CN101535110A

CN101535110A - Continuously variable transmission

Info

Publication number: CN101535110A
Application number: CNA2007800412974A
Authority: CN
Inventors: 克里斯托弗·约翰·格林伍德
Original assignee: Torotrak Development Ltd
Current assignee: Allison Transmission Inc
Priority date: 2006-09-26
Filing date: 2007-09-24
Publication date: 2009-09-16
Anticipated expiration: 2027-09-24
Also published as: KR101440848B1; JP2010505074A; JP2015007481A; DE112007002280T5; JP2018200115A; KR20090064590A; GB0618929D0; GB2455030B; GB0904809D0; CN101535110B; WO2008038043A2; GB2455030A; KR20140063777A; JP2017062039A; DE112007002280B4; JP6926379B2; WO2008038043A3

Abstract

The invention is concerned with control of a continuously variable vehicle transmission. The transmission in question is to have a variator (10) which is coupled between a rotary transmission input (32) and a rotary transmission output (46), to provide continuous variation in a transmission drive ratio, via a launch device such as a clutch (62; 68). The variator and the launch device are constructed and arranged to exert a required torque, defined by an input signal. In accordance with the invention, the same control signal is used to control both the variator torque and the torque capacity of the launch device. In such an arrangement, vehicle launch (i.e. moving away from rest) can be controlled in a straightforward manner by progressively raising the relevant control signal, preferably a hydraulic pressure signal. Further independent claims are including for applying traction load to races (20, 22) of the variator and for a method setting torque of the launch device (62; 68) higher than torque of the variator (10).

Description

Positive infinite variable driving device

Technical field

The present invention relates to positive infinite variable driving device (continuously variabletransmission, toric transmission).One aspect of the present invention relates to the control to launch device in this driving device (launch device) and change-speed box (variator).

Background technology

The device that in any positive infinite variable driving device, all has the stepless variation that realizes transmitting ratio.This device is called " change-speed box " here.

In vehicle transmission gear, it is ready to be necessary for " starting " (that is, vehicle being quickened so that it breaks away from the state of standing start).About this point, some drivings device depend on " launch device " of use such as power-transfer clutch.Power-transfer clutch is used for driving engine is separated with driven wheel when stationary vehicle.Move in order to make vehicle derailing standing start state, driving device is placed low gear, set driving engine producing suitable moment of torsion, and engage launch device gradually, thereby increase the speed that is driven wheel.Yet the management of this process may more complicated.

A kind of known alternative method is that output with change-speed box is applied to planet mixing gear (epicyclic mixing gear) in the positive infinite variable driving device technology, this makes the state that reaches so-called " geared neutral " become possibility, wherein driving device provides infinite speed effectively, and does not need physically driving device output to be separated with the driving device input.In such driving device, do not need such launch device.By transmission ratio (variator ratio) is removed and has been realized simply starting from " geared neutral " value.Yet this driving device must relate to the structural complexity of gear transmission aspect, and relates to some difficult problem about control.

It is useful distinguishing between the change-speed box to the change-speed box of " transmitting ratio control (ratio controlled) " and those " torque controls ".The change-speed box of transmitting ratio control has some transmitting ratios that are used to regulate himself to reach the physical mechanism of setting value.For example, known " semi-circular " rolling traction type (" half-toroidal " rolling-traction type) change-speed box typically uses a kind of like this valve, the part of this valve (for example, spool)) operationally be attached to variator roller, the position of these rollers is corresponding with transmission ratio, and another part of this valve (for example, forming the removable sleeve pipe of valve port) moves to the transmission ratio place of setting.The state of valve depends on the relative position of these two parts, and this valve control is applied to the pressure that acts on the piston/cylinder arrangements on the variator roller.The result obtains a hydro-mechanical feedback loop, and wherein valve constantly compares transmission ratio and expectation value, and then regulates transmission ratio so that it reaches this expectation value.The electronics package that is associated is selected the transmission ratio of expectation and will be represented the signal of this transmission ratio to be sent to driving device.

