CN100476248C - Hydraulic controller for belt driving stepless speed variator and control method thereof - Google Patents
Hydraulic controller for belt driving stepless speed variator and control method thereof Download PDFInfo
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- CN100476248C CN100476248C CNB2005100723976A CN200510072397A CN100476248C CN 100476248 C CN100476248 C CN 100476248C CN B2005100723976 A CNB2005100723976 A CN B2005100723976A CN 200510072397 A CN200510072397 A CN 200510072397A CN 100476248 C CN100476248 C CN 100476248C
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Abstract
The present invention discloses a hydraulic control equipment for belt transmission stepless speed-changer and its control method. When the oil pump output learning mark is set as ON, it can execute the following steps: outputting hydraulic command value higher than pipeline pressure P(L) to linear coil (SLS); adopting inversion mode to output control load of linear coil (SLT); using hydraulic sensor for detecting hydraulic pressure regulated by linear electromagnetic valve (SLS) to detect pipeline pressure P(L); and learning and correcting diagram of relationship between the inversion control load of linear coil (SLT) and detected pipeline pressure.
Description
Technical field
The present invention relates to be used for the control apparatus of stepless speed variator, more specifically, relate to the hydraulic-pressure control apparatus and the controlling method thereof that are used for continuously variable belt transmission.
Background technique
As basic structural element, continuously variable belt transmission comprises driving side rotating member, slave end rotating member, reaches the dirivig member (driving belt) that twines driving side rotating member and slave end rotating member.Stepless speed variator is controlled the speed ratio of speed changer by to the hydraulic control of dirivig member with respect to the winding radius of driving side rotating member.
Continuously variable belt transmission comprises: input shaft is input to this input shaft from the torque of motor; The output shaft that be arranged in parallel with input shaft; Be arranged on the primary pulley on the input shaft side; With the secondary pulley that is arranged on the output shaft side.Primary pulley have the fixedly wheel disc that is fixed to input shaft and can input shaft axially on the removable wheel disc that moves.Secondary pulley have the fixedly wheel disc that is fixed to output shaft and can output shaft axially on the removable wheel disc that moves.Band twines primary pulley and secondary pulley.In addition, stepless speed variator is provided with first hydraulic chamber (oil pressure chamber) and second hydraulic chamber, the operation of the removable wheel disc of first hydraulic chamber control primary pulley, the operation of the removable wheel disc of second hydraulic chamber control secondary pulley.
The velocity variations control device is set assigns to control the hydraulic pressure of first hydraulic chamber.The velocity variations control section comprises that the speed that is connected to the loine pressure control valve increases solenoid valve and speed reduces solenoid valve; And speed increases flow control valve and speed reduces flow control valve.Speed increases flow control valve and has spool, control room, spring housing, input port and output port.Speed reduces flow control valve and has spool, control room, spring housing, input port and discharge port.The control room that speed increases flow control valve is connected to the output port that speed increases solenoid valve, and the output port of speed increase flow control valve is connected to first hydraulic chamber.
On the other hand, the input port that speed reduces flow control valve is connected to first hydraulic chamber, is connected to the output port that speed reduces solenoid valve and speed reduces the control room of flow control valve.In addition, the output port of speed increase solenoid valve is connected to the spring housing that speed reduces flow control valve.The output port that speed reduces solenoid valve is connected to the spring housing that speed increases flow control valve.Band pressure hydraulic control valve is connected to second hydraulic chamber, and loine pressure is applied to the input port of band pressure hydraulic control valve.
Utilize above-mentioned structure, the output hydraulic control of oil pump is predetermined loine pressure by the loine pressure control valve.This loine pressure speed that is applied to increases the input port of flow control valve and the input port of band pressure hydraulic control valve.More specifically, by these two solenoid valves are switched between different opening and closing position groupings, velocity variations control section control: (a) increase flow control valve and be fed to oil (liquid) flow rate of first hydraulic chamber and (b) reduce the oily flow rate that flow control valve is discharged from first hydraulic chamber via speed via speed.
Utilize this structure, change the groove width of primary pulley by the hydraulic pressure of controlling first hydraulic chamber, change in other words on the primary pulley side with the winding radius, control speed ratio.In addition, control the clamping force that is applied to band by the hydraulic pressure of controlling second hydraulic chamber.So, can keep the tension force consistent with driving torque.
