set to control the running speed N of the first motor M1 on demand
M1Or the running speed N of the second motor M2
M2, keep engine speed N simultaneously
EConstant or control engine speed N on demand
EIn the alignment chart from Fig. 3 obviously as seen, for example in order to improve the engine speed N in the running process of vehicle
E, mixed power control gear 52 improves the running speed N of the first motor M1
M2While is by the running speed N of the second definite motor M2 of vehicle velocity V (speed of driving wheel 38)
M2Keep constant.
Stepless speed variator part 11 switches to the non-differential state (fixed speed ratio speed change state) of wherein having set up the machine power bang path.Under this non-differential state, the first motor M1 that there is no need to operate as generator produces anti-torque, makes the driving torque that is produced by the first motor M1 as generator work under the control of mixed power control gear 52 can be delivered to transmission part 18.Thereby, mixed power control gear 52 can be set to separately or and the second motor M2, one biconditional operation, the first motor M1, control engine speed N
E, stepless speed variator part 11 places step change state (fixed speed ratio speed change state) simultaneously.Yet in the step change state of stepless speed variator part 11, the speed of the second rotatable member RE2 of power splitting mechanism 16 (the first sun gear S1) is also influenced by vehicle velocity V, makes engine speed N
EVariance ratio be lower than the stepless change state of speed changer part 11.In the non-differential state of the stepless speed variator part of being set up by the engagement action of switching break B0 11, the first motor M1 is fixed to gearbox 12, and cannot rotate and control engine speed N
E
Top gear decision maker 62 be set to judge gear 10 under vehicle condition and according to be stored in the storage device 56 and in Fig. 6 the speed change border line chart by 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 break B0 which, gear 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 mixed power control gear 52 can not carry out mixed power control or stepless change control, make step change apparatus 54 can carry out predetermined step change control, in this step change control, speed changer 20 is according to being stored in speed change border line chart automaitc shfit in the storage device 56 and pass through example shown in Fig. 6.Fig. 2 represents the combination of the engagement action of hydraulic control friction coupling device C0, C1, C2, B0, B1, B2 and B3, and this figure is stored in the storage device 56, and optionally is used for the automaitc shfit of step change transmission part 20.In the step change state, the gear 10 that is made of stepless speed variator part 11 and step change transmission part 20 plays according to the table automaitc shfit among Fig. 2 so-called a grade automatic transmission is arranged as a whole.
When top gear decision maker 62 has judged that gear 10 should shift into the 5th gear, switching control 50 order hydraulic control units 42 discharge switch clutch C0 and break B0 is switched in engagement, so that stepless speed variator part 11 can work to have the auxiliary gear box of 0.7 fixed speed ratio γ 0, for example, make gear 10 make the as a whole high gear that places with so-called " hypervelocity gear " of being lower than 1.0 speed ratio.When top gear decision maker 62 does not also judge that gear 10 should shift into the 5th gear, switching control 50 order hydraulic control units, 42 engagement switch clutch CO also discharge switching break B0, so that stepless speed variator part 11 can work to have the auxiliary gear box of 1.0 fixed speed ratio γ 0, for example, make gear 10 do as a whole placing and have the deceleration gear that is not less than 1.0 speed ratio.Thereby, when gear 10 switches to the step change state by switching control 50, under the control of switching control 50, stepless speed variator part 11 as auxiliary gear box work is placed in selected gear in two gears, the step change transmission part 20 that is connected in series to stepless speed variator part 11 simultaneously plays step change transmission, and making gear 10 play what is called as a whole has a grade automatic transmission.
Judge vehicle condition when switching control 50 and be in stepless change when zone that gear 10 is placed the stepless change state, switching control 50 order hydraulic control units 42 discharge switch clutch C0 and break B0, and stepless speed variator part 11 is placed the stepless change state.Simultaneously, switching control 50 makes mixed power control gear 52 can carry out mixed power control, and order step change control gear 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 storage device 56 and the speed change border line chart automaitc shfit by example shown in Fig. 6.In the latter case, step change control gear 54 is carried out automatic shift control by the combination (except the combination of the engagement that comprises switch clutch C0 and break B0) that option table compatibly is shown in the working state of the friction coupling device in the table among Fig. 2.Thereby, the stepless speed variator part 11 that switches to the stepless change state under the control of switching control 50 plays stepless speed variator, and the step change transmission part 20 that is connected in series to stepless speed variator part 11 simultaneously plays step change transmission, make gear 10 that enough vehicle drive forces are provided, make to be delivered to and place first (promptly to the speed that rotatablely moves of the speed changer part 20 of the gear in fourth speed position, the rotating speed of transmission part 18) changes continuously, make speed ratio continuous variable on the scope of being scheduled to of when speed changer part 20 places gear of these gears gear 10.Thereby the speed ratio of speed changer part 20 is continuous variable on adjacent gear, thus, and the overall ratio γ T continuous variable of gear 10.
Differential state determining apparatus 80 is set to judge whether power splitting mechanism 16 places differential state, that is, whether stepless speed variator 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 gear 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 speed changer part of carrying out.For example, based on switching control 50 according to the handoff boundary line chart by example shown in Fig. 6 to by vehicle velocity V and output torque T
OUTWhether the vehicle condition of expression is in the step change zone that is used for gear 10 is placed the step change state, or be in the judgement that is used for gear 10 is placed the stepless gear shift zone of stepless change state, whether 80 pairs of stepless speed variator 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 stepless speed variator part 11 places differential state, make the speed Control of stepless speed variator part 11 and the 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 gear 10, stepless speed variator part 11 is placed in differential state simultaneously.
Torque reduces control gear 82 and is set to reduce the torque that will be delivered to driving wheel 38.For example, by by the aperture that reduces electrical throttle valve 94 or the supplying fuel amount of fuel injection apparatus 96, or carry out the firing time of 98 pairs of motors 8 of post ignition device and reduce engine torque T
EEngine torque reduce control, torque reduces the input torque T that control gear 82 reduces step change transmission parts 20
INReduce the torque that will be delivered to driving wheel 38.Torque minimizing control gear 82 also is set to control or be additional to the engine torque minimizing by the minimizing of replacement engine 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 motor M2, make when electric accumulator 60 is charged, temporarily produce reverse vehicle traction torque by inverter 58, or regenerative brake torque.
Step change transmission part 20 upgrades under the control of step change control gear 54, gear 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 speed changer part 20 stands shifting shock owing to so-called " inertia torque ", this inertia torque increases input torque T
INAnd the torque of increase output subsequently T
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 speed changer part 20 or transmission part 18
EDecline produce by the energy that temporarily produces by motor 8.
If do as a whole step change transmission part 20 gear shift under the control of step change control gear 54 in the infinite variable speed state that under the control of switching control 50, places at gear 10, then under the control of mixed power control gear 52, carry out the speed Control of stepless speed variator part 11, to prevent before the gear shift action of speed changer part 20 and the variation of the overall ratio γ T of gear 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 speed changer 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 the speed of the input speed of speed changer part 20 or transmission part 18, 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 rotatable member RE4-RE8 of step change transmission part 20 produces.In this case, because inertia torque has speed changer 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 speed changer part 20 action because of the descend reason of the inertia torque that produced of the speed of the second and/or the 3rd rotatable member RE2, the RE3 of speed changer part 11, stepless speed variator part 11 also can stand shifting shock.
In view of above-mentioned possibility, under the control of step change control gear 54 in its gear shift course of action, torque reduces the input torque T that control gear 82 is set to reduce step change transmission part 20
INParticularly, by carrying out the one or both in above-mentioned engine torque minimizing control and the motor torque minimizing control, torque reduces the input torque T that control gear 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 speed Control of 52 pairs of stepless speed variator parts 11 of mixed power control gear, torque reduces 82 couples of input torque T of control gear
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 gear 82 is set to reduce step change transmission part 20
IN, the torque pulsation variable quantity when make reducing under the control of step change control gear 54 engagement and coming the engagement action of the suitable friction coupling device of speed changer part 20 gear shift finished, the mesh impact of the coupling device of reducing friction thus.
With the figure that describes in detail among Fig. 6.Shown in Figure 6 and be stored in speed change border line chart (speed Control figure or relation) in the storage device 56 and be used to judge that step change transmission part 20 whether should gear shift by the mode of example, and by vehicle velocity V and required output torque T
OUTThe Control Parameter 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 travelling
OUTOutput torque upper limit T1, just judge that above it motor vehicle driven by mixed power is in high output travelling state.Output torque T
OUTBe the example of drive-force-related value, it relates to the driving force 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 double dot dash line.Thereby the dotted line of Fig. 6 and double dot dash line constitute the handoff boundary line chart (switching controls figure or relation) of storage, and it is switched control gear 50 and utilizes with based on vehicle velocity V and output torque T
OUTWhether the Control Parameter 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 storage device 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 vehicle velocity 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 actuating force source switching figure can use comparison and the actual output torque T of the actual vehicle speed V that stored and 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 gear 10 to the step change state.
More than Biao Shi drive-force-related value 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 driving force.Parameter can be: based on the operation amount A of accelerator pedal
CCOr the aperture of throttle valve (or air inflow, empty so than or fuel injection amount) and engine speed N
EThe actual value of being calculated; Or required (target) engine torque T
E, speed changer part 20 required (target) output torque T
OUT, and the estimated value of required vehicle drive force (based on the operation amount A of accelerator pedal
CCOr the operating angle of throttle valve and calculate) in any one.Above-mentioned vehicle traction torque not only can be based on output torque T
OUTDeng calculating, also can obtain based on the speed ratio of differential gearing 36 and the radius calculation of driving 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 gear 10 places the step change state when vehicle is in high-speed travel state.If gear 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 performance characteristic of the first motor M1, this first motor is undersized, and its maximum electric energy output is less relatively, make and to export in the travelling state when higher relatively at the height of vehicle that the anti-torque of the first motor M1 can be not excessive when motor output.
