CN107588191A - The control device of variable v-belt drive - Google Patents
The control device of variable v-belt drive Download PDFInfo
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- CN107588191A CN107588191A CN201710537959.2A CN201710537959A CN107588191A CN 107588191 A CN107588191 A CN 107588191A CN 201710537959 A CN201710537959 A CN 201710537959A CN 107588191 A CN107588191 A CN 107588191A
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Abstract
The present invention provides a kind of control device of variable v-belt drive.The variable v-belt drive includes head pulley, secondary pulley and the transmission belt being reeved on the head pulley and the secondary pulley.The control device includes electronic-controlled installation.The electronic-controlled installation is calculated the band sliding velocity of the transmission belt.The electronic-controlled installation the sliding velocity within a predetermined range in the case of, the band clamping pressure of the transmission belt is controlled, so that the sliding velocity deviates from predetermined scope.
Description
Technical field
The present invention relates to a kind of control device of variable v-belt drive, more particularly, to NV (noise/vibration) rank
Reduce.
Background technology
It is known to have to possess the side of head pulley, secondary pulley and the transmission belt being wound around in the head pulley and secondary pulley
Formula and the variable v-belt drive formed.Buncher described in Japanese Patent Laid-Open 11-44359 is exactly this belt
Buncher.Following situation is disclosed in Japanese Patent Laid-Open 11-44359, i.e. be possible to produce buncher
Band sliding in the case of, by making the hydraulic actuator being adjusted with clamping pressure to the pulley to the buncher
The supply hydraulic pressure of supply is pressurized to increase band clamping pressure temporarily, so as to suppress to band sliding.In addition, also describe as follows
Situation, i.e. after supply hydraulic pressure is added, during by supply hydraulic pressure relief to the common hydraulic pressure, the speed change of buncher
Than bigger, then more reduce the decompression rate of supply hydraulic pressure.
The content of the invention
As described above, in Japanese Patent Laid-Open 11-44359 buncher, it is being possible to produce stepless change
In the case of the band sliding of fast device, it is pressurized temporarily by the supply hydraulic pressure for making to supply to hydraulic actuator and clamps pressure to increase band
Power, so as to suppress to band sliding.Although the degree of boost of the supply hydraulic pressure is obtained beforehand through experiment, parsing, examine
Consider difference of vehicle etc. and be set to hydraulic pressure with the amount with safe clearance and superfluous.Its result is, in order to sliding to band
Shift-in row suppress and to the hydraulic pressure of hydraulic actuator excess supply, it is possible to causing oil consumption rate correspondingly to deteriorate.
The present invention provides a kind of Vehicular vibration that can be reduced caused by the band sliding of variable v-belt drive, noise,
And the control device of the deterioration of oil consumption rate can be suppressed.
The control device of variable v-belt drive involved by the mode of the present invention is provided.The Belt-type Adjustable-speed
Device includes head pulley, secondary pulley and the transmission belt being reeved on the head pulley and the secondary pulley.The control
Device includes electronic-controlled installation.The electronic-controlled installation is calculated the band sliding velocity of the transmission belt.The electricity
Sub- control device the sliding velocity within a predetermined range in the case of, the band clamping pressure of the transmission belt is carried out
Control, so that the sliding velocity deviates from predetermined scope.
Control device according to involved by which, sliding velocity within a predetermined range in the case of, to band press from both sides
Compaction forces are controlled such that sliding velocity deviates from predetermined scope.Produced on variable v-belt drive during driving
In raw vibration, the caused self-excited vibration between band and pulley, it was found that following situation, i.e. not only clamped in increase band
Pressure and in the case of reducing sliding velocity, and reduce band clamping pressure and in the case of increasing sliding velocity, from exciting
Dynamic vibration mode (frequency) can also change, so that Vehicular vibration and noise are lowered.Therefore, by according to traveling
State and suitably reduce band clamping pressure to increase sliding velocity, sliding velocity can be made to deviate from predetermined scope, and make because of oneself
Vehicular vibration and noise caused by excited vibration are lowered, also, by preventing the unwanted increase with clamping pressure, consumption
The deterioration of oil cut rate will be suppressed.
, can also be in the following way in the control device involved by aforesaid way, i.e. the predetermined scope is,
It is set in advance, in the lower limit more than zero and the region more than the sliding velocity between the higher limit of the lower limit.
The electronic-controlled installation is in the case where the sliding velocity is in the predetermined scope, according to the transport condition of vehicle
And the band clamping pressure of the transmission belt is controlled, so that the sliding velocity turns into more than the higher limit, or make
The sliding velocity turns into below the lower limit.
Control device according to involved by which, sliding velocity within a predetermined range in the case of, according to car
Transport condition and sliding velocity is gone above higher limit or less than lower limit, therefore sliding velocity can be made from predetermined
Scope deviates.Therefore, Vehicular vibration and noise are lowered.In addition, sliding velocity is made by the transport condition according to vehicle
More than higher limit so as to reduce band clamping pressure, therefore can anti-stop-band clamping pressure increase so that oil consumption rate deteriorates
To suppression.
, can also be in the following way in the control device involved by aforesaid way, i.e. the electronic-controlled installation exists
The sliding velocity is in the predetermined scope and the difference of the sliding velocity and the higher limit is less than the sliding
In the case of the difference of speed and the lower limit, the band clamping pressure of the transmission belt is controlled, so that the sliding
Speed turns into more than the higher limit.
Control device according to involved by which, it is less than sliding velocity and lower limit in the difference of sliding velocity and higher limit
In the case of the difference of value, sliding velocity is turned into more than higher limit, therefore, make sliding velocity into higher limit and lower limit
Nearer side movement, so as to make sliding velocity rapidly deviate from predetermined scope.
, can also be in the following way in the control device involved by aforesaid way, i.e. the electronic-controlled installation exists
In the case that the sliding velocity is in the predetermined scope, to from current sliding velocity to reaching the higher limit
Untill the first arrival time and the second arrival time from current sliding velocity untill the lower limit is reached carry out
Infer.The electronic-controlled installation is being inferred as in the case that first arrival time is shorter than second arrival time, right
The band clamping pressure of the transmission belt is controlled, so that the sliding velocity turns into more than the higher limit.
Control device according to involved by which, sliding velocity to from current sliding velocity to reach higher limit with
And the side movement that arrival time required for lower limit is shorter, therefore sliding velocity can be made rapidly inclined from predetermined scope
From.
, can also be in the following way in the control device involved by aforesaid way, i.e. the electronic-controlled installation exists
The sliding velocity is in the case of below the lower limit of the predetermined scope, and in the rotation speed change of the secondary pulley
In the case of more than predetermined value set in advance, the lower limit of the predetermined scope is reduced.
Control device according to involved by which, in the case where sliding velocity is below lower limit, and in secondary
In the case that the rotation speed change of belt wheel is more than predetermined value, the lower limit of predetermined scope is set to diminish.Self-excited vibration and secondary pulley
Rotation speed change relation it is deeper, there is the bigger tendency of the more big then self-excited vibration of rotation speed change of secondary pulley.In addition, from exciting
It is dynamic also because the individual difference XOR of each vehicle changes by the time characteristic to be made to change.Therefore, although sliding velocity is
, also will be to reduce lower limit and make sliding in the case where the rotation speed change of secondary pulley is more than predetermined value below lower limit
The mode that speed turns into below new lower limit is controlled, so as to prevent the individual difference XOR time dependent because of each vehicle
Change caused by Vehicular vibration and noise become big situation.
, can also be in the following way in the control device involved by aforesaid way, i.e. the variable v-belt drive
Possesses the clutch that can be changed to torque capacity between the secondary pulley and driving wheel.The electronic-controlled installation
It is controlled in the case where the sliding velocity is in the predetermined scope in a manner of making the clutch slip.
Control device according to involved by which, sliding velocity within a predetermined range in the case of, make the cunning
Move speed from predetermined scope to deviate, and make clutch slip, so as to reduce the self-excited vibration to driving wheel transmission
Transmission capacity, and then Vehicular vibration and noise caused by self-excited vibration is further reduced.
, can also be in the following way in the control device involved by aforesaid way, i.e. the lower limit is set
To make the rotation speed change of the secondary pulley as the value below predetermined value set in advance.
Control device according to involved by which, lower limit are set to make the rotation speed change of secondary pulley to turn into advance
Value below the predetermined value of setting, therefore, by the way that sliding velocity control will be reduced into self-excited vibration below lower limit, and drop
The low Vehicular vibration caused by self-excited vibration and noise.
, can also be in the following way in the control device involved by aforesaid way, i.e. the higher limit is set
To make the value by deviateing with sliding and the frequency of caused vibration from the frequency band of Vehicular vibration.
Control device according to involved by which, higher limit be set to make by with sliding and the frequency of caused vibration
The value that rate deviates from the frequency band of Vehicular vibration, therefore, by being more than higher limit by sliding velocity control, it becomes possible to make to pass through band
Sliding and the frequency of caused vibration deviates from the frequency band of Vehicular vibration.Therefore, also will not because by band sliding caused by from
Excited vibration and Vehicular vibration is become big, so as to reduce Vehicular vibration and noise.