The open flat 7-117150 of No. of Japan Patent (Japanese patent application discloses the flat 4-131564 of No. in early days) discloses a kind of example of hydraulic-pressure control apparatus of automobile-used continuously variable belt transmission, and the individual difference that wherein produces the pressure regulator valve of basic hydraulic pressure can not make the precision of control hydraulic regulation reduce.The hydraulic-pressure control apparatus of this automobile-used continuously variable belt transmission comprises pressure regulator valve, linear valve, adjusting part, hydrostatic sensor, output signal pressure arresting stop and learning device.Pressure regulator valve can use choke pressure and velocity variations pressure to regulate to be used to apply the basic hydraulic pressure of clamping pressure to driving belt at least.Linear valve will be fed to pressure regulator valve by continually varying output signal pressure according to control signal value, and the hydraulic pressure of being regulated with pressure regulator valve is set to the optimum pressure less than basic hydraulic pressure.The output signal pressure of regulating part linear adjustment valve to be eliminating poor between basic hydraulic pressure and the optimum pressure, and basic hydraulic pressure and optimum pressure are based on that the relation therebetween of storage in advance calculates respectively.Hydrostatic sensor detects the hydraulic pressure of being regulated by pressure regulator valve, and output signal pressure arresting stop stop supplies output signal pressure is to pressure regulator valve.By output signal pressure arresting stop stop supplies output signal pressure during to pressure regulator valve, learning device makes hydrostatic sensor detect actual basic hydraulic pressure when.Then, learning device is set up the relation that is used to calculate basic hydraulic pressure based on the actual hydraulic pressure that is detected.
Hydraulic-pressure control apparatus according to this automobile-used continuously variable belt transmission, by output signal pressure arresting stop stop supplies output signal pressure during to pressure regulator valve, learning device is set up the relation that is used to calculate basic hydraulic pressure based on the actual hydraulic pressure that hydrostatic sensor detected when.So,, also make from proofreading and correct basic hydraulic pressure that the back relation the calculates more close actual hydraulic pressure in ground that meets the requirements even because the individual difference of pressure regulator valve causes that the output characteristics of basic hydraulic pressure changes.Thus, the precision that can prevent from the to control hydraulic regulation influence of individual difference of modulating valve that is under pressure.
In addition, Japanese Patent Laid Open Publication No. flat 9-217800 discloses the another kind of hydraulic-pressure control apparatus that is used for continuously variable belt transmission etc.This hydraulic-pressure control apparatus formation wherein uses hydraulic switch to carry out the system of the cheapness of learning correction.By carrying out correct operation under the situation when hydraulic pressure will can not influence performance, learn reliably to handle and judge in simple relatively mode.The hydraulic-pressure control apparatus of this continuously variable belt transmission is a kind of like this hydraulic-pressure control apparatus of speed changer, and it can control the hydraulically operated operation pressure that is used for changes in vehicle speed mechanism.Under the situation when the big young pathbreaker of operation pressure can not influence transmission operating, hydraulic-pressure control apparatus produces to detect uses hydraulic pressure; And hydraulic-pressure control apparatus comes the correcting value of learning manipulation pressure based on the response of the hydraulic detection device that is provided with in whether having from the operation pressure loop when producing detection with hydraulic pressure.
Be used for the hydraulic-pressure control apparatus of continuously variable belt transmission etc. according to this, the hydraulic-pressure control apparatus of the operation pressure that this hydraulic operation that is used for velocity variations mechanism is used, produce under the situation in the time of can not influencing transmission operating based on size and detect when using hydraulic pressure at operation pressure, whether response from the hydraulic detection device that is provided with in the operation pressure loop is arranged, come the correcting value of learning manipulation pressure.So, need not to be provided for the expensive hydrostatic sensor of feedback control, just can realize correct and the self-correcting of shirtsleeve operation pressure.And, constructed a kind of low cost system that uses simple hydraulic switch to learn and proofread and correct.In addition, according to above-mentioned hydraulic-pressure control apparatus, even cause the fluctuation of delivery pressure,, also can provide hydraulic-pressure control apparatus with the function that can carry out accurate operation pressure control even perhaps in time deterioration takes place by the individual difference of the solenoid valve that uses in the system etc.In addition, by carrying out correct operation under the situation when hydraulic pressure does not influence performance, can learn to handle and judge in simple relatively mode, and high reliability is provided.