In the change-speed box of torque control, be not used in this physical unit that transmission ratio is adjusted to expectation value.Alternatively, change-speed box receives the control signal of the moment of torsion that a representative will produce.At the publication number such as Torotrak Development Limited (Torotrak Development Co., Ltd) is that this signal is taked the form of hydraulic pressure in the situation of the known loopful shape change-speed box described among International Patent Application PCT/GB2005/03098 of WO 2006/027540.In response to this signal, change-speed box produces the moment of torsion that needs in its I/O place.The actual transmission that can allow change-speed box is than automatically changing, to adapt to the velocity variations that this torque applications is caused in relevant inertia (relevant inertia).Therefore, at the pusher side/input side that starts of driving device, the moment of torsion that is produced by change-speed box and the summation of engine output torque have determined to act on the clean moment of torsion on the rotor inertia of driving engine and associated components, and have determined engine acceleration thus.At the wheel side/outgoing side of driving device, the moment of torsion that produces by change-speed box with because the summation of the moment of torsion that the outside of brake, road gradient etc. applies has determined to can be used to the clean moment of torsion to vehicle acceleration itself.Follow the variation of transmission ratio in the consequential velocity variations of input and output place, and change-speed box automatically adapts to these variations.

In the loopful shape rolling traction change-speed box of known torque control type, change-speed box is used for producing " reaction torque (the reaction torque) " corresponding to control signal.Reaction torque is the summation of the moment of torsion of gear box input and output place.On a 50-50 basis, reaction torque can be defined as and must work to prevent the moment of torsion of its rotation to erection of transmission seat (mounting).

Typically, change-speed box depends on the traction between the turning unit that is used for transferring power (drive drives).For example, in the situation of ring raceway (toroidal-race) rolling traction change-speed box, roller frictionally engages with the variator races that annular is recessed into, and by this frictional engagement, power is passed to gearbox output with variable-speed ratio from gear box input.For the traction between roller and the raceway is provided, must make their bias voltages towards each other.Be used for producing the biasing force that draws and be called " drawbar load " at this at change-speed box.In principle, can use fixing drawbar load.Yet this need be set at drawbar load sufficiently high value to be avoided the excessive slip between all situations lower roller and the raceway.Therefore, selected traction load value will be excessive for most applications, thereby cause the too early wearing and tearing of lower energy efficiency and rolling member.Therefore, make drawbar load along with the moment of torsion that applies as one man changes usually.More specifically, in the change-speed box of torque control, drawbar load typically changes pro rata with reaction torque.This has the advantage that constant traction coefficient is provided.Sometimes must regulate drawbar load very apace, in the situation of unexpected " transition " incident (such as emergency brake), slide preventing.In some existing systems, this realizes by using hydraulic efficiency gear to apply drawbar load.Particularly, the hydraulic pressure that will be supplied to control plunger (these pistons are attached to variator roller) also leads to the hydraulic actuator that is used to produce drawbar load, thereby the power and the drawbar load that are applied to variator roller are as one man changed.

In such hydraulic efficiency pressure system, the motion of hydraulic pressure " terminal point block (end stop) " with the limiting transmission roller is provided usually, thereby prevents from these variator roller are driven the disengaging raceway.For example, this can realize by such layout: when arriving the terminal point of its predetermined stroke for one in the above-mentioned piston, comprise fluid egress point on the hydraulic actuating cylinder of this piston by this piston sealing itself, and the pressure increase that produces in the hydraulic actuating cylinder is used for stoping the motion of piston.The pressure that increases also is applied to traction load actuator, if will being cooperated by the respective change of drawbar load, the variation of the reaction torque that produces owing to the effect of terminal point block (do not produce slip if do the time spent at block, the respective change of drawbar load is necessary so), the pressure of Zeng Jiaing must be applied to traction load actuator so.