With reference to Fig. 8, handoff boundary line chart (switching controls figure or relation) is shown, this figure is stored in the storage device 56, and limits as judging the motor output line that whether vehicle condition is in level or stepless change zone by the boundary line of switching control 50 uses.These motor output lines are by engine speed N
ELimit with the Control Parameter of engine 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 engine 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 vehicle velocity V and output torque T
OUTRelation (figure) in the two-dimensional coordinate system that the Control Parameter of form limits is determined.
The step change zone that is limited by 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 vehicle velocity V is higher relatively when the torque of motor 8, carry out step change control, relatively low or when vehicle velocity V is relatively low when the torque of motor 8 simultaneously, that is, when motor 8 is in normal output state, carry out stepless change control.
Similarly, the step change area limiting that is limited by the handoff boundary line chart of Fig. 8 is engine 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 engine torque N
TWith speed N
EAnd the output of the motor 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 motor 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 motor 8 when relatively low (, when motor 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 vehicle velocity V or motor output.
In above-mentioned present embodiment, gear 10 is placed in the low speed of vehicle or the medium velocity travelling state or is placed in the stepless change state in the low output of vehicle or middle output travelling state, guarantees the fuel economy of vehicle higher degree.Be higher than at vehicle in the running at high speed under the vehicle velocity V of upper limit V1, gear 10 places the step change state, wherein the output of motor 8 mainly is delivered to driving wheel 38 by the mechanical energy bang path, makes to improve fuel economy because mechanical energy is converted to conversion loss (doing the time spent when 11 electric controlling stepless variable speed devices of stepless speed variator part can the take place) minimizing of electric energy.
At output torque T
OUTThe height that is higher than the vehicle of upper limit T1 is exported in the travelling state, and gear 10 places the step change state.Thereby, only when vehicle velocity V is relatively low or medium or when motor output is relatively low or medium, just gear 10 is placed the stepless change state, make the required electric weight that produces by the first motor M1 (the maximum electric weight that must transmit from the first motor M1) to reduce, the required electric reaction force of the first motor M1 can reduce thus, can make the required size of the first motor M1 and the second motor M2 thus and comprise that the required size of the drive system of these motor minimizes.
That is, determine upper limit TE1, make as motor output T
EWhen not being higher than upper limit TE1, the first motor M1 can resist anti-torque, when vehicle is in wherein engine torque T
EWhen being higher than the height output travelling state of upper limit TE1, stepless speed variator part 11 places the step change state.Therefore, in the step change state of speed changer part 11, the first motor M1 do not need as in the stepless change state of speed changer part 11 with respect to engine torque T
EThe opposing anti-torque, the feasible deterioration that can reduce the durability of the first motor M1 prevents the increase of its required size simultaneously.In other words, in the present embodiment, the required maximum output of the first motor M1 can be less than exporting T corresponding to motor
EPeaked anti-torque bearing capacity.That is, the required maximum output of the first motor M1 can be determined, and makes the anti-torque bearing capacity less than corresponding to the engine torque T that surpasses upper limit TE1
EValue, make the size of the motor M1 that wins can be less.
The maximum output of the first motor M1 is in motor nominal rating value by this definite motor of experiment in the environment of work.Above-mentioned engine torque T
EThe upper limit be determined by experiment, make that the upper limit is to be equal to or less than engine torque T
EPeaked value, below the value, the first motor M1 can resist anti-torque at this, the durability of the motor M1 that wins is worsened can access minimizing.
As shown in FIG. 8, more need to improve the durability of vehicle rather than improve in the high output of the vehicle travelling state of Economy of fuel oil in vehicle operators, gear 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 speed changer 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 speed change lever 92, speed change lever 92 is near the seat cross setting of vehicle operators, and be operated to select: parking spot P by one in the following shift position of forming, be used for gear 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 releasing state and break B0 all disconnects and the output shaft 22 of while speed changer part 20 is in the lock state; Reverse direction actuation position R is used for powered vehicle rearward; Neutral position N is used for the gear 10 neutral position state that drive path in the gear 10 are disconnected that is placed in one; Automatic forerunner's shift pattern D; And manual forerunner's shift pattern M.
For example, speed change lever 92 is mechanically connected to the hand control valve that is included in the hydraulic control unit 42, make hand control valve in response to a selected shift position of manually being operated into of speed change lever 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 by 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 non-driven states selected when vehicle is not driven, 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 releasing state) power interruption state.Reverse direction actuation position R and automatic and manual forerunner's shift pattern D, M are activation points selected when vehicle is driven, in this activation point, as as shown in the table of Fig. 2, the power transfer path in speed changer part 20 is in the power delivery status that at least one clutch among wherein the first clutch C1 and second clutch C2 is in engagement.
Detailed description, when speed change lever 92 from Parking position P or neutral position N manually-operable during to reverse direction actuation position R, engagement second clutch C2 switches to power delivery status with the drive path in the speed changer part 20 from power interruption state.When speed change lever 92 during from neutral position N manually-operable to automatic forerunner's shift pattern D, meshing at least, first clutch C1 switches to power delivery status with the drive path in the speed changer part 20 from power interruption state.Automatically forerunner's shift pattern D provides position the most at a high speed, and selectable position " 4 " to " L " is the engine braking position that wherein applies engine braking 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 front wheel driving shift pattern D on the side direction of vehicle.Speed change lever 92 is operable to manual front wheel driving shift pattern M and comes chosen position " D " manually to arrive a position in " L ".Detailed description, speed change lever 92 can from manual forerunner's shift pattern M move to upgrade position "+" and downshift position "-" (each other vehicle vertically on spaced apart).Each speed change lever 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 gear 10, that is, and and corresponding to the minimum of each different overall ratio γ T of the highest output speed of gear 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 be determined by the quantity of selected selectable gear.Speed change lever 48 is made speed change lever 92 automatically be back to manual forerunner's shift pattern M from upgrade position "+" and downshift position "-" by the biasing arrangement biasing such as spring.Gearshift 90 is provided with can be operated to detect the shift pattern sensor of selected speed change lever 92 current locations, makes and represents selected speed change lever 98 work at present position P
SHAnd the signal provision of the quantity of the variable speed operation of speed change lever 92 arrives electric control device 40 in manual forerunner's shift pattern M.
For example, when speed change lever 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 gear 10, mixed power control gear 52 is carried out the stepless change control of power splitting mechanism 16, and the control gear of step change simultaneously 54 is carried out the automatic shift control of step change transmission part 20.For example, when gear 10 placed the step change state, the gear shift of gear 10 action is automatically controlled selected suitable gear in first gear to the, five gears (representing) in Fig. 2.When gear 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 automatically controlled selects first gear suitable gear in the fourth speed position, makes the overall ratio γ T of gear 10 be controlled to continuous variable in predetermined scope.Automatically forerunner position D is the selected position of setting up automatic shift mode (automatic mode), gear 10 gear shift automatically in this pattern.
On the other hand, when speed change lever 92 is operated manual forerunner's shift pattern M, the gear shift action of gear 10 is switched control gear 50, mixed power control gear 52 and step change control gear 54 and automatically controls, make overall ratio γ T variable in predetermined scope, the lower limit of this scope is determined that by the gear with lowest speed ratio this gear is determined by the manually selected gear in the gear " D " to " L ".For example, when gear 10 placed the step change state, the gear shift of gear 10 action is control automatically in the prespecified range of above-mentioned overall ratio γ T.When gear 10 places the stepless change state, the speed ratio of power splitting mechanism 16 changes continuously, a suitable gear (quantity of this gear is determined by manually selected in the gear " D " to " L " gear) of selecting in the gear is automatically controlled in the gear shift of step change transmission part 20 action simultaneously, makes the overall ratio γ T of gear 10 be controlled to continuous variable in predetermined scope.Manually front wheel 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 gear 10 is manually selected.
The major control operation that the flowcharting of Figure 11 is carried out by electric control device 40 promptly, is used for controlling in the speed Control process of step change transmission part 20 the speed Control program of the variable speed operation of stepless speed variator part 11.This 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 gear 10 and places the stepless change state as level speed changer part 20 from the upgrade control operation of third gear of second gear.
The speed Control program determines with step S1 (" step " the is following to be omitted) beginning corresponding to step change control gear 54 whether the gear shift action of step change transmission part 20 should take place.This judgement by the gear determining speed changer part 20 and should gear shift arrive one of them whether based on output torque T by vehicle velocity V and speed changer part 20
OUTThe vehicle condition of expression and basis are determined to carry out by 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 speed changer portion 20 from second gear to third gear should take place at time point T1.
When obtaining sure judgement in S1, 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 stepless speed variator part 11 places the stepless change state.Whether this judgement relies on vehicle condition to be in by by 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, gear 10 should place the stepless change state.
If obtain negative judgement in S2, then control flow proceeds to the S6 corresponding to step change control gear 54, carries out the speed Control of the gear shift action of judging in S1 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 gear 54, carry out the speed Control of the gear shift action of in S1, determining of carrying out speed changer part 20, then proceed to S4 corresponding to mixed power control gear 52, carry out the speed Control with the synchronous stepless speed variator part 11 of the speed Control of step change transmission part 20 in S3, make the speed ratio of speed changer 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 speed changer part 20.For example, the speed Control of the speed ratio of stepless speed variator part 11 and speed changer part in S3 has synchronously changed amount corresponding to the variable quantity step by step of the speed ratio of speed changer part 20 step by step in the direction that changes in the opposite direction step by step with the speed ratio of step change transmission part 20, prevents before the gear shift action of speed changer part 20 and the overall ratio γ T transient changing of gear 10 afterwards.
