CN101089428A - Device and method of controlling a belt-type continuously variable transmission - Google Patents
Device and method of controlling a belt-type continuously variable transmission Download PDFInfo
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- CN101089428A CN101089428A CN 200710106723 CN200710106723A CN101089428A CN 101089428 A CN101089428 A CN 101089428A CN 200710106723 CN200710106723 CN 200710106723 CN 200710106723 A CN200710106723 A CN 200710106723A CN 101089428 A CN101089428 A CN 101089428A
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Abstract
The line oil pressure P L that is a basic pressure of a needed Pin pressure and a Pd pressure is set by line oil pressure setting means (160) on the basis of the higher oil pressure of the oil pressure values obtained by adding reference margin values EX to the needed Pin pressure and the to Pd pressure. Therefore, a requirement minimum line oil pressure P L with respect to the needed Pin pressure needed for shifting and the Pd pressure needed for the belt clamping pressure is appropriately set so that good shifting performance and good belt clamping pressure are secured.
Description
Technical field
[0001] the present invention relates to the control gear and the controlling method of variable v-belt drive, described variable v-belt drive has the belt wheel and the right driving belt of described belt wheel of reeling that a pair of effective diameter is changed by oil hydraulic cylinder.Especially, the present invention relates to setting to the basic pressure of the oil pressure in the oil hydraulic cylinder of described variable v-belt drive.
Background technique
[0002] have the control gear of the variable v-belt drive that effective diameter combines by the driving belt of the oil hydraulic cylinder a pair of belt wheel that changes and described two belt wheels of reeling, the basic pressure of suitably setting the interior oil pressure of oil hydraulic cylinder is known.
[0003] present technique example is that publication number is the hydraulic control device of the described hydraulic operation speed changer of Japanese patent application (hereinafter being called JP-A-6-109114) of JP-A-6-109114.JP-A-6-109114 has described a kind of stepless speed variator with band of these two belt wheels of primary pulley, secondary pulley and coiling.In described stepless speed variator, the gear ratio of control by described primary pulley and the strap clamp compaction forces by described secondary pulley, thereby be with and two belt wheels between do not slide.In conjunction with described stepless speed variator, JP-A-6-109114 has described based on Engine torque and gear ratio, prevent to improve simultaneously with slip the hydraulic control device of fuel economy reliably by setting pipeline (line) pressure, described pipeline pressure is the basic pressure of the oil pressure (hereinafter referred to as " elementary oil pressure ") in the primary pulley grease chamber and the basic pressure of the oil pressure in the secondary pulley grease chamber (hereinafter referred to as " secondary oil pressure ").
[0004] in the hydraulic control device that JP-A-6-109114 describes, constructed an oil hydraulic circuit, so that directly described pipeline pressure is incorporated into the secondary pulley grease chamber, and in fact described pipeline pressure is controlled to be identical pressure with secondary oil pressure.Therefore, though guaranteed the pipeline pressure that secondary oil pressure is required, when described pipeline pressure is lower than required secondary oil pressure, gear shift response (shit response) possible deviation.That is to say that described pipeline pressure is not merely by secondary oil pressure, promptly the strap clamp compaction forces determines, but need be set so that guarantee good shift property (shifting performance) and good strap clamp compaction forces.
[0005] so far, can construct an oil hydraulic circuit, so that described pipeline pressure is controlled separately, and irrelevant with described elementary oil pressure or secondary oil pressure.Yet, for controlling individually under the situation of described pipeline pressure, how to set pipeline pressure and guarantee good shift property and good strap clamp compaction forces, also do not advise.
Summary of the invention
[0006] the invention provides a kind of control gear that is used for variable v-belt drive, it guarantees good shift property and good strap clamp compaction forces by correctly setting the basic pressure of oil pressure in the oil hydraulic cylinder.
[0007] first aspect of the present invention relates to the control gear that is used for variable v-belt drive.In the vehicle of the stepless speed variator on being equipped with the power transmission path that is arranged between vehicle power source and the driving wheel, described stepless speed variator has the band of described two belt wheels of primary pulley, secondary pulley and coiling, the described control gear that is used for variable v-belt drive comprises the primary hydraulic pressure cylinder of the groove width of adjusting primary pulley and adjusts the secondary oil hydraulic cylinder of the groove width of secondary pulley, and control the strap clamp compaction forces by primary pulley oil hydraulic cylinder control gear ratio with by the secondary pulley oil hydraulic cylinder, so that between described band and two belt wheels, do not slide.Described control gear comprises basic pressure setting device, and it is set in the primary pulley oil hydraulic cylinder and the basic oil pressure in the secondary pulley oil hydraulic cylinder based on the higher oil pressure in the oil pressure in oil pressure in the primary pulley oil hydraulic cylinder or the secondary pulley oil hydraulic cylinder.
[0008] because described structure based on the higher person of the oil pressure in primary hydraulic pressure cylinder or secondary oil hydraulic cylinder, is set the basic oil pressure that device is set in primary hydraulic pressure cylinder and secondary oil hydraulic cylinder by basic pressure.Therefore, about the oil pressure in the primary hydraulic pressure cylinder, i.e. the pressure that gear shift needs, with the oil pressure in the secondary oil hydraulic cylinder, be the required pressure of strap clamp compaction forces, suitably set the minimum basic pressure that needs, thereby guarantee good gear shift function and good strap clamp compaction forces.
[0009] described basic pressure is set device and can be set basic pressure based on the higher person of oil pressure, and described oil pressure will be by being scheduled to enough and to spare value (margin value) and adding oil pressure in the primary pulley oil hydraulic cylinder respectively to and the oil pressure of secondary pulley oil hydraulic cylinder obtaining.Because described structure, the control accuracy that comprises actual basic pressure and the suitable basic pressure of vehicle-state have been set.
[0010] may differ from one another for oil pressure in the primary hydraulic pressure cylinder and the predetermined enough and to spare value set for the oil pressure in secondary oil hydraulic cylinder.With described structure, the enough and to spare value of setting has comprised in the primary hydraulic pressure cylinder and the difference between the control mode of oil pressure in the secondary oil hydraulic cylinder, and therefore sets suitable basic pressure.For example, when the oil pressure in the direct control oil hydraulic cylinder, only need comprise the residual quantity (dispersion) of actual pipeline pressure, and therefore set relatively little enough and to spare value with respect to the basic pressure of setting.Selectively, when oil pressure in the oil hydraulic cylinder is not directly control but estimated value, be necessary to comprise the error of estimated value etc., so that set big relatively enough and to spare value.
[0011] when setting with respect to basic pressure for the basic pressure that device sets, when the control accuracy of actual basic pressure descends, can set described predetermined enough and to spare value greater than the enough and to spare value when described control accuracy is high.Because described structure is even when the control accuracy of actual basic pressure descends, also can set suitable basic pressure.Because when the temperature of working oil (working oil) is low, the viscosity height of described working oil, control accuracy when being lower than the usually oil temperature so the control accuracy of actual basic pressure becomes.Therefore, because predetermined enough and to spare value is set to when working oil temperature is low greater than the enough and to spare value when normal oil is warm, so even when the control accuracy of actual basic pressure descends, also can set suitable basic pressure.In addition, even when the viscosity of working oil is low, such as when oily warm when high, the control accuracy of described actual basic pressure also may descend in some cases.Under these circumstances, because predetermined enough and to spare value is set up when working oil temperature is high greater than the enough and to spare value when normal oil is warm, so even when the control accuracy of actual basic pressure descends, also can set suitable basic pressure.
Described predetermined enough and to spare value when [0012] needing unexpected gear shift in vehicle driving can be set greater than in vehicle is normally stable when travelling predetermined enough and to spare value.Because described structure is even in gear shift suddenly, also can set suitable basic pressure.
[0013] can be set in the predetermined enough and to spare value when sharply not changing of belt transmission torque in the vehicle driving less than the predetermined enough and to spare value of normally stablizing at vehicle in the running process.Because described structure, when belt transmission torque in the vehicle driving does not sharply change, that is to say, not sharply do not quicken or slow down need the time, can therefore reduce predetermined enough and to spare value, for example, in carrying out the process that Ruiss Controll (cruise control) waits, set described basic pressure and be lower than the basic pressure of normally stablizing when travelling.Thereby, further improve fuel economy.
[0014] described control gear may further include the elementary oil pressure estimator spare that is used to estimate the oil pressure in the primary pulley oil hydraulic cylinder, if wherein estimate accurately to estimate described oil pressure that by described elementary oil pressure then described basic pressure is set device and set described basic pressure based on the oil pressure in described secondary oil hydraulic cylinder.Because described structure, in the time can not accurately estimating necessary Pin pressure, for example, when turn-sensitive device breaks down, at lower category such as firing an engine (power-on downshift), close throttle and upgrade in the transfer process of unexpected gear shift of (power-off upshift) etc., perhaps in hand shift, only set suitable basic pressure, thereby the variation of gear shift responsiveness is minimized based on the oil pressure in the secondary oil hydraulic cylinder.
[0015] in unexpected gearshift procedure, described basic pressure is set device and is set described basic pressure based on the oil pressure in secondary oil hydraulic cylinder.Because described structure,, also can set suitable basic pressure even in lower category, close the unexpected gearshift procedure that throttle upgrades etc. such as firing an engine, promptly can not accurately estimate in the process of the oil pressure in the primary hydraulic pressure cylinder.
[0016] based on the safe load of band, described basic pressure is set device can set the CLV ceiling limit value of basic pressure, and can set basic pressure and be less than or equal to described CLV ceiling limit value.
[0017] second aspect of the present invention relates to the controlling method of variable v-belt drive.In the vehicle of the stepless speed variator on being equipped with the power transmission path that is arranged between vehicle power source and the driving wheel, described stepless speed variator has the band of described two belt wheels of primary pulley, secondary pulley and coiling, described controlling method is used for variable v-belt drive, described stepless speed variator comprises the primary pulley oil hydraulic cylinder of the groove width that is used to change primary pulley and is used to change the secondary pulley oil hydraulic cylinder of the groove width of secondary pulley.Described controlling method is by primary hydraulic pressure cylinder control gear ratio with by secondary oil hydraulic cylinder control strap clamp compaction forces, so that do not slide between described band and two belt wheels.Described controlling method relates to based on the higher oil pressure in the oil pressure in oil pressure in the primary hydraulic pressure cylinder or the secondary oil hydraulic cylinder, is set in the primary hydraulic pressure cylinder and the basic oil pressure in the secondary pulley oil hydraulic cylinder.
[0018] the common gear shift control of stepless speed variator can be adopted various control modes, for example, this mode: by supplying with and discharge the groove width that changes described primary pulley about the working oil of primary pulley oil hydraulic cylinder, in this mode, the target change gear ratio that obtains is according to predetermined shift condition, and gear ratio is a feedback control, thereby actual gear ratio reaches described target change gear ratio; This mode: by supplying with and discharge the groove width that changes primary pulley about the working oil of primary pulley oil hydraulic cylinder, the rotating speed of target of the input side that obtains (driving source) is according to the speed of a motor vehicle, output speed (rotating speed of driven wheel side) etc., and gear ratio is a feedback control, thereby actual input speed reaches the target input speed.
