CN100404919C - Control device of non-stage transmission - Google Patents
Control device of non-stage transmission Download PDFInfo
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- CN100404919C CN100404919C CNB200510084386XA CN200510084386A CN100404919C CN 100404919 C CN100404919 C CN 100404919C CN B200510084386X A CNB200510084386X A CN B200510084386XA CN 200510084386 A CN200510084386 A CN 200510084386A CN 100404919 C CN100404919 C CN 100404919C
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Abstract
The present invention provides a continuously variable transmission control device for suppressing the worsening of drivability. An ECT ECU executes a program which includes a step (S202) of counting a frequency within a preset time Delta T when an output time TO for a control signal is longer than a preset time TA (MIN) and shorter than a preset time TA (MAX) when the output of a control signal to a first solenoid valve and the output of a control signal to a second solenoid valve hunt each other, and a step (S206) of correcting duty ratio-flow rate control output property to suppress the responsiveness of a hydraulic actuator when the counted frequency A is more than a preset frequency A(0) (YES in S204).
Description
Technical field
The present invention relates to the control gear of stepless speed variator, relate in particular to the stepless speed variator of gear ratio is controlled in use by the working oil of electromagnetic valve control gear.
Background technique
In the past, known have a variable v-belt drive (CVT:Continuously VariableTransmission).The following formation of this variable v-belt drive, that is: the roll coil of strip hangs over driving side belt wheel (the input shaft belt wheel with V-belt race, primary pulley) and slave end belt wheel (output pulley, secondary pulley) on, the groove width of the pulley groove by enlarging a belt wheel also reduces the groove width of the pulley groove of another belt wheel, make band hang radius (effective radius) and change continuously, thereby infinitely set gear ratio with respect to the volume of each belt wheel.Torque transmitted is and the corresponding torque of load that acts on band and the direction that is in contact with one another of belt wheel in this variable v-belt drive, therefore, and by belt wheel clamping band, so that add tension force to band application.
In addition, as mentioned above, speed change is to be undertaken by the groove width that enlarges, dwindles pulley groove, specifically, constitute each belt wheel by fast pulley and movable belt pulley, and movable belt pulley is moved before and after on axial direction, thereby carry out speed change by the oil pressure activated device of being located at the movable belt pulley back side one side.Being provided for the deceleration that the flow of the working oil of oil pressure activated device used with flow control valve and deceleration conversion by the speedup used of speed-raising conversion controls with flow control valve.Furthermore, speedup with flow control valve by the speedup electromagnetic valve.Slow down with flow control valve by the deceleration electromagnetic valve.
During the speed-raising conversion, by the dutycycle control that speedup is opened repeatedly and closed with solenoid valve, thereby working oil flows into the grease chamber of primary pulley with flow control valve from speedup.Thus, increase the V-belt volume and hang over the turning radius of the part on the primary pulley, thereby raise speed conversion.And when the deceleration conversion,, make that the working oil in the grease chamber of primary pulley flows out with flow control valve from deceleration by dutycycle control to slowing down and opening repeatedly and to close with solenoid valve.Thus, reduce the V-belt volume and hang over the turning radius of the part on the primary pulley, thereby slow down conversion.Determine the flow of the working oil that flows into, flow out from flow control valve herein, based on the value of the dutycycle of solenoid valve.About the dutycycle of solenoid valve, in advance dutycycle-flow control output characteristics is stored in ECU (Electronic ControlUnit; Electronic control unit) in the storage,, thereby determines its value then by calculating the corresponding dutycycle of flow with the working oil that is used to obtain desired gear ratio.
But, owing in flow control valve and solenoid valve, can produce manufacture deviation, so in its dutycycle-flow control output characteristics, also can produce deviation.Therefore, the dutycycle of being stored in the storage of ECU-flow control output characteristics may not be consistent with actual dutycycle-flow control output characteristics, and it is poor to produce characteristic therebetween.Therefore, can between the flow of desired flow and reality, produce error, thereby actual gear ratio is to the tracing property deterioration of desired gear ratio.Improve for this tracing property is worsened, the dutycycle-flow control output characteristics of being stored is learnt to revise.
The Japanese documentation spy opens 2003-227564 communique (patent documentation 1) and discloses a kind of control gear to dutycycle-stepless speed variator that the valve port area characteristic is revised of being stored in the electric control device.The control gear of record comprises in the patent documentation 1: flow control portion is controlled in the gear working oil flow that flows into, flows out based on the oil pressure control signal of being imported; Oil pressure control signal calculating part stores the oil pressure control signal-flow control output characteristics of flow control portion, and goes out with the flow control that is used to obtain desired gear ratio to export corresponding oil pressure control signal based on property calculation; The oil capacity detection unit detects the variation of the in-house working oil capacity of scheduled time internal speed-changing in the gear shifting operation; Oil capacity reckoning portion, the variation of calculating the in-house working oil capacity of scheduled time internal speed-changing based on the physical model of having considered the oil pressure control signal; And correction portion, revise oil pressure control signal-flow control output characteristics that oil pressure control signal calculating part is stored based on the deviation between the reckoning value of the checkout value of oil capacity detection unit and oil capacity reckoning portion.
According to the disclosed control gear of this communique, owing to revise the oil pressure control signal-flow control output characteristics of being stored in the oil pressure control signal calculating part, so the characteristic that can learn more accurately to revise between the oil pressure control signal-flow control output characteristics of reality of the oil pressure control signal-flow control output characteristics figure stored in the oil pressure control signal calculating part and flow control portion is poor based on the deviation between the reckoning value of the checkout value of oil capacity detection unit and oil capacity reckoning portion.Therefore, can suppress the error between desired flow and the actual flow, thereby improve the tracing property of actual gear ratio desired gear ratio.
Patent documentation 1: the Japanese documentation spy opens the 2003-227564 communique.