Speed Control in S3 and S4 or in the speed Control process of S6, the torque of carrying out the input torque TIN that reduces step change transmission part 20 in the step S5 that reduces control gear 82 corresponding to torque reduces control (during the time period of representing from time point t2 to time point t3) in Figure 12.For example, in the speed Control process of S3 and S4, the speed NE of motor does not change as illustrated in fig. 12, but because the result that the speed of the rotatable member of step change transmission part 20 descends and the speed of the rotatable member of stepless speed variator part 11 descends, and produced the inertia torque that increases output torque TOUT.In the 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 engine torque TE or use second motor M2 operating motor torque minimizing control to come minimizing input torque TIN in S5 by carrying out engine 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 gear that proceed to S7 cause electric controller 40 are carried out various controls, rather than the speed Control of step change transmission part 20, carry out circulation for one that perhaps finishes current speed Control program.For example, when gear 10 places the stepless change state, mixed power control gear 52 is carried out the speed Control of stepless speed variator part 11 based on vehicle condition.
As mentioned above, present embodiment is set to, the speed ratio of stepless speed variator part 11 changes the variable quantity step by step that reduces step change transmission part 20 speed ratio in the speed Control process under the control of mixed power control gear 52 (stepless change control gear), make that overall ratio (whole speed ratio) the γ T of the gear 10 (drive system) determined by the speed ratio of the speed ratio of speed changer part 11 and speed changer 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 gear 10 to make the as a whole stepless speed variator that plays a part, and has improved fuel economy thus.
In addition, in the speed Control of in the inertia phase that the gear shift of step change transmission part 20 is moved, carrying out stepless speed variator part 11 under the control of mixed power control gear 52.That is the synchronous execution of speed Control of the speed Control of stepless speed variator part 11 and speed changer part 20.In addition, carry out the speed Control of stepless speed variator part 11 and come on the direction that the speed ratio with speed changer part 20 changes in the opposite direction step by step, to change the amount of the speed ratio of speed changer part 11, reduced the variable quantity of the overall ratio γ T of gear 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 speed changer part 20 and the variable quantity of engine speed NE afterwards, made and further reduce shifting shock.
Present embodiment also is set to reduce inertia torque that input torque TIN produces corresponding to the result owing to the velocity variations of the rotatable member of step change transmission part 20 and the amount of the inertia torque that produces owing to the result of the velocity variations of the rotatable member of stepless speed variator part 11 under torque reduces the control of control gear 82, these inertia torques produce in the gear shift course of action of speed changer part 20.Thereby, reduced shifting shock.
Other embodiments of the present invention will be described.In being described below, the reference symbol identical with the symbol that uses in the above-described embodiments will be used for representing corresponding element.
Second embodiment
In the aforementioned embodiment, mixed power control gear 52 be set to the speed Control of step change transmission part 20 synchronously (promptly, in moving of speed changer part 20 made inertia phase in the process) speed Control of the stepless speed variator part 11 carried out, make the overall ratio γ T of gear 10 before the gear shift action of step change transmission part 20 and change continuously afterwards.And present embodiment provides some examples, be illustrated in the speed Control of the stepless speed variator 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 speed changer part 20 and afterwards the overall ratio of gear 10 change continuously.
In the foregoing embodiments, carry out the speed Control of stepless speed variator part 11 by mixed power control gear 52, the direction that makes the speed ratio of speed changer part 11 change in the opposite direction at the speed ratio with step change transmission part 20 changes, and makes the overall ratio γ T of gear 10 before the gear shift action of speed changer part 20 and change continuously afterwards.In order to prevent gear 10 before the gear shift of speed changer part 20 action and overall ratio γ T transient changing afterwards, the speed ratio change direction of speed changer part 11 is required to change in the opposite direction with the speed ratio of speed changer part 20.In order only to guarantee before speed changer part 20 and the continuous variation of the overall ratio γ T of gear 10 afterwards, the above-mentioned requirements relevant with the speed ratio change direction is dispensable.
Promptly, can carry out the speed Control of stepless speed variator part 11 of speed ratio that is used for before the gear shift of step change transmission part 20 action and continuously changes the overall ratio γ T of gear 10 afterwards, make the speed ratio of speed changer part 11 on the speed ratio change direction of speed changer part 20, change.In concrete examples more of the present invention, the speed ratio of speed changer part 11 changes in the speed ratio change direction of speed changer part 20.
Corresponding to the functional block diagram among Figure 13 of the block diagram among Figure 15 major control function according to the electric control device 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 entered inertia phase and enters decision maker 84.
Inertia phase enters decision maker 84 and is set to based on after will discharging the coupling device release movement of carrying out the gear shift action, whether the velocity variations of transmission part 18 (the second motor M2) begins owing to the gear shift action that the engagement torque that begins to produce the coupling device that will mesh is used to carry out the speed changer part 20 judged by step change control gear 54, carries out whether having entered about the speed Control of step change transmission part 20 judgement of inertia phase.
For example; By inertia phase enter that decision maker 84 makes about the variation of the second electromotor velocity NM2 whether owing to begin to produce the judgement whether the engagement torque of carrying out the gear shift action of step change transmission part 20 under the control of step speed change control device 54 to be engaged 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 the amount of being scheduled to of acquisition by experiment; Perhaps whether the time span of generation zero hour of the engagement torque by determining to be carved into coupling device to be engaged when step speed change control device 54 carries out the judgement of gear shift action of step change transmission part 20 has surpassed the predetermined time in the above-mentioned moment that obtains by experiment and begin corresponding to the generation of engagement torque, and perhaps whether the engagement hydraulic pressure by the coupling device determining to mesh has been increased to the predetermined transient pressure value PC that obtains by experiment and produce the above-mentioned moment of beginning corresponding to the engagement torque.
The flow chart of Figure 14 shows the major control operation of being carried out by electric control device 40, promptly is used for being controlled at the speed Control program of variable speed operation of the speed Control process stepless speed variator part 11 of step change transmission part 20.This speed Control program repeats in the short cycle time of tens of microseconds in for example approximate number microsecond.The flow chart of Figure 14 is corresponding to the flow chart of Figure 11, and the flow chart that is different from Figure 11 mainly is to have increased the S3 ' of the judgement that the inertia phase of the gear shift action that is used for determining speed changer part 20 enters in the flow chart of Figure 14.
The time diagram of Figure 15 shows in the control operation shown in the flow chart of Figure 14, places the stepless change state at gear 10, carries out this operation as level speed changer part 20 when second gear upgrades third gear.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 to have increased hydraulic pressure signal output (hydraulic pressure) in Figure 15.
The time diagram of Figure 16 shows the control operation shown in the flow chart of Figure 14, places the stepless change state at gear 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 flow chart of Figure 14, places the stepless change state at gear 10, carries out this control operation as level speed changer part 20 when second gear upgrades third gear.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 stepless speed variator part 11 changes in the time diagram of Figure 17 on the speed ratio change direction of step change transmission part 20.
The time diagram of Figure 18 shows in the control operation shown in the flow chart of Figure 14, places the stepless change state at gear 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 stepless speed variator part 11 changes in the time diagram of Figure 18 on the speed ratio change direction of step change transmission part 20.
To Figure 18, will only describe the aspect that the present invention is different from the previous embodiment of Figure 11 and Figure 12 with reference to Figure 14, other aspects will not described.
The speed Control program begins with the S1 corresponding to step change control gear 54, judges whether the gear shift action of step change transmission part 20 should take place.This judgement is by based on by the represented vehicle condition of the output torque TOUT of vehicle velocity V and speed changer part 20 and according to judging that by the exemplary speed change border line chart that illustrates in Fig. 6 the gear that speed changer 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 speed changer 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 speed changer part 20 at time point t1 from third gear to second gear.
When having obtained sure judgement in S1, 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 stepless speed variator part 11 places the stepless change state.Whether this judgement is being undertaken by the stepless change zone that limits by the speed change border line chart shown in the example in Fig. 6 based on vehicle condition, and gear 10 should place the stepless change state in this stepless change zone.
If obtained the judgement negating in S2, then control flow proceeds to the S6 corresponding to step change control gear 54, carries out the speed Control of the gear shift action that is used for carrying out the step change transmission part 20 determined at S1.
If obtained sure judgement in S2, then control flow proceeds to the S3 corresponding to step change control gear 54, carries out the speed Control of the gear shift action that is used for carrying out the speed changer part 20 determined at 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 release pressure PB2 of the second break 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 speed changer part 20, at this time point t1, the release pressure PB1 of the first break B1 (coupling device to be discharged) begins to reduce.
Then, control flow proceeds to the S3 ' that enters decision maker 84 corresponding to inertia phase, judges whether the gear shift action of step change transmission part 20 has entered inertia phase.For example, the judgement that whether entered 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 prearranging quatity that obtains by experiment based on the second electromotor velocity NM2 is carried out, perhaps whether surpassed by experiment and obtained and corresponding to the preset time of the above-mentioned zero hour, whether the engagement hydraulic pressure of coupling device perhaps to be meshed has been increased to the predetermined transient pressure value PC that obtains by experiment and produce the zero hour corresponding to the engagement torque of coupling device to be meshed up to the time span of generation zero hour of the engagement torque of coupling device to be joined.
At Figure 15, Figure 16, in the example of Figure 17 and Figure 18, judge entering of inertia phase at time point T1, this is because the second electromotor velocity NM2 has changed the prearranging quatity that obtains has by experiment entered inertia phase with detection judgement, that perhaps obtain by experiment and corresponding to the scheduled time of engagement generation of torque zero hour of coupling device to be meshed over and done with judgement, perhaps the engagement hydraulic pressure of coupling device has been increased to by experiment the result of judgement of the predetermined transient pressure value PC of the above-mentioned zero hour that obtains and produce corresponding to engagement torque.In the example of Figure 15 and Figure 17, coupling device to be meshed is the first break B1 with engagement hydraulic pressure PB1.In the example of Figure 16 and Figure 18, coupling device to be meshed is the second break 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 mixed power control gear 52, come synchronously to carry out the speed Control of stepless speed variator part 11, make the overall ratio γ T of gear 10 before the gear shift action of speed changer part 20 and change continuously afterwards with the 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 speed changer 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 direction that the speed ratio of stepless speed variator part 11 changes in the opposite direction at the speed ratio with step change transmission part 20 changes step by step corresponding to the speed ratio of speed changer part 20 amount of variable quantity step by step, prevent before the gear shift action of speed changer part 20 and the variation of the overall ratio γ T of gear 10 afterwards, that is, prevent before the gear shift action of speed changer 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 speed changer 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 stepless speed variator part 11 changes on the direction of the speed ratio change direction of step change transmission part 20, makes the overall ratio γ T of gear before the gear shift of speed changer part 20 action and change continuously afterwards.Thereby engine speed NE is owing to the variation of the overall ratio γ T of gear 10 changes, and this is opposite with engine speed NE in the example of Figure 15 and Figure 16.
