CN107848523A - Automatic gear shifting control device and automatic gear shifting method - Google Patents
Automatic gear shifting control device and automatic gear shifting method Download PDFInfo
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- CN107848523A CN107848523A CN201680044453.1A CN201680044453A CN107848523A CN 107848523 A CN107848523 A CN 107848523A CN 201680044453 A CN201680044453 A CN 201680044453A CN 107848523 A CN107848523 A CN 107848523A
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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
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D45/00—Electrical control not provided for in groups F02D41/00 - F02D43/00
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Transmission Device (AREA)
- Control Of Driving Devices And Active Controlling Of Vehicle (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
Automatic gear shifting control device (20) is configured to be controlled as follows：After AMT (15) is switched into target gear (Gx), clutch apparatus (14) is connected with half-clutch device state, and, the output torque (Te) of engine (11) is set to the first moment of torsion (Tc), next, after the torsion that power transmission shaft (16) generates caused by the first moment of torsion (Tc), the output torque (Te) of engine (11) is set to from the first moment of torsion (Tc) to require moment of torsion (Tb), also, clutch apparatus (14) is fully connected from half-clutch device state.
Description
Technical field
The present invention relates to automatic gear shifting control device and automatic gear shifting method, more specifically, is related to suppression and is cutting automatically
Gear shift shock caused by the gear of automatic mechanical transmission is changed, to shorten time when gear switches and improve driving
Automatic gear shifting control device and automatic gear shifting method.
Background technology
In the oversize vehicle such as truck or bus, the vehicle for being equipped with automatic gear shifting control device be present, this is automatic
Speed-change control device sets up driver etc. automatically to control gear to switch to clutch apparatus or mechanical transmission.
Automatic mechanical transmission (the Automated Manual carried out automatically in the automatic gear shifting control device
Transmission, AMT) gear switching in, connected after the completion of gear switches clutch apparatus with by the defeated of engine
Go out the control that moment of torsion is set to the desired moment of torsion of driver.But now exist due to generation gear shift shock and driving deterioration
The problem of such.
On the other hand, propose following automatic gear shifting control device：In the gear switching of automatic mechanical transmission, by temporarily
When separated clutch apparatus connection when control the output torque of engine so that it turns into the rotational resistance of offsetting the engine
Moment of torsion (for example, referring to patent document 1).
The device is after the completion of the gear switching of automatic mechanical transmission, in engine speed and the rotating speed of clutch rotational speed
Difference be predetermined value within the case of, enter to be about to the control that clutch apparatus is set to half-clutch device state.It is about to draw next, entering
The output torque held up is set to offset the control of the moment of torsion of the rotational resistance of engine.Next, it is fully connected by clutch apparatus
It is laggard exercise its rise to the control of the desired moment of torsion of driver.
Thus, after the completion of gear switching, by being sprayed with producing the degree of the moment of torsion of the rotational resistance of counteracting engine
Fuel, so as to avoid the deceleration caused by the rotational resistance of engine, so that gear shift shock will not occur.
Prior art literature
Patent document
Patent document 1：Japanese Unexamined Patent Publication 2006-70708 publications
The content of the invention
The invention problem to be solved
On the other hand, the inventor of the present application is found that：After clutch apparatus is fully connected after speed change, in car
If traveling in the power transmission shaft of state that is passed to slightly to reverse of the output torque from engine, the power transmission shaft with it is logical
The reason for normal state is compared and larger reversed, and the torsion causes to produce backswing on power transmission shaft, and the backswing is gear shift shock.
Caused backswing is due to and connects to deliver larger output from engine after clutch apparatus and turn round on power transmission shaft
Power transmission shaft is significantly reversed because of elastic deformation during square and the torsion reaction force to be recovered is exaggerated, so as to caused existing
As.If producing the backswing, on power transmission shaft, the change in torque of both forward and reverse directions is exaggerated simultaneously due to the backswing from driven wheel side
Show.Moreover, the change in torque after being exaggerated causes the rotation to the torque fluctuation of wheel transmission and wheel to change, therefore,
The larger swing of fore-and-aft direction occurs for vehicle.Particularly in oversize vehicle, because the power transmission shaft is longer to cause elastic deformation
Measure larger, the vibration caused by backswing is larger, so larger in gear shift shock caused by speed change.
In above-mentioned device, for as the caused backswing on power transmission shaft the reason for the gear shift shock, not doing
Go out any countermeasure.Specifically, after clutch apparatus is fully connected, driver institute is risen to making the output torque of engine
During desired moment of torsion, power transmission shaft is significantly reversed, and backswing is produced on power transmission shaft.Accordingly, there exist can not suppress the power transmission shaft
The problem of gear shift shock caused by backswing is such.