[0019] by for example using figure, travel condition of vehicle as the CALCULATION OF PARAMETERS representation etc., set above-mentioned predetermined shift condition, above-mentioned travel condition of vehicle comprises the output quantity (acceleration amount of needs) of driver's needs, as accelerator operation amount etc., speed of a motor vehicle (corresponding to output speed) etc.
[0020], is extensive use of internal-combustion engine such as petrol engine, diesel engine etc. as vehicle power source.Except above-mentioned motor, motor etc. can be used as the service vehicle power source.And also allow only to use motor as vehicle power source.
Description of drawings
[0021] from the description below in conjunction with the embodiment of accompanying drawing, above-mentioned and other purpose of the present invention, feature and advantage will become obvious.Wherein identical numeral is used to represent identical parts, wherein:
Fig. 1 is the figure that shows according to the vehicle drive unit of first embodiment of the invention;
Fig. 2 shows the block diagram that is arranged on the control system part that is used to control vehicle drive unit shown in Figure 1 in the vehicle etc.;
Fig. 3 shows with the control of the strap clamp compaction forces of stepless speed variator, gear ratio control and is used for the forward clutch relevant with the shift level operation or retreats the relevant hydraulic control circuit hydraulic circuit diagram partly of engagement oil pressure control of break;
Fig. 4 shows the figure that is used for obtaining in the legend of the target input speed of the gear shift control of stepless speed variator;
Fig. 5 shows that the strap clamp that obtains the strap clamp compaction forces according to the gear ratio in the control of the clamping pressure of stepless speed variator etc. presses the figure of the example of trying hard to;
Fig. 6 is the functional block diagram that shows the control funtion part of electric control device shown in Figure 2;
Fig. 7 is the figure that shows the example of the principle that the pipeline oil pressure is set;
Fig. 8 shows that with the throttle valve open degree be parameter, and the figure (engine torque map) of the example of relation is determined in the experiment that prestores between the Engine torque of engine speed and estimation;
Fig. 9 shows in execution Ruiss Controll process to reach the figure that reduces subsequently with reference to the example of enough and to spare value in not carrying out the Ruiss Controll process;
Figure 10 is the flow chart that shows the control operation part of electric control device shown in Figure 2, that is to say, shows the control operation that the pipeline oil pressure suitably is set on the basis of necessary Pin pressure and Pd pressure;
Figure 11 shows in the time can not accurately estimating necessary Pin pressure, and the figure of example of the principle of pipeline oil pressure is set;
Figure 12 shows according to second embodiment, the functional block diagram of the control funtion part of electric control device shown in Figure 2; With
Figure 13 shows that according to second embodiment flow chart of the control operation of electric control device shown in Figure 2 part that is to say, shows the control operation that the pipeline oil pressure suitably is set.
Embodiment
[0022] hereinafter, will describe embodiments of the invention in conjunction with the accompanying drawings in detail.
[0023] Fig. 1 is the figure that shows according to the structure of the vehicle drive unit 10 of first embodiment of the invention.Described vehicle drive unit 10 is the horizontal mount type automatic transimissions that are suitable for use in FF (front engine, front-wheel drive) the type vehicle, and has the motor 12 as vehicle power source.The output of the motor 12 that constitutes by internal-combustion engine from the crankshaft of motor 12 through torque converter 14 (being the fluid type transmission device), forward/backward conversion equipment 16, variable v-belt drive (CVT) 18 and deceleration shifting device 20, be transferred to differential gearing 22, be distributed to a left side and right driving wheel 24L, 24R then.
[0024] described torque converter 14 comprises the fuel pump impeller 14p of the bent axle that is connected to described motor 12, with be connected to turbine pump impeller (turbine impeller) 14t of described forward/backward conversion equipment 16 via turbine shaft 34 corresponding to the outlet side parts of described torque converter 14, and be designed to by liquid transfer power.Between the fuel pump impeller 14p of described torque converter 14 and turbine pump impeller 14t, be provided with lock-up clutch 26.According to supplying with oil pressure to the engagement grease chamber with discharge the grease chamber, mesh or discharge described lock-up clutch 26, this is by being arranged on conversion such as locking control valve (L/C control valve) in the hydraulic control circuit 100 (referring to Fig. 2 and Fig. 3) (not shown go out).When meshing described lock-up clutch 26 fully, described fuel pump impeller 14p and turbine pump impeller 14t are as the whole rotation of parts.Mechanical oil pump 28 is connected to fuel pump impeller 14p.Because described oil pump 28 is driven by motor 12 rotations, described oil pump 28 generates oil pressure to carry out the gear shift control of stepless speed variator 18, or produce described strap clamp compaction forces, or carry out the engagement/release control of described lock-up clutch 26, or lubricant oil is supplied to various piece.
[0025] described forward/backward conversion equipment 16 mainly is made of double-pinion type planetary pinion device.The turbine shaft 34 of described torque converter 14 is connected to sun gear 16s by integral body, and the input shaft 36 of described stepless speed variator 18 is connected to planetary carrier (carrier) 16c by integral body.Described planetary carrier 16c and sun gear 16s selectively are connected to each other via forward clutch C1.By retreating break B1 ring gear 16r selectively is fixed to shell.Described forward clutch C1 with retreat break B1 corresponding to being connected/cut off, and each is the hydraulic friction engagement device that realizes friction engagement by oil hydraulic cylinder.
[0026] when the clutch C1 that advances is engaged and retreats break B1 and is released, the described forward/backward conversion equipment 16 that travels rotates as parts, that is to say, described turbine shaft 34 is directly connected to the input shaft 36 of stepless speed variator 18.Therefore, be provided with (having obtained) onward impulse drive path, so will be transferred to described stepless speed variator 18 sides in the driving force of direction of advance.When engagement retreats service brake B1 and discharges forward clutch C1, in described forward/backward conversion equipment 16, be provided with (having obtained) and retreat power transmission path, that is to say that the input shaft 36 of stepless speed variator 18 rotates on the direction opposite with the sense of rotation of described turbine shaft 34.Therefore, the driving force with direction of retreat is transferred to described stepless speed variator 18.In addition, when advancing clutch C1 and when retreating break B1 and all being released, described forward/backward conversion equipment 16 presents neutral gear (neutral) state (off state) that does not transmit power.
[0027] described stepless speed variator 18 comprises input variable pulley (primary pulley) 42, and its input block and its effective diameter that is arranged on the input shaft 36 is variable; Output variable pulley (secondary pulley) 46, it is arranged on the output block on the output shaft 44; With rotating band 48, its described two variable pulleys 42,46 of reeling.Power transmits by the friction between described variable pulley 42,46 and the rotating band 48.
[0028] described variable belt wheel 42 and 46 each by the fixed rotor 42a, the 46a that are fixed in corresponding input shaft 36 and the output shaft 44, being provided for can not be around described input shaft 36 or described output shaft 44 rotation and removable rotor 42b, the 46b that can not move on the axial direction that inputs or outputs axle relatively, and is provided for applied thrust with the width that changes the v-depression between fixing and the removable rotor, corresponding to input hydraulic cylinder (primary hydraulic pressure cylinder) 42c with export a structure among oil hydraulic cylinder (secondary oil hydraulic cylinder) 46c.Because the supply/emission flow of the working oil of input hydraulic cylinder 42c by hydraulic control circuit 100 controls, changes the belt wheel contact diameter (effective diameter) of described rotating band 48, the wide change of V-shaped groove of described two variable pulleys 42,46.Therefore, described change gear (=input shaft rotating speed N
IN/ output shaft rotational speed N
OUT) continuously change.In addition, by pressure-adjusting control that 100 pairs of described hydraulic control circuits are exported the oil pressure (strap clamp compaction forces Pd) of oil hydraulic cylinder 64c, can control described strap clamp compaction forces, thereby described rotating band 48 does not slide.As the result of these controls, produce the oil pressure (gear shift pilot pressure Pin) of described input hydraulic cylinder 42c.
[0029] Fig. 2 shows the block diagram that is arranged on the control system part that is used to control vehicle drive unit shown in Figure 1 10 in the vehicle etc.Described electric control device 50 comprises for example, having the so-called microcomputer of CPU, RAM, ROM and input/output interface etc.CPU carries out signal processing according to the program that is pre-stored among the ROM, uses the interim memory function of RAM to carry out the Maximum Torque control etc. of the output control of described motor 12, the gear shift control of described stepless speed variator 18, the control of described strap clamp compaction forces, described lock-up clutch 26 simultaneously.Described electric control device 50 be can construct as required separately, the hydraulic control of engine control, stepless speed variator 18 and lock-up clutch 26 etc. are used for.
[0030] described electric control device 50 provides the signal of expression speed of crankshaft, crank angle (position) A that described speed of crankshaft detects corresponding to engine rotation speed sensor 52
CR(°), and corresponding to rotating speed (engine speed) N of motor 12
EExpression is by rotating speed (secondary speed) N of the turbine shaft 34 of turbine speed sensor 54 detections
TSignal; Rotating speed (input shaft rotating speed) N of expression input shaft 36
INSignal, described rotating speed is the input speed of the stepless speed variator 18 that detected by transfer input shaft speed sensors 56; Expression is corresponding to rotating speed (output shaft rotating speed) N of output shaft 44
OUTThe vehicle speed signal of vehicle velocity V, that is, and the output shaft rotational speed N
OUT, it is the output speed by the stepless speed variator 18 of vehicle speed sensor (OSS) 58 detections; The throttle valve open degree θ of the electronic throttle 30 that the suction tude that is arranged on motor 12 32 (referring to Fig. 1) that expression is detected by throttle valve sensor 60 is interior
THThrottle valve open degree signal; Expression is by the cooling water temperature T of the motor 12 of cooling-water temperature sensor 62 detections
WSignal; Expression is by the oily temperature T of the oil hydraulic circuit of stepless speed variator 18 grades of CVT oil temperature sensor 64 detections
CVTSignal; Expression accelerator operation amount A
CCThe accelerator operation amount signal, that is, and the operation amount of the accelerator pedal 68 that detects by accelerator operation amount sensor 66; The pedal brake that expression is detected by pedal brake switch 70, that is, and the operation B of driving pedal brake
ONExistence/non-existent brake service signal; Expression is by bar position (operating position) P of the shift level 74 of bar position transducer 72 detections
SHThe operating position signal, etc.