But if adopt technology similar to the above to carry out learning control in the hydraulic-pressure control apparatus that oil pump delivery pressure and strap clamp compaction forces are independently controlled, problem then discussed below will become obviously.That is, such hydraulic-pressure control apparatus is provided with: be used to control the linear solenoid valve of safety valve (pressure reduces valve), this safety valve is adjusted to loine pressure with the oil pump delivery pressure; With the linear solenoid valve that is used to control safety valve (pressure reduces valve), this safety valve is adjusted to the strap clamp compaction forces with loine pressure.These valves are arranged in the different oil hydraulic circuits.So,, the hydraulic pressure detecting sensor need be set in each hydraulic control system in order to learn the individual difference of each linear solenoid valve and safety valve.
More specifically, the hydrostatic sensor of detection strap clamp compaction forces is set usually in feedback control, to use.As a result, can learn the characteristic of the hydraulic equipment that in the strap clamp clamping system, uses.But, for study and the control of carrying out the loine pressure control system, need be provided for the hydrostatic sensor of signal piping pressure extraly, this cost that causes not expecting improves.
Summary of the invention
The invention provides solution to the problems referred to above, and the purpose of this invention is to provide the hydraulic-pressure control apparatus and the controlling method thereof that are used for continuously variable belt transmission, its can be in the hydraulic control circuit that comprises two linear electromagnetic valve systems relation between learning control signal and the hydraulic pressure value, and do not require any raising on the cost.
According to first aspect present invention, the hydraulic-pressure control apparatus that is used for continuously variable belt transmission comprises: be used for will be from the hydraulic regulation of oil pump output to loine pressure first pressure regulator; Be used for described loine pressure is adjusted to second pressure regulator of the tight hydraulic pressure of strap clamp; Be used to detect the detection device of the tight hydraulic pressure of regulating by described second pressure regulator of described strap clamp; Be used for storing in advance storage device to the control signal and the relation between the described loine pressure of first pressure regulator; And correcting device, described correcting device is under the pressure of described second pressure regulator reduces to operate situation when not carrying out, based on when the described control signal to described first pressure regulator is changed by the detected hydraulic pressure of described detection device, proofread and correct the described control signal of described first pressure regulator and the described relation between the described loine pressure.
According to first aspect, as its initial setting up, storage device is stored in advance to the relation between value of the control signal of first pressure regulator (load) and the loine pressure.When satisfying condition " vehicle that this continuously variable belt transmission is installed is stopped ", the pressure adjusting operation that stops second pressure regulator of adjusting belt clamping hydraulic can not cause serious problem.So when the pressure of loine pressure reduces (it is that the pressure of second pressure regulator is regulated operation) when being stopped, the hydraulic pressure that is applied to second pressure regulator does not just change and is output.If the control signal value to first pressure regulator is changed in these cases, then the detection device of the hydraulic pressure of having been regulated by second pressure regulator by common detection detects this hydraulic pressure value.At this moment, the pressure of second pressure regulator is regulated operation and is stopped, therefore the pressure of being regulated by first pressure regulator by the detected hydraulic pressure value of detection device.Relation between this detected hydraulic pressure value and the control signal value and the relation of the storage in the storage device compare.Under situation about there are differences between these relations, determine the control signal value of first pressure regulator and the relation between the loine pressure are changed owing to individual difference or deterioration in time, and proofread and correct by nearest relation is stored in the storage device thus.Result as adopting this structure does not need to be provided with line-pressure sensor and directly detects the hydraulic pressure of being regulated by first pressure regulator.So, can be provided for the hydraulic-pressure control apparatus of continuously variable belt transmission and its controlling method, it makes it possible to learn control signal in the hydraulic control circuit that comprises two linear electromagnetic valve systems and the relation between the hydraulic pressure value and does not require any raising of cost.
The structure of first aspect can be such, and its described relation that is corrected is to the described control signal of described first pressure regulator and the dependency relation between the described loine pressure.
In the case, for example, first pressure regulator can be reduced valve by the pressure that linearity coil is controlled, and the load and the dependency relation between the loine pressure that are applied to the control electric current of linearity coil can be stored in the storage device in advance.This dependency relation can be used for accurately calculating the load with the corresponding control electric current of required loine pressure.Traditionally, delivery pressure that need oil pump is set to high slightly level, comes to make accurate dependency relation not know that this fact stays leeway for individual difference and deterioration in time.This causes the moving loss of pump of oil pump again.But the structure of first aspect can be suppressed the moving loss of the pump of this type.
In addition, first aspect can be configured to described loine pressure and be supplied to the hydraulic chamber of driving side belt wheel via switching valve, and the tight hydraulic pressure of described strap clamp is supplied to the hydraulic chamber of slave end belt wheel.