Brief description of the drawings
Hereinafter, feature, advantage and the technology to exemplary embodiment of the invention and industrial significance are carried out referring to the drawings
Description, wherein, identical symbology identical element.
Fig. 1 is the figure illustrated to the Sketch for applying the vehicle of the present invention.
Fig. 2 be for the power transmission using Fig. 1 the engagement element for each driving mode engaging table come pair
The figure that the switching of the driving mode illustrates.
Fig. 3 is to being carried out in Fig. 1 vehicle for the control function of various controls and the major part of control system
The figure of explanation.
Fig. 4 is for being that the gear ratio beyond maximum gear ratio or maximum gear ratio enters to the gear ratio of buncher
The judgement setting chart that row judges.
Fig. 5 is sets for the judgement of sliding velocity for whether being judged outside predetermined scope to use to sliding velocity
Determine chart.
Fig. 6 is the major part to the control action of Fig. 3 electronic-controlled installation, specifically to for suppress because
The flow chart that the control action of Vehicular vibration and noise illustrates caused by caused self-excited vibration in CVT travelings.
Fig. 7 is the flow illustrated to the control action of the electronic-controlled installation of other embodiments as the present invention
Figure.
Embodiment
Hereinafter, embodiments of the invention are described in detail referring to the drawings.In addition, accompanying drawing quilt below in an example
It is appropriate to simplify or deform, and the size ratio of each part and shape etc. may not be described exactly.
Fig. 1 is the figure illustrated to the Sketch for applying the vehicle 10 of the present invention.In Fig. 1, vehicle 10 possesses：
The engine 12 of function is played as the drive force source of traveling；Driving wheel 14；And it is arranged on engine 12 and driving
Power transmission 16 between wheel 14.Power transmission 16 possesses in the shell 18 as on-rotatably moving part：With starting
The known torque-converters 20 as fluid-type transmission device that machine 12 links；With the whirlpool of the output rotary part as torque-converters 20
The input shaft 22 that wheel shaft is integrally provided；The known Belt-type Adjustable-speed as stepless speed changing mechanism linked with input shaft 22
Device 24 (hereinafter referred to as buncher 24)；The forward-reverse switching device 26 equally linked with input shaft 22；After advance
Move back switching device 26 and link with input shaft 22 and be provided as the gear mechanism of transmission mechanism side by side with buncher 24
Structure 28；As buncher 24 and the output shaft 30 of the common output rotary part of gear mechanism 28；Countershaft 32；By one
The back gear 34 formed to gear, the pair of gear are arranged on output in a manner of it can not rotate against respectively
On axle 30 and countershaft 32, and it is engaged with each other；With being arranged on the gear on countershaft 32 in a manner of it can not rotate against
36 differential gears 38 linked；And a pair of vehicle bridge 40 linked with differential gear 38 etc..In the power formed by this way
In transfer device 16, the power (also synonymous with torque or power in the case where not making a distinction especially) of engine 12 successively via
It is torque-converters 20, buncher 24 (or forward-reverse switching device 26 and gear mechanism 28), back gear 34, poor
Fast gear 38 and the grade of vehicle bridge 40 and transmitted to a pair of driving wheels 14.
In this way, power transmission 16 possesses is arranged at engine 12 (herein also with being passed engine 12 side by side
Power as input rotary part input shaft 22 it is synonymous) and driving wheel 14 (herein also with to driving wheel 14 export start
The power of machine 12 as output rotary part output shaft 30 it is synonymous) between power transfer path on buncher 24
And gear mechanism 28.Thus, power transmission 16 possesses the power of engine 12 from input shaft 22 via variable speed
Device 24 and the first power transfer path transmitted to the side of driving wheel 14 (i.e. output shaft 30), and by the power of engine 12 from defeated
The second power transfer path for entering axle 22 via gear mechanism 28 and being transmitted to the side of driving wheel 14 (i.e. output shaft 30), and power
Transfer device 16 is configured to, according to the transport condition of vehicle 10 to first power transfer path and the second power transmission
Path switches over.Cut therefore, power transmission 16 possesses as by the power transmission in above-mentioned first power transfer path
The CVT traveling clutch C2 of disconnected or connection clutch mechanism, and as will be in above-mentioned second power transfer path move
Brake B1 is used in the forward clutch C1 for the clutch mechanism that power transmission is cut off or connected and retrogressing, and it is optionally right to be used as
The clutch mechanism that above-mentioned first power transfer path and above-mentioned second power transfer path switch over.CVT traveling clutches
Device C2, forward clutch C1 and retrogressing, equivalent to cut-out/attachment means, and are to pass through hydraulic actuation with brake B1
Device and the known hydraulic friction clamping close device (friction clutch) for the engaging that rubs.In addition, as described below, advance clutch
Device C1 and retrogressing one of key element that brake B1 is respectively composition forward-reverse switching device 26.
Forward-reverse switching device 26 is set in a manner of concentric relative to input shaft 22 around the input shaft 22, and
And based on the epicyclic gearing 26p, forward clutch C1 and retrogressing of double-pinion type with brake B1 and by structure
Into.Epicyclic gearing 26p tooth rest 26c integratedly links with input shaft 22, epicyclic gearing 26p inside engaged gear
26r optionally links via retrogressing brake B1 with shell 18, epicyclic gearing 26p central gear 26s with
And the mode that can rotate against concentric relative to input shaft 22 and link around the small-diameter gear 42 that the input shaft 22 is set.
In addition, tooth rest 26c and central gear 26s are optionally linked via forward clutch C1.In structure by this way
Into forward-reverse switching device 26 in, when forward clutch C1 is engaged and retreat be released with brake B1 when, it is defeated
Enter axle 22 with small-diameter gear 42 directly to link, so as to make in above-mentioned second power transfer path advance power transfer path into
Vertical (reaching).In addition, when retrogressing is engaged with brake B1 and forward clutch C1 is released, small-diameter gear 42 is relative
Rotated in the opposite direction in input shaft 22, so as to make in above-mentioned second power transfer path retrogressing power transfer path into
It is vertical.In addition, when forward clutch C1 and retrogressing are released with brake B1, above-mentioned second power transfer path turns into
The neutral state (power transmission dissengaged positions) that power transmission is cut off.
Gear mechanism 28 is configured to comprising small-diameter gear 42 and is arranged at gear mechanism in a manner of it can not rotate against
The large diameter gear 46 engaged on structure countershaft 44 and with the small-diameter gear 42.Therefore, gear mechanism 28 is one gear stage of formation
The transmission mechanism of (gear ratio).Gear is surrounded in a manner of concentric relative to gear mechanism countershaft 44 and can rotate against
Mechanism countershaft 44 is provided with idle pulley 48.Between gear mechanism countershaft 44 and idle pulley 48, it is also about gear mechanism countershaft 44 and sets
The engaged clutch D1 that selectively will between the two connect or disconnect.Therefore, engaged clutch D1 is used as and is set
Clutch mechanism in power transmission 16, that the power transmission in above-mentioned second power transfer path is cut off or connected
And play function.Specifically, engaged clutch D1 is configured to, including first be formed on gear mechanism countershaft 44
Gear 50, the second gear 52 being formed on idle pulley 48, formed with can be with above-mentioned first gear 50 and second gear
The bushing sleeves 54 of the internal tooth of 52 chimeric (can engage, can engage).In the engaged clutch D1 formed by this way
In, by making bushing sleeves 54 chimeric with above-mentioned first gear 50 and second gear 52, so that gear mechanism countershaft 44
It is joined together with idle pulley 48.In addition, engaged clutch D1 is also equipped with being fitted together to by first gear 50 and second gear 52
When make that rotation is synchronous, known synchromesh gear mechanism S1 as lazy-tongs.Idle pulley 48 is more than the idle pulley 48 with diameter
Output gear 56 engages.Output gear 56 is surrounded with the identical axis of rotation of output shaft 30 and with can not relative to the output shaft 30
The mode rotated against is set.When forward clutch C1 and retrogressing it is engaged with the side in brake B1 and it is engagement type from
When clutch D1 is engaged, make the power of engine 12 from input shaft 22 successively via forward-reverse switching device 26, gear mechanism
28th, idle pulley 48 and output gear 56 and be passed to the second power transfer path on output shaft 30 set up (connection).
Buncher 24 is arranged in the power transfer path between input shaft 22 and output shaft 30.Buncher
24 possess the variable head pulley 58 of the effective diameter being arranged on input shaft 22, are arranged on the rotation concentric with output shaft 30
The variable secondary pulley 62 of effective diameter and the transmission belt being reeved between this pair of variable pulleys 58,62 in rotating shaft 60
64, also, buncher 24 implements power biography for the frictional force between a pair of variable pulleys 58,62 and transmission belt 64
The buncher for the well known thrust type passed.