Open in the control gear that the 2003-227564 communique put down in writing the variation of calculating the working oil capacity based on physical model the Japanese documentation spy.But if physical model itself just contains error, reckoning value so also contains error.At this moment, oil pressure control signal-flow control output characteristics figure of being stored is revised by study mistakenly.If oil pressure control signal-flow control output characteristics figure is learnt by mistake, make that the operation amount of oil pressure activated device is too much, then tracing property is good excessively.In stepless speed variator, the control gear ratio, make the actual input revolution NIN of primary pulley with based on accelerator open degree etc. and the target of determining to import revolution NINT consistent.Therefore, if tracing property is good excessively, speed change vibration (the Japanese original text: speed change Ha Application チ Application グ) that actual input revolution NIN surpasses target repeatedly with respect to target input revolution NINT and do not reach target can take place then.Thus, the problem that has driveability deterioration.
Summary of the invention
The present invention finishes in order to address the above problem just, and its purpose is, a kind of control gear that can suppress the stepless speed variator of driveability deterioration is provided.
The control gear of the stepless speed variator of first invention is the control gear that is loaded in the stepless speed variator on the vehicle.The gear ratio of stepless speed variator is controlled by working oil.The flow of working oil is by electromagnetic valve.Control gear comprises control unit, this control unit is based on the predetermined information relevant with the flow of working oil, by being sent to solenoid valve, control signal comes control electromagnetic valve, and detect the number of oscillation of control signal, revise predetermined information based on the number of oscillation of the control signal in the scheduled period.
According to first invention, detect send to the number of times of vibration of control signal of solenoid valve from control gear after, based on the number of times correction predetermined information relevant of the vibration of the control signal in the scheduled period with the flow of working oil.For example,, then revise predetermined information, the responsiveness during with inhibition control gear ratio if the number of oscillation of the control signal in the scheduled period is more than pre-determined number.Thus,, can suppress actual input revolution NIN and surpass target and do not reach target so that the actual input revolution NIN of primary pulley imports in the consistent stepless speed variator of revolution with target in the control gear ratio with respect to target input revolution NINT.Therefore, can suppress the deterioration of cornering ability.A kind of control gear that can suppress the stepless speed variator of driveability deterioration consequently can be provided.
The control gear of the stepless speed variator of second invention is except the structure of first invention, and control unit also comprises as lower device: the number of oscillation that this device is used for the control signal in the scheduled period is revised predetermined information than predetermined times for a long time.
According to second invention,, then revise predetermined information if the number of oscillation of the control signal in the scheduled period is more than pre-determined number.For example revise predetermined information, the responsiveness during with inhibition control gear ratio.Thus,, can suppress actual input revolution NIN and surpass target and do not reach target so that the actual input revolution NIN of primary pulley imports in the consistent stepless speed variator of revolution NINT with target in the control gear ratio with respect to target input revolution NINT.Therefore, can suppress the deterioration of cornering ability.
The control gear of the stepless speed variator of the 3rd invention is except the structure of first invention, and control unit correction predetermined information is so that the responsiveness when suppressing the control gear ratio.
According to the 3rd invention, revise predetermined information, so that the responsiveness when suppressing the control gear ratio.Thus,, can suppress actual input revolution NIN and surpass target and do not reach target so that the actual input revolution NIN of primary pulley imports in the consistent stepless speed variator of revolution with target in the control gear ratio with respect to target input revolution NINT.Therefore, can suppress the deterioration of cornering ability.
The control gear of the stepless speed variator of the 4th invention is except the structure of first invention, and wherein, control unit is revised predetermined information according to the travelling state of vehicle.
According to the 4th the invention, for example under normal state and sliding state under, the difference vehicle travelling state and revise predetermined information.In the stepless speed variator of the actual input revolution NIN of control primary pulley with the inhibition fuel consume, if travelling state is a normal state, the frequency of the frequency ratio deceleration conversion of the conversion of then raising speed is many.In such normal state, the vibration in the time of can suppressing to raise speed conversion by revising the predetermined information relevant with the flow of working oil.On the other hand, make that the speed of a motor vehicle is low and in the stepless speed variator that gear ratio is high controlling, because the speed of a motor vehicle reduces during sliding state, so the frequency of the frequency ratio of deceleration conversion speed-raising conversion is many.In such sliding state, the vibration in the time of can suppressing to slow down conversion by revising predetermined information.
The control gear of the stepless speed variator of the 5th invention is except the structure of first to fourth invention, and wherein, control unit detects the generation of vibrating when in the scope of the output cycle of control signal at predetermined period.
According to the 5th invention, when in control signal is scope at predetermined period, being output, detecting and produced vibration.Thus, when detecting the vibration that has influence on such cycle of cornering ability, revise the predetermined information relevant, thereby can suppress the deterioration of cornering ability with working oil.
The control gear of the stepless speed variator of the 6th invention is except the structure of the 5th invention, and wherein, predetermined period is and the corresponding cycle of the travelling state of vehicle.
According to the 6th invention, the travelling state of difference vehicle when the normal state of speed-raising conversion tendency is arranged and when the sliding state of deceleration conversion tendency is arranged for example.Being detected the output cycle quilt that has produced vibration is set according to travelling state.Thus, the Characteristics Detection of contrast travelling state goes out vibration, thereby can suppress the deterioration of cornering ability.
Description of drawings
Fig. 1 is the control block diagram of the control gear in the embodiment of the present invention;
Fig. 2 is the details drawing of CVT shown in Figure 1;
Fig. 3 is the schematic representation of a part of oil hydraulic circuit that is used for the speed Control of CVT;
Fig. 4 is a schematic representation of exporting to the control signal of solenoid valve from ECT_ECU with the short period;
Fig. 5 be from ECT_ECU with the cycle export to the schematic representation of the control signal of solenoid valve;
Fig. 6 is the schematic representation by the control structure of the performed program of the ECU of the control gear in the embodiment of the present invention;
Fig. 7 represents to input to the sequential chart of the control signal of solenoid valve from ECT_ECU when the travelling state of vehicle is normal state.