If in addition, making the output torque of engine rise at leisure to not produce backswing in power transmission shaft, to spend
The time of the desired moment of torsion of driver is raised to, the problem of shifting time is elongated such be present.
The present invention provides a kind of can mitigate because being produced on the power transmission shaft when switching the gear of automatic mechanical transmission
Backswing caused by gear shift shock, shorten gear switching when time and improve driving automatic gear shifting control device and
Automatic gear shifting method.
Means for solving the problems
The automatic gear shifting control device of the scheme of the present invention has：Engine, clutch apparatus, it will come from above-mentioned draw
The driving force held up is switched off/on, automatic mechanical transmission, and it is connected via above-mentioned clutch apparatus with above-mentioned engine, and
And with the transmission axis connection to driving wheel passing power, and control unit, it is with above-mentioned engine, above-mentioned clutch apparatus, with
And above-mentioned automatic mechanical transmission connects respectively, and it is controlled；Above-mentioned control unit is controlled as follows：By above-mentioned machine
After tool formula automatic transmission is switched to target gear corresponding with the operational situation of vehicle, pass through the above-mentioned clutch that will be temporarily separated
Device device connects, so as to which the output torque of above-mentioned engine to be set to drive from the initial torque set according to above-mentioned target gear
Requirement moment of torsion required by member；Above-mentioned control unit after above-mentioned target gear is switched to, enter to be about to above-mentioned clutch apparatus with
The control of half-clutch device state connection, also, the output torque for entering to be about to above-mentioned engine is set to be set at above-mentioned initial torque
With the control between above-mentioned requirements moment of torsion；Above-mentioned control unit is generated from above-mentioned engine via above-mentioned clutch in above-mentioned power transmission shaft
Device device and above-mentioned automatic mechanical transmission and after torsion caused by above-mentioned first moment of torsion that transmits, enter and be about to above-mentioned engine
Output torque be set to above-mentioned requirements moment of torsion and above-mentioned clutch apparatus is complete from half-clutch device state from above-mentioned first moment of torsion
The control connected entirely.
Automatic mechanical transmission is being switched to the operating with vehicle by the automatic gear shifting method of the scheme of the present invention
After the corresponding target gear of situation, by the way that the clutch apparatus being temporarily separated is connected, so as to by the output torque of engine from root
The initial torque set according to the target gear is set to the requirement moment of torsion required by driver；Automatic gear shifting method is controlled as follows
System：After above-mentioned target gear is switched to, above-mentioned clutch apparatus is connected with half-clutch device state, also, by above-mentioned engine
Output torque control to be set at the first moment of torsion between above-mentioned initial torque and above-mentioned requirements moment of torsion, produced in power transmission shaft
, will after via the torsion caused by above-mentioned clutch apparatus and above-mentioned first moment of torsion of above-mentioned automatic mechanical transmission transmission
The output torque of above-mentioned engine is set to above-mentioned requirements moment of torsion from above-mentioned first moment of torsion, also, by above-mentioned clutch apparatus from half from
Clutch state is fully connected.
Invention effect
According to the automatic gear shifting control device and automatic gear shifting method of the present invention, it is switched to by automatic mechanical transmission
After target gear corresponding with the operational situation of vehicle, as the first stage, clutch apparatus is connected with half-clutch device state,
Also, the output torque of engine is initially set to the first moment of torsion from initial torque, so that power transmission shaft produces torsion in advance.As
Second stage, after power transmission shaft generates torsion, the output torque of engine is set to require moment of torsion from the first moment of torsion, with from first
Moment of torsion offsets the torsion reaction force to be recovered of power transmission shaft to the ascending amount for requiring moment of torsion.Then, the output torque of engine
Reach requirement moment of torsion, also, clutch apparatus is fully connected so as to complete automatic mechanical transmission from half-clutch device state
Speed change.
By control as progress, so as to suppress because of the torsion of power transmission shaft and on power transmission shaft caused by backswing.
Thereby, it is possible to avoid calibrating because of caused by backswing switching the spent time so as to shorten gear, further, it is possible to mitigate with this
Backswing for cause gear shift shock so as to improving driving.
Especially, the present invention is effective in upshift automatic mechanical transmission, in upshift automatic mechanical transmission, energy
It is enough mitigate the backswing because caused by power transmission shaft caused by gear shift shock so as to improving driving.
Brief description of the drawings
Fig. 1 is the pie graph for the automatic gear shifting control device for illustrating embodiments of the present invention.