Head pulley 58 possesses：Consolidating for rotary body is fixed to be installed as input side in a manner of coaxial relative to input shaft 22
Fixed pulley 58a；Set in a manner of it can not rotate against and can move in axial direction around axle relative to input shaft 22
Movable sheave 58b as the movable rotary body of input side；And in order to be changed to the V well widths between the two pulleys and
Produce the master hydraulic actuator 58c (hereinafter referred to as hydraulic actuator 58c) of the thrust for moving movable sheave 58b.
Secondary pulley 62 is configured to, and is possessed：The fixed block 62a of rotary body is fixed as outlet side；With relative to this
Mode that fixed block 62a can not be rotated against around axle and can moved in axial direction and be provided as outlet side and movably revolve
The movable sheave 62b of swivel；And produced to be changed to the V well widths between the two pulleys for making movable cunning
Take turns the primary side hydraulic actuator 62c (hereinafter referred to as hydraulic actuator 62c) of the thrust of 62b movements.
In buncher 24, changed by the V well widths of a pair of variable pulleys 58,62 to make transmission belt 64
Wrapping diameter (effective diameter) is changed, so that (=input shaft rotating speed Nin/ exports rotating speed to gear ratio (gear ratio) γ
Nout) consecutive variations.For example, when the V well widths of constriction head pulley 58, (i.e. buncher 24 is risen for gear ratio γ reductions
Shelves).In addition, when the V well widths of broadening head pulley 58, gear ratio γ increases (i.e. buncher 24 is downshifted).Output shaft
30 are configured in a manner of concentric relative to rotary shaft 60 and can rotate against around the rotary shaft 60.CVT traveling with from
Clutch C2 is arranged on (is arranged on secondary pulley 62 and driving wheel 14 compared with buncher 24 by the side of driving wheel 14
Between (output shaft 30)), and optionally will be connected or disconnect between secondary pulley 62 and output shaft 30 (driving wheel 14).When
When CVT travelings are engaged with clutch C2, the power of engine 12 is set to be passed from input shaft 22 via buncher 24
The first power transfer path being delivered on output shaft 30 sets up (connection).
The action to power transmission 16 illustrates below.Fig. 2 is for being directed to using power transmission 16
The figure that the engaging table of the engagement element of each driving mode illustrates come the switching to the driving mode.In fig. 2, C1 corresponds to
Forward clutch C1 operating state, C2 correspond to CVT travelings clutch C2 operating state, and B1 corresponds to retrogressing system
Dynamic device B1 operating state, D1 correspond to engaged clutch D1 operating state, and "○" represents engaging (connection), and "×" represents
Discharge (cut-out).
First, the driving mode on output shaft 30 is passed to via gear mechanism 28 to the power as engine 12
The gear traveling of (driving mode for carrying out passing power by the second power transfer path) illustrates.As shown in Fig. 2 at this
In gear traveling, such as forward clutch C1 and engaged clutch D1 be engaged, and CVT travelings with clutch C2 and
Retrogressing is released with brake B1.
Specifically, when forward clutch C1 is engaged, the planet tooth of composition forward-reverse switching device 26 can be made
Wheel apparatus 26p is rotated integrally, therefore makes small-diameter gear 42 to be rotated with the identical rotating speed of input shaft 22.Further, since path tooth
Wheel 42 engages with the large diameter gear 46 being arranged on gear mechanism countershaft 44, therefore can make gear mechanism countershaft 44 similarly
Rotated.Also, because engaged clutch D1 is engaged, therefore gear mechanism countershaft 44 and idle pulley 48 are connected one
Rise.Because the idle pulley 48 engages with output gear 56, therefore the output shaft 30 that can make to be integrally provided with output gear 56 rotates.
In this way, when forward clutch C1 and engaged clutch D1 is engaged, the power of engine 12 is successively via torque-converters
20th, forward-reverse switching device 26, gear mechanism 28 and idle pulley 48 etc. and be passed on output shaft 30.In addition, in the tooth
In wheel traveling, such as when retrogressing is engaged with brake B1 and engaged clutch D1, and CVT travelings with clutch C2 and
When forward clutch C1 is released, retrogressing traveling can be carried out.
Next, the traveling on output shaft 30 is passed to via buncher 24 to the power as engine 12
The CVT travelings of pattern (driving mode for carrying out passing power by the first power transfer path) illustrate.Travelled in the CVT
In, as shown in Fig. 2 CVT travelings (high speed), such as CVT travelings are engaged with clutch C2, and forward clutch C1, after
Move back and be released with brake B1 and engaged clutch D1.
Specifically, when CVT travelings are engaged with clutch C2, secondary pulley 62 is connected one with output shaft 30
Rise, therefore secondary pulley 62 can be made to be rotated integrally with output shaft 30.In this way, when CVT travelings are engaged with clutch C2, start
The power of machine 12 is passed on output shaft 30 via torque-converters 20 and the grade of buncher 24 successively.Travelled in the CVT
In (high speed), engaged clutch D1 be released be in order to, such as eliminate CVT traveling in the grade of gear mechanism 28 dragging,
And the situation for preventing the grade of gear mechanism 28 generation at high vehicle speeds from rotating at a high speed.
The gear traveling is chosen in the low vehicle-speed region in for example stopping comprising vehicle.Second power transmits road
Gear ratio γ 1 (the gear ratio EL formed by gear mechanism 28) in footpath is set to be greater than to be formed by buncher 24
Maximum gear ratio (i.e. as minimum speed side gear ratio lowest speed gear ratio) γ max value (the i.e. number of teeth of low speed side
Than).Such as gear ratio γ 1 is equivalent to the first fast number of teeth of the gear ratio as first speed gear level in power transmission 16
Than γ 1, the lowest speed gear ratio γ max of buncher 24 are used as second-speed gear level equivalent in power transmission 16
Gear ratio the second fast gear ratio γ 2.Thus, for example gear traveling and CVT travel the change according to known step change transmission
It is used to switch over the shift cable that first speed gear level and second-speed gear level switch in speed setting chart.This
Outside, such as in CVT travelings, performed based on transport conditions such as accelerator opening θ acc, vehicle velocity Vs and made using known method
The speed change (such as CVT speed changes, variable speed) of gear ratio γ changes.Here, cut being travelled from gear to CVT travelings (high speed)
Change, or from CVT travelings (high speed) to gear during traveling switching, as shown in Fig. 2 transiently travelling (middle car via CVT
Speed) and switch over.
Such as in the case where being travelled from gear to CVT travelings (high speed) switching, before corresponding with gear traveling
Enter with clutch C1 and engaged clutch D1 be engaged state, transiently switch to CVT traveling clutch C2 with
And the state that engaged clutch D1 is engaged is CVT travelings (middle speed).That is, perform so that forward clutch C1 to be discharged simultaneously
Mode that CVT travelings are engaged with clutch C2 is changed into speed change in gear (such as clutch to clutch (clutch to
Clutch) formula speed change (hereinafter referred to as C to C speed changes)).Now, power transfer path is changed to from the second power transfer path
First power transfer path, substantially upshiftd in power transmission 16.Also, it is switched it in power transfer path
Afterwards, in order to prevent it is unwanted dragging or the grade of gear mechanism 28 high speed rotation and discharge engaged clutch D1 (reference picture 2
By driving input cut-out).In this way, engaged clutch D1 being inputted by driving as the input cut-out of the side of self-powered driving wheel in future 14
Cut off clutch and play function.
In addition, in the case of the traveling switching for example from CVT travelings (high speed) to gear, switch as being travelled to gear
Switching prepare and switch to from the CVT traveling clutches C2 status transitions being engaged and further make engaged clutch
The state of D1 engagings is CVT travelings (middle speed) (downshift of reference picture 2 prepares).In the CVT travels (middle speed), turn into also
The state of rotation is transmitted to epicyclic gearing 26p central gear 26s via gear mechanism 28.When from the CVT travel (middle car
Speed) state perform in a manner of CVT travelings to be discharged with clutch C2 and engages forward clutch C1 to change extension clutch
During speed change (such as C to C speed changes) of device, gear will be switched to travel.Now, power transfer path transmits road from the first power
Footpath is changed to the second power transfer path, is substantially downshifted in power transmission 16.
Fig. 3 is to being illustrated for the control function of various controls and the major part of control system in vehicle 10
Figure.In figure 3, possesses the vehicle 10 for example switched over comprising the driving mode to power transmission 16 in vehicle 10
Control device including electronic-controlled installation 80.Thus, Fig. 3 is the input-output system for representing electronic-controlled installation 80
Figure, in addition, being the functional block line chart illustrated to the major part for the control function realized by electronic-controlled installation 80.Electricity
Sub- control device 80 is configured to comprising the so-called microcomputer possessed such as CPU, RAM, ROM, input/output interface,
CPU using RAM interim storage function and carry out signal transacting according to the program being stored in advance in ROM, so as to perform
The various controls of vehicle 10.For example, electronic-controlled installation 80 is configured to, output control, the variable speed of engine 12 are performed
The speed Control of device 24 and the switching control that CVT travelings or gear traveling are switched to clamping pressure control, by driving mode
Deng, and it is divided into engine control is used, speed Control is used etc. as needed.