[0031] 50 outputs of described electric control device are used to control the output engine control command signal S of the output of motor 12
EFor example, be used to drive the throttle valve signal of throttle valve actuator 76 with the On/Off of control electronic throttle 30, be used to control fire signal from the amount of fuel of fuel injection apparatus 78 injections, be used to control the ignition timing signal of the ignition timing of the motor of carrying out by ignition mechanism 80 12, etc.In addition, described electric control device 50 output command signals to the computer 82 of Ruiss Controll purposes to carry out the so-called Ruiss Controll of automatic control vehicle velocity V, so that reach the target vehicle speed V that the driver sets
*In addition, the various signals of described electric control device 50 outputs are to hydraulic control circuit 100, and these signals comprise: the gear shift control command signal S that is used to change the change gear of stepless speed variator 18
T, for example, be used for drive controlling to the solenoid valve DS1 of the working oil flow of input hydraulic cylinder 42c and the command signal of solenoid valve DS2; Be used to regulate the clamping pressure control command signal S of the clamping pressure of rotating band 48
B, for example, be used to drive the command signal of the linear solenoid valve SLS of adjusting belt clamping pressure Pd, be used for controlling plumbing fixtures oil pressure P
LPipeline oil pressure control command signal S
PL, for example, be used for driving adjusting pipeline oil pressure P
LThe command signal of linear solenoid valve SLT; Deng.
[0032] for example, described shift level 74 is arranged near the driver's seat, but and is designed to arbitrary position of manually-operable in five bar positions " P " that order is provided with, " R ", " N ", " D " and " L " (see figure 3).
[0033] described " P " position (scope) is a parking spot, the power transmission path that is used for unlocking vehicle drive unit 10, that is to say, be used for producing neutral state, and be used for mechanically stopping the rotation of (locking) output shaft 44 by the mechanical parking device with the power transmission disconnection of vehicle drive unit 10.Described " R " position is to retreat the mobile position, is used for the sense of rotation of the output shaft 44 of vehicle drive unit 10 is set to reverse directions.Described " N " position is a neutral position, is used for being created in vehicle drive unit 10 powerdriven neutral state does not take place.Described " D " position is the mobile position of advancing, and is used for carrying out Automatic Shift Control by set up automatic shift mode in the shift range that allows stepless speed variator 18 gear shift.Described " L " position is the engine braking position, is used to cause strong engine braking effect.Therefore, described " P " position and right and wrong mobile position, " N " position, it is selected when vehicle is not mobile.On the other hand, described " R " position, " D " position and " L " position are the vehicle mobile positions, and it is selected when vehicle moves.
[0034] Fig. 3 is the hydraulic circuit diagram that shows with the control of the strap clamp compaction forces of stepless speed variator 18, gear ratio control and the forward clutch C1 relevant with the operation of shift level 74 or retreat the part of the hydraulic control circuit 100 that the engagement oil pressure control of break B1 is correlated with.In Fig. 3, described hydraulic control circuit 100 comprises the clamping pressure control valve 110 of the strap clamp compaction forces Pd of the oil pressure of regulating output oil hydraulic cylinder 46c, thereby described rotating band 48 does not slide; Gear ratio control valve UP114 and gear ratio control valve DN116, it controls to the working oil flow of input hydraulic cylinder 42c, thereby changes described change gear continuously; Thrust is than control valve 118, and it is set to predetermined relationship with the ratio between gear shift pilot pressure Pin and the strap clamp compaction forces Pd; With manually operated valve 120, oil pipe (oil passageway) is according to the conversion of shift level 74 with operating machine therein, thus engagement or discharge described forward clutch C1 and retreat break B1.
[0035] passes through release type (relieftype) primary regulator valve (pipeline oil pressure adjusting valve) 122 with described pipeline oil pressure P
LBe adjusted to and corresponding value such as engine load, for example, based on control oil pressure P
SLT, promptly the output oil pressure of linear solenoid valve SLT rotates the basic pressure that the mechanical oil pump 28 (referring to Fig. 1) that drives is exported the operating oil pressure of (generation) by the use conduct from passing through motor 12.
[0036] more specifically, described primary regulator valve 122 comprises spool member 122a, it is arranged on the direction of axle movably so that open or close inlet opening 122i, thereby the operating oil pressure that oil pump 28 generates is received and enters into fuel sucking pipe 124 by delivery outlet 122t discharging; As promoting the spring 122b that device is provided with, be used on the valve closing direction, advancing described spool member 122a; The 122c of grease chamber, it comprises spring 122b and receives control oil pressure P
SLT, so that at the valve closing direction to described spool member 122a applied thrust; With the 122d of grease chamber, it receives the operating oil pressure that oil pump 28 generates, so as in the opening of valves direction to described spool member 122a applied thrust.
[0037] in the primary regulator valve 122 of constructing as mentioned above, state of equilibrium is expressed by following representation (1):
P
L×b＝P
SLT×a+F
s...(1)
F wherein
sBe the spring force of spring 122b, a is the control oil pressure P in the 122c of grease chamber
SLTThe pressure receiving area, b is the pipeline oil pressure P in the 122d of grease chamber
LThe pressure receiving area.Therefore, pipeline oil pressure P
LExpressed by following representation (2), representation (2) shows described pipeline oil pressure P
LWith control oil pressure P
SLTBe proportional.
P
L＝P
SLT(a/b)+F
s/b...(2)
[0038] described primary regulator valve 122 and linear solenoid valve SLT are as pressure regulator, and it is based on pipeline oil pressure control command signal S
PLThe pressure of the working oil that will eject from oil pump 28 is adjusted to pipeline oil pressure P
L, described pipeline oil pressure control command signal S
PLIt is the oil pressure bid value.
[0039] modulator oil pressure P
MBe used as control oil pressure P
SLTBasic pressure and be used for control oil pressure P as the output oil pressure of linear solenoid valve SLS
SLSDescribed modulator oil pressure P
MAlso be used as control oil pressure P
DS1Basic pressure, described control oil pressure P
DS1Be output oil pressure by the solenoid valve DS1 of electric control device 50 duties controls (duty-controlled), and described modulator oil pressure P
MBe used for control oil pressure P as the output oil pressure of solenoid valve DS2
DS2By with pipeline oil pressure P
LAs basic pressure, by modulator valve 126 with described modulator oil pressure P
MBe adjusted to constant pressure.
[0040] based on described control oil pressure P
SLT, by pipeline pressure modulator NO.2 valve 128, by with pipeline oil pressure P
LRegulate described output oil pressure P as basic pressure
LM2
[0041] in manually operated valve 120, with output oil pressure P
LM2Be supplied to inlet opening 120a.Then, when described shift level 74 is operated into " D " position or " L " position, with the conversion of the oil pipe of described manually operated valve 120, so as by the delivery outlet 120f that advances with output oil pressure P
LM2Be fed to forward clutch C1 as moving forward delivery pressure, and described in retreating break B1 working oil by from retreat delivery outlet 120r through floss hole EX discharge (discharging) to, for example, barometric pressure.Therefore, engagement forward clutch C1 and release retreat break B1.
[0042] when described shift level 74 is operated into " R " position, with the oil pipe conversion of described manually operated valve 120, so that through retreating delivery outlet 120r with output oil pressure P
LM2Be fed to as mobile delivery pressure backward and retreat break B1, and the pressure of the working oil in forward clutch C1 by from advance delivery outlet 120f through floss hole EX discharge (discharging) to, for example, in the air.Therefore, engagement retreats break B1 and discharges forward clutch C1.
[0043] when described shift level 74 is operated into " P " position or " N " position, oil pipe conversion with described manually operated valve 120, so that the oil pipe from inlet opening 120a to the delivery outlet 120f that advances and all be disconnected to the oil pipe that retreats delivery outlet 120r from inlet opening 120a, and forward clutch C1 and the working oil that retreats in the break B1 are all discharged from manually operated valve 120.Therefore, forward clutch C1 and retreat break B1 and all be released.
[0044] described gear ratio control valve UP114 comprises spool member 114a, and it is arranged on the direction of axle movably, so that be positioned at the position that upgrades, and in the described position that upgrades, described pipeline oil pressure P
LCan by inlet opening 114i be received and by I/O port 114j be supplied to the input variable pulley 42, and be closed at the described position I/O port 114k that upgrades, with so that spool member 114a is positioned at the home position, described input variable pulley 42 is connected by I/O port 114j and I/O port 114k in described home position; Be set to promote the spring 114b of device, be used for pushing described spool member 114a to the home position side; The 114c of grease chamber, it comprises spring 114b and receives control oil pressure P
DS2, so that push described spool member 114a to the home position side; With the 114d of grease chamber, it receives control oil pressure P
DS1, so that push described spool member 114a to the position side that upgrades.
[0045] described gear ratio control valve DN116 comprises spool member 116a, it is arranged on the direction of axle movably, so that be positioned at the downshift position that I/O port 116j and floss hole EX be connected and be positioned at I/O port 116j and home position that I/O port 116k is connected; Be set to promote the spring 116b of device, be used for pushing described spool member 116a to the home position side; The 116c of grease chamber, it comprises spring 116b and receives control oil pressure P
DS1, so that push described spool member 116a to the home position side; With the 116d of grease chamber, it receives control oil pressure P
DS2, so that push described spool member 116a to the downshift position side.
[0046] in the gear ratio control valve UP114 and gear ratio control valve DN116 that construct as mentioned above, when the line of the heart therein left-half as shown in Figure 3 shown, spring force by spring 114b, when described spool member 114a was maintained at the home position, I/O port 114j and I/O port 114k were connected so that working oil flows to I/O port 116j from input variable pulley 42.In addition, shown as center line right side half part of Fig. 3, because the elastic force of spring 116b when remaining on the home position, I/O port 116j and I/O port 116k are connected, and make thrust than control oil pressure P as spool member 116a
τCan pass to I/O port 114k than control valve 118 from described thrust.
[0047] as described control oil pressure P
DS1When being supplied to the 114d of grease chamber, shown in the right one side of something of center line, by according to control oil pressure P
DS1Thrust, spool member 114a is moved to the position that upgrades against the elastic force of spring 114b.Described pipeline oil pressure P
LBy with control oil pressure P
DS1Corresponding amount is fed to input hydraulic cylinder 42c from inlet opening 114i through I/O port 114j.Simultaneously, disconnect described I/O port 114k and flow to gear ratio control valve DN116 side to stop described working oil.Therefore, gear shift pilot pressure Pin increases, so the width of the V groove of input variable pulley 42 reduces, it reduces change gear, that is to say, stepless speed variator 18 is upgraded.
[0048] as described control oil pressure P
DS2When being supplied to the 116d of grease chamber, shown in the one side of something of a center line left side, by with control oil pressure P
DS2Corresponding thrust, spool member 116a is moved to the downshift position against the elastic force of spring 116b.Therefore, the working oil in input side oil hydraulic cylinder 42c by with control oil pressure P
DS2Corresponding amount is discharged through I/O port 114j, I/O port 114k and I/O port 116j afterwards from floss hole EX.Thus, gear shift pilot pressure Pin reduces, thus the increase of the width of the V-shaped groove of input side variable pulley 42, and the change gear increase, that is to say that stepless speed variator 18 is lowered category.