In the speed Control or the 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 gear 82 step S5.For example, in the speed Control process, owing to the speed of the rotatable member of step change transmission part 20 descends and the speed of the rotatable member of step change transmission part 11 descends and caused increasing the inertia torque of exporting 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 exporting torque TOUT.Inertia torque in view of above-mentioned generation, input torque TIN for example reduces engine torque TE by carrying out engine torque minimizing control, perhaps, reduce because the increasing amount of the output torque TOUT that inertia torque produced by using the second motor M2 operating motor torque to reduce control.Perhaps, reduce the pulsatile change that output torque TIN reduces the output torque TOUT when finishing 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 vehicle deceleration 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 travelled, do not need to 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 rotatable member of step change and stepless speed variator 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, reducing the engagement action of carrying out the gear shift action of step change transmission part 20 when the friction coupling device finishes, when engine speed NE keeps constant simultaneously, export the pulsatile change of torque TOUT, lowered the mesh impact of coupling device thus.In the example of the Figure 16 that in the coast running process of speed changer part 20, lowers category, there is not to carry out the torque minimizing control that reduces the increasing amount of output torque TOUT owing to inertia torque at vehicle.Yet, operate simultaneously under the situation that speed changer part 20 lowers category in the process of accelerator pedal in vehicle driving, as in the example of Figure 15, carry out torque and reduce that control reduces because the output amount of torque 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 rotatable member of level and stepless speed variator part 20,11 arranged.
In the example of Figure 18 that speed changer part 20 lowers category in the coast running process of vehicle, do not carry out torque minimizing control and reduce because the output torque increasing amount of inertia torque.Yet, as in the example of Figure 17, to operate simultaneously under the situation that speed changer part 20 lowers category in the process of accelerator pedal in vehicle driving, torque reduces control and carries out and reduce because the output torque increasing amount of inertia torque.
If obtained the judgement negating in S1, control flow proceeds to the various controls that S7 carries out the various control gear of electric control device 40, rather than the speed Control of step change transmission part 20, carries out circulation for one that perhaps finishes this speed Control program.For example, when gear 10 places the stepless change state, mixed power control gear 52 is carried out the speed Control of stepless speed variator part 11 based on vehicle condition.
As mentioned above, present embodiment has the advantage identical with previous embodiment.For example, under the control of mixed power control gear 52 (stepless change control gear), carry out (promptly synchronously with the gear shift action of step change transmission part 20, in the gear shift of speed changer part 20 action inertia phase) speed Control of stepless speed variator part 11, guarantee the continuous variation of overall ratio (Sum velocity ratio) the γ T (determining) of gear 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 speed changer part 11 and the speed ratio of speed changer part 20.Before the gear shift of step change transmission part 20 action and speed NE afterwards, reduced its shifting shock thus.In addition, this is provided with and allows gear 10 to make the as a whole stepless speed changing mechanism that plays a part, and has improved fuel economy thus.
The 3rd embodiment
Schematic representation with reference to Figure 19, show the setting of the gear 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 hydraulic control that is used for setting up respectively those gears of expression gear 70, and Figure 21 is the alignment chart that is used to illustrate the variable speed operation of gear 70.
As in the aforementioned embodiment, gear 70 comprises stepless speed variator part 11, and this stepless speed variator part 11 has the first motor M1, power splitting mechanism 16 and the second motor M2.Gear 70 further comprises the step change transmission part 72 with three forerunner positions.Speed changer part 72 is arranged between stepless speed variator part 11 and the output shaft 22, and is connected in series to stepless speed variator part 11 and output shaft 22 by transmission part 18.Power splitting mechanism 16 comprises single pinion type first planetary gear set 24 and the switch clutch C0 with for example about 0.418 velocity ratio ρ 1 and switches break B0.Step change transmission part 72 comprises single pinion type second planetary gear set 26 with velocity ratio ρ 2 of for example about 0.532 and the single pinion type the third line star gear train 28 with for example about 0.418 velocity ratio ρ 3.The second sun gear S2 of second planetary gear set 26 and the 3rd sun gear S3 of the third line star gear train 28 be fixed to one another integratedly to become a unit, and optionally be connected to transmission part 18 by second clutch C2, be fixed to gearbox 12 by the first break B1 selectivity.Second planetary wheel carrier CA2 of second planetary gear set 26 and the 3rd gear ring R3 of the third line star gear train 28 are fixed to one another integratedly, and are fixed to output shaft 22.The second gear ring R2 optionally is connected to transmission part 18 by first clutch C1, and the third line star wheel frame CA3 optionally is fixed to gearbox 12 by the second break B2.
By in the gear 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 by 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 break B0, the first break B1 and the second break B2 as shown in the table of Figure 20.These gears have into the corresponding speed ratio γ (input shaft speed NIN/ output shaft speed NOUT) that geometrical progression changes.Concrete, note, the power splitting mechanism 16 that is provided with switch clutch C0 and break 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 by the engagement of switch clutch C0 or switching break B0, and places mechanism 16 to can be used as the stepless change state of above-mentioned stepless speed variator work.Thereby in this gear 70, step change transmission places the stepless speed variator part 11 of fixed speed ratio speed change state to form by speed changer part 20 and by the engagement of switch clutch C0 or switching break B0.Further, stepless speed variator constitutes by speed changer part 20 with because of switch clutch C0 and break B0 all do not mesh the stepless speed variator part 11 that places the stepless change state.In other words, gear 70 switches to the step change state by one among engagement switch clutch C0 and the switching break B0, and switches to the stepless change state by discharging switch clutch C0 and switching break B0.
For example, play a part under the step change transmission situation at gear 70, as shown in Figure 20, by the engagement action of switch clutch C0, first clutch C1 and the second break B2 set up have for example be about 2.804 the most at a high speed than first gear of γ 1, set up by the engagement action of switch clutch C0, first clutch C1 and the first break 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 by 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 by first clutch C1, second clutch C2 and the engagement action of switching break 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 by the engagement action of the second clutch C2 and the second break B2.Set up neutral gear N by only meshing switch clutch C0.
On the other hand, play the time spent of doing of stepless speed variator when gear 70, discharge switch clutch C0 and switch break B0, make stepless speed variator part 11 play a part stepless speed variator, the step change transmission part 72 that is connected in series to stepless speed variator part 11 simultaneously plays a part step change transmission, be delivered to thus and place first gear (promptly to the speed that rotatablely moves of the speed changer portion 72 of a gear of third gear, the rotational speed of transmission part 18) continuous variable, the speed ratio of feasible gear 10 when speed changer part 72 places gear of those gears is continuous variable on predetermined scope.Thereby the overall ratio of speed changer part 72 is continuous variable on adjacent gear, and thus, the overall ratio γ T that makes as a whole gear 70 is a continuous variable.
The alignment chart of Figure 21 is illustrated in the relation between the rotating speed of the rotatable member in each gear of gear 70 by straight line, gear 70 is made of stepless speed variator part 11 that plays the stepless speed variator part or the first speed changer partial action and the speed changer part 72 that plays the step change transmission part or the second speed changer partial action.The alignment chart of Figure 21 is represented the rotating speed of the discrete component of stepless speed variator part 11 when discharging switch clutch C0 and break B0, with the rotational speed of those elements when engaging switch clutch C0 or break B0 engagement, as in the foregoing embodiments.
In Figure 21, represent fixing the second and the 3rd sun gear S2, the 4th rotatable member (quaternary part) RE4 of S3 form of one each other respectively corresponding to automatic transmission 72 and four vertical line Y4, Y5, Y6 and Y7 being set to vertical direction, the relative rotation speed of the 7th rotatable member (the 7th element) RE7 of the second planetary wheel carrier CA2 that the 5th rotatable member (the 5th element) RE5 of the third line star wheel frame CA3 form, one are fixed to one another and the 6th rotatable member (the hexa-atomic) RE6 of the 3rd gear ring R3 form and the second gear ring R2 form.In automatic transmission 72, the 4th rotatable member RE4 optionally is connected to transmission part 18 by second clutch C2, and optionally be fixed to gearbox 12, the five rotatable member RE5 by the first break B1 and optionally be fixed to gearbox 12 by the second break B2.Output shaft 22, the seven rotatable member RE7 that the 6th rotatable member RE6 is fixed to automatic transmission 72 optionally are connected to transmission part 18 by first clutch C1.
When the engagement first clutch C1 and the second break B2, step change transmission part 72 places first gear.As shown in Figure 21, the intersection point that the rotating speed of the output shaft 22 in first gear is fixed to by expression between the straight line L1 of the vertical line Y6 of the 6th rotatable member RE6 rotating speed of output shaft 22 and inclination represents, angled straight lines L1 is by at the intersection point between the vertical line Y7 of the rotational speed of expression the 7th rotatable member RE7 (R2) and the horizontal line X2 and at the vertical line Y5 of the rotational speed of representing the 5th rotatable member RE5 (CA3) and the intersection point between the horizontal line X1.Similarly, the rotation rotating speed of the output shaft 22 in second gear of setting up by the engagement action of the first clutch C1 and the first break B1, be fixed to by determined angled straight lines L2 of those engagement action and expression output shaft 22 the 6th rotatable member RE6 (CA2, R3) rotating speed vertical line Y6 between intersection point represent.The rotating speed of the output shaft 22 in the third gear of setting up by 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 vertical line Y6 of rotating speed of the 6th rotatable member RE6 of output shaft 22.Switch clutch C0 place engagement first to third gear, the 7th rotatable member RE7 utilizes the driving force that receives from stepless speed variator part 11 with the speed rotation identical with the speed NE of motor.When switching break B0 replaced switch clutch C0 engagement, the 6th rotatable member RE6 utilized from the driving force of stepless speed variator part 11 receptions and rotates to be higher than engine speed NE.By first clutch C1, second clutch C2 and the rotational speed of switching the output shaft 22 in the fourth speed position that the engagement action of break B0 sets up represent by the intersection point between the vertical line Y6 of the determined horizontal line L 4 of those engagement action and the rotating speed of the 6th rotatable member RE6 that represents to be fixed to output shaft 22.