In the case, the velocity variations of continuously variable belt transmission can followingly be carried out, be that hydraulic chamber that described loine pressure is supplied to the driving side belt wheel comes execution speed to increase or speed reduces control, and the tight hydraulic pressure of described strap clamp is supplied to the hydraulic chamber of slave end belt wheel to produce required strap clamp compaction forces.
According to first aspect, described driving side belt wheel and described slave end belt wheel does not rotate and driving torque effect situation thereon under, described correcting device can be proofreaied and correct the control signal of first pressure regulator and the relation between the loine pressure.
In the case, when belt wheel does not rotate and driving torque effect thereon the time, between belt wheel and band slide relative does not take place.So the pressure adjusting operation that stops second pressure regulator can not cause problem.Thus, for example when shift pattern is parking spot, can learn the control signal load of first pressure regulator and the dependency relation between the loine pressure.
According to first aspect, correcting device can be according to coming correction relationship by the detected hydraulic pressure of detection device when the control signal that changes first correcting device.
In the case, make the dependency relation between the control signal of first pressure regulator load and the loine pressure consistent with the hydraulic pressure value that actual detected arrives.So, can determine the control load, so that under the situation of considering individual difference and deterioration in time, produce the loine pressure of expectation.
In addition, according to first aspect, correcting device can based on (i) when the described control signal to described first pressure regulator is changed by detected discretely discrete hydraulic pressure of described detection device and (ii) calculated value by obtaining from described discrete hydraulic pressure interpolation, proofread and correct described relation.
In the case, locate to detect the loine pressure relevant in a plurality of different detection times with the load of control signal.So, can use interpolation (for example linear interpolation) to calculate, and needn't in different detection times, use hydrostatic sensor detect the load of the control signal of first pressure regulator and the dependency relation between the loine pressure.
Description of drawings
When considering in conjunction with the accompanying drawings, by reading following detailed description, will understand above-mentioned aspect of the present invention and other forms, purpose, feature, advantage, technology and industrial significance better to exemplary embodiment of the present, in the accompanying drawing:
Fig. 1 is the control block diagram according to the automatic transmission that hydraulic control circuit was applied to of the embodiment of the invention;
Fig. 2 is the detail drawing of ECU shown in Figure 1;
Fig. 3 shows the hydraulic control circuit according to the embodiment of the invention;
Fig. 4 shows the flow chart by the control structure of the performed program of ECU of Fig. 1; With
Fig. 5 illustrates and how to learn and proofread and correct.
Embodiment
Below, explain embodiments of the invention with reference to the accompanying drawings.
Explain the power assembly comprise according to the vehicle of the hydraulic-pressure control apparatus of the embodiment of the invention with reference to Fig. 1.Be applied to the power assembly of Fig. 1 according to the hydraulic-pressure control apparatus of the embodiment of the invention, and implement by hydraulic control part 1100.Before the oil hydraulic circuit of explaining this hydraulic control part 1100, will introduce power assembly.
As shown in Figure 1, this power assembly comprise motor 100, torque-converters 200, the switching device 290 that advances-move backward, continuously variable belt transmission (CVT) 300, differential mechanism 800, electronic control unit (ECU) 1000 and hydraulic control part 1100.
The rotating output shaft of motor 100 is connected to the rotation input shaft of torque-converters 200.So motor 100 and torque-converters 200 couple together by running shaft.The input shaft revolution (pump revolution) of the output shaft revolution NE of motor 100 and torque-converters 200 is detected by unshowned engine rotation sensor.Suppose that under the said structure situation output shaft revolution NE is identical with the input shaft revolution.
Torque-converters 200 is by constituting with lower member: the lock-up clutch 210 that input shaft and output shaft is placed direct coupled condition; Pump impeller 220 on the input shaft side; Turbine 230 on the output shaft side; Overrunning clutch 250; With the stator 240 that is used to increase torque.Torque-converters 200 and CVT 300 couple together by running shaft.Output shaft revolution NT (turbine revolution NT) is detected by turbine revolution sensing 400.
CVT 300 is connected to torque-converters 200 via the switching device 290 that advances-move backward.CVT 300 is by the secondary pulley on the primary pulley on the input side 500, the outlet side 600 and be wrapped in primary pulley 500 and constitute with metal tape 700 on the secondary pulley 600.Primary pulley 500 is formed by the removable wheel disc that is fixed to the fixedly wheel disc on the elementary axle and be supported on slidably on the elementary axle.Secondary pulley 600 is formed by the removable wheel disc that is fixed to the fixedly wheel disc on the secondary axle and be supported on slidably on the secondary axle.The revolution NIN of the primary pulley of CVT 300 is detected by primary pulley tachometer generator 410, and the revolution NOUT of secondary pulley is detected by secondary pulley tachometer generator 420.