Summary of the invention

The object of the present invention is to provide a kind of improved CVT.More specifically (but needing not to be uniquely) the object of the present invention is to provide the simple CVT of a kind of structure and mode.

According to a first aspect of the invention, has a kind of vehicle positive infinite variable driving device, it comprises the rotation input that can be connected to rotating driver, can be connected to the rotation output of wheel, be connected between rotation input and the rotation output so that the change-speed box of stepless variable drive ratio to be provided, and be arranged to optionally connect/separate the rotation input and rotate the launch device of exporting, change-speed box is configured and is arranged to apply the moment of torsion that needs, and launch device is configured and is arranged to provide torque peak (the torque capacity that needs, torque capacity), this driving device is characterised in that, this driving device comprises control setup, this control setup is sent to the moment of torsion that change-speed box needs with setting with identical control signal, and is sent to launch device to set its torque peak.

The torque peak of launch device (this device can adopt the form of power-transfer clutch) is can be passed to change-speed box and by the torque peak of the degree of engagement of power-transfer clutch decision, for example in the hydraulic-driven power-transfer clutch by the fluid pressure decision that applies.By using common control clutch of mono-signal and transmission torque, not only be used for driving device control devices needed and simplified significantly, and the control of launch process is more prone to.

According to a second aspect of the invention, have a kind of change-speed box, it comprises: the recessed raceway of at least one pair of part annular, and the variator cavities of a cardinal principle annular of the common qualification of these raceways and they are installed on a common variator axis rotates; And at least two rollers, these rollers are arranged between the raceway with running on the recessed surface of the part annular of raceway and thus with transmission ratio transferring power between raceway, these rollers are installed by this way, promptly allow them to tilt to change the degree of dip of raceway axis with respect to variator axis, thereby and the stepless change of permission transmission ratio, this change-speed box is characterised in that, one of them raceway of change-speed box is attached to an adapter shaft by the mechanical traction force-input device, this mechanical traction force-input device both had been used for transfer torque between adapter shaft and variator races, also be used on raceway, applying drawbar load power (function of the moment of torsion that this power is transmitted), drawbar load power is ordered about variator races and is engaged with roller, to provide transferring power needed traction, and it is characterized in that this change-speed box comprises restriction roller bevelled machinery meeting device (mechanical abutment).

The combination of mechanical traction force-input device (replacement hydraulic efficiency gear) and mechanical end block (replacing hydraulic pressure terminal point block) is highly beneficial.The drawbar load that machinery produces can change along with the speed of needs.Because this drawbar load produces in response to acting on the moment of torsion on the associated transmissions raceway, rather than produce in response to the power that is applied to roller, so the variation of the transmission torque that is produced by the effect of terminal point block automatically causes the suitable variation of drawbar load, and does not need terminal point block itself operatively is attached to the traction force-input device.

According to a third aspect of the invention we, method with a kind of control vehicle positive infinite variable driving device, this driving device comprises: can be connected to the rotation input of rotating driver, can be connected to the rotation output of wheel, be connected between rotation input and the rotation output so that the change-speed box of stepless variable drive ratio to be provided, and the launch device that optionally connection/separation rotation is imported and rotation is exported, this control method comprises: control this change-speed box so that the reaction torque of expectation to be provided, and as one man control the torque peak of launch device with exercised over variator reaction torque, so that the moment of torsion that is applied to launch device by change-speed box is always less than the torque peak of launch device.

Therefore, simplified the co-operative control of the torque peak of reaction torque and launch device.In addition, by little by little increasing the torque peak of exercised over variator reaction torque and launch device, the very favorable method that this method is started management is convenient more, the torque peak of launch device always surpasses the moment of torsion that is applied to this launch device by change-speed box, till stopping at least to the slip of launch device, thereby until then, driving device keeps its fastest ratio by be passed to (refer to) its moment of torsion by launch device always.