[0049] therefore, described pipeline oil pressure P
LThe basic pressure that is used as gear shift pilot pressure Pin.As described control oil pressure P
DS1When being output, be input to the pipeline oil pressure P of gear ratio control valve UP114
LBe supplied to input hydraulic cylinder 42c, thereby described gear shift pilot pressure Pin is increased, and causes upgrading continuously.As described control oil pressure P
DS2When being output, the working oil of input hydraulic cylinder 42c is discharged from floss hole EX, thereby described gear shift pilot pressure Pin is reduced, and causes lowering category continuously.
[0050] for example, use vehicle velocity V and target input shaft rotating speed N
IN *Between the relation of prestoring (gearshift map), described target input shaft rotating speed is the target input speed of stepless speed variator 18, with use accelerator operation amount Acc (as, parameter shown in Figure 4), based on actual vehicle speed V and the represented vehicle-state of actual accelerator operation amount Acc, come target setting input shaft rotating speed N
INThen, by with target input shaft rotating speed N
IN *With actual input shaft rotating speed N
INBetween speed discrepancy (deviation) Δ N
IN(N
IN *-N
IN) corresponding feedback control, stepless speed variator 18 carries out gear shift, thus target input shaft rotating speed N
IN *With actual input shaft rotating speed N
INBecome equal.Especially, described working oil is supplied to input hydraulic cylinder 42c or discharges from input hydraulic cylinder 42c, with the width of the V-shaped groove that changes two variable- diameter belt wheels 42,46, and therefore continuously changes described change gear by described feedback control.
[0051] gearshift map of Fig. 4 is corresponding to shift condition, and is configured with target setting input shaft rotating speed N
IN *, vehicle velocity V is more little and accelerator operation amount Acc is big more, and change gear increases.In addition, because the corresponding output shaft rotational speed N of vehicle velocity V
OUTSo, as input shaft rotating speed N
INThe target input shaft rotating speed N of desired value
IN *Corresponding target speed change ratio gamma
*(=N
IN */ N
OUT), it is set in the scope between minimum change gear min and the maximum change gear max.
[0052] in addition, described control oil pressure P
DS1Be supplied to the 116c of grease chamber of gear ratio control valve DN116, limit and lower category so that gear ratio control valve DN116 enters closed condition, and do not consider to control oil pressure P
DS2On the other hand, described control oil pressure P
DS2Be supplied to the 114c of grease chamber of gear ratio control valve UP114, forbid upgrading so that gear ratio control valve UP114 enters closed condition, and do not consider to control oil pressure P
DS1That is to say, not only do not supplying control oil pressure P
DS1With control oil pressure P
DS2The time, and at supply control oil pressure P
DS1With control oil pressure P
DS2The time, each of gear ratio control valve UP114 and gear ratio control valve DN116 all is maintained at the closed condition that spool member is in the home position.Therefore, even make solenoid valve DS1, DS2 one of them break down breaking down owing to electric power system etc., and, control oil pressure P
DS1Or control oil pressure P
DS2Therefore when continuing export, also may prevent the generation that upgrades suddenly or lower category and the generation of the band slip that causes by unexpected gear shift with pressure maximum.
[0053] described clamping pressure control valve 110 comprises spool member 110a, its be arranged on movably the axle direction on opening and closing inlet opening 110i, thereby pipeline oil pressure P
LBe fed to the variable pulley 46 of outlet side and thrust via inlet opening 110i and delivery outlet 110t than control valve 118, and therefore strap clamp compaction forces Pd is provided thereon; Be used as the spring 110b of pushing device device, be used on the opening of valves direction, advancing described spool member 110a; The 110c of grease chamber, it comprises spring 110b and receives control oil pressure P
SLS, so that in the opening of valves direction to described spool member 110a applied thrust; Feedback oil 110d, it is from delivery outlet 110t receiving belt clamping pressure Pd so that at the valve closing direction to described spool member 110a applied thrust; With the 110e of grease chamber, it receives modulator oil pressure P
M, so that at the valve closing direction to described spool member 110a applied thrust.
[0054] in the clamping pressure control valve 110 of constructing as mentioned above, by pipeline oil pressure P
LContinuous pressure regulate control, described strap clamp compaction forces Pd is from delivery outlet 110t output, thus rotating band 48 does not slide, it is by controlling oil pressure P that described continuous pressure is regulated control
SLSRealize as pilot pressure.Therefore, with described pipeline oil pressure P
LBasic pressure as strap clamp compaction forces Pd.
[0055] for example, as shown in Figure 5, use change gear and strap clamp to press strong Pd
*Between the relation of prestoring (strap clamp press try hard to), the driving torque of the corresponding accelerator operation amount Acc that obtains with experiment is a parameter, can not take place thereby band is slided,, judge that (calculating) strap clamp presses strong Pd based on the vehicle-state of representing by actual change gear and accelerator operation amount Acc
*Then, regulate the strap clamp compaction forces Pd of the oil hydraulic cylinder 46c of outlet side, thus the strap clamp compaction forces Pd that acquisition calculates.According to described strap clamp compaction forces Pd, adjust strap clamp and press strong Pd
*, just, the frictional force between variable pulley 42,46 and the rotating band 48.
[0056] described thrust comprises spool member 118a than control valve 118, its be arranged on movably the axle direction on opening and closing inlet opening 118i, thereby pipeline oil pressure P
LBe fed to gear ratio control valve DN116 via inlet opening 118i and delivery outlet 118t, and therefore supplied thrust thereon than control oil pressure P
τBe used as and promote the spring 118b that device is provided with, be used on the opening of valves direction, promoting described spool member 118a; The 118c of grease chamber, it comprises spring 118b and receiving belt clamping pressure Pd so that in the opening of valves direction to described spool member 118a applied thrust; With feedback oil 118d, it receives thrust than control oil pressure P from delivery outlet 118t
τ, so that at the valve closing direction to described spool member 118a applied thrust.
[0057] as mentioned above the structure thrust than control valve 118 in, state of equilibrium is expressed by following representation (3):
P
τ×b＝Pd×a+F
s...(3)
Wherein a is the pressure receiving area to strap clamp compaction forces Pd in the 118c of grease chamber, and b is than control oil pressure P to the thrust in the feedback oil 118d
τThe pressure receiving area, F
sIt is the spring force of spring 118b.Therefore, thrust is than control oil pressure P
τExpressed by following representation (4), it shows that described thrust is than control oil pressure P
τPd is proportional with the strap clamp compaction forces.
P
τ＝Pd×(a/b)+F
s/b...(4)
[0058] when not supplying described control oil pressure P
DS1Or control oil pressure P
DS2The time, and as described control oil pressure P
DS1And P
DS2During all more than or equal to separately predetermined pressure, close each gear ratio control valve UP114 and gear ratio control valve DN116, and described spool member remains on the home position.In this case, thrust is than control oil pressure P
τBe supplied to input hydraulic cylinder 42c, thereby make gear shift pilot pressure Pin equal described thrust than control oil pressure P
τThat is to say that thrust is than the described thrust ratio of control valve 118 outputs control oil pressure P
τ, that is, and gear shift pilot pressure Pin, it remains on predetermined relationship with the ratio between gear shift pilot pressure Pin and the strap clamp compaction forces Pd.
[0059] for example, because the restriction of vehicle speed sensor 58 when the speed of a motor vehicle is very low, that is to say that when the speed of a motor vehicle was lower than preset vehicle speed, vehicle velocity V was detected exactly.When vehicle travels with the low-down speed of a motor vehicle or starts, be used to eliminate speed discrepancy (deviation) Δ N
INThe feedback control of change gear replaced supply control oil pressure P all in sealing control by the execution of what is called sealing control (closing-in control)
DS1Or control oil pressure P
DS2, so gear ratio control valve UP114 and gear ratio control valve DN116 are closed.Therefore, when starting vehicle, Pin is supplied to input hydraulic cylinder 42c with the proportional gear shift pilot pressure of strap clamp compaction forces Pd, thereby makes the ratio between gear shift pilot pressure Pin and the strap clamp compaction forces Pd be in predetermined relationship.Therefore, stop or during the low-down speed of a motor vehicle, prevented that rotating band 48 from sliding at vehicle.At this moment, if set (a/b) and F wherein among first of representation (4) right side
s/ b, enable to realize than corresponding to the thrust of maximum change gear max than the big thrust of τ than τ (=output thrust hydraulic cylinder W
OUT/ input hydraulic cylinder thrust W
IN, W wherein
OUTBe the cross-section area that strap clamp compaction forces Pd multiply by output oil hydraulic cylinder 46c, W
INBe the cross-section area that gear shift pilot pressure Pin multiply by input hydraulic cylinder 42c), then vehicle steadily starts with maximum change gear max or change gear max ' in its vicinity.In addition, preset vehicle speed is the lower limit speed of a motor vehicle, i.e. vehicle velocity V is in this vehicle velocity V, as input shaft rotating speed N
INThe rotating speed of predetermined rotary component become very little so that can not detect, and described preset vehicle speed can be carried out feedback on reservation control.For example, preset vehicle speed can be set as about 2km/h.
[0060] Fig. 6 is the functional block diagram that shows the control funtion part of electric control device 50 execution.In Fig. 6, based on the vehicle-state of being represented by actual vehicle speed V and actual accelerator operation amount Acc, target input rotation is set device 150 and is set input shaft rotating speed N by using the gearshift map that prestores as shown in Figure 4
INTarget input shaft rotating speed N
IN *
[0061] controller for shifting spare 152 is according to rotation speed difference deltan N
IN(=N
IN *-N
IN) carry out the feedback control of the gear shift of stepless speed variator 18, thus actual input shaft rotating speed N
INBecome and equal the target input shaft rotating speed N that device 150 settings are set in target input rotation
IN *Particularly, controller for shifting spare 152 passes through gear shift control command signal (oil pressure order) S
TOutput to hydraulic control circuit 100, continuously change described change gear, described gear shift control command signal is used for changing by the flow of the working oil of control input hydraulic cylinder 42c the width of the V-shaped groove of two variable pulleys 42,46.
[0062] actual the change gear (=input shaft rotating speed N that calculates based on electric control device 50 and accelerator operation amount Acc
IN/ output shaft rotational speed N
OUT), described strap clamp presses strong setting device 154 setting strap clamps and presses strong Pd
*, for example, strap clamp definite from experiment shown in Figure 5 and that prestore presses tries hard to.That is to say that the strap clamp compaction forces Pd that strap clamp presses strong setting device 154 setting output oil hydraulic cylinder 46c presses strong Pd so that strap clamp to be provided
*
[0063] strap clamp compaction forces control means 156 is by output clamping pressure control command signal S
BIncrease or reduce strap clamp to hydraulic control pipeline 100 and press strong Pd
*, described clamping pressure control command signal S
BThe strap clamp compaction forces Pd that is used to regulate output oil hydraulic cylinder 46c presses the strap clamp that strong setting device 154 sets and presses strong Pd to reach strap clamp
*
[0064] described hydraulic control circuit 100 is by activating solenoid valve DS1 and solenoid valve DS2 control and be fed to or from the work oil mass of described input hydraulic cylinder 42c discharging, thereby stepless speed variator 18 is according to gear shift control command signal S
TAnd gear shift, and by actuating linear solenoid valve SLS adjusting belt clamping pressure Pd, thereby described strap clamp presses strong Pd
*According to described clamping pressure control command signal S
BIncrease or reduce.