Embodiment
Below, with reference to the description of drawings embodiments of the present invention.In the following description, the identical label of mark on identical parts.Its title and function are also identical.Therefore do not repeat it is elaborated.
With reference to Fig. 1, the transmission system of the vehicle that comprises the control gear in the present embodiment is described.Control gear in the present embodiment is by ECT shown in Figure 1 (Electronic ControlledAutomatic Transmission; Electronic automatic transmission) _ ECU 900 realizations.
As shown in Figure 1, power source 100 is connected with gear 200, and the output shaft 300 of this gear 200 is connected on the left and right sidesing driving wheel 500 via differential gear 400.Herein, power source 100 comprises the various power sources that can use in vehicle, and as internal-combustion engines such as petrol engine, diesel engine, perhaps motor such as motor has made up the device of these internal-combustion engines and motor etc. in addition.In the following description, as power source 100, with the petrol engine that adopts so-called straight spray petrol engine or have a electronic throttle that can free electric control throttle valve opening be example describe (below, power source 100 notes are made motor 100), described straight spray petrol engine can inject fuel directly into cylinder interior, and realizes homogeneous combustion or stratification burning opportunity by controlling its emitted dose and injection.
This motor 100 is constituted as and can carries out electrical control, and is provided with the Engine ECU 800 based on the microcomputer that is used for this control.This Engine ECU 800 is configured the output of controlling motor 100 at least, and the output request amount of output shaft revolution (engine revolution) NE and accelerator open degree PA etc. is exported as the data that are used to control.
This output request amount is the signal that is used to increase, reduce the output of motor 100, it can adopt the operation amount signal of acceleration and deceleration operation equipment 700 such as gas pedal of driver's operation or this operation amount of electric treatment and the signal that obtains, and in addition, can also be from the output request amount signal that is used for the speed of a motor vehicle is maintained the cruise control system (not shown) of setting the speed of a motor vehicle etc.
Gear 200 is made of fluid driving mechanism 210, forward-reverse switching mechanism 220, variable v-belt drive (CVT) 230.
On the position near fluid driving mechanism 210 oil pressure pump is set, the motor 100 that wherein said oil pressure pump is used as power source rotates, and improves ejection pressure according to its revolution.Specifically, be to be configured between fluid driving mechanism 210 and the forward-reverse switching mechanism 220.Certainly, when fluid driving mechanism 210 being set for the state that stops at vehicle also continues to drive motor 100, can use based on the state of vehicle and automatically interrupted automatic clutch replace above-mentioned fluid driving mechanism 210.
The output block of the input block of fluid driving mechanism 210 and motor 100 is connected, and the input block of the output block of fluid driving mechanism 210 and forward-reverse switching mechanism 220 is connected.This forward-reverse switching mechanism 220 is made of the two gear type planetary gears as an example, though especially do not illustrate, but have: brake component, with in sun gear and the planet carrier any one is input element, and be output element with another, simultaneously that gear ring is optionally fixing; Clutch element optionally connects any two rotatable members in this three element of sun gear and planetary wheel carrier and gear ring, thereby makes the whole one that forms of planetary gears.That is, will make the clutch element engagement be set at forward travel state, and set fallback state by brake component is meshed.
Variable v-belt drive 230 shown in Figure 1 be can make its input side parts revolution and the revolution of the parts of outlet side ratio, be the variable v-belt drive that gear ratio stepless (continuously) changes.An example of this variable v-belt drive 230 is described with reference to Fig. 2.
It comprises: driving side belt wheel (primary pulley) 232, slave end belt wheel (secondary pulley) 234 and volume hang over is with 236 on these belt wheels 232,234.The free fast pulley 238,240 of each of these belt wheels 232,234 and can to this fast pulley 238,240 near or from its away from movable belt pulley 242,244 constitute, and be provided with movable belt pulley 242,244 to oil pressure activated device 246,248 near the direction pushing of fast pulley 238,240.Be formed for rolling up the roll coil of strip hanging groove (pulley groove) that is linked with 236 V flute profile by these each belt pulleys 238,240,242,244.
In addition, to 246 supplies of oil pressure activated device or the discharge working oil of primary pulley 232, to obtain to make the revolution and the consistent gear ratio of target input revolution of input shaft 290.That is, change the size of hanging radius with respect to the volume of each belt wheel 232,234 with 236 by changing groove width in each belt wheel 232,234 (interval of fast pulley 238,240 and movable belt pulley 242,244), thus the speed change of execution.
More particularly, come the working oil of feedback control primary pulley 232 based on the revolution deviation (control deviation) between reality input revolution and the target input revolution, thereby carry out speed change, therefore, this control deviation is big more, and speed change speed is fast more.
With reference to Fig. 3, the oil hydraulic circuit of carrying out speed Control is described.
Working oil is undertaken by flow control the supply or the discharge of primary pulley 232.The valve system that is used for it constitutes as shown in Figure 3.That is, the oil pressure activated device 246 of primary pulley 232 is connected with providing pipe to press the first flow control valve 3100 of PL and be connected in second flow control valve 3200 that leaks end.First flow control valve 3100 is the valves that are used to carry out the speed-raising conversion, and it is constituted as: by guiding valve 3500 come switch provide input port 3300 that pipe presses PL and with output port 3400 that the oil pressure activated device 246 of primary pulley 232 is communicated with between stream.The one distolateral spring 3600 that disposes of this guiding valve 3500 simultaneously, clips this guiding valve 3500 is formed for applying signal pressure in the end of the opposition side of spring 3600 the first signal pressure port 3700.In addition, at an above-mentioned distolateral secondary signal pressure side mouth 3800 that is formed for applying signal pressure that disposes spring 3600.