These tachometer generators 410 and 420 are arranged to face rotation and are detected the gear teeth of using gear, and the rotation detection is installed to the running shaft of primary pulley and secondary pulley with gear or is connected on the transmission shaft of these running shafts.Tachometer generator 410 and 420 can detect primary pulley and the secondary pulley on the output shaft even the small rotation on the input shaft of CVT 300. Tachometer generator 410 and 420 can use the magnetoresistive element that for example is known as semiconductor type sensor usually.
The switching device 290 that advances-move backward has twin-stage pinion type planetary pinion, reversing break B1 (using) and input clutch C1 when reversing.Planetary pinion has the sun gear that is connected to input shaft and supports the first small gear P1 and the second small gear P2 and be coupled to the fixedly planetary wheel carrier CR of wheel disc of primary side.In addition, planetary gear ring R is coupled to the reversing break B1 as the reversing friction engagement element, and input clutch C1 places between planetary wheel carrier CR and the gear ring R.Input clutch 310 (C1) is equivalent to forward clutch.In the switching device 290 that advances-move backward is in position except stop (P), reversing (R) and neutral gear (N), and vehicle is when moving forward, and input clutch 310 necessarily places engagement.
Below, the ECU 1000 and the hydraulic control part 1100 of element of control power assembly is described with reference to Fig. 2.
With reference to Fig. 2, ECU 1000 receives: the signal of (i) representing turbine revolution NT from turbine tachometer generator 400, (ii) from the signal of primary pulley tachometer generator 410 expression primary pulley revolution NIN with (iii) from the signal of secondary pulley speed probe 420 expression secondary pulley revolution NOUT.
As clearly visible from Fig. 1 and 2, hydraulic control part 1100 comprises velocity variations control section 1110, strap clamp compaction forces control section 1120, loine pressure control section 1122, locking engaging pressure control section 1130, clutch pressure control part 1140 and manually operated valve 1150.ECU 1000 outputs a control signal to the velocity variations control load coil (1) 1200 of (i) hydraulic control part 1100, (ii) velocity variations control load coil (2) 1210, (iii) strap clamp compaction forces control linearity coil (SLS) 1220, (iv) loine pressure control linearity coil (SLT) 1222, (v) locking coil 1230 and (vi) locking engaging pressure control load coil 1240.
Below, illustrate in greater detail the structure of ECU1000 of the element of control power assembly with reference to Fig. 2.As shown in Figure 2, ECU 1000 comprises the speed changer control computer 1020 that is used to control the engine control computer 1010 of motor 100 and is used to control CVT 300.
Except input signal shown in Figure 1, speed changer control computer 1020 also receives from parking lamp switch to represent whether the driver steps on the signal of brake petal and represent the signal at the angle of inclination of inclined route from the G sensor, receives back one signal when inclined route etc. is gone up when vehicle is parked in.In addition, engine control computer 1010 receives (i) represents the accelerator pedal aperture from the accelerator pedal jaw opening sensor signal, it is produced by driver's bend the throttle, (ii) represent the signal of electromagnetism throttle opening and (iii) represent the signal of the revolution (NE) of motor 100 from engine rotation sensor from throttle position sensor. Engine control computer 1010 and 1020 interconnection of speed changer control computer.
In hydraulic control part 1100, strap clamp compaction forces control section 1120 is based on the control signal that outputs to strap clamp compaction forces control linearity coil (SLS) 1220 from speed changer control computer 1020, control CVT 300 with 700 clamping pressure; And the engaging pressure of clutch pressure control part 1140 control input clutchs 310.
In addition, loine pressure control section 1122 in the hydraulic control part 1100 arrives the loine pressure of expectation based on the control signal that outputs to loine pressure control linearity coil (SLT) 1222 from speed changer control computer 1020 with the hydraulic control of oil pump 2020 outputs.
Fig. 3 shows the part of hydraulic control part 1100 shown in Figure 1.Below, oil hydraulic circuit will be described.This oil hydraulic circuit comprises the element according to the hydraulic-pressure control apparatus of the embodiment of the invention.