Based on by the various sensors of the possessed of vehicle 10 (such as engine speed sensor 82, input shaft rotating speed sense
Device 84, OSS 86, accel sensor 88, engine load sensor 90, foot brake switch 92,
G sensor 94, hydrostatic sensor 98,99 etc.) various actual values (such as engine speed obtained by the detection signal that detects
Ne, the input shaft rotating speed Nin of the rotating speed as head pulley 58 corresponding with secondary speed Nt and the corresponding conduct of vehicle velocity V
The output rotating speed Nout of the rotating speed of secondary pulley 62, the operational ton as the accelerator pedal of the acceleration request amount of driver are
Accelerator opening θ acc, throttle th, the signal for being denoted as the state that the foot brake of service brake has been operated
I.e. brake open Bon, vehicle 10 fore-aft acceleration G, to head pulley 58 hydraulic actuator 58c supply principal pressure Pin,
Second pressure Pout supplied to the hydraulic actuator 62c of secondary pulley 62 etc.), it is respectively supplied to electronic-controlled installation 80
In.
Exported respectively from electronic-controlled installation 80：Engine output control for the output control of engine 12 instructs letter
Number Se；Hydraulic control command signal Scvt for the hydraulic control related to the speed change of buncher 24；For pair with it is dynamic
The related forward-reverse switching device 26 of the switching of the driving mode of force transfering device 16, CVT traveling clutch C2 and nibble
Hydraulic control command signal Sswt that type clutch D1 is controlled etc..Specifically, instructed as engine output control
Signal Se, and export for being driven the air throttle being controlled so as to the opening and closing to electronic throttle to throttle actuator
Injection signal that signal, the amount for the fuel to being ejected from fuel injection device are controlled, for igniter pair
Ignition timing signal that the ignition timing of engine 12 is controlled etc..In addition, as hydraulic control command signal Scvt, and to
Hydraulic control circuit 96 exports the magnetic valve of the principal pressure Pin for being supplied to the hydraulic actuator 58c adjusted to head pulley 58
The command signal that is driven, for the second pressure Pout's that is supplied to the hydraulic actuator 62c adjusted to secondary pulley 62
Command signal that magnetic valve is driven etc..In addition, as hydraulic control command signal Sswt, and it is defeated to hydraulic control circuit 96
Go out for command signal for being driven to each magnetic valve etc., each magnetic valve is to making forward clutch C1, retreat and use
Each hydraulic pressure of the supplies such as the actuator that brake B1, CVT traveling are worked with clutch C2, bushing sleeves 54 is controlled.
Electronic-controlled installation 80 functionally possesses engine output control part 100 (engine output control unit), become
Fast control unit 102 (shift control unit), slip rate calculating part 104 (slip rate computing unit), sliding velocity calculating part 106
(sliding velocity computing unit), sliding velocity judging part 108 (sliding velocity judging unit), (the study control of study control unit 110
Unit) and rotation speed change judging part 112 (rotation speed change judging unit).In addition, speed Control portion 102 corresponds to the present invention's
Control unit.
Engine output control part 100 for example for the output control of engine 12, and respectively to throttle actuator, combustion
Expect injection apparatus, igniter output engine output control command signal Se.Engine output control part 100 is according to for example pre-
The relation (not shown) (driving force setting chart) first determined, and accelerator opening θ acc and vehicle velocity V based on reality, are calculated
As the requirement driving output Pdem of the driving required amount proposed by driver, and set for obtaining requirement driving output
Pdem target engine torque Tetgt, and in a manner of obtaining target engine torque Tetgt, caused by air throttle
Dynamic device electronic throttle is opened and closed control, and in addition, also fuel injection amount is controlled by fuel injection device,
Ignition timing is controlled by igniter.
Speed Control portion 102 exports the gear ratio γ to buncher 24 in CVT travelings to hydraulic control circuit 96
The hydraulic control command signal Scvt being controlled, with as based on accelerator opening θ acc, vehicle velocity V, brake signal Bon etc.
The target gear ratio γ tgt calculated.Specifically, speed Control portion 102 is to reaching the target gear ratio of buncher 24
γ tgt predetermined relation (such as CVT speed changes setting chart) is stored, and is opened according to the relation and based on accelerator
θ acc and vehicle velocity V etc. are spent, to determine the main instruction pressure of the command value as the principal pressure Pin supplied to actuator 58c
Pintgt and command value as the second pressure Pout supplied to hydraulic actuator 62c secondary instruction pressure Pouttgt,
And main instruction pressure Pintgt and secondary instruction pressure Pouttgt are exported to hydraulic control circuit 96, is become so as to perform CVT
Speed, wherein, under the target gear ratio γ tgt, can by buncher 24 with clamping pressure be adjusted to optimal value and
The operating point of engine 12 is set to be on predetermined optimal line (such as engine calculated fuel consumption rate line).
In addition, speed Control portion 102 performs is passed to output shaft to the power of engine 12 via gear mechanism 28
The CVT that is passed to via buncher 24 on output shaft 30 of power of gear traveling and engine 12 on 30 travel into
The switching control of row switching.Specifically, speed Control portion 102 to whether switch vehicle traveling in driving mode sentence
It is disconnected.For example, speed Control portion 102 is utilized for a couple first fast gear ratio γ 1 corresponding with the gear ratio EL in gear traveling
The upshift line and drop that the second corresponding fast gear ratio γ 2 is switched over the lowest speed gear ratio γ max in being travelled with CVT
Shelves line, and speed change (switching of gear ratio) is judged based on vehicle velocity V and accelerator opening θ acc, and it is based on the judgement knot
Fruit and to whether switch vehicle traveling in driving mode judge.Above-mentioned upshift line and downshift line are predetermined change
Fast line, there is predetermined hysteresis.
Speed Control portion 102 performs the switching of driving mode when being judged as switching driving mode.For example, speed Control
When portion 102 judges upshift in gear traveling, travelled from gear to CVT travelings (high speed) switching.Speed Control portion 102 exists
In the case that gear is travelled to CVT travelings (high speed) switching, first, by discharging and inciting somebody to action forward clutch C1
C to C speed changes that CVT travelings are engaged with clutch C2 perform upshift.The state transiently switches corresponding to Fig. 2's
CVT travels (middle speed), and the power transfer path in power transmission 16 is from via the second of the passing power of gear mechanism 28
Power transfer path switches to the first power transfer path via the passing power of buncher 24.Next, speed Control
Portion 102 exports in a manner of by the engaged clutch D1 releases in engaging and makes what lazy-tongs S1 bushing sleeves 54 worked
Instruction, to travel (high speed) switching to CVT.Bushing sleeves 54 are driven by hydraulic actuator (not shown), also, logical
Cross to the hydraulic pressure that the hydraulic actuator supplies and make to be conditioned to the press pressure that bushing sleeves 54 apply.
In addition, speed Control portion 102 CVT travel (high speed) in judge downshift when, from CVT traveling (high speed) to
Gear traveling switching.Speed Control portion 102 is in the case where travelling (high speed) from CVT to gear traveling switching, first, output
The instruction that makes lazy-tongs S1 bushing sleeves 54 work in a manner of by the engaged clutch D1 engagings in release, with to
CVT travelings (middle speed) switching.Next, speed Control portion 102 with clutch C2 by discharging and will advance CVT travelings
Downshift is performed with the C to C speed changes of clutch C1 engagings.The state travels corresponding to Fig. 2 gear, power transmission 16
In power transfer path switched to from the first power transfer path via the passing power of buncher 24 via gear mechanism
Second power transfer path of the passing power of structure 28.In this way, speed Control portion 102 be during the traveling of vehicle 10 from via
In the case that the power transmission of buncher 24 switches to the power transmission via gear mechanism 28, make engaged clutch
D1 discharges CVT travelings with clutch C2 after being acted to engaging side.
However, in CVT travelings, it may occur that due between each pulley 58,62 and transmission belt 64 of buncher 24
Self-excited vibration caused by caused sliding (band sliding), also, because of the self-excited vibration and caused by Vehicular vibration and noise
As problem.In order to suppress to the problem, in the prior art, by increase band clamping pressure and reduce band sliding so as to
Reduce self-excited vibration.However, on the incrementss with clamping pressure, if difference, safe clearance in view of each vehicle etc.,
Then need to be set as value compared with the optimal value of each vehicle and superfluous.Therefore, band clamping pressure is made to become big all the time, therefore
The hydraulic pressure supplied to hydraulic actuator 58c, 62c also uprises, so that oil consumption rate deteriorates.Furthermore, it is necessary to useful life longevity is higher
Transmission belt, therefore also exist make the increased possibility of manufacturing cost.