Fig. 2 is the flow chart for the automatic shift control method for illustrating embodiments of the present invention.
Fig. 3 is to illustrate accelerator open degree, engine speed, clutch rotational speed, output torque, travel of clutch in temporal sequence
Figure.
Fig. 4 is the figure for illustrating the first moment of torsion chart.
Fig. 5 is the flow chart for the calculation method for illustrating the first moment of torsion.
Embodiment
Hereinafter, with reference to the accompanying drawings of embodiments of the present invention.Fig. 1 illustration embodiments of the present invention are formed automatic
Speed-change control device 20.The automatic gear shifting control device 20 is equipped on vehicle 10, carry out according to the operational situation of vehicle 10 come
Automatic mechanical transmission (Automated Manual Transmission, hereinafter referred to as AMT) 15 is automatically switched into target
Gear Gx control.
Vehicle 10 is the oversize vehicles such as the bus that engine 11 is made up of diesel motor or truck.In the vehicle 10,
Using the burning of the fuel by being formed in multiple (being 4 in this example embodiment) cylinders 12 in engine 11 and caused heat
Can, rotation driving crank axle 13.The rotary power of the crank axle 13 passes through dry clutch device (hereinafter referred to as clutch device
Put) 14 and be passed to AMT15.
For AMT15, with including can be by the basic transmission structure of the rotary power inputted multistage ground speed change and can
By exemplified by the AMT for the auxiliary transmission structure that the rotary power speed change of the basic transmission structure transmission is slow speed turbine stage and high speed level this two-stage
Illustrate, still, it is constructed without being particularly limited to.
Differential gear 17 is passed to by power transmission shaft 16 by the rotary power after AMT15 speed changes, and via drive shaft
18 are assigned to a pair of driving wheels 19 respectively as driving force.
Automatic gear shifting control device 20 is configured to have：Engine control device 21, it is connected and main with engine 11
Control engine 11；Speed change control device 22, it is connected respectively with clutch apparatus 14 and AMT15 and major control clutch device
Put 14 and AMT15；And CAN (Controller Area Network：Controller zone network) etc. In-vehicle networking 23, it makes
Obtaining the data of these control devices can be in communication with each other.
The accelerator open degree that engine is used as accelerator open degree AO with the amount of treading in of control device 21 and detection gas pedal P1 passes
The sensors such as sensor 24 and detecting and alarm rotating speed Ne CKP 25 connect.Moreover, the detected value based on them
To adjust the fuel injection amount from electronic control type injector (hereinafter referred to as injector) 26, the output torque of engine 11 is controlled
Te increase and decrease.
Speed change control device 22 is by controlling clutch driver 27, so as to control the work of clutch apparatus 14.
The job control of the clutch apparatus 14 is to control as follows：By the way that compressed air (not shown) is supplied to clutch driver 27
Give, so as to which clutch apparatus 14 is separated to cut off the transmission of the power from engine 11 with the clutch driver 27, or
Person, by releasing compressed air from clutch with driver 27, drawn so as to which the clutch apparatus 14 of separation be connected with that will come from
The power for holding up 11 transmits to AMT15.
In addition, the speed change with control device 22 with detection power transmission shaft 16 rotating speed of transmission shaft Np or according to the power transmission shaft
The grade of the rotating speed of transmission shaft sensor 28 sensor connection of rotating speed Np detection vehicle velocity Vs.Moreover, controlled using speed change driver 29
Switchings of the AMT15 to target gear Gx corresponding with the operational situation of vehicle 10.In addition, the speed change with driver 29 also with clutch
Device is similarly acted with driver 27 with compressed air, and still, these drivers can also enter action using electromagnet
The electromagnetic driver of work.
In addition, the speed change control device 22 also clutch with the clutch rotational speed Nc of detection clutch apparatus 14
Speed probe 30 connects.In addition, clutch rotational speed Nc is the rotating speed that AMT15 is input to from clutch apparatus 14, can also not
Detect clutch rotational speed Nc with clutch rotational speed sensor 30, and according to rotating speed of transmission shaft Np and AMT15 gearratio come
Obtain.
Herein, below, using the switching control to target gear Gx corresponding with the operational situation of the vehicle 10 as automatic
The function of speed-change control device 20 illustrates.First, speed change obtains vehicle velocity V and accelerator open degree AO with control device 22.Next,
Speed change is with the vehicle velocity V and accelerator open degree AO of operational situation of the control device 22 based on vehicle 10 come selection target gear Gx.More
For body, speed change control device 22 is with reference to being stored in advance in speed change control device 22 and be based on vehicle velocity V and accelerator open degree
AO and the gear shift chart M1 for being set with target gear Gx, according to gear shift chart M1 selection target gears Gx.