[0065] motor o controller spare 158 output motor output control command signal S
EOutput with control motor 12.Especially, for example, described motor o controller spare 158 can output to throttle valve actuator 76, fuel injection apparatus 78, ignition mechanism 80 with throttle valve signal, injection signal, ignition timing signal etc. respectively.For example, described motor o controller spare 158 to described valve actuator 76, is controlled Engine torque T by the output throttling valve signal
E, described throttle valve signal is used to open or close described electronic throttle 30 to reach the throttle valve open degree θ corresponding to accelerator operation amount Acc
TH
[0066] in addition, be necessary to set described pipeline oil pressure P
L, it is when for good shift property is provided, for example, good gear shift responsiveness (hereinafter being called " necessary Pin pressure "), required gear shift pilot pressure Pin when described change gear is carried out feedback control, and be used to generate described strap clamp and press strong Pd
*The basic pressure of described strap clamp compaction forces Pd (hereinafter being called " Pd pressure "), thereby can guarantee necessary Pin pressure and Pd pressure.
[0067] that is to say, if pipeline oil pressure P
LBe relatively higher than necessary Pin pressure and Pd pressure, the good and band of then gear shift responsiveness is not easy to slide.Yet, if described pipeline oil pressure P
LBe higher than requiredly, then fuel economy is with variation.In addition, if pipeline oil pressure P
LBe lower than necessary Pin pressure, then gear shift responsiveness may reduce.If described pipeline oil pressure P
LBe lower than described Pd pressure, then band slides to become and takes place easily.
[0068] therefore, based on the higher person in necessary Pin pressure or the Pd pressure, set the pipeline oil pressure of device as basic pressure and set the pipeline oil pressure P that device 160 is set by linear solenoid valve SLT control
L, described control be independent of by solenoid valve DS1 and solenoid valve DS2 carry out about the control of the working oil flow of input hydraulic cylinder 42c and linear solenoid valve SLS control to Pd pressure.
[0069] for example, based on being increased to the higher person in the oil pressure value that each necessary Pin pressure or Pd pressure obtains by being scheduled to the enough and to spare value, the pipeline oil pressure is set device 160 and is set pipeline oil pressure P
L, described pipeline oil pressure P
LComprised relevant pipeline oil pressure P
LControl accuracy and vehicle-state.
[0070] Fig. 7 shows how pipeline oil pressure P is set
LThe figure of example.As shown in Figure 7, experiment predetermined reference enough and to spare value EX is the necessary Pin pressure that is used for necessary Pin pressure with reference to enough and to spare value EXin and the Pd pressure that is used for Pd pressure with reference to enough and to spare value EXd.Therefore, for reference enough and to spare value EX, the value of setting for necessary Pin pressure and differ from one another for the value of Pd pressure setting.Then, by necessary Pin pressure is added to oil pressure value that necessary Pin pressure obtains and by adding Pd pressure in the oil pressure that Pd pressure obtains the higher person with reference to enough and to spare value EXd, is set to required pipeline oil pressure P with reference to enough and to spare value EXin
LBe used to provide required pipeline oil pressure P
LPipeline oil pressure control command signal S
PLBe output.
[0071] particularly, based on actual change gear, target speed change ratio gamma
*(=N
IN */ N
OUT) variance ratio d (γ
*)/dt is by with change gear, target speed change ratio gamma
*Variance ratio d (γ
*)/dt, input torque T
IN, Pd pressure etc. is as variable, as the necessary Pin calculation of pressure device 162 of elementary oil pressure estimator spare, the relation (calculation expression: necessary Pin pressure=f (γ, d (γ of determining and prestoring from the experiment that is used to estimate necessary Pin pressure
*)/dt, T
IN, Pd pressure)) the necessary Pin pressure of calculating, described target speed change ratio gamma
*Variance ratio d (γ
*)/dt sets the target input shaft rotating speed N that device 150 is set by electric control device 50 in based target input rotation
IN *, corresponding to input torque T
INEngine torque estimated value T
E0, strap clamp the strap clamp that provides that strong setting device 154 sets is provided presses strong Pd
*Pd pressure etc. and calculate.Described Pd pressure can be the detected pressure of oil pressure sensor that is provided with by for detection Pd pressure.
[0072] for example, from as shown in Figure 8 with throttle valve open degree θ
THEngine speed N for parameter
EWith Engine torque estimated value T
E0Between the experiment relation (engine torque map) determining and prestore, based on practical engine speeds N
EWith actual throttle valve open degree θ
TH, Engine torque calculating device 164 calculates the Engine torque estimated value T that estimates
E0
[0073] described setting with reference to enough and to spare value EX will be described in more detail below.
[0074] according to clamping pressure control command signal S by 156 outputs of strap clamp compaction forces control means
B, directly regulate and control described Pd pressure by activating linear solenoid valve SLS, provide described strap clamp to press strong Pd to reach
*Pd pressure.Therefore, Pd pressure set with reference to the enough and to spare value that device 166 sets that experiment is determined and the Pd pressure that prestores with reference to enough and to spare value EXd, only consider pipeline oil pressure control command signal S
PLWith actual pipeline oil pressure P
LBetween residual quantity, just, by this way: even if actual pipeline oil pressure P
LDepart from pipeline oil pressure control command signal S
PL, so actual pipeline oil pressure P
LAlso will be above Pd pressure.
[0075] on the other hand, necessary Pin pressure is for reaching target input shaft rotating speed N
IN *(target speed change ratio gamma
*) feedback control the time, the oil pressure that generates as the result of working oil flow control and strap clamp compaction forces control, and necessary Pin pressure directly do not regulated, but the oil pressure that is calculated as estimated value by necessary Pin calculation of pressure device 162 as mentioned above.In addition, because be to carry out described gear shift, be necessary to increase oil pressure so that input hydraulic cylinder thrust W to be provided reliably by feedback control
IN, described thrust is that to change change gear except keeping constant change gear needed.Therefore, necessary Pin pressure set with reference to the enough and to spare value that device 168 sets that experiment is determined and the necessary Pin pressure that prestores with reference to enough and to spare value EXin, thereby necessary Pin pressure with reference to enough and to spare value EXin greater than including only pipeline oil pressure control command signal S
PLAnd the residual quantity between the actual pipeline oil pressure PL and the Pd pressure set are with reference to enough and to spare value EXd.Therefore, for necessary Pin pressure and Pd pressure, set different reference enough and to spare value EX.
[0076] in addition, based on the state (travelling state) of vehicle, Pd pressure with reference to the enough and to spare value set device 166 and necessary Pin pressure with reference to the enough and to spare value set device 168 change respectively described Pd pressure with reference to enough and to spare value EXd and necessary Pin pressure with reference to enough and to spare value EXin.
[0077] for example, when with when its control accuracy is high, compare described actual pipeline oil pressure P
LWith respect to pipeline oil pressure control command signal S
PLControl accuracy when descending, Pd pressure with reference to the enough and to spare value set device 166 and necessary Pin pressure with reference to the enough and to spare value set device 168 increase described Pd pressure with reference to enough and to spare value EXd and necessary Pin pressure with reference to enough and to spare value EXin.For example, when thereby the viscosity of the low working oil of working oil temperature becomes high low oily temperature state, EXd and EXin value when Pd pressure is set device 166 and necessary Pin pressure and set device 168 and be set at greater than the conventional oil temperature state that at working oil temperature is ordinary temp with reference to enough and to spare value EXd and necessary Pin pressure with reference to enough and to spare value EXin described Pd pressure with reference to the enough and to spare value with reference to the enough and to spare value, because when low oil is warm, actual pipeline oil pressure P
LWith respect to pipeline oil pressure control command signal S
PLControl accuracy descend, thereby actual pipeline oil pressure P
LWith pipeline oil pressure control command signal S
PLGap become big.More specifically, set Pd pressure with reference to enough and to spare value EXd and necessary Pin pressure with reference to enough and to spare value EXin so that it is big more, it is low more that described oil pressure becomes.Perhaps, when predetermined low temperature, be determined by experiment and the predetermined value that prestores is set so that Pd pressure with reference to enough and to spare value EXd and necessary Pin pressure with reference to enough and to spare value EXin greater than EXd and EXin value when the conventional oil temperature.About described conventional oil temperature, for example, the oil temperature after heat (warm-up) that is envisioned for motor finishes.
[0078] in addition, because the fluctuation of change gear is very little, thereby compare during with gear shift, allow the enough and to spare amount of the described change gear of change very little during normally stable travelling, so Pd pressure sets device 166 with reference to the enough and to spare value and necessary Pin pressure will be set at reference to enough and to spare value EXin less than EXd and EXin value in the gearshift procedure of change gear change with reference to enough and to spare value EXd and necessary Pin pressure at the normal described Pd pressure of stablizing in the running process that keeps constant change gear with reference to enough and to spare value setting device 168.For example, obtain by experiment and the predetermined value that prestores set respectively Pd pressure with reference to enough and to spare value EXd and necessary Pin pressure with reference to enough and to spare value EXin so that its when normal stable travelling less than it during in common gear shift.Described common gear shift is that the variance ratio in change gear is no more than the gear shift in the process that changes described change gear in the scope of predetermined value.
[0079] in addition, when needing unexpected gear shift in the process of moving, just, in the unexpected gearshift procedure when the variance ratio of change gear surpasses the predetermined value of variance ratio of change gear, Pd pressure is set device 166 and necessary Pin pressure with reference to the enough and to spare value and is set device 168 with reference to the enough and to spare value described Pd pressure is set at greater than EXd and EXin value when the common gear shift or when normal stable the travelling with reference to enough and to spare value EXin with reference to enough and to spare value EXd and necessary Pin pressure, because when gear shift suddenly, in order greatly to change described change gear, need big enough and to spare amount.For example, obtain by experiment and the prearranging quatity that prestores set respectively Pd pressure with reference to enough and to spare value EXd and necessary Pin pressure with reference to enough and to spare value EXin so that its when gear shift suddenly greater than it during in common gear shift.Need the example of imagining of unexpected gear shift to comprise when running process: accelerator pedal 68 sharply returns when travelling, thereby the process that the pass throttle of carrying out rapid speed increase in transmission shown in the line A of band arrow among Fig. 4 upgrades, and shown in the line B of band arrow, change gear is along target input shaft rotating speed N when travelling
IN *Lower limit change, thereby cause process that the rapid speed in transmission increases etc.