As shown in Figure 3, oil hydraulic circuit comprises food tray 2000, oil pump 2020, safety valve (pressure reduces valve) 2222, loine pressure control linearity coil (SLT) 1222, the safety valve (pressure reduces valve) 2220 that is used to reduce loine pressure, clamping pressure control linearity coil (SLS) 1220, three-way valve 2040 and hydrostatic sensor 2030.The hydraulic oil that oil pump 2020 outputs drink up from food tray 2000 via filter 2010.Safety valve (pressure reduces valve) 2222 reduces the hydraulic pressure by oil pump 2020 outputs.Three-way valve 2040 is connected to the primary pulley hydraulic chamber and the oil drain passage (these elements clearly do not illustrate) of driving side.Hydrostatic sensor 2030 detects the hydraulic pressure value of the hydraulic oil that is fed to slave end secondary pulley hydraulic chamber (clearly not illustrating).Loine pressure control linearity coil (SLT) 1222 control safety valves (pressure reduces valve) 2222 make the loine pressure that obtains to expect based on from the control signal of speed changer control computer 1020.First pressure regulator is made of for example loine pressure control linearity coil 1222 and safety valve 2222.In addition, clamping pressure control linearity coil (SLS) 1220 control safety valves (pressure reduces valve) 2222 make based on the strap clamp compaction forces that obtains expectation from the control signal of speed changer control computer 1020.Second pressure regulator for example is made of clamping force control linearity coil 1220 and safety valve (pressure reduces valve) 2220.In addition, detection device is made of for example hydrostatic sensor 2030.Note, in the embodiment shown in fig. 3, delivery pressure or loine pressure that hydrostatic sensor detects oil pump 2020 are not set.
Three-way valve 2040 uses with velocity variations control load coil (1) 1200 corresponding speed and increases lateral coil 2042 and reduce lateral coil 2044 with velocity variations control load coil (2) 1210 corresponding speed, with connect and notconnect state between switch loine pressure supply port, discharge port 2046 and being connected to the output port of primary pulley hydraulic chamber.
When speed increased lateral coil 2042 connections, loine pressure and primary pulley hydraulic chamber were connected, and loine pressure is fed to the primary pulley hydraulic chamber.Perhaps, when speed reduced lateral coil 2044 connections, primary pulley hydraulic chamber and discharge port 2046 were connected, and hydraulic oil is discharged from the primary pulley hydraulic chamber.
Fig. 4 shows the flow chart according to the control structure of the performed program of the speed changer control computer 1020 of this embodiment's ECU 1000.
In step 100, speed changer control computer 1020 judges whether oil pump delivery pressure study sign is ON (connection).When (a) driving side belt wheel and slave end belt wheel are in off working state, and (b) when driving torque does not act on the belt wheel, this sign is set to ON.For example, if the shift pattern of vehicle is a parking spot, and learnt processing since last time and passed through predetermined amount of time, then oil pump delivery pressure study sign is set to ON.If the study of oil pump delivery pressure is masked as ON (being "Yes" among the step S100), then handles and proceed to step S110.On the other hand, if the study of oil pump delivery pressure is masked as OFF (disconnection) (step S100 is a "No"), then handle stopping.
In step S110, speed changer control computer 1020 output hydraulic pressure bid value P (OUT) (=P (L)+α: α be on the occasion of) control linearity coil (SLS) 1220 to clamping pressure.At this moment, for example when bid value was output as current value, current value 0 was output as the hydraulic pressure bid value.
In step S120, the hydraulic pressure bid value of the linear coils of speed changer control computer 1020 output pipe pressure control (SLT) 1222, make the hydraulic pressure bid value from than the low value alternation to high value.For example, can carry out this moment from 0 ampere to 1.0 amperes alternation.In step S130, speed changer control computer 1020 detects the hydraulic pressure value P (L) of the loine pressure that is detected by hydrostatic sensor 2030.At this moment, (=P (L)+α) has been output to clamping pressure control linearity coil (SLS) 1220 to hydraulic pressure bid value P (OUT), and safety valve does not reduce carrying out pressure.So the hydraulic pressure that is detected by hydrostatic sensor 2030 is the hydraulic pressure value P (L) of loine pressure.
In step S140, speed changer control computer 1020 is stored the loine pressure P (L) as detected hydraulic pressure value in its storage.Notice that in order to reduce data volume, loine pressure P (L) can be stored as discrete data.When the discrete data of loine pressure P (L) was stored, serial relation therebetween can use interpolation (for example linear interpolation) to calculate.