Next, speed change controls clutch driver 27 with control device 22, clutch apparatus 14 is separated, by engine
The transmission of 11 and AMT15 power is cut off.Next, engine is controlled as follows with control device 21：Adjust injector 26
Fuel injection amount, the initial torque Ta that the output torque Te of engine 11 is set to be set according to selected target gear Gx.
For example, in AMT15 upshift, separate clutch apparatus 14 and be reduced to the output torque Te of engine 11 initially
Torque T a.In addition, the separation control of the clutch apparatus 14 and the output torque Te of engine 11 reduction control can also be simultaneously
Carry out, gently separate clutch apparatus 14 on one side, the output torque Te of engine 11 is gently set to initial torque Ta on one side.
Initial torque Ta be to each moment of torsion set in advance of AMT15 each gear, be set to gearratio into than
Example ground becomes big.For example, in the case of 12 grades of speed changes that the basic transmission in AMT15 is six grades, auxiliary transmission is two level, to this 12
Every one-level setting initial torque Ta of level.
Next, speed change controls speed change to be switched to target gear Gx with driver 29 and by AMT15 with control device 22.More
Specifically, speed change controls speed change driver 29 with control device 22, does not scheme what is engaged with the gear synchronous currently selected
The synchronizer separation shown, and synchronizer is synchronously engaged to target gear Gx.
Next, speed change controls clutch driver 27 with control device 22, and connect clutch apparatus 14, transmit from
Power of the engine 11 to AMT15.Next, engine adjusts the fuel injection amount of injector 26 with control device 21, by engine 11
Output torque Te be set to requirement torque T b required by driver.More specifically, speed change control device 22 is set to
The requirement torque T b set based on accelerator open degree AO, AMT15 gear switching are completed.
For example, in AMT15 upshift, i.e., driver treads in gas pedal P1 and vehicle 10 is cut by AMT15 when accelerating
After changing to target gear Gx, rise to the output torque Te of engine 11 and require that torque T b, AMT15 upshift are completed.
So, when AMT15 is switched into target gear Gx corresponding with the operational situation of vehicle 10, controlled as follows
System：In the requirement torque T b being switched to after target gear Gx required by the output torque Te of engine 11 to be set to driver.But
If the output of engine 11 is directly set to require torque T b and is fully connected the clutch apparatus 14 being temporarily separated, power transmission shaft
16 can significantly be reversed with elastic deformation and produce backswing.
Therefore, automatic gear shifting control device 20 of the invention is configured to carry out following control.As the first stage,
After being switched to target gear Gx corresponding with the operational situation of vehicle 10, enter to be about to clutch apparatus 14 and connected with half-clutch device state
The control connect, also, the output torque Te for entering to be about to engine 11 is set between being set at initial torque Ta and requiring torque T b
The first torque T c control.As second stage, controlled as follows：Due to from engine 11 via clutch apparatus 14 and
The first torque T c that AMT15 is transmitted and after generating the torsion of power transmission shaft 16, by the output torque Te of engine 11 from the first moment of torsion
Tc is set to require torque T b, also, clutch apparatus 14 is fully connected from half-clutch device state.
First torque T c is the moment of torsion for being set at initial torque Ta and requiring the size between torque T b, is drawn than offsetting
Hold up the big moment of torsion of the moment of torsion of 11 rotational resistance.It is anti-when first torque T c size determines the twist recovery of power transmission shaft 16
The size of active force.
The first torque T c is by speed change rotation speed difference deltan of the control device 22 based on engine speed Ne Yu clutch rotational speed Nc
Nec or engine speed Ne and rotating speed of transmission shaft Np rotation speed difference deltan Nx is set.For example, for first torque T c, first
Beginning torque T a and require torque T b it is poor larger when, be set it is larger to increase twist recovery when reaction force, it is another
Aspect, initial torque Ta and require torque T b difference it is smaller when, be set it is smaller to reduce twist recovery when anti-work
Firmly.In addition, for first torque T c, when engine speed Ne and clutch rotational speed Nc rotation speed difference deltan Nec is larger, by it
Be set to it is larger to increase twist recovery when reaction force, on the other hand, when rotation speed difference deltan Nec is smaller, be set
It is smaller to reduce twist recovery when reaction force.
That is, the twist recovery of power transmission shaft 16 when reaction force it is proportional to first torque T c size.Therefore, it is intended that
First torque T c, which is set so that, to be set to the output torque Te of engine 11 to require that the power transmission shaft 16 after torque T b reaches advance
The torsional capacity Qa of setting value.In addition, torsional capacity Qa is the amount that the power transmission shaft 16 in the traveling of vehicle 10 is reversed, it is logical in advance
Cross experiment or experiment and obtain.