[0080] in addition, when belt transmission torque does not sharply change in the process of moving, that is to say, when not requiring in the running process sharply to quicken or slowing down, perhaps, from another viewpoint, when the degree of acceleration that is required by driver's operation or deceleration is low in the process of moving, Pd pressure is set device 166 and necessary Pin pressure with reference to the enough and to spare value and is set device 168 with reference to the enough and to spare value described Pd pressure is set at less than when the common gear shift or when normal stable the travelling with reference to enough and to spare value EXin with reference to enough and to spare value EXd and necessary Pin pressure, because when belt transmission torque does not sharply change in the process of moving, for the enough and to spare amount of quickening or deceleration is provided with allows very little.For example, do not require rapid acceleration in the process of moving or when slowing down, the predetermined value that obtains by experiment and prestore, with respect in the value of normally stablizing in the running process, each Pd pressure is lowered with reference to enough and to spare value EXin with reference to enough and to spare value EXd and necessary Pin pressure.The process that does not need sharply acceleration in the process of moving or slow down, the example that can imagine comprises: the change of belt transmission torque in the process of moving is less than predetermined value, and for example, in constant speed drive, Ruiss Controll computer 82 is carried out processes such as Ruiss Controll.As shown in Figure 9, if at time point t
1Place's output command signal is to Ruiss Controll computer 82, then set by predetermined value, at time point t
1Reference enough and to spare value EX in the constant speed drive process of back execution Ruiss Controll is not carrying out the normal value of stablizing in the running process of Ruiss Controll less than it.
[0081] as shown in figure 12, shown in the pipeline oil pressure set device 160 and comprise Pd pressure-purposes (pressure-purpose) pipeline oil pressure calculating device 170, it is used for based on Pd calculation of pressure Pd pressure-purposes pipeline oil pressure P
LD; Pin pressure-purposes pipeline oil pressure calculating device 172, it is used for based on necessary Pin calculation of pressure Pin pressure-purposes pipeline oil pressure P
LIn; With pressure maximum selector 174, it is used to select Pd pressure-purposes pipeline oil pressure P
LThe pipeline oil pressure of d or Pin pressure-purposes pipeline oil pressure P
LThe higher person among the in.Described pipeline oil pressure is set device 160 and is set the pipeline oil pressure of selecting by pressure maximum selector 174, as required pipeline oil pressure P
L
[0082] for example, the oil pressure value that described Pd pressure-purposes pipeline oil pressure calculating device 170 calculates is as Pd pressure-purposes pipeline oil pressure P
LD, described oil pressure value are by Pd pressure is set Pd pressure that device 166 sets with reference to enough and to spare value EXd with reference to the enough and to spare value, add strap clamp to and press the strap clamp that strong setting device 154 sets and press strong Pd
*Obtain, particularly, be used to provide strap clamp to press strong Pd
*Pd pressure.
[0083] in addition, the oil pressure value that described Pin pressure-purposes pipeline oil pressure calculating device 172 calculates is as Pin pressure-purposes pipeline oil pressure P
LIn, described oil pressure value obtain with reference to the necessary Pin pressure that enough and to spare value EXin adds necessary Pin calculation of pressure device 162 calculating to by the necessary Pin pressure of necessary Pin pressure being set device 168 settings with reference to the enough and to spare value.
[0084] described pipeline oil pressure setting device 160 will be by the Pd pressure-purposes pipeline oil pressure P of pressure maximum selector 174 selections
LD and Pin pressure-purposes pipeline oil pressure P
LHigher pipeline oil pressure among the in is set at required pipeline oil pressure P
LBy way of parenthesis, as shown in Figure 7, required pipeline oil pressure P
LBe set, avoid described pipeline oil pressure P simultaneously
LSurpass rotating band 48 safe load, experiment obtains and the pipeline oil pressure MAX guard that determines is used as the upper limit.Described pipeline oil pressure MAX guard can be defined as considering to replace or append to fuel economy the situation of the safe load of rotating band 48.
[0085] sets the required pipeline oil pressure P that device 160 is set by being used to provide by the pipeline oil pressure
LPipeline oil pressure control command signal S
PLOutput to hydraulic control circuit 100, pipeline oil pressure control spare 176 is regulated pipeline oil pressure P
L
[0086] hydraulic control circuit 100 activates described linear solenoid valve SLT, thereby according to pipeline oil pressure control command signal S
PLRegulate pipeline oil pressure P
L
[0087] Figure 10 is the flow chart that shows the control operation part of electric control device 50, that is to say, shows based on necessary Pin pressure and Pd pressure pipeline oil pressure P suitably is set
LControl operation, and periodically to carry out to the time lag of tens msec such as about several msec.
[0088] at first, in step (hereinafter will omit " step ") S1,, press strong setting device 154, set strap clamp and press strong Pd by strap clamp based on actual change gear and actual accelerator operation amount Acc
*, particularly, be used to provide strap clamp to press strong Pd
*Pd pressure, for example, press strong figure from as shown in Figure 5 strap clamp.
[0089] next, in S2, set device 166 with reference to the enough and to spare value by Pd pressure, set that experiment is determined and the Pd pressure that prestores with reference to enough and to spare value EXd.By way of parenthesis, change Pd pressure with reference to enough and to spare value EXd based on vehicle-state (travelling state).
[0090] next, in S3, by necessary Pin calculation of pressure device 162, based on actual change gear and based target input shaft rotating speed N
IN *The target speed change ratio gamma of calculating
*Variance ratio d (γ
*)/dt; Corresponding to input torque T
INEstimated engine torque T
E0The Pd pressure of in S1, setting, etc., the relation (necessary Pin pressure=f (γ, the d (γ that obtain and prestore from the experiment that is used to estimate necessary Pin pressure
*)/dt, T
IN, Pd pressure)) the necessary Pin pressure of calculating.
[0091] next, in S4, set device 168 with reference to the enough and to spare value by necessary Pin pressure, set that experiment is determined and the necessary Pin pressure that prestores with reference to enough and to spare value EXin so that its greater than Pd pressure with reference to enough and to spare value EXd.In addition, change necessary Pin pressure with reference to enough and to spare value EXin, similarly, be applicable to that Pd pressure is with reference to enough and to spare value EXd based on vehicle-state (travelling state).
[0092] next, in S5, set device 160 (Pd pressure-purposes pipeline oil pressure calculating device 170, Pin pressure-purposes pipeline oil pressure calculating device 172, pressure maximum selector 174) by the pipeline oil pressure, add the oil pressure value that the Pd pressure set among the S1 obtains by the Pd pressure that will in S2, set to reference to enough and to spare value EXd and be calculated as Pd pressure-purposes pipeline oil pressure P
LD, and add the oil pressure value that the necessary Pin pressure that calculates among the S3 obtains by the necessary Pin pressure that will in S4, set to reference to enough and to spare value EXin and be calculated as Pin pressure-purposes pipeline oil pressure P
LIn selects Pd pressure-purposes pipeline oil pressure P
LD and Pin pressure-purposes pipeline oil pressure P
LHigher pipeline oil pressure among the in, selected higher pipeline oil pressure is set to required pipeline oil pressure P
L
[0093] as mentioned above, according to embodiment, as the pipeline oil pressure P of the basic pressure of necessary Pin pressure and Pd pressure
L, set device 160 by the pipeline oil pressure and set based on the higher oil pressure in necessary Pin pressure and the Pd pressure.Therefore, with the necessary Pin pressure of gear shift needs and the Pd pressure of strap clamp compaction forces needs, suitably set required minimum pipeline oil pressure P
LThereby, guarantee good shift property and good strap clamp compaction forces.
[0094] in addition, according to this embodiment, because pipeline oil pressure P
LBe based on by reference enough and to spare value EX being added to the higher person in the oil pressure value that necessary Pin pressure and Pd pressure obtains, set by the pipeline oil pressure that device 160 sets, comprise actual pipeline oil pressure P so can set
LControl accuracy and the suitable pipeline oil pressure P of vehicle-state
L
[0095] in addition, according to this embodiment, because set different reference enough and to spare value EX for necessary Pin pressure with Pd pressure, thus set the reference enough and to spare value EX of the different control mode that comprises necessary Pin pressure and Pd pressure, thus set suitable pipeline oil pressure P
LFor example, be used to provide strap clamp to press strong Pd by activating direct adjusting of linear solenoid valve SLS and control Pd pressure so that obtain
*The situation of Pd pressure under, that need comprise only is actual pipeline oil pressure P
LWith respect to pipeline oil pressure control command signal S
PLResidual quantity, therefore set less relatively Pd pressure with reference to enough and to spare value EXd.At necessary Pin pressure is to control so that reach target speed change ratio gamma as the flow control and the strap clamp compaction forces of the working oil in the feedback control of carrying out
*Result's situation about being provided under, directly do not regulate and control necessary Pin pressure, but be calculated as estimated value, in addition, in order to keep or to change change gear, the sum of errors that is necessary to comprise estimated value adds makes required input thrust hydraulic cylinder W
INGuaranteed oil pressure.Therefore, set greater than Pd pressure with reference to the necessary Pin pressure of enough and to spare value EXd with reference to enough and to spare value EXin.
[0096] in addition, according to this embodiment, as actual pipeline oil pressure P
LFor pipeline oil pressure control command signal S
PLControl accuracy be lower than when its control accuracy is high, set bigger Pd pressure with reference to enough and to spare value EXd and bigger Pin pressure with reference to enough and to spare value EXin.Therefore, even as actual pipeline oil pressure P
LFor pipeline oil pressure control command signal S
PLControl accuracy when low, also can set suitable pipeline oil pressure P
LFor example, thereby when the viscosity of the low working oil of oil temperature is high relatively, actual pipeline oil pressure P
LFor pipeline oil pressure control command signal S
PLControl accuracy be lower than control accuracy when the conventional oil temperature, therefore set reference enough and to spare value EX than conventional oil Wen Shida.Thereby, even as actual pipeline oil pressure P
LFor pipeline oil pressure control command signal S
PLControl accuracy when low, as when the oil temperature is low, also can set suitable pipeline oil pressure P
L
[0097] in addition, according to this embodiment, when needing unexpected gear shift in the process of moving, set with reference to enough and to spare value EX greater than when the common gear shift or in vehicle is normally stable when travelling value.Therefore, even when gear shift suddenly, also can set suitable pipeline oil pressure P
L
[0098] in addition, according to this embodiment, when belt transmission torque does not sharply change in the process of moving, will be set at less than the enough and to spare value when normal stable the travelling with reference to enough and to spare value EX.Therefore, when not needing acceleration suddenly or deceleration in the process of moving, can set little reference enough and to spare value EX, for example, when in the constant speed drive process, carrying out Ruiss Controll, pipeline oil pressure P
LBe set less than the pipeline oil pressure when normal stable the travelling.Therefore, further improved fuel economy.