In step S150, speed changer control computer 1020 relatively (i) is stored in figure (the control current value of loine pressure control linearity coil (SLT) 1222 and the relation between the detected loine pressure P (L) are shown) in the storage and the loine pressure P (L) that (ii) stores in step S140.Speed changer control computer 1020 judges then whether this figure needs to be corrected.If be stored in loine pressure P (L) in the storage and very big by the deviation between the hydrostatic sensor 2030 detected loine pressure values, then to proofread and correct be necessary (promptly being "Yes" in step S150) to judgement figure, and handle and proceed to step S160.On the other hand, if figure proofreaies and correct unnecessary (being "No") in step S150, termination under the situation of correction chart not then.
In step S160, the control current value of loine pressure control linearity coil (SLT) 1222 and the figure of the relation between the detected loine pressure P (L) have been stipulated in 1020 corrections of speed changer control computer.
Below, will illustrate that the figure that carries out learns operation in comprising according to the vehicle of hydraulic-pressure control apparatus of the present invention based on said structure and flow chart.
When vehicle is travelling, and shift pattern is when being changed to parking spot, indicates through predetermined amount of time gear pump output study and is being set to ON handling since study last time.So judged result is a "Yes" among the step S100, and hydraulic pressure bid value P (OUT) (=P (L)+α) is output to clamping pressure control linearity coil (SLS) 1220.In other words, control signal is output to clamping pressure control linearity coil (SLS) 1220, so that the hydraulic pressure (in step S110) that hydraulic pressure becomes and is higher than loine pressure P (L).At this moment, clamping pressure control linearity coil (SLS) 1220 does not start the hydraulic pressure that safety valve (pressure reduces valve) 2220 reduces to be supplied.
The hydraulic pressure bid value of loine pressure control linearity coil (SLT) 1222 is output then, with from 0 ampere of alternation to 1.0 ampere.At this moment, be loine pressure P (L) (in step S130) by hydrostatic sensor 2030 detected hydraulic pressure values.Detected loine pressure P (L) is stored in (in step S140) in the storage.Then, if stipulated to have very large deviation between loine pressure P (L) figure of nearest detected loine pressure P (L) figure of relation between the control current value of loine pressure control coil (SLT) 1222 and the institute's signal piping pressure P (L) and current storage, then to proofread and correct be necessary (promptly being "Yes" in step S150) to judgement figure.So, stipulated that the figure of relation between the control current value of loine pressure control coil (SLT) 1222 and the institute's signal piping pressure P (L) is corrected.In this time, as shown in Figure 5, detected loine pressure P (L) compares bigger in some cases with the loine pressure of storage in advance, and less in other cases.In either case, the loine pressure figure of storage changes to the nearest figure of relation between control current value that loine pressure control linearity coil (SLT) 1222 is shown and the loine pressure P (L) in advance.
Use the figure after proofreading and correct, can accurately calculate the control current value of pipeline pressure control line coil (SLT) 1222, this value is that the required loine pressure of the velocity variations control of generation CVT 300 is desired.Traditionally, if cause the variation of figure, then exist the delivery pressure that improves oil pump to increase loine pressure to guarantee the trend of required loine pressure by individual difference and deterioration in time.The result who does like this causes the oil pump loss exactly.But, utilize hydraulic-pressure control apparatus according to present embodiment, learning and proofreading and correct provides figure accurately.So, the moving loss of pump of oil pump can not take place.In addition, when the inoperation of clamping pressure control linearity coil (SLS), use the hydrostatic sensor that detects clamping pressure to carry out learning control.So, can be in the hydraulic control circuit that comprises two linear electromagnetic valve systems relation between learning control load and the hydraulic pressure value, and need not to increase the quantity of hydrostatic sensor, or in other words can not cause cost to improve.
Though the present invention has been described, has been to be understood that to the invention is not restricted to this exemplary embodiment or structure with reference to exemplary embodiment of the present invention.On the contrary, this invention is intended to cover various modifications and equivalent arrangement.In addition, though show the various elements of exemplary embodiment, comprise other combinations more, still less or only discrete component and structure also within the spirit and scope of the present invention with exemplary various combinations and structure.