Also constitute according to gear 70 of the present invention, make this gear 70 have the advantage that is similar to first embodiment by stepless speed variator part 11 that plays the stepless speed variator part and the first speed changer partial action and the step change transmission part 72 that plays level (automatically) speed changer part or the second speed changer partial action.
The 4th embodiment
But Figure 22 has shown the seesaw switch 44 (hereinafter referred to as " switch 44 ") that the speed change state selection device effect of the differential state (unlock state) of power splitting mechanism 16 and/or non-differential state (lock state) (promptly selecting the stepless change state or the step change state of gear 10) is selected in manually-operable.This switch 44 allows the user to select required speed change state in the running process of vehicle.As shown in Figure 22, seesaw switch 44 has and is used for vehicle and in the sign that the stepless change state travels travel button and be used for vehicle and in the sign that the step change state travels the step change of " stepless change " button that travels arranged of the stepless change of " step change " is arranged.When the user presses stepless change when travelling button, switch 44 places the stepless change position, with the stepless change state of selecting gear 10 to work as electric steplessly variable transmission.When the user presses step change when travelling button, switch 44 places the step change state to select the step change state of gear as step change transmission work.
In foregoing example, the speed change state of gear 10 is based on vehicle condition, and according to automatically switching by the handoff boundary line chart shown in the example in Fig. 6.Yet the speed change state of gear 10,70 can be switched by the manually-operable that replaces automatically switching operation or the seesaw switch except automatically switching operation 44.That is, switching control 50 can be set to optionally gear 10 be 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 wishes that gear 10 is worked as stepless speed variator or when wanting to improve the fuel economy of motor, user's manual operation switch 44 places the stepless change state with gear 10, perhaps wish 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 gear 10 as the user.
Switch 44 can have and not have stepless change and the chosen neutral position of step change state.Under this situation, when the user did not select required speed change state or do not wish that gear 10 automatically places state of stepless change and step change state, switch 44 can place neutral position.
Speed change state at gear 10 is automatically not selected, but by under the manually selected situation of the manually-operable of switch 44, step S2 in the flow chart of Figure 11 or Figure 14 is stated as makes whether place differential state about power splitting mechanism 16, promptly, the judgement whether stepless speed variator 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 gear 10 to judge.
The 5th embodiment
Figure 23 is the major control functional block diagram that electric control device 40 is shown.In Figure 23, accelerator operation amount variance ratio computing device 100 is set to based on the operation amount of expression accelerator pedal 46 and is applied to the service speed of accelerator pedal 46 of variance ratio ACC ' form of operation amount of the operation amount signal ACC computation accelerator pedal of electric control device 40.This variance ratio 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 travelled, when accelerator pedal 46 operation suddenly, promptly when required vehicle drive force is relatively large, variance ratio ACC ' be higher relatively on the occasion of.For the vehicle that travels under constant speed, when the variance ratio of required vehicle drive force is relatively low, that is, when the operation amount of accelerator pedal 46 keeps constant, variance ratio 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 stepless speed variator part 11 places the stepless change state.When definite step change transmission part 20 should gear shift, for example, when having determined 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 gear 54 of Fig. 6.For example, based on switching control 50 about whether being in be used for gear 10 is placed the step change zone of step change state or is in the judgement that is used for gear 10 is placed the stepless change zone of stepless change state by the vehicle condition of representing according to the vehicle velocity V by the handoff boundary line chart shown in the example in Fig. 6 and output torque TOUT, differential state determining apparatus 80 carries out whether being in about stepless speed variator part 11 judgement of stepless change state.
Provide differential state determining apparatus 80 to determine whether stepless speed variator part 11 places differential state, make when the gear shift action of determining step change transmission part 20 whether be in differential state or be in non-differential state based on stepless speed variator part 11 and control engine speed.
Engine speed control gear 104 comprises stepless variable engine control gear 106 and step change engine controlling 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 motor of step change transmission part 20 by the stepless change action of control stepless speed variator part 11 by the speed Control process of the step change transmission part 20 of step change control gear 54 control.
When power splitting mechanism 16 is in differential state when beginning the gear shift action under the control of step change control gear 54 in step change transmission part 20, operating slepless transmission engine controlling unit 106.The first motor M1 that stepless variable engine control gear 106 is set to order mixed power control gear 52 control stepless speed variator parts 11 carries out the stepless change action, makes the velocity variations of the sun gear S1 that wins make the speed NE of motor when the gear shift action of step change transmission part 20 is finished and target engine speed value NE
*Consistent.Stepless variable engine speed device 106 further is set to order step change control gear and controls the 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 motor output of required vehicle drive force is satisfied in acquisition when the gear shift action of level speed changer part 20 is finished, mixed power control unit 52 controls of engine speed NE make motor 8 along the best curve that Control Parameter the limited operation by engine speed NE and engine torque TE form of being stored.
Generally speaking, after the moment that the gear shift action of being determined step change transmission part 20 by step change control gear 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 hydraulic control and release movement to begin to cause.In order to reduce this operating lag, and the output of acquisition required motor after finishing the gear shift action fast, stepless variable engine control gear 106 is set to after being judged by the gear shift action of step change control gear 54, by speed by the mixed power control gear 52 control first motor M1, rather than by utilizing since the engine speed NE of the gear shift action of step change transmission part 20 change the speed NE that changes motor apace step by step.
For example, when level gear change control device 54 judges that the shift-down action of speed changer part 20 should take place, stepless variable engine control gear 106 order mixed power control gear 52 improve the speed of the first motor M1, thus, improved the speed NE of motor, rather than allowed to improve the speed NE of motor owing to shift-down action.At this moment, the speed of the stepless variable engine control gear 106 order mixed power control gear 52 controls first motor M1 is so that engine speed NE and above-mentioned target engine speed NE
*Consistent.Simultaneously, consider the speed of transmission part 18 and the gear of speed changer part 20, this speed is determined by the input speed (being vehicle velocity V) of the step change transmission part 20 that risen by shift-down action.
Stepless variable engine control gear 106 is based on the variance ratio ACC ' of accelerator pedal operation amount and the variance ratio of control engine speed NE.As mentioned above, the variance ratio 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 variance ratio of the motor output of required driving force corresponding to needs.In this respect, variance ratio ACC ' is regarded as representing the variance ratio of engine speed.For example, the speed of the stepless variable engine control gear 106 order mixed power control gear 52 controls first motor M1 increases the rate of climb 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 speed Control of step change transmission part 20 under the control of step change control gear 54 begins, 108 work of step change engine controlling unit.The device 108 of step change engine control is set to the speed Control that order step change control gear 54 is carried out step change transmission part 20, make the speed NE of motor change step by step, make when the gear shift action of finishing speed changer part 20 and step change target engine speed value NE owing to the result of the gear shift action of speed changer part 20
*Consistent.Step change target engine speed value NE
*Be the engine speed NE that is determined by the speed of transmission part 18, the speed of transmission part 18 is determined by the fixed speed ratio of vehicle velocity V and stepless speed variator part 11.
Step change engine controlling unit 108 further is set to the speed of the order mixed power control gear 52 control first motor M1 and/or the second 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 rotatable member that jointing state is used for mechanism 16 when rotating as a unit, the speed of the step change engine controlling unit 108 order mixed power control gear 52 control first motor M1 and/or the second 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 gear 54, engine speed control gear 104 is controlled the speed of motor by starting step change engine controlling unit 108 rather than stepless variable engine control gear 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 gear 104 is when being set to when the speed Control at step change control gear 54 begins power splitting mechanism 16 and being in non-differential state, by the speed controlling of step change control gear 54 execution motors, to improve the gear shift response of step change transmission part 20.
Thereby, in the speed Control process of step change transmission part 20, whether utilization places a method of two selected engine speed controlling methods of differential state or non-differential state, engine speed control gear 104 optionally to start the speed that stepless variable engine control gear 106 or step change engine controlling unit 108 are controlled motor when the speed Control by step change control gear 54 begins based on power splitting mechanism 16.
In other words, engine speed control gear 104 is set to whether place differential state or non-differential state based on power splitting mechanism 16 when the speed Control of the speed changer part of being controlled by step change control gear 54 20 begins, by selecting by the engine speed control of stepless variable engine control gear 106 with by a control in the engine speed control of step change engine speed control gear 108, in the speed Control process of step change transmission part 20, change the shifting control method of step change transmission part 20.
The flow chart of Figure 24 shows the major control operation of being carried out by electric control device 40, the i.e. control of the engine speed in the speed Control process of step change transmission part 20.This engine speed control program is done microsecond at for example approximate number and is extremely repeated the short cycle time of tens of microseconds.