Then, on the first signal pressure port 3700, connect first solenoid valve 3900 that improves delivery pressure according to dutycycle, on secondary signal pressure side mouth 3800, connect second solenoid valve 4000 that improves delivery pressure according to dutycycle, and apply the signal pressure of described solenoid valve 3900,4000 outputs to each signal pressure port 3700,3800.Promptly, improve the oil pressure that imposes on the first signal pressure port 3700 and open input port 3300, thereby working oil is offered the oil pressure activated device 246 of primary pulley 232 from output port 3400, thereby the groove width of primary pulley 232 is narrowed down, consequently make gear ratio reduce.That is, raise speed.In addition, by increasing the supply flow of working oil at this moment, speed change speed can be accelerated.
In addition, second flow control valve 3200 is the valves that are used to carry out the deceleration conversion, it is constituted as: first port 4100 that will be communicated with the oil pressure activated device 246 of primary pulley 232 by guiding valve 4400, optionally with provide that to press PL with pipe be that original second port 4200 and the leak port 4300 of compressing into the oil pressure after the capable pressure regulation is communicated with.At a distolateral configuration spring 4500 of this guiding valve 4400, and at the distolateral first signal pressure port 4600 that is formed for applying signal pressure of one.Clip guiding valve 4400 and be formed for applying the secondary signal pressure side mouth 4700 of signal pressure in the end of the opposition side of spring 4500.
Then, on the first signal pressure port 4600, connect first solenoid valve 3900, and on secondary signal pressure side mouth 4700, connect second solenoid valve 4000, thereby on each signal pressure port 4600,4700, apply the signal pressure of described solenoid valve 3900,4000 outputs.Promptly, improving the oil pressure that imposes on secondary signal pressure side mouth 4700 makes first port 4100 be communicated with leak port 4300, thereby discharge working oil from the oil pressure activated device 246 of primary pulley 232,, consequently make gear ratio increase so the groove width of primary pulley 232 becomes greatly.Promptly slow down.By increasing the discharge flow rate of working oil at this moment, speed change speed can be accelerated in addition.
In addition, second port 4200 at second flow control valve 3200 is connected with pressure regulator valve 4800.This pressure regulator valve 4800 is valves as follows, that is: form the input port 5100 that pipe pressure PL is provided in the front of the piston 5000 that is pushed by spring 4900 side, and have the output port 5200 that is communicated with front one side and the back side one side of this piston 5000, this output port 5200 is communicated with second port 4200 of second flow control valve 3200.In addition, will manage pressure PL via the little double small hole structure 5300 of opening area and offer input port 5100.That is, this pressure regulator valve 4800 is constituted as and makes at this output port 5200, promptly produces on second port 4200 of second flow control valve 3200 from pipe and press PL to deduct the oil pressure of pressure of the elastic force gained of spring 4900.
If further specifically describe, if under input port 3300 closing state of first flow control valve 3100, first port 4100 of second flow control valve 3200 is communicated with second port 4200, then is provided for the oil pressure activated device 246 of primary pulley 232 via second port 4200 by the working oil of pressure regulator valve 4800 pressure regulation.The flow of this moment is by the small quantity of double small hole structure 5300 restrictions.Consequently, though the oil pressure of the oil pressure activated device 246 of primary pulley 232 raises, but because the oil pressure of this oil pressure activated device acts on the back side one side of the piston 5000 in the pressure regulator valve 4800, so this pressure is the pressure of pressing PL to deduct the elastic force of spring 4900 and obtaining from managing, so piston 5000 is pushed to input port 5,100 one sides, thereby close input port 5100, stop thus and continue to provide working oil.Therefore, neither make working oil offer the oil pressure activated device 246 of primary pulley 232 from first flow control port 3100, it is discharged under these so-called pocketed oil (filling) states, the oil pressure that the oil pressure of the oil pressure activated device 246 of primary pulley 232 has been maintained in through pressure regulator valve 4800 pressure regulation from second flow control valve 3200.
It is the same with the situation of the inevitable leakage of oil of generation in the pocketed oil control that this oil pressure is kept state, when the leakage that produces oil from oil hydraulic circuit or oil pressure control apparatus etc., when thereby the oil pressure of the oil pressure activated device 246 of primary pulley 232 reduces, provide working oil from the input port 5100 of pressure regulator valve 4800 bit by bit to the oil pressure activated device 246 of primary pulley 232, to keep the pressure regulation value of pressure regulator valve 4800.Consequently, having the speed-raising conversion to be inclined to though the state of speed change is faint, is the slow speed-raising conversion that gear ratio bit by bit reduces.
In variable v-belt drive 230, hang under the state of radius maximum with respect to the volume of secondary pulley 234 with respect to the volume extension radius minimum of primary pulley 232 and with 236 with 236, gear ratio (maximum gear ratio: the maximum deceleration state) when setting lowest speed, in addition, in contrast, in that to hang radius with 236 with respect to the volume of primary pulley 232 maximum and hang under the state of radius minimum with respect to the volume of secondary pulley 234 with 236, gear ratio (the minimum gear ratio: maximum acceleration mode) when setting high speed.
Along with the engagement of the lock-up clutch in the gear 200 212, unclamp and slide, the switching of the control of each state of half engagement, the forward-reverse by forward-reverse switching mechanism 220 and the control of the gear ratio in the variable v-belt drive 230, basically be based on the travelling state of vehicle and controlled, so that the fuel efficiency ideal.Be provided with the ECT_ECU 900 that constitutes based on microcomputer in order to carry out this control.
This ECT_ECU 900 and above-mentioned Engine ECU 800 can be carried out data communication ground and be connected, and the data of the revolution (actual output revolutions NOUT) of the revolution of the input side of the input speed of a motor vehicle or gear 200 (the actual revolution NIN that imports), outlet side etc. are used as the data that are used to control.Tachometer generator 600 is in order to carry out speed Control in the variable v-belt drive 230 and the sensor of the revolution of detection of primary belt wheel 232 or secondary pulley 234 etc., as an example, the tooth of pulse gear (not shown) is by front end one side of electromagnetism adapter (not shown), thereby produce pulse signal at the electromagnetism adapter, obtain above-mentioned actual input revolution NIN and actual output revolutions NOUT thereby wait based on the interval of this pulse signal or pulse width.