Description of drawings

Referring now to accompanying drawing, only specific embodiments of the invention are described in the mode of example, in the accompanying drawings:

Fig. 1 is the scheme drawing of positive infinite variable driving device (" CVT ") constructed according to the invention;

Fig. 2 a is the more detailed view of the traction force-input device that uses in CVT seen along radial direction;

Fig. 2 b is the transparent view of variator races, wherein shows the back side of this raceway;

Fig. 3 is the scheme drawing of the hydraulic control device of CVT; And

Fig. 4 shows some parts of the change-speed box of seeing along axial direction that uses in CVT.

The specific embodiment

Fig. 1 shows the CVT of the change-speed box 10 that uses the ring raceway rolling traction type.More specifically, this is the loopful shape change-speed box of a two-chamber.This change-speed box has the first input raceway 12 and the second input raceway 14, and these two raceways have semi-circular

recessed surface

16,18 separately.Between these input raceways is the first output raceway 20 and the second output raceway 22, and these two raceways also have semi-circular

recessed surface

24,26 separately, thereby between the first input raceway 12 and the first output raceway 20, be formed with first annular chamber 28, and between the second input raceway 14 and the second output raceway 22, be formed with second annular chamber 30.These raceways have the common axis of rotation line that is limited by main shaft (by 32 schematically indications), and these raceways rotate around above-mentioned main shaft.

Each

chamber

28,30 all comprises set of

rollers

34,36 separately.Each roller all is mounted to around rotating such as 38 roller axis, and each roller all moves on the annular surface of input raceway that is associated with it and output raceway, so that power is transmitted to another raceway from a raceway.The mount pad of these rollers (not shown among Fig. 1, but will briefly describe) also allow roller to change its degree of dip according to the variation of transmission ratio, the angle between roller axis 38 and the main shaft 32 promptly changed.Main shaft 32 is as the rotation input of change-speed box, and to the rotating driver such as driving engine, it takes the form of combustion engine (schematically illustrated by 40) in this specific embodiment to connect (directly connect or by the intermediate gear driving coupling, not shown).The dissimilar rotating driver of use such as electrical motor, external combustion engine etc. also can be realized the present invention equally well.The

input raceway

12,14 of change-speed box is fixed to main shaft 32, thereby along with main shaft rotates together, and therefore drive by driving engine 40.

Output raceway

20,22 can rotate with respect to main shaft 40.In the illustrated embodiment, this is realized that by

cylindrical bearing

42,44 these output raceways are installed in respectively on the main shaft 32 by cylindrical bearing.By

roller

34,36 power is passed to output raceway 20,22 (perhaps vice versa, under " hypervelocity (over-run) " state) with variable-speed ratio from input raceway 12,14.

Output raceway

20,22 can operationally be attached to the final transmission 46 of leading to wheel, and this will be described briefly.

In the change-speed box 10 that illustrates, by machinery (non-hydraulic pressure) traction force-input device 48 drawbar load is provided, this traction force-input device be used for with the proportional power of the output torque of change-speed box (" drawbar load ") bias

voltage variator races

12,14,16,18 so that these raceways engage with variator roller 34,36.This realizes away from each other by ordering about two innermost raceways (in the illustrated embodiment, these two raceways are

output raceways

20,22).By

roller

34,36 drawbar load is passed to outmost raceway (in the present embodiment, these outmost raceways are input raceways 12,14), and these raceways guide power into main shaft 32 again, main shaft is in the tension state thus.By by this way drawbar load being guided into main shaft 32, without any need for the thrust baring of opposing drawbar load.

Traction force-input device 48 uses simple slope device (ramp arrangement) to transmit output torque, and this slope device produces the drawbar load along axial direction, this drawbar load by the function of transfer torque (and more specifically, in the present embodiment, with proportional) by transfer torque.