The engine speed control program judges with step S11 (" step " the is following to be omitted) beginning corresponding to step change control gear 54 whether the gear shift action of step change transmission part 20 should take place.This judgement by determine speed changer part 20 should gear shift to a gear in based on by the represented vehicle condition of the output torque TOUT of vehicle velocity V and speed changer part 20 and according to determining whether and gear shift carry out by the speed change border line chart shown in the example in Fig. 6.When obtaining the judgement negating in S11, 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 variance ratio computing device 100, and wherein accelerator operation amount variance ratio ACC ' is based on the operation amount of expression accelerator pedal 46 and be applied to the operation amount signal ACC of electric control device 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 stepless speed variator part 11 places the stepless change state.Whether this judgement dependence vehicle condition is in by the stepless change zone that limits by the speed change border line chart shown in the example in Fig. 6 is judged that gear 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 gear 104, wherein by step change control gear 54 by utilizing since the result's of gear shift action engine speed NE change the speed NE that the speed Control of carrying out the step change transmission part 20 of carrying out the gear shift action judged in S11 is controlled motor step by step.Simultaneously, execution is corresponding to the S15 of engine speed control gear 104, wherein, the speed of the first motor M1 and/or the second motor M2 is by 2 controls of mixed power control gear, power splitting mechanism 16 remains on non-differential state by switching control 50 simultaneously, makes engine speed NE equal target engine speed value NE as far as possible when step change transmission part 20 is finished the gear shift action
*
When in S13, obtaining sure judgement, control flow proceeds to the S16 corresponding to engine speed control gear 104, wherein, control the speed that the first motor M1 controls the first sun gear S1, control the speed NE of motor thus by mixed power control gear 52.Simultaneously, carry out S17, wherein, carry out the speed Control of step change transmission part 20 by step change control gear 54 corresponding to engine speed control gear 104.Thereby, come when finishing step change and move and target engine speed value NE by the speed NE that uses first motor in S16 and S17, to control motor than 20 gear shift
*Be consistent.
The time diagram of Figure 25 to Figure 28 shows each example in the control operation shown in the flow chart of Figure 24.
Figure 25 shows as the result who tramples operation of accelerator pedal when gear 10 places the stepless change state, and speed changer 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 flow chart of Figure 24.That is, in the definite shift-down action from the fourth speed position to second gear of the time point t1 of Fig. 2, at this moment, accelerator pedal is trampled.Judge that in response to this first motor M1 is controlled to the speed that improves the first sun gear S1, improves engine speed NE thus, the speed Control of step change transmission part 20 has begun.Because the operating lag of the gear shift of speed changer part 20 action, the speed of speed changer part 20 keep not becoming, up to time point t2.Yet, the no matter gear shift of speed changer part 20 action, engine speed NE is improved (during the time period from time point t1 to time point t2) fast, and this is because stepless speed variator 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 speed Control was finished) by since the engine speed that the gear shift action of speed changer part 20 causes change and do not carry out, but carried out by controlling the first 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 speed changer part 20, the speed of motor increases with respect to traditional engine speed control (by the line of the single-point in Figure 25 expression).In addition, the output of motor is also increased fast.Under the relatively low situation of the variance ratio ACC ' of accelerator pedal operation amount, promptly under the relatively low situation of the service speed of accelerator pedal, the speed of motor can be as 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 gear 10 places the example of the portion of speed changer 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 flow chart of Figure 24.That is, determine 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 speed Control of beginning step change transmission part 20 in response to this.Because the operating lag of the switching speed of speed changer part 20, the input speed of speed changer 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, speed changer 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 motor thus.Thereby the speed Control of speed changer part 20 is finished fast.In order to reduce the time period from time point t2 to time point t3, the speed NE of motor can be controlled by controlling the first motor M1 and/or the second motor M2.Further, engine speed NE fine adjustment can after stepless speed variator part 11 is switched to the stepless change state, use the first motor M1 to carry out by during the time period from time point t3 to time point t4.This switches among the S15 that switches in diagram 24 flow chart of stepless change state and can carry out.Under the relatively low situation of the variance ratio ACC ' of accelerator pedal operation amount, promptly, under the low relatively situation of the service speed of accelerator pedal, the speed of motor can be shown in dotted line is controlled (during the time period from time point t2 to time point t5).
Figure 27 shows because the speed of a motor vehicle increases, and gear 10 places the result of stepless change state simultaneously, speed changer 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 flow chart of Figure 24.Promptly determine 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 motor M1 is controlled to the speed that reduces by the first sun gear S1, has reduced engine speed NE thus, the speed Control of beginning step change transmission part 20.Because the operating lag of the gear shift of speed changer part 20 action, the input speed of speed changer part 20 keep not changing, up to time point t2.Yet, the no matter gear shift of speed changer part 20 action, engine speed NE reduces (during the time period from time point t1 to time point t2) apace, and this is because stepless speed variator part 11 remains on infinite variable speed state.Promptly, up to time point t3 (at this moment, the speed Control of step change transmission part 20 is finished) speed controlling of motor do not have owing to the change of the engine speed of the gear shift action of speed changer part 20 is carried out, but carry out by controlling the first motor M1, make speed Control to finish 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 speed changer 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 service speed of accelerator pedal, the speed of motor can shown in dotted linely be controlled (during the time period from time point t1 to time point t4).
Figure 28 shows because the increase of the speed of a motor vehicle, and gear 10 places the result of step change state simultaneously, and speed changer part 20 is from the upgrade example of speed changer part of fourth speed position of third gear.In the example of Figure 28, control operation is made up of the S11 in the flow chart of Figure 24, S12, S13, S14 and S16 (carrying out in proper order with this).That is,, obtain increasing in this time point speed of a motor vehicle in the definite shift-up action of the time point t1 of Figure 27 from third gear to the fourth speed position.Judge the speed Control of beginning step change transmission part 20 in response to this.Because the operating lag of the gear shift of speed changer part 20 action, the remaining unchanged of input speed of speed changer 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 switch motion of differential state.In this non-differential state, speed changer 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 motor thus.Thereby the speed Control of speed changer part 20 is finished fast.In order to reduce the time period from time point t2 to t3, the speed N8 of motor can be by controlling the first motor M1 and/or the second dynamo-electric machine M2 is controlled.Further, engine speed NE fine adjustment can use the first motor M1 to carry out after stepless speed variator 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 flow chart S15 of Figure 24 or after S15.
As mentioned above, gear 10 according to the present invention comprises the switch clutch C0 and the switching break B0 that can operate so that power splitting mechanism 16 is switched between the non-differential state that stepless speed variator part 11 is not partly worked as stepless speed variator as the differential state and the speed changer part 11 of electric steplessly variable transmission work.In this gear 10, by utilizing the function of stepless speed variator part 11 as electric steplessly variable transmission, promptly by utilizing the differential function of power splitting mechanism 16, launched motor speed control gear 104 controls of the speed NE of the motor in the speed Control process of step change transmission part 20.Thereby, the speed NE of motor changes fast along with improved response, and zero hour of the gear shift of step change transmission part 20 action no matter, and because speed Control and engine speed control execution simultaneously, the speed Control of speed changer part 20 is finished fast.For example, when speed changer part 20 lowered category in response to the trampling operation of accelerator pedal, engine speed NE improved after trampling of accelerator pedal operated fast, makes the output (power) of motor be able to quick increase.In addition, because the control that lowers category is carried out simultaneously with the control of engine speed, the shift-down action of speed changer part 20 is finished fast.
The device 104 that engine speed control in the present invention is set further is set to by utilizing the speed NE of first motor M1 control motor, makes speed and the gear shift of step change transmission part 20 of the motor when the gear shift action of step change transmission part 20 is finished move target engine speed value NE when finishing
*Unanimity makes that the response to the speed NE of the motor of gear shift action is improved, and no matter because the variation of the engine speed NE of the gear shift action of speed changer part 20.
Present embodiment further is arranged so that the variance ratio ACC of the speed control unit 104 of motor based on accelerator pedal operation amount
*And the variance ratio 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 controlling method of engine speed NE of the control gear 104 of engine speed, when the 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 of motor change fast, 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 control unit 104 of motor is controlled the speed NE of motor by the differential function of utilizing power splitting mechanism 16 in the speed Control process of step change transmission part 20, make the speed NE of motor change fast, and zero hour of the gear shift of speed changer part 20 action no matter, this makes the response of engine speed NE improve, and because speed Control and engine speed are controlled finishing of while, the speed Control of speed changer part 20 is finished fast.
Be in power splitting mechanism 16 under the situation of non-differential state, the speed control unit 106 of motor in the speed Control process of step change transmission part 20 by utilizing because the speed NE of the variation control motor of the engine speed that the gear shift of speed changer part 20 action causes, make that the speed NE of motor changes fast with improved response in the gear shift working procedure of speed changer 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 gear 106 of engine speed in the speed Control process of step change transmission part 20 by utilize the first motor M1 and/or the second motor M2 control motor speed, keep power splitting mechanism 16 to be in non-differential state simultaneously, make the speed NE of motor 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 motor is controlled by utilizing motor M1, M2, makes the speed NE of motor and target engine speed value NE when the gear shift of speed changer part 20 action is finished
*Unanimity makes the response of gear shift action be further enhanced.
The 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 speed Control of step change transmission part 20 begins, make engine speed NE change fast, the speed of motor 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 control unit 104 of motor is controlled the speed NE of motor by the differential function of utilizing power splitting mechanism 16 in the gear shift working procedure of speed changer part 20, speed Control when allowing speed changer part 20 simultaneously, make the speed NE of motor change fast, and zero hour of the gear shift of speed changer part 20 action no matter, this makes the raising of response of engine speed NE, and because speed Control is controlled the speed Control of carrying out speed changer part 20 simultaneously with engine speed finishes fast.
Be in power splitting mechanism 16 under the situation of non-differential state, engine speed control gear 104 in the speed Control process of step change transmission part 20 by utilizing because the speed NE of the variation control motor of the engine speed that the gear shift of speed changer part 20 action causes, keep power splitting mechanism 16 to be in non-differential state simultaneously, make that the speed NE of motor changes fast with improved response in the gear shift working procedure of speed changer part 20, and power splitting mechanism 16 is not switched to differential state from non-differential state.
Although embodiments of the invention by describing with reference to the accompanying drawings, it will be understood that the present invention can embody in other mode in detail in the above.