Gearshift 100 is set, is used to select following each state (position), described state has: halted state (parking spot: the P position); Fallback state is (to the car position: the R position); Neutral condition (neutral position: the N position); Thereby according to the travelling state of vehicle come the automatic forward travel state that the automatic setting gear ratio travels normally (steering position: the D position); Pumping loss with motor 100 is the state (application position: the B position) of braking force; And forbid setting the above high speed gear ratio of predetermined value state (SD position).This gearshift 1000 is electrically connected with ECT_ECU 900.
In addition, ECT_ECU 900 is stored in dutycycle-flow control input characteristics in the storage (not shown), and described dutycycle-flow control input characteristics is the dutycycle (dutycycle command value) of the control signal of first solenoid valve 3900 and second solenoid valve 4000 and from the relation between the flow of first flow control valve 3100 and the supply of second flow control valve 3200 or the working oil of discharging.
ECT_ECU 900 calculates the dutycycle that is used to obtain expecting gear ratio based on dutycycle-flow control output characteristics.Yet, in first flow control valve 3100, second flow control valve 3200, first solenoid valve 3900 and second solenoid valve 4000, have the individual difference that deviation caused when making.Therefore, the flow of actual the working oil of supplying or discharging is different with the dutycycle of being stored-flow control output characteristics sometimes.At this moment, carry out the study correction of the dutycycle-flow control output characteristics of being stored.
In order to carry out the study correction of dutycycle-flow control output characteristics, ECT_ECU 900 calculates and is beginning in the time that speed change finishes from speed change or the speed-change process in the preset time, the variable quantity reckoning value of the working oil capacity of oil pressure activated device 246.The reckoning value of the variable quantity of working oil capacity is to utilize the physical model of the first flow control valve 3100 and second flow control valve 3200, and has considered that dutycycle calculates.Physical model is stored in the storage.In addition, the method about the variable quantity reckoning value of calculating oil capacity owing to utilize known general technology just passable, no longer repeats further detailed explanation.
In addition, ECT_ECU 900 calculates from the variable quantity of gear ratio and is beginning in the time that speed change finishes from speed change or the speed-change process in the preset time, the amount of movement of the movable belt pulley 242 of primary pulley 232.ECT_ECU 900 calculates based on the amount of movement of movable belt pulley 242 and begins in the time that speed change finishes or the speed-change process in the preset time from speed change, the variable quantity checkout value of the working oil capacity of oil pressure activated device 246.
Yet the physical model of being stored in the storage may not be consistent with the first flow control valve 3100 and second flow control valve 3200 of reality.Therefore, in the variable quantity reckoning value of working oil capacity, contain error.If revise dutycycle-flow control output characteristics based on such reckoning value study, the worry of the study of missing then arranged.
In addition, in variable v-belt drive 230, control oil pressure activated device 246 and to make that actual input revolution NIN and the target of primary pulley 232 are imported revolution NINT consistent.Here,, then exist the operation amount of oil pressure activated device 246 too much if dutycycle-flow control input characteristics of having learnt based on mistake calculates dutycycle and controls first solenoid valve 3900 and second solenoid valve 4000, thus the good excessively situation of responsiveness.
At this moment, actual input revolution NIN and target input revolution NINT are inconsistent.Therefore, as shown in Figure 4, from ECT_ECU 900 to the output of the control signal of first solenoid valve 3900 and to the output of the control signal of second solenoid valve 4000 in short period (vibration in 0～50msec) (alternately input).
In addition, as shown in Figure 5, from ECT_ECU 900 to the output of the control signal of first solenoid valve 3900 and to the output of the control signal of second solenoid valve 4000 vibration in the cycle (about 200msec).
Thus, produce the speed change vibration that actual input revolution NIN surpasses target repeatedly with respect to target input revolution NINT and do not reach target.After producing the speed change vibration, because the actual input revolution NIN of primary pulley 232 periodically increases and decreases, so the output revolutions of secondary pulley 234, be that the speed of a motor vehicle periodically increases and decreases.Thus, on vehicle, produce porpoise, driveability deterioration.The speed change vibration that the mistake study of 900 pairs of dutycycles of the control gear ECT_ECU of present embodiment-flow control output characteristics is caused suppresses.
With reference to Fig. 6, the control structure of the performed program of the control gear ECT_ECU 900 of present embodiment is described.In addition, carry out following program repeatedly with the predetermined cycle.
In step 100 (following abbreviate step as S), ECT_ECU 900 obtains to give dutycycle command value, accelerator open degree, brake signal, engine revolution, actual input shaft revolution NIN, the actual output revolutions NOUT of solenoid valve and the information of calculating input torque.In addition, the information of accelerator open degree and brake signal is sent to ECT_ECU 900 via Engine ECU 800 from acceleration and deceleration operation equipment 700.Engine revolution is sent to ECT_ECU 900 from Engine ECU 800.Calculate that input torque is calculated based on engine revolution by ECT_ECU 900 from chart.
In S200, ECT_ECU 900 judges based on obtained information whether the travelling state of vehicle is normal state.Whether about differentiating is the method for normal state, owing to utilize known general technology to get final product, so locate not repeat to its detailed description.If during normal state (being "Yes" among the S200), then handle and shift to S202.When no (being "No" among the S200), handle and shift to S300.
In S202, ECT_ECU counts below 900 pairs, promptly, to in preset time Δ T, be that the number of times A of time longer, shorter than preset time TA (MAX) than preset time TA (MIN) counts to the output time TO of the output of the control signal of first solenoid valve 3900 and the control signal when the output of the control signal of second solenoid valve 4000 is vibrated.That is, 900 couples of ECT_ECU are in preset time Δ T, and be that the number of times A of time longer, shorter than preset time TA (MAX) than preset time TA (MIN) counts period of vibration.In the present embodiment, TA (MIN) is set to 0msec, and TA (MAX) is set to 50msec.