Fig. 2 a and Fig. 2 b have illustrated the structure of traction force-input device 48.Output driven gear 50 is mounted to the back side of output raceway 22 regularly.On its surface away from output raceway 22, this output driven gear 50 has one group of ramp-like recesses, shown in dotted line (phantom) 52 among Fig. 2 a.Output raceway 20 has corresponding one group of ramp-like recesses 54 on the back side of himself, illustrate best in Fig. 2 b.When the circumferential direction in Fig. 1 is seen, the cross section that these

recesses

52,54 have part circular, to hold roller 56, these rollers form ball in this embodiment.When radial direction is seen, these

grooves

52,54 seem to have the shape of shallow " V " shape.As shown in Fig. 2 a, when the darkest regional alignment of

groove

52,54, the interval minimum of output driven gear 50 and output raceway 20, thus these balls 56 will himself be positioned in these zones.Yet, when the needs gearbox output is kept a moment of torsion, consider what's going on.It should be noted that output raceway 20 can rotate with respect to output driven gear 50 by bearing 42,44.Because output torque causes the relative rotation of these parts, so the darkest zone of

recess

52,54 is no longer aimed at, and these balls 56 are advanced (ride on) on " V " shape recess thus, thereby thereby force output raceway 20 also to produce the drawbar load that needs away from output driven gear 50.When the drawbar load that produces during by the equilibrium of torques that transmitted, this relatively rotates and stops.Therefore, as previously mentioned, drawbar load is the function of output torque.The definite characteristic of this function depends on the structure of

recess

52,54, but in the illustrated embodiment, drawbar load and output torque are proportional.

Shown driving device can provide D Drive gear (forward gear) and reverse gearwheel (reverse gear) (in other words, its can reverse the hand of rotation of final transmission 46).This is by providing two paths to realize for the takeoff output from output raceway 20,22.First path is through being formed on first group of tooth 58 on the output driven gear 50, output driven gear is by messenger chain driving chain gear (chain gear) 60, for the sake of clarity, in Fig. 1, omitted messenger chain, but messenger chain moves on tooth 58 and sprocket gear 60.And sprocket gear 60 operationally is attached to a side of forward gear clutch 62, and the opposite side of forward gear clutch operationally is attached to final transmission 46.Be used for obtaining second path of takeoff output through being formed on second group of tooth 64 on the output driven gear 50.These teeth 64 and gear 66 engagements, this gear 66 operationally is attached to a side of reverse clutch 68, and the opposite side of reverse clutch operationally is attached to final transmission 46.It should be noted, be used to obtain

first path

58,60,62 of takeoff output because it uses chain-driving, so the reversing of hand of rotation is not provided.

Second path

64,66,68 that is used to obtain takeoff output is because it uses a pair of gear, so produce the reversing of direction.Thus, the joint of forward gear clutch 62 makes final transmission produce rotation along a direction, and the joint of power-transfer clutch 68 makes final transmission produce rotation along opposite direction.It should be noted that in this specific embodiment, forward gear clutch 62 and reverse clutch 68 are constructed to prevent the mode that they engage simultaneously.

Final transmission 46 comprises the wheel word 70 that finally leads to the wheel (not shown).

As noted above, omitted the mount pad that is used for

roller

34,36 among Fig. 1.A kind of suitable form of mount pad has been shown among Fig. 4.In this figure, in

variator races

12,14,20 or 22 can be seen, two

rollers

34 or 36 can also be seen.Their position is changed by control lever 72, and this control lever is pivotably mounted on the fulcrum 74, and fulcrum is contained in the groove 76 of control lever.The control lever has a radially-protruding substantially throw of lever 78, and this throw of lever and crossbeam 80 are integrally formed inverse-T-shaped to form.Spherical coupling (the ball coupling) 82,84 that is positioned at the relative end of crossbeam 80 connects crossbeam with corresponding roller bracket (roller-bearer) 86,88, the roller bracket carrying also is rotatably mounted corresponding roller.Should also be noted that two spherical couplings 82,84 are not in (though can't see) in the common sagittal plane in Fig. 4.In Fig. 1, the sagittal plane of annular chamber 30 centers is by dotted line 90 indications.Two spherical couplings 86,88 leave this centre plane 90 separately and are provided with and are on the opposite side of this centre plane, so that the line from the center of each spherical coupling to the center of each