By so setting the first torque T c, so as to be set to by the output torque Te of engine 11 from the first torque T c
It is required that the moment of torsion of difference during torque T b is set to the first torque T c come the output torque Te offset engine 11 and has been passed this
The reaction force during twist recovery of the first torque T c power transmission shaft 16, the torsion of power transmission shaft 16 is set to the torsional capacity in traveling
Qa is to suppress the backswing of power transmission shaft 16.
Hereinafter, the flow chart shown in reference picture 2, on the present invention first embodiment automatic gear shifting method, as
The function of automatic gear shifting control device 20 illustrates.In addition, following, when AMT15 upshift exemplified by illustrate.In addition,
The automatic gear shifting method is separated and engine 11 in the above-mentioned clutch apparatus 14 into target gear Gx switching control
Output torque Te is reduced to after the initial torque Ta and AMT15 set according to target gear Gx be switched to target gear Gx
Start.
First, in step slo, speed change controls clutch driver 27 with control device 22, by clutch apparatus 14
Connected with half-clutch device state.The so-called half-clutch device state, it is that the tightening state of clutch apparatus 14 is 50% or so shape
State, some slips can also occur sometimes in clutch apparatus 14.
Next, in step S20, the output torque Te of engine 11 is risen to the first moment of torsion by engine with control device 21
Tc.By step S20, the first torque T c is transmitted via clutch apparatus 14 and AMT15 to power transmission shaft 16, utilizes first torsion
Square Tc reverses power transmission shaft 16 more than the torsional capacity Qa in traveling.Produced using due to the first torque T c on power transmission shaft 16
Torsion, the torsion reaction force to be recovered is exaggerated on power transmission shaft 16.
In addition, step S10 and step S20 is carried out simultaneously.Next, in step s 30, speed change will with control device 22
Clutch is maintained the half-clutch device state set in step slo with the travel of clutch CS of driver 27.
Next, in step s 40, speed change judges engine speed Ne and clutch rotational speed Nc rotating speed with control device 22
Whether poor Δ Nec is in preset range set in advance.
Preset range is set to following scope：It can determine that and be reduced to initial torque with the output torque Te of engine 11
Ta and become the engine speed Ne lower than the rotating speed of transmission shaft Np of power transmission shaft 16, close to the equal rotating speeds of rotating speed of transmission shaft Np from
Clutch rotating speed Nc.The preset range is set beforehand through experiment or experiment, such as is preferably configured the model near zero
Enclose.In the present embodiment, lower limit is set to zero, value Δ Na higher limit being set near zero.In addition, rotation speed difference deltan
Lower limit also comprising negative value, i.e. situation higher than clutch rotational speed Nc engine speed Ne, can also be set as bearing by Nec sometimes
Value.
In step S40, rotation speed difference deltan Nec outside the predetermined range in the case of, return to step S30, the opposing party
Face, rotation speed difference deltan Nec within a predetermined range in the case of, into step S50.In addition, returning to step from step S40
In the case of S30, engine speed Ne is controlled so that rotation speed difference deltan Nec reaches in preset range.For example, in rotation speed difference deltan
In the case that Nec is smaller than lower limit, increase the fuel injection amount of engine 11, it is on the other hand, bigger than higher limit in rotation speed difference deltan Nec
In the case of, the fuel injection amount of reduction engine 11.
So, by the way that engine speed Ne and clutch rotational speed Nc rotation speed difference deltan Nec are converged in preset range, so as to
The torsion of deceleration direction can be avoided producing on power transmission shaft 16.
Next, in step s 50, engine with control device 21 by the output torque Te of engine 11 from the first torque T c
It is raised to and requires torque T b.Now, the reaction force of the twist recovery of power transmission shaft 16 is raised the requirement torque T b's of engine 11
Output torque Te is offset, and the twisting states of power transmission shaft 16 reach torsional capacity Qa.
Next, in step S60, speed change controls clutch driver 27 with control device 22, by clutch apparatus
14 are fully connected, and the automatic gear shifting method is completed.In addition, step S50 and step S60 is carried out simultaneously.
Fig. 3 in temporal sequence exemplified with accelerator open degree AO when AMT15 to be switched to target gear Gx, engine speed Ne,
Clutch rotational speed Nc, the output torque Te of engine 11, the stroke CS of clutch driver 27.
In time t1, start the separation of clutch apparatus 14, also, start the output torque Te of engine 11 reduction.