In order to eliminate above-mentioned unfavorable condition, in the present embodiment, by a manner of as described below to variable speed
The band clamping pressure of device 24 is controlled, so as to press down to the Vehicular vibration caused by self-excited vibration and noise
Oil consumption rate is deteriorated while processed and suppressed.
Vehicle-state judging part 103 to whether in self-excited vibration turn into problem transport condition judge.From exciting
Move not turns into problem all the time in CVT travelings, but becomes notable in the case where vehicle is in predetermined transport condition.Cause
This, vehicle-state judging part 103 becomes significant transport condition to self-excited vibration and stored in advance, and turns into vehicle and be somebody's turn to do
During transport condition, it is judged as performing the control described hereinafter for suppressing Vehicular vibration and noise.The self-excited vibration
Become significant transport condition experimentally to be obtained in advance, such as gear ratio γ, input torque according to buncher 24
Tin, various rotating speeds (input shaft rotating speed Nin etc.) etc. and be prescribed.Vehicle-state judging part 103 is detecting such as variable speed
When the gear ratio γ of device 24 has been entered in the scope that self-excited vibration becomes significantly predetermined, it is judged as performing to Vehicular vibration
And the control that noise is suppressed.In this way, become significantly to travel to obtain self-excited vibration by testing (or parsing) in advance
State, as long as in the case where becoming the transport condition, it is carried out described hereinafter pressing down Vehicular vibration and noise
The control of system, so as to reduce the control load that electronic-controlled installation 80 is undertaken.In addition, it is input into buncher 24
In input torque Tin be calculated by the product of motor torque Te and the torque ratio of torque-converters 14.
It is judged as performing the control for suppressing Vehicular vibration and noise when by vehicle-state judging part 103
When, slip rate calculating part 104 is performed.Slip rate calculating part 104 is between the pulley 58,62 and transmission belt 64 in CVT travelings
Slip rate η calculated.
Whether slip rate calculating part 104 is that maximum gear ratio γ max are carried out first to the gear ratio γ of buncher 24
Judge.Judge to set chart using the gear ratio γ shown in Fig. 4 whether to be that maximum gear ratio γ max are carried out to gear ratio γ
Judge.In the judgement setting chart shown in Fig. 4, transverse axis represents the second pressure Pout of secondary pulley 62, and the longitudinal axis represents main cunning
The principal pressure Pin of wheel 58.The curve shown in Fig. 4 is expressed as the region for maximum gear ratio γ max with turning into maximum gear ratio
Boundary line between the region of gear ratio γ beyond γ max, represent to turn into maximum tooth number ratio on the right side relative to the boundary line
γ max region, relative to boundary line keep left side represent turn into region of the maximum tooth number than the gear ratio γ beyond γ max.Root
According to Fig. 4, in the higher regions of second pressure Pout, turn into maximum gear ratio γ max, in the higher regions of principal pressure Pin,
As the gear ratio γ beyond maximum gear ratio γ max.In addition, Fig. 4 judgement setting chart beforehand through experiment or parsing and
Obtained and stored.Slip rate calculating part 104 sets chart using Fig. 4 judgement, and based on the principal pressure Pin of reality
And second pressure Pout, and which region, which judges, is in current gear ratio γ.For instance in the maximum number of teeth
In the case of in region than γ max, slip rate calculating part 104 is judged as that gear ratio γ is maximum gear ratio γ max, in
In the case of in the region of gear ratio γ beyond maximum gear ratio γ max, slip rate calculating part 104 is judged as that gear ratio γ is
Gear ratio γ beyond maximum gear ratio γ max.
In addition, slip rate calculating part 104 be judged as gear ratio γ be maximum gear ratio γ max in the case of, based on
Under mathematical expression (1) and calculate slip rate η.In addition, theoretical γ max are, the structure based on buncher 24 and it is unique really
Fixed maximum gear ratio γ.Mathematical expression (1) represents that, in the case where gear ratio is in maximum gear ratio γ max, slip rate η leads to
Cross with actual input shaft rotating speed Nin and the input shaft rotating speed (Nout × theoretical γ calculated according to output rotating speed Nout
Max difference (Nin-Nout × theoretical γ max) divided by input shaft rotating speed Nin) and obtained.
η=(Nin-Nout × theoretical γ max)/Nin ... (1)
In addition, slip rate calculating part 104 is in the case where being judged as that gear ratio γ is in beyond maximum gear ratio γ max,
Inferential slip rate η is calculated using relational expression or relation the setting chart obtained beforehand through experiment or parsing.Institute
State relational expression or relation setting chart by the input torque Tin that will for example be input into buncher 24, equivalent to
The principal pressure Pin with clamping pressure of the side of head pulley 58, the second pressure with clamping pressure equivalent to the side of secondary pulley 62
Pout and gear ratio γ are formed as parameter.Above-mentioned input torque Tin, principal pressure Pin, second pressure Pout, gear ratio
γ is the parameter related to slip rate η, so as to be inferred based on these parameters to slip rate η.Slip rate calculates
Portion 104 by input torque Tin, principal pressure Pin, second pressure Pout and the gear ratio γ of reality by being applied to above-mentioned relation
Formula or relation setting chart in, and inferential calculate slip rate η.
Sliding velocity calculating part 106 is based on the slip rate η calculated by slip rate calculating part 104 and is used as head pulley 58
Rotating speed input shaft rotating speed Nin, and calculate sliding velocity Δ N.Sliding velocity Δ N based on following mathematical expression (2) and by
Calculate.Shown by mathematical expression (2), sliding velocity Δ N is counted by slip rate η and input shaft rotating speed Nin product
Calculate.
Δ N=η × Nin ... (2)
Whether sliding velocity judging part 108 is to the sliding velocity Δ N calculated by sliding velocity calculating part 106 in pre-
Judged outside the predetermined scope first set.Whether Fig. 5 is to enter to sliding velocity Δ N outside the predetermined scope
The judgement for the sliding velocity Δ N that row judges and used, obtained beforehand through experiment or parsing sets chart.In Figure 5, it is horizontal
Axle represents engine speed Ne, and the longitudinal axis represents sliding velocity Δ N."○" shown in Fig. 5 is represented in pulley 58,62 and transmission belt
The size of caused self-excited vibration turns into the sliding velocity Δ N below predetermined value between 64.In addition, the size on self-excited vibration
Whether it is below predetermined value, is advance in the output rotating speed Nout of the rotating speed as secondary pulley 62 rotation speed change Δ Nout
In the case of below the predetermined value beta of setting, it is judged as the size of self-excited vibration for below predetermined value, the predetermined value beta is set to
Driver will not because by self-excited vibration and caused by Vehicular vibration and noise and the value of the degree for the sense that do not feel well.
"×" shown in Fig. 5 represents that the self-excited vibration between pulley 58,62 and transmission belt 64 is more than predetermined value (i.e. output shaft
Rotating speed Nout rotation speed change Δ Nout has exceeded predetermined value beta) sliding velocity Δ N.In addition, " " shown in Fig. 5 though represent
Right self-excited vibration is more than predetermined value but the self-excited vibration does not turn into the sliding velocity Δ N of problem.Here, self-excited vibration does not turn into
The following situation of problem representation, i.e. although the self-excited vibration is more than predetermined value, driver do not have reason in the self-excited vibration and
Caused Vehicular vibration and noise and be affected.
Vehicular vibration is the caused vibration on steering wheel, seat, floor etc., in detection, for example, by being pacified respectively
Acceleration transducer on steering wheel, seat, floor etc. and detected.Also, detected by each sensor
Vibration be not reaching to the setting impacted to driver in the case of, be judged as that Vehicular vibration has no problem.In addition, close
In noise, detected for example, by being arranged on the microphone of in-car, and driver is impacted being not reaching to
Setting in the case of, be also judged as having no problem for the noise.Thus, the sliding velocity Δ N shown in " " is represented such as
Under situation, i.e. although self-excited vibration is more than predetermined value, Vehicular vibration and noise are not above the setting.In addition,
Sliding velocity Δ N shown in "×" represents following situation, i.e. self-excited vibration is more than predetermined value, and Vehicular vibration and noise
In at least one party exceed setting.In addition, the sliding velocity Δ N shown in "○" represents following situation, i.e. self-excited vibration is small
In predetermined value, and Vehicular vibration and noise are not above setting.
As shown in Figure 5, it is thus identified that following situation, i.e. even if engine speed Ne changes, shown in "×" from exciting
The dynamic sliding velocity Δ N as more than predetermined value turns into the sliding velocity Δ N below predetermined value with the self-excited vibration shown in "○"
Between the value on border can also turn into approximately fixed value.The value on the border is set to predetermined value A (lower limit).In other words,
Predetermined value A is set to self-excited vibration less than predetermined value (the rotating speed Nout of secondary pulley 62 is below predetermined value beta) and vehicle
Vibration and noise are not above the value of setting.