[0099] next, second embodiment of the present invention will be described.In the following description, common in an embodiment of the present invention part is given and identical reference character, and its description will no longer repeat.
[0100] in first embodiment, estimates necessary Pin pressure by required Pin calculation of pressure device 162.If under first embodiment's situation, can not accurately estimate necessary Pin pressure by required Pin calculation of pressure device 162, then, set device 160 by the pipeline oil pressure and set described pipeline oil pressure P based on the necessary Pin pressure of low precision
L, cause possibility such as the shift property variation of gear shift responsiveness.Therefore, when required Pin calculation of pressure device 162 can not accurately be estimated necessary Pin pressure, in a second embodiment, set described pipeline oil pressure P based on Pd pressure separately
L, rather than set based on necessary Pin pressure and Pd pressure.
[0101] that is to say, when required Pin calculation of pressure device 162 can accurately be estimated necessary Pin pressure, the pipeline oil pressure is set device 160 the higher person based on the oil pressure value that reference enough and to spare value EX is added to necessary Pin pressure and obtain to Pd pressure, sets described pipeline oil pressure P
LOn the other hand, when necessary Pin calculation of pressure device 162 can not accurately be estimated necessary Pin pressure, only need not to use necessary Pin pressure or set described pipeline oil pressure P with reference to enough and to spare value EX based on Pd pressure
L
The example of the unwarrantable situation of validity of passing through the necessary Pin pressure that necessary Pin calculation of pressure device 162 estimates that [0102] can expect comprises: since the each several part that is used for estimating any one break down etc., and can not estimate the situation of necessary Pin pressure, as be used to detect input shaft rotating speed N
INTransfer input shaft speed sensors 56 when breaking down, described input shaft rotating speed N
INBe used for estimating the actual change gear of necessary Pin press process calculating (or target speed change ratio gamma
*), detecting the output shaft rotational speed N
OUTOSS 58 when breaking down, owing to detect throttle valve open degree θ
THThrottle valve sensor 60 break down and can not calculate input torque T
IN(Engine torque estimated value T
E0) time, if be used as Pd pressure at the pressure of sensor, and the oil pressure sensor that detects Pd pressure is when breaking down, etc.The above-mentioned example of expecting also comprises the low situation of estimated accuracy of relevant necessary Pin pressure, as target speed change ratio gamma
*Variance ratio d (γ
*The situation that the calculation accuracy of)/dt is low, for example, lower category and close in the unexpected gear shift transfer process that throttle upgrades comprising firing an engine, in described process Pd pressure with reference to enough and to spare value EXd and necessary Pin pressure with reference to enough and to spare value EXin be set greater than when the common gear shift and when normal stable the travelling (as, in the rapid return of accelerator pedal 68 or sharply depress operation, or follow closely after so rapid pedal return, or follow closely in such process after sharply depressing), may greatly change target speed change ratio gamma
*And as changing the situation that change gear causes the known hand shift of unexpected gear shift by the operation shift level, etc.
[0103] Figure 11 is that the precision that shows the necessary Pin pressure of being estimated by necessary Pin calculation of pressure device 162 can not guarantee under the good situation, the figure of the example of the notion of setting pipeline oil pressure PL.As shown in figure 11, set pipeline oil pressure P
LShown in solid line, particularly, set from following formula (5) based on Pd pressure, rather than shown in dotted line, with pipeline oil pressure P
LBe set at by adding necessary Pin pressure to Pin pressure-purposes pipeline oil pressure P that necessary Pin pressure obtains with reference to enough and to spare value EXin
LIn and by adding Pd pressure to Pd pressure-purposes pipeline oil pressure P that Pd pressure obtains with reference to enough and to spare value EXd
LThe higher pipeline oil pressure of d among both.
P
L=α * Pd pressure+β ... (5)
Wherein α and β are the experiment constants that obtain and prestore, and obviously, it makes pipeline oil pressure P
LBe higher than Pd pressure-purposes pipeline oil pressure P
LD, and it also makes pipeline oil pressure P reliably
LBe higher than the Pin pressure-purposes pipeline oil pressure P that in the different conditions of vehicle, can expect
LAmong the in any one.
[0104] more specifically, Figure 12 is the functional block diagram of the part of the control function that shows that electric control device 50 is carried out, and corresponding to Fig. 6.In Figure 12, with different being provided with among Fig. 6 mainly be to be provided with necessary Pin pressure precision guarantee decision device 178 with further judgement in estimation by 162 pairs of necessary Pin pressure of necessary Pin calculation of pressure device, whether guarantee good precision, main difference also is to guarantee based on necessary Pin pressure precision the result of the judgement of decision device 178, and the pipeline oil pressure is set device 160 and carried out pipeline oil pressure P
LSetting, etc.
[0105] necessary Pin pressure precision guarantees that decision device 178 judgements are in the estimation by 162 pairs of necessary Pin pressure of necessary Pin calculation of pressure device, whether guarantee good precision, for example, based on whether estimating necessary Pin pressure by necessary Pin calculation of pressure device 162.Particularly, necessary Pin pressure precision guarantees decision device 178 judgements, for example, whether there is fault in transfer input shaft speed sensors 56, whether there is fault in OSS 58, whether there is fault in throttle valve sensor 60, whether be used as under the situation of Pd pressure at pressure with sensor, there is fault in the oil pressure sensor that is used to detect Pd pressure, based on various signals from these sensor inputs, then, based on the result of described judgement, judge and whether can estimate described necessary Pin pressure.
[0106] in addition, for example, whether based on the estimated accuracy of necessary Pin pressure descends, and necessary Pin pressure precision guarantees that decision device 178 judges whether necessary Pin calculation of pressure device 162 can accurately estimate necessary Pin pressure.Particularly, for example, based on whether current state is in the conversion of unexpected gear shift, as fires an engine and lower category, close throttle and upgrade etc., perhaps whether carry out hand shift, necessary Pin pressure precision guarantees that decision device 178 judges that whether the estimated accuracy of necessary Pin pressure descends.
[0107] when necessary Pin pressure precision guaranteed that decision device 178 judges that necessary Pin calculation of pressure device 162 can accurately be estimated necessary Pin pressure, the pipeline oil pressure was set Pd pressure-purposes pipeline oil pressure P that device 160 is selected pressure maximum selector 174
LD or Pin pressure-purposes pipeline oil pressure P
LThe higher person is set at required pipeline oil pressure P among the in
LOn the other hand, when necessary Pin pressure precision guarantees that decision device 178 judges that necessary Pin calculation of pressure device 162 can not accurately be estimated necessary Pin pressure, press the strap clamp that strong setting device 154 sets based on strap clamp and press strong Pd
*, particularly, be used to provide described strap clamp to press strong Pd
*Pd pressure, the pipeline oil pressure is set device 160 and is set pipeline oil pressure P from representation (5)
L
[0108] Figure 13 is the flow chart that shows the control operation part of electric control device 50, that is to say, shows pipeline oil pressure P suitably is set
LControl operation.Control operation shown in the flow chart is periodically to carry out to the time lag of tens msec such as about several msec.
[0109] at first, in S10, press strong setting device 154, set strap clamp and press strong Pd corresponding to strap clamp
*, particularly, setting is used to provide strap clamp to press strong Pd
*Pd pressure, for example, press strong figure from strap clamp as shown in Figure 5 based on actual change gear and actual accelerator operation amount Acc.
[0110] next, in S20, set device 166 with reference to the enough and to spare value corresponding to Pd pressure, set that experiment is determined and the Pd pressure that prestores with reference to enough and to spare value EXd.In addition, change Pd pressure with reference to enough and to spare value EXd based on vehicle-state (travelling state).
[0111] next, in S30, corresponding to necessary Pin calculation of pressure device 162, based on actual change gear and based target input shaft rotating speed N
IN *The target speed change ratio gamma of calculating
*Variance ratio d (γ
*)/dt; Corresponding to input torque T
INThe Engine torque T of estimation
E0The Pd pressure of in S1, setting, etc., the relation (necessary Pin pressure=f (γ, the d (γ that obtain and prestore from the experiment that is used to estimate necessary Pin pressure
*)/dt, T
IN, Pd pressure)) the necessary Pin pressure of calculating.
[0112] next, in S40, set device 168 with reference to the enough and to spare value corresponding to necessary Pin pressure, set that experiment is determined and the necessary Pin pressure that prestores with reference to enough and to spare value EXin so that its greater than Pd pressure with reference to enough and to spare value EXd.By way of parenthesis, change necessary Pin pressure with reference to enough and to spare value EXin, similarly, be applicable to that Pd pressure is with reference to enough and to spare value EXd based on vehicle-state (travelling state).
[0113] next, in S50, guarantee decision device 178 corresponding to necessary Pin pressure precision, based on, for example, whether can estimate the necessary Pin pressure in S30, perhaps the estimated accuracy of necessary Pin pressure descends, and judges the necessary Pin pressure that whether can accurately estimate in S30.
[0114] can estimate accurately that necessary Pin pressure and the judgement that therefore obtains are sure if judge in S50, then process proceeds to S51, set device 160 (Pd pressure-purposes pipeline oil pressure calculating device 170, Pin pressure-purposes pipeline oil pressure calculating device 172, pressure maximum selector 174) corresponding to the pipeline oil pressure, in S51, add the oil pressure value that the Pd pressure set among the S10 obtains by the Pd pressure that will in S20, set to reference to enough and to spare value EXd, be calculated as Pd pressure-purposes pipeline oil pressure P
LD, and add the oil pressure value that the necessary Pin pressure that calculates among the S30 obtains to reference to enough and to spare value EXin by the necessary Pin pressure that will in S40, set, be calculated as Pin pressure-purposes pipeline oil pressure P
LIn selects Pd pressure-purposes pipeline oil pressure P
LD or Pin pressure-purposes pipeline oil pressure P
LHigher pipeline oil pressure among the in, selected higher pipeline oil pressure is set to required pipeline oil pressure P
L
[0115] can not estimate accurately that necessary Pin pressure and the judgement that therefore obtains are negated that then process proceeds to S52, sets device 160 corresponding to the pipeline oil pressure if judge in S50.In S52, set pipeline oil pressure P based on the Pd pressure of in step S10, setting from representation (5)
L
[0116] as mentioned above, according to this embodiment, can reach above-mentioned first embodiment's effect.In addition, in the time can not accurately estimating necessary Pin pressure, set the Pd pressure of device 160 based on the pipeline oil pressure and set pipeline oil pressure P by necessary Pin calculation of pressure device 162
LTherefore, in the time can not accurately estimating necessary Pin pressure, for example, when turn-sensitive device breaks down, as fire an engine and lower category or closes in the transfer process of the unexpected gear shift that throttle upgrades etc., or when hand shift, only based on the suitable pipeline oil pressure P of Pd pressure setting
LThereby, minimize the variation of gear shift responsiveness.