Time t2, the separation of clutch apparatus 14 is completed, also, the output torque Te of engine 11 is reduced to initial torque Ta.
In time t3, the switching to target gear Gx since time t2 is completed, also, start clutch apparatus 14 to
The connection of half-clutch device state, further, start the output torque Te of engine 11 rising.
In time t4, clutch apparatus 14 connects under half-clutch device state, and the output torque Te of engine 11 rises to
One torque T c, power transmission shaft 16 are torqued into more than torsional capacity Qa.In time t5, engine speed Ne and clutch rotational speed Nc speed discrepancy
Δ Nec reaches in preset range, aims at the moment, starts the output torque Te of engine 11 rising.In addition, simultaneously, start from
The work of clutch driver 27 so that clutch apparatus 14 is fully connected from half-clutch device state.
In time t6, the output torque Te of engine 11, which rises to, requires torque T b, and the tightening state of clutch apparatus 14
For 100%, i.e. clutch apparatus 14 is fully connected, and the automatic gear shifting method is completed.
So,, will as the first stage after AMT15 is switched to target gear Gx by the operational situation according to vehicle 10
Clutch apparatus 14 is connected with half-clutch device state, also, the output torque Te of engine 11 is initially set to from initial torque Ta
First torque T c, so as to produce the torsion caused by first torque T c on power transmission shaft 16.As second stage, in power transmission shaft
After generating torsion on 16, the output torque Te of engine 11 is set to require torque T b from the first torque T c, with from the first moment of torsion
Tc offsets the torsion reaction force to be recovered of power transmission shaft 16 to the moment of torsion Δ T for the ascending amount for requiring torque T b.Then, engine
11 output torque Te reaches requirement torque T b, also, clutch apparatus 14 is fully connected from half-clutch device state, completes
AMT15 speed change.
By being controlled as progress, the twist recovery of power transmission shaft 16 can be offset using the moment of torsion Δ T of the ascending amount
When reaction force.I.e., initially, reversed using the first torque T c, power transmission shaft 16 little by little, by being driven in the twist recovery
Axle 16 so that its counterforce counteraction, so as to suppress the backswing because of caused by the torsion of power transmission shaft 16.
Thereby, it is possible to suppress caused backswing on the power transmission shaft 16 when AMT15 to be switched to target gear Gx, avoid with
Backswing is by the calibration of cause so as to shortening the time t7 that target gear Gx switching is spent.Further, since it can mitigate with this
Backswing is the gear shift shock of cause, so driving can be improved.
In above-mentioned automatic gear shifting control device 20, in upshift AMT15, by the output torque Te of engine 11 from first
Beginning torque T a is risen to after the first torque T c, after the torsion for generating the power transmission shaft 16 caused by first torque T c, on
It is raised to and requires torque T b, so as to further improves driving when especially gear shift shock becomes big upshift.
In addition, above-mentioned automatic gear shifting control device 20 is configured to have the first moment of torsion chart M2.First torque diagram
Table M2 is the engine speed Ne that target gear Gx is marked and drawed on the longitudinal axis and targeting engine rotating speed Na and reality are marked and drawed on transverse axis
Rotation speed difference deltan Nx chart.First moment of torsion chart M2 is set with the first moment of torsion based on target gear Gx and rotation speed difference deltan Nx
Tc(Gx、ΔNx).First torque T c (Gx, Δ Nx) is set to make to be set to require torque T b by the output torque Te of engine 11
Power transmission shaft 16 afterwards reaches torsional capacity Qa set in advance value.
Targeting engine rotating speed Na is calculated according to the rotating speed of transmission shaft Np and target gear Gx of power transmission shaft 16 gearratio
's.In addition, actual engine speed Ne is detected by CKP 25.In addition, targeting engine rotating speed Na also can be by
Based on target gear Gx and rotation speed difference deltan Nec can also be set with by being replaced as clutch rotational speed Nc, the first moment of torsion chart M2
One torque T c (Gx, Δ Necx).
Fig. 4 illustrates the first moment of torsion chart M2.The first moment of torsion chart M2 beforehand through experiment or experiment and be produced, be by
The chart being stored in advance in speed change control device 22.
Hereinafter, the flow chart shown in reference picture 5, on the first torque T c (Gx, Δ Nx) calculation method, become as automatic
The function of velocity control device 20 illustrates.
First, in the step s 100, speed change determines target gear Gx with control device 22.Next, in step s 110,
Speed change obtains rotating speed of transmission shaft Np with control device 22 from rotating speed of transmission shaft sensor 28.
Next, in the step s 120, rotating speed of transmission shaft Np and target of the speed change with control device 22 according to power transmission shaft 16
Gear Gx gearratio calculates targeting engine rotating speed Na.