On the other hand, more than predetermined value Vehicular vibration and grass are not influenceed although self-excited vibration turns into
" " shown in sliding velocity Δ N can be changed according to engine speed Ne.Specifically, engine speed Ne more under
Drop, the sliding velocity Δ N shown in " " become higher.Should " " although shown in self-excited vibration exceed predetermined value but Vehicular vibration
And noise turn into problem sliding velocity Δ N and "×" shown in sliding velocity between border value, be set to
The predetermined value B (higher limit) linearly to be changed according to engine speed Ne.In addition, risen in engine speed Ne
During predetermined speed, predetermined value A is consistent with predetermined value B.Between the predetermined value A more than zero and the predetermined value B more than predetermined value A
Region be set to sliding velocity Δ N predetermined scope.
Here, in the region that sliding velocity Δ N is more than predetermined value B, should even if self-excited vibration goes above predetermined value
Self-excited vibration will not also turn into the reason for problem and be that the frequency of self-excited vibration changes.It is predetermined value in sliding velocity Δ N
In more than B region, because the frequency of self-excited vibration changes, so as to deviate from the frequency band of Vehicular vibration and noise.Its
As a result it is that will not be resonated because of self-excited vibration, therefore Vehicular vibration and noise are hardly by the shadow of self-excited vibration
Ring.Therefore, it is not only, in the case where sliding velocity Δ N is arranged on below predetermined value A, to be arranged on by sliding velocity Δ N
In the case of more than predetermined value B, it can also suppress Vehicular vibration and noise.Therefore, predetermined value B is set to, and makes self-excited vibration
(by with sliding and caused vibration) the value that deviates from the frequency band of Vehicular vibration of frequency.
Sliding velocity judging part 108 is using Fig. 5 sliding velocity Δ N judgement setting chart and to current sliding velocity
Whether whether Δ N be below predetermined value A or be more than predetermined value B to be judged.Sliding velocity Δ N be in predetermined value A with
In the case of in the lower or region in more than predetermined value B, it is judged as that sliding velocity Δ N is in outside predetermined scope.It is another
Aspect, it is more than predetermined value A in sliding velocity Δ N and makes a reservation for less than in the case of predetermined value B, being judged as that sliding velocity Δ N is in
In the range of.
When being judged as sliding velocity Δ N within a predetermined range by sliding velocity judging part 108, speed Control portion
102 in a manner of making sliding velocity Δ N from predetermined scope deviation and to band clamping pressure (the i.e. principal pressure of transmission belt 64
Pin, second pressure Pout) carry out feedback control.That is, so that sliding velocity Δ N turns into below predetermined value A or makes sliding velocity
Δ N turns into more than predetermined value B mode, and feedback control is carried out to band clamping pressure.
Difference L1 (=Δ N-A) and cunning of the speed Control portion 102 for example to current sliding velocity Δ N and predetermined value A
The difference L2 (=B- Δ N) for moving speed Δ N and predetermined value B is calculated, and sliding velocity Δ N is become to the less side of difference
Change.Specifically, speed Control portion 102 is in the case where difference L1 is less than difference L2, so that sliding velocity Δ N turns into predetermined value
Below A mode and to band clamping pressure carry out feedback control, difference L2 be less than difference L1 in the case of so that sliding velocity
Δ N carries out feedback control as more than predetermined value B mode to band clamping pressure.
When setting sliding velocity Δ N desired value Δ N*, speed Control portion 102 is so that sliding velocity Δ N follows the mesh
Scale value Δ N* mode and to band clamping pressure perform feedback control.In addition, sliding velocity Δ N desired value Δ N* is set
For the predetermined value (predetermined value A or predetermined value B) of the less side of the difference, to further contemplate the difference of vehicle
Deng and consider the value of surplus in advance.Speed Control portion 102 is to by between desired value Δ N* and current sliding velocity Δ N
The controlled quentity controlled variable that deviation (=Δ N*- Δ N) is multiplied by gain set in advance (proportional gain K etc.) and obtained is calculated, it is specific and
Speech, the second pressure Pout of main instruction pressure Pintgt and secondary pulley 62 to the principal pressure Pin of head pulley 58 secondary
Instruction pressure Pouttgt is calculated.Also, speed Control portion 102 is by the main instruction pressure Pintgt calculated and secondary
Level instruction pressure Pouttgrt exports to hydraulic control circuit 96.
For example, speed Control portion 102 is in the secondary instruction pressure that sliding velocity Δ N will be made to decline (or rising)
When Pouttgt is calculated as the controlled quentity controlled variable of feedback control, based on predetermined relation, relative to second pressure Pout
Change and it is (in this case, real to maintaining the gear ratio γ of buncher 24 main instruction pressure Pintgt to be calculated
Feedback control is carried out to second pressure Pout in matter).By above-mentioned control, sliding velocity Δ N deviates from predetermined scope, because
This, Vehicular vibration and noise are suppressed.Especially in the case where sliding velocity Δ N is set into more than predetermined value B, due to applying
The band clamping pressure for adding to transmission belt 64 diminishes, therefore the unwanted increase with clamping pressure is inhibited.Thus, to liquid
The supply hydraulic pressure of hydraulic actuator 58c, 62c supply is reduced, and therefore, the deterioration of oil consumption rate is also suppressed.
In above-mentioned control, being in Vehicular vibration and noise in sliding velocity Δ N turns into the predetermined scope of problem
In the case of, make sliding velocity Δ N into sliding velocity Δ N and predetermined value A and predetermined value B difference L1, L2 less one
Move side.As long as however, making sliding velocity Δ N deviate from predetermined scope, then it is not limited to less in difference L1, L2
Side.For example, it is also possible to sliding velocity Δ N is set to deviate the shorter sidesway of required arrival time to from predetermined scope
It is dynamic.Specifically, the arrival required for current sliding velocity Δ N arrival predetermined values A is obtained by testing or parsing respectively
Time T1 and sliding velocity Δ N reaches the arrival time T2 required for predetermined value B, and makes sliding velocity Δ N to arrival time
Shorter side movement in T1, T2.For example, the arrival time untill predetermined value A is reached from current sliding velocity Δ N
In the case that T1 is shorter than the arrival time T2 untill reaching predetermined value B, by sliding velocity Δ N controls below predetermined value A.This
Outside, in the case that in arrival time, T2 is shorter than arrival time T1, by sliding velocity Δ N controls more than predetermined value B.In addition,
Using input torque Tin, gear ratio γ, liquid temperature etc. as parameter it is various under the conditions of, experimentally obtain arrival time T1, T2.
Although however, the predetermined value A and predetermined value B are set with the initial value obtained in advance, due to of vehicle
Body difference and change year in year out, optimal value can change.On the other hand, study control unit 110 be based on self-excited vibration relation compared with
The rotation speed change Δ Nout of deep secondary pulley 62, to perform predetermined value A study control, so as to the individual difference XOR with vehicle
Change year in year out and independently Vehicular vibration and noise are suppressed.
In the case where being judged as sliding velocity Δ N from predetermined scope deviation by sliding velocity judging part 108, especially
It is in the case where sliding velocity Δ N is below predetermined value A, rotating speed of the rotation speed change judging part 112 based on secondary pulley 62,
Rotating speed Nout is exported, and the rotation speed change Δ Nout to exporting rotating speed Nout is calculated, and to being calculated
Whether rotation speed change Δ Nout is judged below predetermined value beta set in advance.In addition, rotation speed change Δ Nout is per unit
The output rotating speed Nout of time variable quantity, and by carrying out time diffusion to the output rotating speed Nout detected at any time
And calculate.
It is more than predetermined value beta in the rotation speed change Δ Nout for being judged as secondary pulley 62 by rotation speed change judging part 112
In the case of, study control unit 110 reduces predetermined value A.For example, when sliding velocity Δ N is below predetermined value A, it is judged as turning
In the case that speed variation Δ Nout is more than predetermined value beta, current sliding velocity Δ N study is newly pre- by study control unit 110
Definite value A.Its result is that predetermined value A is updated to the value for being less than the predetermined value A before learning.Make when by learning control unit 110
When predetermined value A is updated, speed Control portion 102 performs band in a manner of the predetermined value A after making sliding velocity Δ N be less than renewal
The feedback control of clamping pressure.Independently self-excited vibration is pressed down thereby, it is possible to the individual difference with vehicle and changing year in year out
System.
Fig. 6 is the major part to the control action of electronic-controlled installation 80, specifically, to suppressing because being travelled in CVT
In the flow chart that illustrates of the control action of Vehicular vibration caused by caused self-excited vibration and noise.The flow chart exists
It is performed repeatedly in CVT travelings.
First, it is right in the step S1 (following, omit " step ") corresponding with the function phase of vehicle-state judging part 103
Whether the transport condition of vehicle is to become aobvious by gear ratio γ, input torque Tin, various rotating speeds etc. and the self-excited vibration set
The transport condition of work is judged.It is being judged as not being that S1 makes no in the case that self-excited vibration becomes significant transport condition
It is fixed to judge, and terminate this flow.In the case where being judged as that self-excited vibration becomes significant transport condition, S1 makes to be sentenced certainly
It is disconnected, and enter S2.