roller

34,36 tilts towards this sagittal plane.This degree of dip is known as " kingpin caster angle (castor angle) ".When control lever 72 moves, it is evident that from accompanying drawing two rollers all correspondingly deasil or widdershins move around the axis of main shaft 32.When roller moved like this, it was subjected to the domination (in mode known to those skilled in the art) of the steering-effecting of variator races.Thereby two rollers are all aforesaid relatively, pass the line/axis of spherical coupling center and roller centre and tilt.The steering-effecting that acts on the roller always trends towards making it to form a leaning angle, wherein the axes intersect of the axis of roller and main shaft 32.Because kingpin caster angle, the leaning angle that provides this to intersect always can be provided for they.The result is that the inclination of roller (and transmission ratio thus) is the function of the position of control lever 72.

Importantly, the load that is produced by each roller equates, and in the device of Fig. 4, control lever 72 has allowed the equilibrium of roller load along moving of the cardinal principle that is limited by groove 76 direction radially.

Use actuator 92 that controlled bias power is applied to throw of lever 78.In the present embodiment, actuator 92 is double acting hydraulic efficiency gear.In other words, actuator receives two relative hydraulic pressures, and its power that applies is by the difference decision of these two pressure, thereby it can be shifted to the left side or shift to the right side in Fig. 4.It is also noted that, control two

variator cavities

28,30 lever 72 separately with the mono-actuator in the present embodiment.Though in Fig. 4, can't see the second control lever, it should be understood that bar 94 leads to another lever from a control lever 72, and the piston 96 of actuator 92 connect the mid point of bar so far pivotly.Therefore, the position of piston 96 is corresponding to the position of the mid point of bar, but the relative position of two control levers can change a little, because need the roller between two chambeies of balance to load.

The hydraulic efficiency gear that is used for controlling CVT is described referring now to Fig. 3.In this figure, frame 98 schematically shows the device of the hydraulic fluid that is used to provide adjustable pressure.For those skilled in the art, realize that the suitable means of this purpose are known.This pressure leads to change-speed box change-over valve 100, and by this change-over valve, pressure can be applied to the either side of piston 96, so that promote control lever 72 on a direction or another direction.In Fig. 3, show one and lead to the tapping equipment (exhaust) of fuel tank 102 from the piston low pressure side, although all become emptyly in practice for fear of relevant chamber, alternately, tapping equipment also can lead to low pressure source.Actuator 92 applies power to two control levers 72, and the size of this power is determined by pressure source of supply 98, and the direction of power is by 100 controls of change-speed box change-over valve.By regulating this power, can control exercised over variator reaction torque.

Pressure from source of supply 98 also leads to power-transfer clutch selector valve 104.This valve is used for above-mentioned hydraulic pressure optionally is applied to forward gear clutch 62, perhaps is applied to reverse clutch 68.Inactive clutch green phase valve together is to fuel tank 102 dischargings.Thus, power-transfer clutch selector valve 104 determines that drivings device are in running under the D Drive state or turn round under the reverse gear state, and the power of pressure source of supply 98 when determining effective clutch engagement, and determines the torque peak of effective power-transfer clutch thus.When vehicle was in neutral gear, pressure source of supply 98 was used for optionally separating these parts with disconnecting valve 105 between the power-transfer clutch selector valve 104.