Next, in step s 130, engine obtains current time with control device 21 from CKP 25
Engine speed Ne, speed change receive engine speed Ne with control device 22.Next, in step S140, speed change is filled with control
Put 22 and calculate rotation speed difference deltan Nx.Rotation speed difference deltan Nx is after targeting engine rotating speed Na subtracts engine speed Ne in upshift
Value.
Next, in step S150, speed change is with control device 22 with reference to the first moment of torsion chart M2.Next, in step
In S160, speed change extracts the first torsion based on target gear Gx and rotation speed difference deltan Nx from the first moment of torsion chart M2 with control device 22
Square Tc (Gx, Δ Nx), the calculation method are completed.
So, by calculating the first torque T c (Gx, Δ Nx) from the first moment of torsion chart M2, so as to without the meter of complexity
Calculate, it becomes possible to the amount of torsion when easily calculating the amount and the twist recovery of initial torque drive axle 16, therefore, it is possible to keep away
Exempt from the complication of control.
In addition, in the step S10 and step S20 of above-mentioned embodiment, step can also be started before step S10
S20.Specifically, can also be opened after the step of output torque Te by engine 11 rises to the first torque T c has been started
The step of beginning connects clutch apparatus 14 with half-clutch device state.Switch the spent time in such manner, it is possible to further shorten.
The application, will based on Japan's patent application (Japanese Patent Application 2015-152225) filed in 31 days in 07 month in 2015
Its content is used as reference to be incorporated herein.
Industrial applicibility
The controller of vehicle of the disclosure can be avoided calibrating because of caused by backswing and spent so as to shorten gear switching
Time, further, it is possible to mitigate using the backswing as the gear shift shock of cause so as to improve driving.
The explanation of reference
10 vehicles
11 engines
14 clutch apparatus
16 power transmission shafts
20 automatic gear shifting control devices
Gx target gears
Ta initial torques
Tb requires moment of torsion
The moments of torsion of Tc first
Claims (5)
1. a kind of automatic gear shifting control device, has：
Engine,
Clutch apparatus, the driving force from above-mentioned engine is switched off/on by it,
Automatic mechanical transmission, it is connected via above-mentioned clutch apparatus with above-mentioned engine, also, with to driving wheel transmission
The transmission axis connection of power, and
Control unit, it is connected respectively with above-mentioned engine, above-mentioned clutch apparatus and above-mentioned automatic mechanical transmission, and
It is controlled；
Above-mentioned control unit is controlled as follows：Above-mentioned automatic mechanical transmission is being switched to the operational situation phase with vehicle
After the target gear answered, by by the above-mentioned clutch apparatus being temporarily separated connect, so as to by the output torque of above-mentioned engine from
The initial torque set according to above-mentioned target gear be set to driver required by requirement moment of torsion；
Above-mentioned control unit is entered to be about to above-mentioned clutch apparatus and connected with half-clutch device state after above-mentioned target gear is switched to
Control, also, the output torque for entering to be about to above-mentioned engine be set to be set at above-mentioned initial torque and above-mentioned requirements moment of torsion it
Between control；
Above-mentioned control unit above-mentioned power transmission shaft generate from above-mentioned engine via above-mentioned clutch apparatus and it is above-mentioned it is mechanical from
Dynamic speed changer and after torsion caused by above-mentioned first moment of torsion that transmits, enter to be about to the output torque of above-mentioned engine from above-mentioned first
Moment of torsion is set to above-mentioned requirements moment of torsion and the control for being fully connected above-mentioned clutch apparatus from half-clutch device state.
2. automatic gear shifting control device as claimed in claim 1, wherein,
Switching to above-mentioned target gear is the upshift of above-mentioned automatic mechanical transmission.
3. automatic gear shifting control device as claimed in claim 1 or 2, wherein,
After the torsion that above-mentioned power transmission shaft is generated caused by above-mentioned first moment of torsion and engine speed and the rotating speed of clutch rotational speed
After difference becomes in preset range set in advance, the output torque for entering to be about to above-mentioned engine is set to above-mentioned from above-mentioned first moment of torsion
It is required that the control of moment of torsion.
4. the automatic gear shifting control device as described in any one of claims 1 to 3, wherein,
With part is calculated, this calculates part and calculated according to the rotating speed of transmission shaft of above-mentioned power transmission shaft and the gearratio of above-mentioned target gear
Go out targeting engine rotating speed, and calculate the speed discrepancy of the targeting engine rotating speed and actual engine speed, based on above-mentioned target gear
With the speed discrepancy that is calculated above-mentioned first moment of torsion is extracted from the first moment of torsion chart for being set with the first moment of torsion.