[0117] though described embodiments of the invention in conjunction with the accompanying drawings in detail, the present invention also can otherwise implement.
[0118] for example, though in first embodiment, the necessary Pin pressure of use is the estimated value of being calculated by necessary Pin calculation of pressure device 162, and described Pin pressure also can be the pressure that oil pressure sensor detects.Be used as in the structure of necessary Pin pressure at sensor pressure, detect time that the oil pressure sensor of necessary Pin pressure breaks down corresponding to the situation that can not estimate necessary Pin pressure, necessary Pin calculation of pressure device 162 that is to say, when can not accurately be estimated necessary Pin pressure.
[0119] in addition, in first embodiment's example, as actual pipeline oil pressure P
LRelative duct size oil pressure control command signal S
PLControl accuracy when descending, be exactly when the warm low and working oil viscosity of oil is high.Yet, because working oil viscosity is low, when the oil temperature is high, actual pipeline oil pressure P
LControl accuracy also may descend.Under these circumstances, when working oil temperature was high, Pd pressure was set device 166 and necessary Pin pressure with reference to the enough and to spare value and is set device 168 with reference to the enough and to spare value and set the reference enough and to spare value EX that is higher than when the conventional oil temperature.Therefore, even at actual pipeline oil pressure P
LRelative duct size oil pressure control command signal S
PLControl accuracy when descending, also can set suitable pipeline oil pressure P
L
[0120] in addition, in first embodiment, input shaft rotating speed N
IN, the target input shaft rotating speed N relevant with it
IN *Deng can be by engine speed N
E, the target engine speed N relevant with it
E *Deng replacement, perhaps by secondary speed N
T, the target secondary speed N relevant with it
T *Deng replacement.
[0121] in addition, though in first embodiment, the torque converter 14 that is equipped with lock-up clutch 26 is used as dydraudynamic drive unit (fluid drive device), but described lock-up clutch 26 is optional, and in addition, described torque converter 14 can be replaced by different fluid type actuating unit, as the fluid connector that do not possess the moment of torsion amplification effect etc.
[0122] though described the present invention, is appreciated that the present invention is not limited to described embodiment or structure in conjunction with the embodiment who is considered to its demonstration example.On the contrary, the invention is intended to contain various modifications and of equal value the setting.In addition, though the various parts of invention disclosed all illustrate with various exemplary combinations and configuration, comprise more or less or have only other combination of independent parts and dispose also falling in the spirit and scope of the present invention.
Claims (10)
1, a kind of control gear of variable v-belt drive (50), at vehicle power source (12) and driving wheel (24R, power transmission path 24L) is provided with in the vehicle of stepless speed variator (18), described stepless speed variator has primary pulley (42), the band (48) of the secondary pulley (46) and described two belt wheels of reeling, described variable v-belt drive comprises the primary pulley oil hydraulic cylinder (42c) of the groove width that is used to change primary pulley, secondary pulley oil hydraulic cylinder (46c) with the groove width that is used to change secondary pulley, described variable v-belt drive is controlled the strap clamp compaction forces by primary pulley oil hydraulic cylinder control gear ratio with by the secondary pulley oil hydraulic cylinder, thereby between described band and described two belt wheels, do not slide, it is characterized in that the control gear of described variable v-belt drive (50) comprising:
Basic pressure is set device (160), and it sets the basic pressure of interior oil pressure of primary pulley oil hydraulic cylinder and the oil pressure in the secondary pulley oil hydraulic cylinder based on the higher oil pressure in the oil pressure in oil pressure in the primary pulley oil hydraulic cylinder and the secondary pulley oil hydraulic cylinder.
2, the control gear of variable v-belt drive as claimed in claim 1, wherein, described basic pressure is set device based on setting basic pressure by making oil pressure in the primary pulley oil hydraulic cylinder and the oil pressure in the secondary pulley oil hydraulic cylinder increase the higher person that predetermined enough and to spare value obtains in the oil pressure respectively.
3, the control gear of variable v-belt drive as claimed in claim 2, wherein, the predetermined enough and to spare value that the oil pressure in the primary pulley oil hydraulic cylinder is set is different from the predetermined enough and to spare value that the oil pressure in the secondary pulley oil hydraulic cylinder is set.
4, as the control gear of claim 2 or 3 described variable v-belt drives, wherein, when the control accuracy of actual basic pressure for the basic pressure of being set the device setting by basic pressure descended, described predetermined enough and to spare value was set to greater than the predetermined enough and to spare value when described control accuracy is high.
5, as the control gear of claim 2 or 3 described variable v-belt drives, wherein, if vehicle needs unexpected gear shift just in motion, the described predetermined enough and to spare value when then needing unexpected gear shift during vehicle driving is set to greater than in vehicle is normally stable when travelling predetermined enough and to spare value.
6, as the control gear of claim 2 or 3 described variable v-belt drives, wherein, if vehicle belt transmission torque does not in motion have flip-flop, the predetermined enough and to spare value when then belt transmission torque does not have flip-flop during vehicle driving is set to less than in vehicle is normally stable when travelling predetermined enough and to spare value.
7, the control gear of variable v-belt drive as claimed in claim 1, it further comprises the elementary oil pressure estimation unit that is used to estimate the oil pressure in the primary pulley oil hydraulic cylinder,
Wherein, when described elementary oil pressure estimation unit can not accurately be estimated described oil pressure, described basic pressure was set device and is set described basic pressure based on the oil pressure in the described secondary pulley oil hydraulic cylinder.
8, the control gear of variable v-belt drive as claimed in claim 7, wherein, when unexpected speed change, described basic pressure is set device and is set described basic pressure based on the oil pressure in the described secondary pulley oil hydraulic cylinder.
9, the control gear of variable v-belt drive as claimed in claim 1, wherein, described basic pressure is set device and is set the CLV ceiling limit value of described basic pressure based on the safe load of band, and sets described basic pressure and be less than or equal to described CLV ceiling limit value.
10, a kind of controlling method of variable v-belt drive, power transmission path between vehicle power source and the driving wheel is provided with in the vehicle of stepless speed variator, described stepless speed variator has primary pulley, the band of the secondary pulley and described two belt wheels of reeling, described variable v-belt drive comprises the primary pulley oil hydraulic cylinder of the groove width that is used to change primary pulley, secondary pulley oil hydraulic cylinder with the groove width that is used to change secondary pulley, described variable v-belt drive is controlled the strap clamp compaction forces by primary pulley oil hydraulic cylinder control gear ratio with by the secondary pulley oil hydraulic cylinder, thereby between described band and described two belt wheels, do not slide, described controlling method is characterised in that, comprising:
Based on the higher oil pressure in the oil pressure in oil pressure in the primary pulley oil hydraulic cylinder and the secondary pulley oil hydraulic cylinder, set the basic pressure of interior oil pressure of primary pulley oil hydraulic cylinder and the oil pressure in the secondary pulley oil hydraulic cylinder.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006166709 | 2006-06-15 | ||
| JP2006166709 | 2006-06-15 | ||
| JP2006205379 | 2006-07-27 |
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| Publication Number | Publication Date |
|---|---|
| CN101089428A true CN101089428A (en) | 2007-12-19 |
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ID=38942888
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200710106723 Pending CN101089428A (en) | 2006-06-15 | 2007-06-15 | Device and method of controlling a belt-type continuously variable transmission |
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| Country | Link |
|---|---|
| CN (1) | CN101089428A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102084158A (en) * | 2008-12-15 | 2011-06-01 | 丰田自动车株式会社 | Continuously variable transmission |
| CN102320295A (en) * | 2011-06-20 | 2012-01-18 | 奇瑞汽车股份有限公司 | Self-protection system of car speed control system and control method thereof |
| CN102734454A (en) * | 2011-04-11 | 2012-10-17 | 本田技研工业株式会社 | Control system for belt-type continuously variable transmission |
| CN103988002A (en) * | 2011-12-13 | 2014-08-13 | 丰田自动车株式会社 | Automatic-transmission hydraulic control device |
| CN104527783A (en) * | 2015-01-14 | 2015-04-22 | 陈全强 | Double continuously variable transmission steering mechanism |
| CN105143725A (en) * | 2013-03-27 | 2015-12-09 | 加特可株式会社 | Control device for belt-type continuously variable transmission |
| CN105757229A (en) * | 2014-10-02 | 2016-07-13 | 奥特润株式会社 | Method for controlling slip of a continuously variable transmission |
| WO2016145627A1 (en) * | 2015-03-18 | 2016-09-22 | GM Global Technology Operations LLC | A continuously variable transmission and method for controlling the same |
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- 2007-06-15 CN CN 200710106723 patent/CN101089428A/en active Pending
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102084158B (en) * | 2008-12-15 | 2013-06-05 | 丰田自动车株式会社 | Continuously variable transmission |
| CN102084158A (en) * | 2008-12-15 | 2011-06-01 | 丰田自动车株式会社 | Continuously variable transmission |
| CN102734454B (en) * | 2011-04-11 | 2014-12-17 | 本田技研工业株式会社 | Control device for belt-type continuously variable transmission |
| CN102734454A (en) * | 2011-04-11 | 2012-10-17 | 本田技研工业株式会社 | Control system for belt-type continuously variable transmission |
| US8812206B2 (en) | 2011-04-11 | 2014-08-19 | Honda Motor Co., Ltd. | Control system for belt-type continuously variable transmission |
| CN102320295A (en) * | 2011-06-20 | 2012-01-18 | 奇瑞汽车股份有限公司 | Self-protection system of car speed control system and control method thereof |
| CN103988002A (en) * | 2011-12-13 | 2014-08-13 | 丰田自动车株式会社 | Automatic-transmission hydraulic control device |
| CN105143725A (en) * | 2013-03-27 | 2015-12-09 | 加特可株式会社 | Control device for belt-type continuously variable transmission |
| CN105143725B (en) * | 2013-03-27 | 2017-03-22 | 加特可株式会社 | Control device for belt-type continuously variable transmission |
| CN105757229A (en) * | 2014-10-02 | 2016-07-13 | 奥特润株式会社 | Method for controlling slip of a continuously variable transmission |
| CN105757229B (en) * | 2014-10-02 | 2018-04-10 | 奥特润株式会社 | The control method by sliding of buncher |
| CN104527783A (en) * | 2015-01-14 | 2015-04-22 | 陈全强 | Double continuously variable transmission steering mechanism |
| CN104527783B (en) * | 2015-01-14 | 2017-02-22 | 蓝思智能机器人(长沙)有限公司 | Double continuously variable transmission steering mechanism |
| WO2016145627A1 (en) * | 2015-03-18 | 2016-09-22 | GM Global Technology Operations LLC | A continuously variable transmission and method for controlling the same |
| US10001199B2 (en) | 2015-03-18 | 2018-06-19 | GM Global Technology Operations LLC | Continuously variable transmission and method for controlling the same |
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