In the step S2 corresponding with the function phase of slip rate calculating part 104, based on principal pressure Pin and second pressure
Pout and whether the gear ratio γ to buncher 24 is that maximum gear ratio γ max judge.It is being judged as gear ratio γ
In the case of not being maximum gear ratio γ max, S2 makes negative evaluation, and enters S3.In the function with slip rate calculating part 104
In corresponding S3, based on by input torque Tin, band clamping pressure (principal pressure Pin, second pressure Pout), gear ratio γ structures
Into relational expression or relation setting chart, and inferential calculate slip rate η.On the other hand, it is being judged as the number of teeth in S2
In the case of being maximum gear ratio γ max than γ, S2 makes affirmative determination, and enters S4.In the work(with slip rate calculating part 104
In S4 that can be corresponding, slip rate η is calculated based on above-mentioned mathematical expression (1).
In S5 corresponding with the function phase of sliding velocity calculating part 106, pass through the cunning for making to calculate in S2 or S3
Shifting rate η is multiplied by input shaft rotating speed Nin, so as to calculate sliding velocity Δ N.In the function phase pair with sliding velocity judging part 108
In the S6 answered, whether the sliding velocity Δ N that is calculated is judged below predetermined value A or more than predetermined value B.
Sliding velocity Δ N is more than predetermined value A and less than in the case of predetermined value B, and S6 makes negative evaluation, and enters S9.With speed change
In the corresponding S9 of control unit 102, sliding velocity Δ N desired value Δ N* is set, and so that sliding velocity Δ N is chased after
The feedback control with clamping pressure (principal pressure Pin, second pressure Pout) is performed with desired value Δ N* mode.Thus,
S2~S6, S9 control are repeatedly executed at predetermined intervals, untill sliding velocity Δ N turns into below predetermined value A or more than predetermined value B.
In S6, in the case where being judged as sliding velocity Δ N below predetermined value A or more than predetermined value B, S6 makees
Go out affirmative determination, and enter S7.In S7 corresponding with the function phase of rotation speed change judging part 112, secondary pulley 62 is calculated
Rotation speed change Δ Nout.Next, in the S8 corresponding with rotation speed change judging part 112, to the rotating speed calculated in S7
Change whether Δ Nout is judged below predetermined value beta.In the case where rotation speed change Δ Nout is more than predetermined value beta, S8 makees
Go out negative evaluation, and enter S10.In S10 corresponding with the function phase of study control unit 110, it is in pre- in sliding velocity Δ N
In the case of below definite value A, by current sliding velocity Δ N renewals (setting) as new predetermined value A.That is, predetermined value A is to decline
Side is changed.Also, S6 is returned to, again to sliding velocity Δ N whether below predetermined value A or more than predetermined value B sentences
It is disconnected.S8 is returned, in the case where rotation speed change Δ Nout is below predetermined value beta, terminates this flow.
As described above, according to the present embodiment, sliding velocity Δ N within a predetermined range in the case of so that sliding
Move speed Δ N and feedback control is carried out to band clamping pressure from the mode that predetermined scope deviates.On in buncher 24
Driving during in caused vibration, the caused self-excited vibration between transmission belt 46 and pulley 58,62, it was found that it is as follows
Situation, i.e. not only increase band clamping pressure and in the case of reducing sliding velocity Δ N, and reducing band clamping pressure and
In the case of increasing sliding velocity Δ N, the vibration mode (frequency) of self-excited vibration can be also set to change so that Vehicular vibration
And noise reduces.Therefore, by increasing sliding velocity Δ N according to transport condition suitably to reduce band clamping pressure, so as to
Sliding velocity Δ N is deviateed from predetermined scope, thus reduce the Vehicular vibration caused by self-excited vibration and noise, and
And by preventing the unwanted increase with clamping pressure, so that the deterioration of oil consumption rate is suppressed.
In addition, according to the present embodiment, sliding velocity Δ N within a predetermined range in the case of, according to the row of vehicle
Sail state and sliding velocity Δ N is gone above predetermined value B or less than predetermined value A, therefore sliding velocity Δ N can be made from predetermined
Scope deviate.Therefore, Vehicular vibration and noise are lowered.In addition, make sliding velocity Δ N according to the transport condition of vehicle
More than predetermined value B, so as to diminish with clamping pressure, therefore it is capable of the increase of anti-stop-band clamping pressure, and then make the evil of oil consumption rate
Change and be suppressed.
In addition, according to the present embodiment, it is less than sliding velocity Δ N with making a reservation in sliding velocity Δ N and predetermined value B difference L2
In the case of value A difference L1, sliding velocity Δ N is set to more than predetermined value B, thus make sliding velocity Δ N to predetermined value A with
And the nearer side movement in predetermined value B, so as to make sliding velocity Δ N rapidly deviate from predetermined scope.
In addition, according to the present embodiment, by making sliding velocity Δ N to the arrival predetermined value A from current sliding velocity Δ N
And the shorter side movement in arrival time T1, T2 needed for predetermined value B, can also make sliding velocity Δ N rapidly from
Predetermined scope deviates.
In addition, according to the present embodiment, in the case where sliding velocity Δ N is below predetermined value A, and in secondary pulley 62
Rotation speed change Δ Nout be more than predetermined value beta in the case of, predetermined value A diminishes.Self-excited vibration and the rotating speed of secondary pulley 62 become
Dynamic Δ Nout relations are deeper, and the rotation speed change Δ Nout with secondary pulley 58 becomes more big, and self-excited vibration becomes bigger
Tendency.In addition, self-excited vibration also can make characteristic change because the individual difference XOR of each vehicle changes by the time.Cause
This, although sliding velocity Δ N is more than the situation of predetermined value beta below predetermined value A, in the rotation speed change Δ Nout of secondary pulley 62
Under, to be also controlled in a manner of reducing predetermined value A and sliding velocity Δ N is turned into new below predetermined value A, so as to
Prevent Vehicular vibration and noise from becoming big situation because the individual difference XOR of each vehicle changes by the time.
In addition, according to the present embodiment, predetermined value A is set to make the rotation speed change Δ Nout of secondary pulley 62 to turn into advance
Value below the predetermined value beta of setting, therefore by making sliding velocity Δ N be controlled in below predetermined value A, so that self-excited vibration
Reduce, and then make the Vehicular vibration caused by self-excited vibration and noise reduction.
In addition, according to the present embodiment, predetermined value B be set to make by with sliding and the frequency of caused self-excited vibration from
The value that the frequency band of Vehicular vibration deviates, therefore by making sliding velocity Δ N be controlled in more than predetermined value B, so that passing through band
Sliding and the frequency of caused self-excited vibration deviates from the frequency band of Vehicular vibration.Therefore, by also will not because pass through band sliding institute
Caused self-excited vibration and Vehicular vibration is become big, therefore reduce Vehicular vibration and noise.
Next, other embodiments of the present invention are illustrated.In addition, in the following description, for it is above-mentioned
The common part mark identical symbol and the description thereof will be omitted of embodiment.
In the above-described embodiment, in the case where sliding velocity Δ N is more than predetermined value A and is less than predetermined value B, so that sliding
Speed Δ N is moved as below predetermined value A or more than predetermined value B mode and to band clamping pressure (i.e. principal pressure Pin, secondary
Pressure Pout) carry out feedback control.However, during sliding velocity Δ N is within a predetermined range, self-excited vibration is passed
Onto driving wheel 14, so as to produce Vehicular vibration and noise.Therefore, in the present embodiment, it is in predetermined in sliding velocity Δ N
In the range of during, in addition to the feedback control with clamping pressure, also make to be arranged on buncher 24 with driving
The CVT traveling clutches C2 of the change that can carry out torque capacity between driving wheel 14 is slided, so as to reduce to driving wheel 14
The transmission capacity of the vibration (self-excited vibration) of transmission.The speed Control portion 102 ' (reference picture 3) of the present embodiment is except band clamping pressure
Feedback control outside, also during untill sliding velocity Δ N reaches desired value Δ N*, make CVT traveling clutches
C2 slides target slippage SLIP* set in advance.In addition, target slippage SLIP* obtains beforehand through experiment or parsing,
And it is set to, by reducing the vibration to the transmission of driving wheel 14 so that driver will not be due to producing because of self-excited vibration
Vehicular vibration and noise and the value of the degree for the sense that do not feel well.In addition, CVT clutches C2 corresponds to the clutch of the present invention
Device.
Speed Control portion 102 ' calculates CVT travelings clutch C2 slippage SLIP at any time, and performs and be based on being calculated
The slippage SLIP and the CVT traveling clutches C2 of target slippage SLIP* deviation (SLIP*-SLIP) that go out feedback control
System.By performing above-mentioned control, so as to, with slip is produced in clutch C2, thus make what is transmitted to driving wheel 14 in CVT travelings
Vibration reduces.In addition, speed Control portion 102 ' makes CVT complete with clutch C2 when sliding velocity Δ N reaches desired value Δ N*
Engaging.