Claims (7)
1. hydraulic-pressure control apparatus that is used for continuously variable belt transmission comprises:
Filter, hydraulic oil is fed to oil pump from food tray through described filter;
Be used for will be from the hydraulic regulation of described oil pump output to loine pressure first pressure regulator;
Be used for described loine pressure is adjusted to second pressure regulator of the tight hydraulic pressure of strap clamp;
Be used to detect the detection device of the tight hydraulic pressure of regulating by described second pressure regulator of described strap clamp;
Be used for storing in advance storage device to the control signal and the relation between the described loine pressure of described first pressure regulator; With
Correcting device, described correcting device reduces to operate under the situation of not carrying out at the pressure of described second pressure regulator, based on when the described control signal to described first pressure regulator is changed by the detected hydraulic pressure of described detection device, proofread and correct the described control signal of described first pressure regulator and the described relation between the described loine pressure.
2. hydraulic-pressure control apparatus as claimed in claim 1, wherein
Described loine pressure is supplied to the hydraulic chamber of the driving side belt wheel of described stepless speed variator via switching valve; And
The tight hydraulic pressure of described strap clamp is supplied to the hydraulic chamber of the slave end belt wheel of described stepless speed variator.
3. hydraulic-pressure control apparatus as claimed in claim 1, wherein
At the driving side belt wheel of described stepless speed variator with the slave end belt wheel does not rotate and driving torque does not act under the situation on described driving side belt wheel and the described slave end belt wheel, described correcting device is under the described pressure that is undertaken by described second pressure regulator reduces to operate situation when not carrying out, based on when the described control signal to described first pressure regulator is changed by the detected described hydraulic pressure of described detection device, proofread and correct described relation.
4. hydraulic-pressure control apparatus as claimed in claim 1, wherein
The described relation that described correction is stored in advance by described storage device, with and when the described control signal that changes described first pressure regulator detected described hydraulic pressure of described detection device and to the relationship consistency between the described control signal of described first pressure regulator.
5. hydraulic-pressure control apparatus as claimed in claim 1, wherein
Existed under the situation of deviation between detected described hydraulic pressure and the relation to the described control signal of described first pressure regulator by described detection device in described relation that described storage device is stored with when the described control signal to described first pressure regulator is changed, described correcting device is with the described relation that replaces described storage device to store by the relation of detected described hydraulic pressure of described detection device and described control signal when the described control signal to described first pressure regulator is changed.
6. hydraulic-pressure control apparatus as claimed in claim 1, wherein
Described correcting device is proofreaied and correct described relation based on discrete hydraulic pressure with by the calculated value that obtains from described discrete hydraulic pressure interpolation, and wherein said discrete hydraulic pressure is detected discretely by described detection device when the described control signal to described first pressure regulator is changed.
7. hydraulic control method that is used for continuously variable belt transmission may further comprise the steps:
Change the loine pressure that the hydraulic control signal output to first pressure regulator is regulated the oil circuit of described stepless speed variator, the hydraulic regulation that described first pressure regulator is used for exporting from oil pump is to described loine pressure, and hydraulic oil is fed to described oil pump from food tray through filter;
Stop the operation that second pressure regulator is reduced to the loine pressure of oil circuit the tight hydraulic pressure of strap clamp;
The tight hydraulic pressure of described strap clamp that detection is regulated by described second pressure regulator; With
Under the situation when the described operation of described second pressure regulator is stopped, based on the tight hydraulic pressure of detected described strap clamp when the described hydraulic control signal to described first pressure regulator is changed, proofread and correct the described hydraulic control signal of described first pressure regulator and the relation of storage in advance between the described loine pressure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100723976A CN100476248C (en) | 2005-05-31 | 2005-05-31 | Hydraulic controller for belt driving stepless speed variator and control method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100723976A CN100476248C (en) | 2005-05-31 | 2005-05-31 | Hydraulic controller for belt driving stepless speed variator and control method thereof |
Publications (2)
| Publication Number | Publication Date |
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| CN1873258A CN1873258A (en) | 2006-12-06 |
| CN100476248C true CN100476248C (en) | 2009-04-08 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2005100723976A Expired - Fee Related CN100476248C (en) | 2005-05-31 | 2005-05-31 | Hydraulic controller for belt driving stepless speed variator and control method thereof |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4715817B2 (en) * | 2007-07-18 | 2011-07-06 | トヨタ自動車株式会社 | Shift control device for automatic transmission for vehicle |
| JP4380768B2 (en) * | 2007-12-27 | 2009-12-09 | トヨタ自動車株式会社 | Hydraulic control device for continuously variable transmission |
| MX2012009094A (en) * | 2010-03-09 | 2012-09-07 | Nissan Motor | Automatic transmission and hydraulic oil control method therefor. |
| JP2019120308A (en) * | 2017-12-28 | 2019-07-22 | 日産自動車株式会社 | Control method for power transmission device and control device for power transmission device |
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