5. a kind of automatic gear shifting method, automatic mechanical transmission is being switched to target teeth corresponding with the operational situation of vehicle
After wheel, by the way that the clutch apparatus being temporarily separated is connected, so as to which the output torque of engine be set from according to the target gear
Fixed initial torque is set to the requirement moment of torsion required by driver；
Above-mentioned automatic gear shifting method is controlled as follows：
After above-mentioned target gear is switched to, above-mentioned clutch apparatus is connected with half-clutch device state, also, by above-mentioned engine
Output torque control to be set at the first moment of torsion between above-mentioned initial torque and above-mentioned requirements moment of torsion,
Above-mentioned first moment of torsion via above-mentioned clutch apparatus and above-mentioned automatic mechanical transmission transmission is generated in power transmission shaft
After caused torsion, the output torque of above-mentioned engine is set to above-mentioned requirements moment of torsion from above-mentioned first moment of torsion, also, will be above-mentioned
Clutch apparatus is fully connected from half-clutch device state.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015-152225 | 2015-07-31 | ||
| JP2015152225A JP6593016B2 (en) | 2015-07-31 | 2015-07-31 | Automatic transmission control device and automatic transmission method |
| PCT/JP2016/071580 WO2017022528A1 (en) | 2015-07-31 | 2016-07-22 | Automatic gearshift control device and automatic gearshift method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107848523A true CN107848523A (en) | 2018-03-27 |
| CN107848523B CN107848523B (en) | 2020-05-26 |
Family
ID=57942850
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680044453.1A Active CN107848523B (en) | 2015-07-31 | 2016-07-22 | Automatic transmission control device and automatic transmission method |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6593016B2 (en) |
| CN (1) | CN107848523B (en) |
| WO (1) | WO2017022528A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6926758B2 (en) * | 2017-07-14 | 2021-08-25 | いすゞ自動車株式会社 | Estimator and estimation method |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06346958A (en) * | 1993-06-04 | 1994-12-20 | Toyota Motor Corp | Controller of vehicular automatic transmission |
| JP2003094987A (en) * | 2001-09-20 | 2003-04-03 | Toyota Motor Corp | Control device for engine and transmission |
| JP2004330850A (en) * | 2003-05-07 | 2004-11-25 | Hitachi Ltd | Automobile controlling device and method, transmission controlling device, and automobile |
| JP2006283819A (en) * | 2005-03-31 | 2006-10-19 | Mitsubishi Fuso Truck & Bus Corp | Clutch controller |
| JP2010053941A (en) * | 2008-08-28 | 2010-03-11 | Daihatsu Motor Co Ltd | Method for controlling automatic transmission |
| JP2012031970A (en) * | 2010-08-02 | 2012-02-16 | Aisin Ai Co Ltd | Vehicular power transmission control apparatus |
| CN102958771A (en) * | 2010-10-22 | 2013-03-06 | 日野自动车株式会社 | Vehicle, control method, and program |
-
2015
- 2015-07-31 JP JP2015152225A patent/JP6593016B2/en active Active
-
2016
- 2016-07-22 CN CN201680044453.1A patent/CN107848523B/en active Active
- 2016-07-22 WO PCT/JP2016/071580 patent/WO2017022528A1/en active Application Filing
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06346958A (en) * | 1993-06-04 | 1994-12-20 | Toyota Motor Corp | Controller of vehicular automatic transmission |
| JP2003094987A (en) * | 2001-09-20 | 2003-04-03 | Toyota Motor Corp | Control device for engine and transmission |
| JP2004330850A (en) * | 2003-05-07 | 2004-11-25 | Hitachi Ltd | Automobile controlling device and method, transmission controlling device, and automobile |
| JP2006283819A (en) * | 2005-03-31 | 2006-10-19 | Mitsubishi Fuso Truck & Bus Corp | Clutch controller |
| JP2010053941A (en) * | 2008-08-28 | 2010-03-11 | Daihatsu Motor Co Ltd | Method for controlling automatic transmission |
| JP2012031970A (en) * | 2010-08-02 | 2012-02-16 | Aisin Ai Co Ltd | Vehicular power transmission control apparatus |
| CN102958771A (en) * | 2010-10-22 | 2013-03-06 | 日野自动车株式会社 | Vehicle, control method, and program |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2017022528A1 (en) | 2017-02-09 |
| CN107848523B (en) | 2020-05-26 |
| JP2017030529A (en) | 2017-02-09 |
| JP6593016B2 (en) | 2019-10-23 |
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