In S204, ECT_ECU 900 judges whether the number of times A that is counted is more than predetermined times A (0).If the number of times A that is counted then handles and shifts to S206 than predetermined times A (0) many (being "Yes" among the S204).Otherwise (being "No" among the S204) handled and shifted to S208.
In addition, the condition that the number of times A that also can replace being counted is Duoed than predetermined times A (0), or in addition, the duty command value (dutycycle) when vibration is shifted to S206 than under the big situation of predetermined value with processing.
In S206, ECT_ECU 900 revises the dutycycle-flow control output characteristics of being stored in the storage, thereby revises the operation amount of oil pressure activated device 246.At this moment, the reduction value of establishing oil pressure activated device 246 is GA, and revises dutycycle-flow control output characteristics, so that suppress the responsiveness of oil pressure activated device 246.
In S208, ECT_ECU counts below 900 pairs, that is: in preset time Δ T, be that the number of times B of time longer, shorter than preset time TB (MAX) (TB (MAX)＞TA (MAX)) than preset time TB (MIN) (TB (MIN)＞TA (MIN)) counts to the output time TO of the output of the control signal of first solenoid valve 3900 and the control signal when the output of the control signal of second solenoid valve 4000 is vibrated.That is, 900 couples of ECT_ECU are in preset time Δ T, and be that the number of times B of time longer, shorter than preset time TB (MAX) than preset time TB (MIN) counts period of vibration.In the present embodiment, TB (MIN) is set to 150msec, and TB (MAX) is set to 250msec.
In S210, ECT_ECU 900 judges whether the number of times B that is counted is more than predetermined times B (0).If the number of times B that is counted then handles and shifts to S212 than predetermined times B (0) many (being "Yes" among the S210).Otherwise (being "No" among the S210) this processing finishes.
In addition, the condition that the number of times B that also can replace being counted is Duoed than predetermined times B (0), or in addition, the duty command value (dutycycle) when vibration is shifted to S212 than under the big situation of predetermined value with processing.
In S212, ECT_ECU 900 revises the dutycycle-flow control output characteristics of being stored in the storage, thereby revises the operation amount of oil pressure activated device 246.At this moment, the reduction value of establishing oil pressure activated device 246 is that (GB＞GA), and revise dutycycle-flow control output characteristics is so that suppress the responsiveness of oil pressure activated device 246 for GB.
In S300, ECT_ECU 900 judges based on the information that obtains whether the travelling state of vehicle is sliding state.About judging whether it is the method for sliding state, utilize known general technology to get final product, so go out not repeat to its detailed description.If sliding state (being "Yes" among the S300) is then handled and is shifted to S302.Otherwise (being "No" among the S300), this processing finishes.
In S302, ECT_ECU counts below 900 pairs, that is: in preset time Δ T, be that the number of times C of time longer, shorter than preset time TC (MAX) than preset time TC (MIN) counts to the output time TO of the output of the control signal of first solenoid valve 3900 and the control signal when the output of the control signal of second solenoid valve 4000 is vibrated.That is, 900 couples of ECT_ECU are in preset time Δ T, and be that the number of times C of time longer, shorter than preset time TC (MAX) than preset time TC (MIN) counts period of vibration.
In addition, TC (MIN) can be and the identical value of TA (MIN), also can be according to the output characteristics of the control signal under the sliding state, be set into the different value of TA (MIN).Equally, TC (MAX) can be and the identical value of TA (MAX), also can be according to the output characteristics of the control signal under the sliding state, be set into the different value of TA (MAX).
In S204, ECT_ECU 900 judges that whether the number of times C that is counted is than predetermined times C (0) many (C (0)＜A (0)).If the number of times C that is counted then handles and shifts to S306 than predetermined times C (0) many (being "Yes" among the S304).Otherwise (being "No" among the S304) handled and shifted to S308.
In addition, the condition that the number of times C that also can replace being counted is Duoed than predetermined times C (0), or in addition, the duty command value (dutycycle) when vibration is shifted to S306 than under the big situation of predetermined value with processing.
In S306, ECT_ECU 900 revises the dutycycle-flow control output characteristics of being stored in the storage, thereby revises the operation amount of oil pressure activated device 246.At this moment, the reduction value of establishing oil pressure activated device 246 is GC, and revises dutycycle-flow control output characteristics, so that suppress the responsiveness of oil pressure activated device 246.In addition, reduction value GC can be the value identical with reduction value GA, also can be according to the output characteristics of the control signal under the sliding state, and be set and be the value different with reduction value GA.
In S308, ECT_ECU counts below 900 pairs, that is: in preset time Δ T, be than preset time TD (MIN) long (TD (MIN)＞TC (MIN)), count than the number of times D of time of preset time TD (MAX) short (TD (MAX)＞TC (MAX)) to the output time TO of the output of the control signal of first solenoid valve 3900 and the control signal when the output of the control signal of second solenoid valve 4000 is vibrated.That is, 900 couples of ECT_ECU are in preset time Δ T, and be that the number of times D of time longer, shorter than preset time TD (MAX) than preset time TD (MIN) counts period of vibration.
In addition, TD (MIN) can be and the identical value of TB (MIN), also can be that the output characteristics according to the control signal of sliding state is set at the different value with TB (MIN).Equally, TD (MAX) can be and the identical value of TB (MAX), also can be that the output characteristics according to the control signal of sliding state is set at the different value with TB (MAX).
In S310, ECT_ECU 900 judges that whether the number of times D that is counted is than predetermined times D (0) many (D (0)＞B (0)).If the number of times D that is counted then handles and shifts to S312 than predetermined times D (0) many (being "Yes" among the S310).Otherwise (being "No" among the S310) this processing finishes.
In addition, the condition that the number of times D that also can replace being counted is Duoed than predetermined times D (0), or in addition, the duty command value (dutycycle) when vibration is shifted to S312 than under the big situation of predetermined value with processing.