In shown embodiment, power splitting mechanism 16 was switched before differential state and non-differential state, made gear 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 gear 10 plays the step change transmission effect at stepless speed changing mechanism 10.Yet, principle of the present invention can be applied to the gear 10,70 that can not place the step change state, be that stepless speed variator part (differential portion) 11 is not provided with switch clutch C0 and break B0, and can operate the gear that works with as electric steplessly variable transmission (electric controlled differential device).In this case, switching control 50 shown in Figure 5, high gear decision maker 62 and differential state determining apparatus 80 are not necessarily, judge in the flow chart in Figure 11 and Figure 14 gear 16 differential state step S2 not necessarily, make that step S6 neither be necessary.The present invention can also be applied to the speed changer that stepless speed variator part 11 is known stepless speed variator (CVT).
In an illustrated embodiment, gear 10,70 is by switching as the differential state of electric steplessly variable transmission work and speed changer part 11 stepless speed variator part 11 (power splitting mechanism 16) between not as the non-differential state (lock state) of electric steplessly variable transmission work and switch between stepless change state and step change state in speed changer part 11.Yet gear 10,70 can play a part step change transmission, and the speed ratio of stepless speed variator part 11 changes step by step, rather than changes continuously, and this speed changer part 11 is keeping differential state simultaneously.In other words, the differential and non-differential state of stepless speed variator part 11 does not need to correspond respectively to the stepless and step change state of gear 10,70, and stepless speed variator part 11 needn't be switched between stepless and step change state.Principle of the present invention is applied to can switch any gear (its stepless speed variator part 11 or power splitting mechanism 16) between differential state and non-differential state.
In the foregoing embodiments, the speed Control of carrying out stepless speed variator part 11 prevents from the variation of engine speed NE from promptly, to prevent the variation of the overall ratio of gear 10, and is represented as 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 speed Control, and guarantee the continuous variation of engine speed, the speed Control that just needn't carry out speed changer 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 gear 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 motor 8, the first sun gear S1 and is fixed to the first motor M1, and the first sun gear R1 is fixed to transmission part 18.Yet this layout is optional.Motor 8, the first motor M1 and transmission part 18 can be fixed to three element CA1, S1 being selected from first planetary gear set 24 and any other element of R1.
Although motor 8 directly is fixed to input shaft 14 in shown embodiment, motor 8 can be operably connected to input shaft 14 by any suitable parts such as gear and band, and does not need and input shaft 14 coaxial settings.
In shown embodiment, the first motor M1 and the second motor M2 and input shaft 14 coaxial settings, and be respectively fixed to the first sun gear S1 and transmission part S8.Yet this layout is dispensable.For example, the first and second motor M1, M2 can be operably connected to the first sun gear S1 and transmission part 18 respectively by gear or band.
Although 16 being provided with switch clutch C0 and switching break B0 in shown embodiment, power splitting mechanism 16 needn't be provided with clutch C0 and break B0.Although switch clutch C0 provides optionally the first sun gear S1 and the first planetary wheel carrier CA1 is connected to each other, but switch clutch C0 can provide selectivity that the first sun gear 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 planetary gear set 24.
Although in shown embodiment's driving mechanism 10,70, switch clutch C0 meshes and sets up neutral gear N, and switch clutch C0 needn't mesh and set up neutral gear.
As the hydraulic control friction coupling device of switch clutch C0, switching break 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 clutch), magnetic clutch and engagement type canine tooth clutch.
In shown embodiment, the second motor M2 is fixed to transmission part 18.Yet the second motor M2 can be fixed to output shaft 22 and be fixed to the rotary component of transfer part 20,72.
In an illustrated embodiment, step change transmission part 20,72 is arranged on driving wheel 38 and is in the drive path between the power transmission member 18 of output block of stepless speed variator part 11 or power splitting mechanism 16.Yet, speed changer part 20,72 can be used such as stepless speed variator (CVT) (a kind of automatic transmission), as manual transmission and the parallel biaxial type speed changer of known a kind of permanent engagement, and the power transmitting deice of any other type of the automatic transmission that automaticallyes switch by gear selecting cylinder and gear shifting cylinder replaces.Under the situation that stepless speed variator (CVT) is provided, when power splitting mechanism 16 placed the fixed speed ratio speed change state, gear placed the step change state as a whole.The fixed speed ratio speed change state is restricted to power and mainly transmits by the machine power bang path, and does not carry out the state of transmission of power by circuit.Stepless speed variator 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 speed changer part in the aforementioned embodiment 20,27 is connected in series to stepless speed variator part 11 by transmission part 18, speed changer part 20,72 can be installed to the jack shaft parallel with input shaft 44 and with the coaxial setting of jack shaft.In this case, stepless speed variator part 11 and speed changer part 20,72 operationally are connected to each other by one group of two power transmitting deice of the combination of suitable power transmitting deice or for example a pair of driving gear and sprocket wheel and chain.
Provide power splitting mechanism 16 to replace in previous embodiment with the differential gearing that comprises small gear that rotates by motor 8 and the bevel-gear sett that is operably connected to the first and second motor M1, M2 respectively as differential attachment.
Although speed change gear in the aforementioned embodiment 90 is provided with the speed change lever 92 of operationally selecting a plurality of shift patterns, speed change lever 92 can be with the COMM communication such as button push or sliding-type switch of operationally selecting the gear shift position, perhaps selects the COMM communication 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 speed change lever 92 places manual forerunner position M1, required gear (be each shift range high tap position) can place the speed change lever 92 of manual forerunner position M to select by operation.20,70 gear shift of step change transmission part are to selected gear in this case, for example, each speed change lever 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 with single button push switch, two button push switches (optionally being pushed into operated position), bar type switch, sliding-type switch or operationally select stepless change state (differential state) and step change state (non-differential state) in the switch or the COMM communication of any other type of required 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 COMM communication 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 flow chart of Figure 24, step S1 is set to by judging whether the gear that step change transmission part 20 should gear shift arrives is determined 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 speed Control of step change transmission part 20.Under required shift range or the required gear situation manually selected by known gearshift in the prior art, can be in the judgement of carrying out the speed Control execution of speed changer part 20 when speed changer part 20 according to the manually-operable of gearshift during gear shift.Thereby the present invention can be applied in the gear of wherein step change transmission part 20 gear shift in response to the hand gear operation.
In the embodiment of flow chart 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 flow chart 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 at illustrative purpose and describe, the present invention can embody with variations and modifications, these modifications and variations are that the those skilled in the art in present technique field can expect.
Claims (24)
1. control gear that is used for driver for vehicle, comprise stepless change portion and speed changing portion, described stepless change portion comprises differential attachment, described differential attachment has first element that is connected to motor, be connected to second element and the three element that is connected to transmission part of first motor, and described stepless change portion comprises second motor that further comprises in the drive path that is arranged between described transmission part and the driving wheel of vehicle, described stepless change portion plays a part electric steplessly variable transmission, described speed changing portion constitutes the part of described drive path, and described control gear is characterised in that and comprises:
The stepless change control gear, but place of working in the speed Control process of described speed changing portion, be used for synchronously carrying out the speed Control of described speed changing portion, make the speed ratio that is limited by described stepless change portion and described speed changing portion change continuously with the described speed Control of described speed changing portion.
2. control gear that is used for driver for vehicle, comprise stepless change portion and speed changing portion, described stepless change portion is arranged on the drive path that is used for motor output is delivered to the driving wheel of vehicle, and play a part stepless speed variator, described speed changing portion constitutes the part of described drive path and is connected to described stepless change portion, and described control gear is characterised in that and comprises:
The stepless change control gear, in the speed Control process of described speed changing portion, can work, be used for synchronously carrying out the speed Control of described stepless change portion, make the speed ratio that limits by described stepless change portion and described speed changing portion change continuously with the described speed Control of described speed changing portion.
3. control gear according to claim 1 and 2, wherein, described speed changing portion is that a grade automatic transmission is arranged.
4. according to any one described control gear in the claim 1 to 3, wherein, but the described speed Control of described stepless change control gear and described speed changing portion synchronously changes the speed ratio of described stepless change portion with the direction place of working that changes in the opposite direction with the described speed ratio of described speed changing portion, makes the variable quantity that reduces the described speed ratio that is limited by described stepless change portion and described speed changing portion.
5. according to any one described control gear in the claim 1 to 4, wherein, but the speed Control of described stepless change portion is carried out in described stepless change control gear place of working in the inertia phase that the input speed of the described speed changing portion of the gear shift of described speed changing portion action changes.
6. according to any one described control gear in the claim 1 to 5, the moment of torsion that further comprises the input torque that is used to reduce described speed changing portion reduces control gear, and described moment of torsion reduces control gear and reduce described input torque in the described speed Control process of described speed changing portion.
7. control gear that is used for driver for vehicle, comprise stepless change portion and step change portion, described stepless change portion comprises described differential attachment, described differential attachment has first element that is connected to motor, be connected to second element and the three element that is connected to transmission part of first motor, and described stepless change portion comprises second motor that further comprises in the drive path that is arranged between described transmission part and the driving wheel of vehicle, described stepless change portion plays a part electric steplessly variable transmission, described step change portion constitutes the part of described drive path, and play a part to have a grade automatic transmission, described control gear is characterised in that and comprises:
The stepless change control gear, but place of working in the speed Control process of described step change portion, be used for synchronously carrying out the speed Control of described stepless change portion, make the speed ratio of described stepless change portion change with the direction that changes in the opposite direction with the described speed ratio of described speed changing portion with the described speed Control of described step change portion.
8. control gear that is used for driver for vehicle, comprise stepless change portion and step change portion, described stepless change portion is arranged on the driving wheel drive path that is used for motor output is delivered to vehicle, and play a part stepless speed variator, described step change portion constitutes the part of described drive path, play a part to have grade automatic transmission and be connected to described stepless change portion, described control gear is characterised in that and comprises:
The stepless change control gear, in the speed Control process of described step change portion, can work, be used for synchronously carrying out the speed Control of described stepless change portion, make the speed ratio of described stepless change portion change with the direction that changes in the opposite direction with the described speed ratio of described step change portion with the described speed Control of described step change portion.
9. according to claim 7 or 8 described control gear, wherein, but the speed Control of described stepless change portion is carried out in described stepless change control gear place of working in the inertia phase that the input speed of the described step change portion of the gear shift action of described step change portion changes.