Fig. 7 is that the control action of the electronic-controlled installation 80 ' of other embodiments as the present invention is illustrated
Flow chart.When by Fig. 7 flow chart compared with above-mentioned Fig. 6 flow chart, only step has been added after step S9
S20, others control no any change.Hereinafter, mainly step S20 is illustrated.
In the figure 7, in the case where S6 makes negative evaluation, in S9, setting sliding velocity Δ N desired value Δ N*,
And band clamping pressure (principal pressure Pin, second pressure are performed in a manner of sliding velocity Δ N is followed desired value Δ N*
Pout feedback control).Next, in S20 corresponding with the function phase in speed Control portion 102 ', make CVT traveling clutches
Device C2 is slided, so as to reduce the self-excited vibration transmitted to driving wheel 14.Thereby, it is possible to reduce in the feedback control with clamping pressure
In caused Vehicular vibration and noise.
The effect same with the above embodiments can also be obtained by the present embodiment.In addition, it is in sliding velocity Δ N
In the case of in predetermined scope, by making the sliding velocity Δ N deviate from predetermined scope and making CVT traveling clutches
C2 is slided, and so as to reduce the transmission capacity for the self-excited vibration transmitted to driving wheel 14, is thus further reduced because of self-excited vibration
Caused by Vehicular vibration and noise.
Embodiments of the invention are described in detail based on accompanying drawing above, but the present invention is also applicable to other
Mode in.
For example, although in the above-described embodiment, power transmission 16 is to possess buncher 24 and tooth side by side
The device of mechanism 28 is taken turns, but the present invention may not be defined in this.For example, gear mechanism 28 is not necessarily necessary or sent out
Possesses the existing buncher of buncher 24 between motivation 12 and output shaft 30.
Although in addition, in the above-described embodiment, based on by hydrostatic sensor 98,99 and the principal pressure Pin that detects
And second pressure Pout, and whether the gear ratio γ to buncher 24 is that maximum gear ratio γ max judge, but
Can be right based on principal pressure Pin main instruction pressure Pintgt and second pressure Pout secondary instruction pressure Pouttgt
The gear ratio γ of buncher 24 is judged., can in the case where being judged by this way based on instruction pressure
Omit hydrostatic sensor 98,99.
Although in addition, in the above-described embodiment, it is used as the pre- of sliding velocity Δ N by learning control unit 110 to reduce
The predetermined value A of the lower limit of fixed scope, but can also further increase predetermined value A.For example, it is also possible in the following way,
That is, sliding velocity Δ N within a predetermined range in the case of, calculate secondary pulley 62 rotation speed change Δ Nout, in institute
In the case that the rotation speed change Δ Nout calculated is below predetermined value beta, increase predetermined value A.Thereby, it is possible to by learning to control
Portion 110 and make predetermined value A to increase side and reduce side both sides be adjusted.
Although in addition, in the above-described embodiment, based on vehicle-state judging part 103 in gear ratio γ, input torque
Tin, various rotating speeds etc. within a predetermined range in the case of be judged as performing Vehicular vibration and noise suppressed
Control.However, these parameters may not be defined in.For example, for 4WD (4Wheel Drive：Four-wheel drive) vehicle situation
Under, as long as the torque ratio for being switched to the situation of 4WD travelings or being distributed to secondary driving wheel has been exceeded to the feelings of predetermined value
The condition parameter associated with self-excited vibration as condition etc., it becomes possible to appropriate application.In addition it is also possible in the following way, i.e.
Vehicle-state judging part 103 is omitted, and performs the control suppressed to Vehicular vibration and noise all the time in CVT travelings
System.
In addition, an above-mentioned content only embodiment, the present invention being capable of knowing based on those skilled in the art
Know and implemented in a manner of being subject to various changes, improvement.
Claims (8)
1. a kind of control device of variable v-belt drive, the variable v-belt drive include head pulley, secondary pulley and
The transmission belt being reeved on the head pulley and the secondary pulley,
The control device includes the electronic-controlled installation calculated with sliding velocity to the transmission belt,
The electronic-controlled installation the sliding velocity within a predetermined range in the case of, the band of the transmission belt is pressed from both sides
Compaction forces are controlled, so that the sliding velocity deviates from predetermined scope.
2. control device as claimed in claim 1, wherein,
The predetermined scope is, set in advance, in the lower limit more than zero and more than between the higher limit of the lower limit
The region of the sliding velocity,
The electronic-controlled installation is in the case where the sliding velocity is in the predetermined scope, according to the traveling of vehicle
State and the band clamping pressure of the transmission belt is controlled so that the sliding velocity turn into the higher limit more than, or
Person makes the sliding velocity turn into below the lower limit.
3. control device as claimed in claim 2, wherein,
The electronic-controlled installation the sliding velocity be in the predetermined scope and the sliding velocity with it is described on
In the case that the difference of limit value is less than the difference of the sliding velocity and the lower limit, to the band clamping pressure of the transmission belt
It is controlled, so that the sliding velocity turns into more than the higher limit.
4. control device as claimed in claim 2, wherein,
The electronic-controlled installation is in the case where the sliding velocity is in the predetermined scope, to from current sliding
Speed plays the first arrival time untill the higher limit is reached and from current sliding velocity to reaching the lower limit
Untill the second arrival time inferred,
The electronic-controlled installation is being inferred as in the case that first arrival time is shorter than second arrival time, to institute
The band clamping pressure for stating transmission belt is controlled, so that the sliding velocity turns into more than the higher limit.
5. the control device as described in any one in claim 2 to 4, wherein,
In the case that the electronic-controlled installation is below the lower limit that the sliding velocity is the predetermined scope, and
In the case that the rotation speed change of the secondary pulley is more than predetermined value set in advance, the lower limit of the predetermined scope is subtracted
It is small.
6. the control device as described in any one in claim 1 to 5, wherein,
The variable v-belt drive possesses torque capacity can be changed between the secondary pulley and driving wheel
Clutch,
The electronic-controlled installation is in the case where the sliding velocity is in the predetermined scope, so that the clutch
The mode of slip is controlled to the clutch.
7. control device as claimed in claim 2, wherein,
The lower limit is set to, and makes the rotation speed change of the secondary pulley as the value below predetermined value set in advance.
8. control device as claimed in claim 2, wherein,
The higher limit is set to, and is made by deviateing and the frequency of caused vibration from the frequency band of Vehicular vibration with sliding
Value.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016-135502 | 2016-07-07 | ||
| JP2016135502A JP6414151B2 (en) | 2016-07-07 | 2016-07-07 | Control device for belt type continuously variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107588191A true CN107588191A (en) | 2018-01-16 |
| CN107588191B CN107588191B (en) | 2019-06-04 |
Family
ID=60948659
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710537959.2A Expired - Fee Related CN107588191B (en) | 2016-07-07 | 2017-07-04 | The control device of variable v-belt drive |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6414151B2 (en) |
| CN (1) | CN107588191B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110273989A (en) * | 2018-03-13 | 2019-09-24 | 上海汽车集团股份有限公司 | The method and apparatus that steel belt clamps control in a kind of stepless transmission |
| CN110715052A (en) * | 2019-10-28 | 2020-01-21 | 周翔 | Transmission speed change control system |
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| US20020095992A1 (en) * | 2000-11-30 | 2002-07-25 | Armin Gierling | Acoustic recognition of variator slip of a continuously variable transmission |
| CN103339416A (en) * | 2011-02-15 | 2013-10-02 | 日产自动车株式会社 | Speed change control device and control method for continuously variable transmission |
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| JP2001108082A (en) * | 1999-10-13 | 2001-04-20 | Toyota Motor Corp | Control device for winding transmission device |
| JP4415618B2 (en) * | 2003-09-12 | 2010-02-17 | トヨタ自動車株式会社 | Belt slip prediction device |
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| US20020095992A1 (en) * | 2000-11-30 | 2002-07-25 | Armin Gierling | Acoustic recognition of variator slip of a continuously variable transmission |
| JP5455790B2 (en) * | 2010-05-28 | 2014-03-26 | ダイハツ工業株式会社 | Starting clutch control device |
| CN103339416A (en) * | 2011-02-15 | 2013-10-02 | 日产自动车株式会社 | Speed change control device and control method for continuously variable transmission |
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| CN110273989A (en) * | 2018-03-13 | 2019-09-24 | 上海汽车集团股份有限公司 | The method and apparatus that steel belt clamps control in a kind of stepless transmission |
| CN110273989B (en) * | 2018-03-13 | 2021-09-21 | 上海汽车集团股份有限公司 | Method and device for controlling clamping of transmission steel belt in continuously variable transmission |
| CN110715052A (en) * | 2019-10-28 | 2020-01-21 | 周翔 | Transmission speed change control system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6414151B2 (en) | 2018-10-31 |
| CN107588191B (en) | 2019-06-04 |
| JP2018004044A (en) | 2018-01-11 |
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