In S312, ECT_ECU 900 revises the dutycycle-flow control output characteristics of being stored in the storage, thereby revises the operation amount of oil pressure activated device 246.At this moment, the reduction value of establishing oil pressure activated device 246 is that (GD＞GC), revise dutycycle-flow control output characteristics is to suppress the responsiveness of oil pressure activated device 246 for GD.In addition, reduction value GD can be the value identical with reduction value GB, also can be according to the output characteristics of the control signal under the sliding state, and be set and be the value different with reduction value GB.
The action that control gear ECT_ECU 900 in the present embodiment is described based on above such structure and flow chart.
In the middle of vehicle driving,, the information such as duty command value, accelerator open degree, brake signal, engine revolution, actual input shaft revolution NIN, output revolutions and reckoning input torque of solenoid valve have been obtained to give as detecting speed change vibration information necessary.
Whether the travelling state of judging vehicle based on the information that is obtained is normal state (S200).If normal state (being "Yes" among the S200), then in order to judge whether short-period speed change vibration produces, and count following, that is: in preset time Δ T, the output time TO the when output of control signal is vibrated is the number of times A (8202) of time longer, shorter than preset time TA (MAX) than preset time TA (MIN).
If as time Δ T from time T (1) to time T (2) and time Δ T among Fig. 7 from time T (2) to time T (3), the number of times A that is counted lacks (being "No" among the S204) than predetermined times A (0), then do not carry out the correction of dutycycle-flow control output characteristics, promptly do not carry out the correction of the operation amount of oil pressure activated device 246.
On the other hand, if as time Δ T from time T (3) to time T (4), the number of times A that is counted is than predetermined times A (0) many (being "Yes") among the S204, the reduction value of then establishing oil pressure activated device 246 is GA, revise dutycycle-flow control output characteristics, to suppress the responsiveness (S206) of oil pressure activated device 246.Thus, can reduce the operation amount of oil pressure activated device 246, suppress responsiveness, and then suppress the generation of speed change vibration.
In addition, for whether the vibration of the speed change in cycle in judging produces, and count following, that is: in preset time Δ T, the output time TO the when output of control signal is vibrated be longer than preset time TB (MIN), count (S208) than the number of times B of time of preset time TB (MAX).
If the number of times B that is counted in preset time Δ T lacks (being "No" among the S210) than predetermined times B (0), then owing to the speed change in cycle in not producing is vibrated, so do not carry out the correction of dutycycle-flow control output characteristics.
On the other hand, if the number of times B that is counted in preset time Δ T is than predetermined times B (0) many (being "Yes") among the S210, then because the speed change in cycle vibration in producing, so establishing the reduction value of oil pressure activated device 246 is GB, and revise dutycycle-flow control output characteristics, to suppress the responsiveness (S212) of oil pressure activated device 246.Thus, can reduce the operation amount of oil pressure activated device 246, suppress responsiveness, and then suppress the generation of speed change vibration.
Responsiveness when the responsiveness of the oil pressure activated device 246 the when speed change in cycle is vibrated in the generation is vibrated than the short-period speed change of generation is low.The little reduction value of reduction value GA when the reduction value GB of the oil pressure activated device 246 when therefore, the speed change in cycle is vibrated in the generation preferably vibrates than the short-period speed change of generation.
When the travelling state of vehicle is normal state, because control variable v-belt drive 230 is to improve fuel efficiency, so the frequency of the frequency ratio deceleration conversion of speed-raising conversion is many.Therefore, if when normal state, revise dutycycle-flow control output characteristics, thereby then make that for learnt dutycycle-flow control output characteristics in speed-raising conversion mistiming the too much situation of the operation amount of oil pressure activated device 246 is effective.
On the other hand, when being sliding state, the travelling state of vehicle (is "No" among the S200, among the S300 "Yes"), the same for normal state the time, judge and whether produced short-period speed change vibration, so count following, that is: in preset time Δ T, the output time TO of the control signal the when output of control signal is vibrated is the number of times C (S302) of time longer, shorter than preset time TC (MAX) than preset time TC (MIN).
If the number of times C that is counted in the preset time Δ T lacks (being "No" among the S304) than predetermined times C (0), then do not carry out the correction of dutycycle-flow control output characteristics, promptly do not carry out the correction of the operation amount of oil pressure activated device 246.
If the number of times C that is counted in the preset time Δ T (is "Yes") for a long time than predetermined times C (0) among the S304, if the reduction value of oil pressure activated device 246 is GC, and revise dutycycle-flow control output characteristics, to suppress the responsiveness (S306) of oil pressure activated device 246.Thus, can reduce the operation amount of oil pressure activated device 246, suppress responsiveness, and then suppress the generation of short-period speed change vibration.
In addition, in order to judge the speed change vibration that whether has produced the middle cycle, so count to following, that is: in preset time Δ T, the output time TO of the control signal the when output of control signal is vibrated is the number of times D (S308) of time longer, shorter than preset time TD (MAX) than preset time TD (MIN).
If the number of times D that is counted in the preset time Δ T lacks (being "Yes" among the S310) than predetermined times D (0), then owing to the speed change in cycle in not producing is vibrated, so do not carry out the correction of dutycycle-flow control output characteristics.
On the other hand, if the number of times D that is counted in preset time Δ T is than predetermined times D (0) many (being "Yes") among the S310, then because the speed change in cycle vibration in producing, so establishing the reduction value of oil pressure activated device 246 is GD, and revise dutycycle-flow control output characteristics, to suppress the responsiveness (S312) of oil pressure activated device 246.Thus, can reduce the operation amount of oil pressure activated device 246, suppress responsiveness, and then suppress the generation of speed change vibration.
Responsiveness when the responsiveness of the oil pressure activated device 246 the when speed change in cycle is vibrated in the generation is vibrated than the short-period speed change of generation is low.Therefore, the reduction value GD of the oil pressure activated device 246 in the speed change in cycle when vibration is preferably the little reduction value of reduction value GC when producing short-period speed change vibration in the generation.