10. according to any one described control gear among the claim 7-9, the moment of torsion that further comprises the input torque that is used to reduce described speed changing portion reduces control gear, and described moment of torsion reduces control gear and reduce described input torque in the described speed Control process of described speed changing portion.
11. according to any one described control gear among the claim 7-10, wherein, but described stepless change control gear place of working changes the described speed ratio of described stepless change portion in the direction relative with the change direction of the described speed ratio of described step change portion, to reduce the described speed ratio variable quantity that is limited by described stepless change portion and described step change portion.
12. control gear that is used for driver for vehicle, comprise stepless change portion and step change portion, described stepless change portion is arranged on the driving wheel drive path that is used for motor output is delivered to vehicle, and play a part stepless speed variator, described step change portion constitutes the part of described drive path, play a part to have grade automatic transmission and be connected to described stepless change portion, described control gear is characterised in that and comprises:
The engine speed control gear can be worked in the speed Control of described step change portion, is used for controlling by the electric stepless change action of controlling described stepless change portion the speed of described motor.
13. control gear according to claim 12, wherein, described engine speed control gear is by utilizing the described speed of the described motor of described motor control, makes that the described speed of described motor equals the target engine speed value when the gear shift action of described step change portion is finished.
14. according to claim 12 or 13 described control gear, wherein, based on the variance ratio of the operation amount of accelerator pedal, described engine speed control gear is controlled the variance ratio of the described speed of described motor.
15. according to any one described control gear among the claim 12-14, wherein, described differential attachment comprises differential COMM communication, and described differential COMM communication is not operationally switched described stepless change portion as the differential state of electric steplessly variable transmission work and described stepless change portion in described stepless change portion between the non-differential state as electric steplessly variable transmission work.
16. control gear that is used for driver for vehicle, comprise stepless change portion and step change portion, described stepless change portion comprises differential attachment, described differential attachment operationally is assigned to first motor and transmission part with the output of motor, described stepless change portion comprises second motor that further comprises in the drive path that is arranged between described transmission part and the driving wheel of vehicle, described stepless change portion plays a part electric steplessly variable transmission, described step change portion constitutes the part of described drive path, play a part to have a grade automatic transmission, described control gear is characterised in that and comprises:
Differential state switching device, described differential COMM communication is arranged in the described differential attachment, and operationally described stepless change portion is not switched between the non-differential state as electric steplessly variable transmission work as the differential state of electric steplessly variable transmission work and described stepless change portion in described stepless change portion;
The engine speed control gear, in the speed Control of described step change portion, can work, be used for controlling with a method in two engine speed controlling methods the speed of described motor, when the described speed Control of described step change portion begins, rely on described power splitting mechanism whether to place described differential state or the selected described method of described non-differential state in the described speed Control process of described step change portion.
17. control gear according to claim 16, wherein, if described differential attachment is placed in described differential state when the described speed Control of described step change portion begins, then described engine speed control gear is controlled the described speed of described motor by the electric stepless gear shift action of controlling described stepless change portion.
18. according to claim 16 or 17 described control gear, if described differential attachment is placed in described non-differential state when the described speed Control of described step change portion begins, then described engine speed control gear because the variation of the described speed of the described motor that the gear shift of step change portion action causes, is controlled the described speed of described motor by utilizing.
19. control gear according to claim 18, wherein, if described differential attachment is placed in described non-differential state when the described speed Control of described step change portion begins, by utilizing the described speed of the described motor of described motor control, described differential attachment remains on non-differential state to then described engine speed control gear simultaneously in the described speed Control process of described step change portion.
20. control gear that is used for driver for vehicle, comprise stepless change portion and step change portion, described stepless change portion comprises differential attachment, described differential attachment operationally is assigned to first motor and transmission part with the output of motor, described stepless change portion comprises second motor that further comprises in the drive path that is arranged between described transmission part and the driving wheel of vehicle, described stepless change portion plays a part electric steplessly variable transmission, described step change portion constitutes the part of described drive path, play a part to have a grade automatic transmission, described control gear is characterised in that and comprises:
Differential state switching device, described differential COMM communication is arranged in the described differential attachment, and operationally described stepless change portion is not switched between the non-differential state as electric steplessly variable transmission work as the differential state of electric steplessly variable transmission work and described stepless change portion in described stepless change portion;
The engine speed control gear, in the speed Control of described step change portion, can work, be used for controlling with a method in two engine speed controlling methods the speed of described motor, when the described speed Control of described step change portion begins, rely on described power splitting mechanism whether to place described differential state or the selected described method of described non-differential state in the described speed Control process of described step change portion.
21. control gear according to claim 20, wherein, if described differential attachment is placed in described differential state when the described speed Control of described step change portion begins, then described engine speed control gear is controlled the described speed of described motor by the electric stepless gear shift action of controlling described stepless change portion, and carries out the described speed Control of described step change portion.
22. according to claim 20 or 21 described control gear, wherein, if described differential attachment is placed in described non-differential state when the described speed Control of described step change portion begins, then described engine speed control gear is carried out the described speed Control of described step change portion, make the described speed of described motor by utilizing because the variation of the described speed of the described motor that the gear shift of step change portion action causes changes, simultaneously described step change portion remains on non-differential state.
23. according to each described control gear among the claim 15-22, wherein, described differential attachment has first element that is connected to motor, be connected to second element of first motor and be connected to the three element of transmission part,
Wherein, but described differential state switching device place of working allows described first relative to each other to rotate to three element, be used to set up described differential state, and allow described first to three element as the rotation of unit or keep described second element to maintain static, be used to set up described non-differential state.
24. control gear according to claim 23, wherein, described differential state switching device comprises clutch and/or break, described clutch operationally is connected to each other described first in the three element any two, be used for rotating as a unit to three element described first, described break operationally is fixed to described second element and is used to process the fixed fixed component of described second element.
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004132029 | 2004-04-27 | ||
| JP132029/2004 | 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 true CN1950628A (en) | 2007-04-18 |
| CN1950628B CN1950628B (en) | 2012-08-15 |
Family
ID=38019371
Family Applications (2)
| 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) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101825171A (en) * | 2009-03-06 | 2010-09-08 | 日产自动车株式会社 | The control system of automatic transmission |
| CN101244691B (en) * | 2007-02-09 | 2011-06-15 | 丰田自动车株式会社 | Control device for vehicular drive system |
| CN102444483A (en) * | 2010-09-30 | 2012-05-09 | 株式会社电装 | Engine control apparatus |
| CN101801752B (en) * | 2007-09-18 | 2013-01-02 | 丰田自动车株式会社 | Controller for hybrid driver |
| CN103517842A (en) * | 2011-03-01 | 2014-01-15 | 铃木株式会社 | Hybrid vehicle drive control device |
| CN103661382A (en) * | 2012-09-04 | 2014-03-26 | 本田技研工业株式会社 | Vehicle control device |
| CN104245458A (en) * | 2012-03-26 | 2014-12-24 | 丰田自动车株式会社 | Hybrid vehicle drive control device |
| CN105579317A (en) * | 2013-09-25 | 2016-05-11 | 罗伯特·博世有限公司 | Method and device for controlling internal combustion engine of motor vehicle |
| CN107202107A (en) * | 2016-03-18 | 2017-09-26 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN108099898A (en) * | 2016-11-23 | 2018-06-01 | 罗伯特·博世有限公司 | Drive the method for the driving wheel of slidable adjustment motor vehicle and driving slidable adjustment equipment |
Family Cites Families (3)
| 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 |
| US7223200B2 (en) * | 2001-10-22 | 2007-05-29 | Toyota Jidosha Kabushiki Kaisha | Hybrid-vehicle drive system and operation method with a 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 |
-
2005
- 2005-03-28 KR KR1020097010780A patent/KR100954716B1/en active IP Right Grant
- 2005-03-28 CN CN2008101727484A patent/CN101451608B/en not_active Expired - Fee Related
- 2005-03-28 CN CN2005800135243A patent/CN1950628B/en not_active Expired - Fee Related
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101244691B (en) * | 2007-02-09 | 2011-06-15 | 丰田自动车株式会社 | Control device for vehicular drive system |
| CN101801752B (en) * | 2007-09-18 | 2013-01-02 | 丰田自动车株式会社 | Controller for hybrid driver |
| CN101825171B (en) * | 2009-03-06 | 2013-11-20 | 日产自动车株式会社 | Control system for automatic transmission |
| CN101825171A (en) * | 2009-03-06 | 2010-09-08 | 日产自动车株式会社 | The control system of automatic transmission |
| CN102444483A (en) * | 2010-09-30 | 2012-05-09 | 株式会社电装 | Engine control apparatus |
| CN103517842B (en) * | 2011-03-01 | 2016-08-17 | 铃木株式会社 | Motor vehicle driven by mixed power drive dynamic control device |
| CN103517842A (en) * | 2011-03-01 | 2014-01-15 | 铃木株式会社 | 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 |
| CN103661382A (en) * | 2012-09-04 | 2014-03-26 | 本田技研工业株式会社 | Vehicle control device |
| CN103661382B (en) * | 2012-09-04 | 2016-03-09 | 本田技研工业株式会社 | Controller of vehicle |
| CN105579317A (en) * | 2013-09-25 | 2016-05-11 | 罗伯特·博世有限公司 | Method and device for controlling internal combustion engine of motor vehicle |
| CN107202107A (en) * | 2016-03-18 | 2017-09-26 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN107202107B (en) * | 2016-03-18 | 2021-02-26 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| CN108099898A (en) * | 2016-11-23 | 2018-06-01 | 罗伯特·博世有限公司 | Drive the method for the driving wheel of slidable adjustment motor vehicle and driving slidable adjustment equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20090103996A (en) | 2009-10-05 |
| CN101451608B (en) | 2013-07-10 |
| KR100954716B1 (en) | 2010-04-23 |
| CN101451608A (en) | 2009-06-10 |
| CN1950628B (en) | 2012-08-15 |
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Granted publication date: 20120815 |