When the travelling state of vehicle was sliding state, along with the deceleration of the speed of a motor vehicle, the frequency of the frequency ratio of deceleration conversion speed-raising conversion was many.Therefore, if when sliding state, revise dutycycle-flow control output characteristics, thereby then make that for learnt dutycycle-flow control output characteristics as deceleration conversion mistiming the too much situation of the operation amount of oil pressure activated device 246 is effective.
As mentioned above, 900 pairs of following countings of the ECT_ECU of the control gear of present embodiment, that is: in preset time Δ T, the number of times of output time TO in the preset time scope of the control signal the when output of control signal is vibrated.If the number of times of being counted is more than predetermined times, then ECT_ECU revises dutycycle-flow control output characteristics, to suppress the responsiveness of oil pressure activated device.Thus, can reduce the operation amount of oil pressure activated device, suppress responsiveness, and then suppress the generation of speed change vibration.
Should think that all aspects of this disclosed mode of execution all are illustration rather than restriction.Scope of the present invention is not by above-mentioned explanation but represents by claims, its be intended to comprise with claims equivalence and scope in institute change.
Claims (6)
1. the control gear of a stepless speed variator is loaded on the vehicle, and the gear ratio of described stepless speed variator controlled by working oil, and the flow of working oil is by electromagnetic valve, and the control gear of described stepless speed variator is characterised in that, comprising:
Control unit, it is based on the predetermined information relevant with the flow of working oil, come described solenoid valve is controlled by control signal being sent to described solenoid valve, and detect the number of oscillation of described control signal, revise described predetermined information based on the number of oscillation of the described control signal in the scheduled period.
2. the control gear of stepless speed variator as claimed in claim 1, wherein,
The number of oscillation of the described control signal of described control unit in the described scheduled period is revised described predetermined information than predetermined times for a long time.
3. the control gear of stepless speed variator as claimed in claim 1, wherein, the described predetermined information of described control unit correction, the responsiveness when suppressing gear ratio controlled.
4. the control gear of stepless speed variator as claimed in claim 1, wherein, described control unit is revised described predetermined information according to the travelling state of described vehicle.
5. as the control gear of each described stepless speed variator in the claim 1 to 4, wherein,
Described control unit detects the generation of vibration when in the scope of the output cycle of described control signal at predetermined period.
6. the control gear of stepless speed variator as claimed in claim 5, wherein, described predetermined period is and the corresponding cycle of the travelling state of described vehicle.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP229334/2004 | 2004-08-05 | ||
| JP2004229334A JP4556535B2 (en) | 2004-08-05 | 2004-08-05 | Control device for continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1730989A CN1730989A (en) | 2006-02-08 |
| CN100404919C true CN100404919C (en) | 2008-07-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200510084386XA Expired - Fee Related CN100404919C (en) | 2004-08-05 | 2005-07-19 | Control device of non-stage transmission |
Country Status (2)
| Country | Link |
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| JP (1) | JP4556535B2 (en) |
| CN (1) | CN100404919C (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4305488B2 (en) * | 2006-10-04 | 2009-07-29 | トヨタ自動車株式会社 | Control device for continuously variable transmission, control method, program for realizing the method, and recording medium recording the program |
| JP5030608B2 (en) * | 2007-01-31 | 2012-09-19 | ヤマハ発動機株式会社 | Continuously variable transmission, vehicle equipped with the same, control device for continuously variable transmission, and control method therefor |
| JP5131157B2 (en) * | 2008-10-31 | 2013-01-30 | トヨタ自動車株式会社 | Closed control device |
| JP6211704B2 (en) * | 2014-07-29 | 2017-10-11 | ジヤトコ株式会社 | Continuously variable transmission and control method thereof |
| JP6653946B2 (en) * | 2015-03-10 | 2020-02-26 | ダイハツ工業株式会社 | Control device for continuously variable transmission |
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| CN1286186A (en) * | 1999-08-25 | 2001-03-07 | 三菱自动车工业株式会社 | Hydraulic circuit for belt type adjustable speed drive |
| CN1392356A (en) * | 2001-06-18 | 2003-01-22 | 本田技研工业株式会社 | Hydraulic controller of speed changer |
| JP2003028282A (en) * | 2001-07-17 | 2003-01-29 | Toyota Motor Corp | Hydraulic controlling device for continuously variable transmission |
| JP2003227564A (en) * | 2002-02-04 | 2003-08-15 | Toyota Motor Corp | Controller of continuously variable transmission |
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| JP2785225B2 (en) * | 1988-06-07 | 1998-08-13 | アイシン・エィ・ダブリュ株式会社 | Control device for automatic continuously variable transmission for vehicles |
| JP3500798B2 (en) * | 1995-10-16 | 2004-02-23 | 日産自動車株式会社 | Transmission control device for stepped automatic transmission |
| JPH1019117A (en) * | 1996-06-28 | 1998-01-23 | Unisia Jecs Corp | Shift controller for transmission |
| JP2001263469A (en) * | 2000-03-17 | 2001-09-26 | Komatsu Ltd | Method of preventing hunting in automatic transmission |
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2004
- 2004-08-05 JP JP2004229334A patent/JP4556535B2/en not_active Expired - Fee Related
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- 2005-07-19 CN CNB200510084386XA patent/CN100404919C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1286186A (en) * | 1999-08-25 | 2001-03-07 | 三菱自动车工业株式会社 | Hydraulic circuit for belt type adjustable speed drive |
| CN1392356A (en) * | 2001-06-18 | 2003-01-22 | 本田技研工业株式会社 | Hydraulic controller of speed changer |
| JP2003028282A (en) * | 2001-07-17 | 2003-01-29 | Toyota Motor Corp | Hydraulic controlling device for continuously variable transmission |
| JP2003227564A (en) * | 2002-02-04 | 2003-08-15 | Toyota Motor Corp | Controller of continuously variable transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2006046517A (en) | 2006-02-16 |
| CN1730989A (en) | 2006-02-08 |
| JP4556535B2 (en) | 2010-10-06 |
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