As noted above, some devices are set usually to limit minimum and maximum transmission ratio.When not having these devices, to such an extent as to will exist

roller

34,36 over-tiltings to leave the danger of

variator races

12,14,20,22, thus potential catastrophic consequence had.As noted above, this in the prior art " terminal point block " typically the mode with hydraulic pressure realized.Yet, illustrate among the embodiment of the present invention, when roller moves, can place simple electromechanical stop.Particularly, these stop limits are used for controlling the motion of the

single actuator

92,96 of all rollers.In principle, block can be taked many multi-form, but it is shown as the energy disperser 106,108 actuator 92 in Fig. 3, and when the terminal point of piston 96 its strokes of arrival, this energy disperser is the butt piston simply.

The area of piston 96 and the area of the piston in forward gear clutch 62 and the reverse clutch 68 (be can't see latter two piston in the accompanying drawing, and the structure of suitable power-transfer clutch is known for a person skilled in the art) be selected to the output torque that the torque peak of guaranteeing effective power-

transfer clutch

62,68 surpasses change-speed box, the two all receives the identical hydraulic pressure from source of supply 98 certainly.Therefore, consider in the vehicle startup process, to have taken place any situation.Before starting, the pressure that is supplied to power-transfer clutch selector valve 104 is discharged by disconnecting valve 105.The neither one power-transfer clutch engages, and therefore wheel separates with change-speed box.In order to begin to start, setpoint clutch selector valve 104 is to realize D Drive or reverse gear, and pressure source of supply 98 is set at suitable low value, the state of disconnecting valve 105 is changed over this pressure is applied to relevant power-transfer clutch.Because the torque peak of power-transfer clutch always surpasses the output torque of change-speed box, so initial change-speed box will be forced to adopt its fastest ratio, this fastest ratio is determined by end stop buffer 106.No matter change-speed box change-over valve 100 is in any state, this all will take place, but any " the vexed sound " that produces when avoiding owing to clutch moment of torque change-speed box being urged to the terminal point of its gear range in fact, change-over valve 100 also are set as at first and order about change-speed box and reach its fastest ratio.

Effectively the joint of power-transfer clutch is applied to driven wheel with moment of torsion, and vehicle begins to quicken thus.Sometime, the state of change-speed box change-over valve 100 changes in launch process, thereby the hydraulic pressure that applies trends towards ordering about piston 96 away from its energy disperser 106, to increase transmission ratio.The time selection of this variation is inessential, as long as this variation takes place when effective clutch slip, because at this moment, under any circumstance change-speed box all will remain on its fastest ratio place by effective power-

transfer clutch

62 or 68 moments of torsion that apply.When vehicle quickens, increase gradually from the pressure of source of supply 98, and sometime effectively the slip of power-transfer clutch stop.After this, increasing continuously of hydraulic pressure can make piston 96 move away its end buffer 106, thereby transmission ratio can and increase along with the vehicle acceleration.

In acceleration and brake process afterwards,, do not slide so do not expect effective power-transfer clutch because be applied to the torque peak of the load of effective power-transfer clutch by change-speed box less than effective power-transfer clutch.

Effect has provided a kind of like this driving device, wherein can control the management of starting in very direct mode, and this driving device is showing the remarkable simplification that is better than known CVT aspect its hydraulic efficiency gear.

Modern power actuated vehicle typically uses electronics package to realize the coordination strategy that change-speed box and driving engine are controlled.Here, consider CVT is controlled by this way.In this example, two amounts the most basic will controlling are exercised over variator reaction torque (being set by pressure source of supply 98) and engine output torque (being set by the torque demand that is supplied to engine controller).

The foregoing description only provides in the mode of example, and it is evident that for technical personnel, and the present invention can implement with multitude of different ways in practice.For example, the embodiment that illustrates uses mechanical meeting device to limit the stroke of roller, the transmitting ratio of limiting transmission thus.Yet, known in the art be alternatively to use hydraulic efficiency gear, wherein the outlet on the actuator 92 is formed in the side of its hydraulic actuating cylinder, thereby piston excessively advancing on either direction all will be closed this outlet, thereby and provides the function of terminal point block.The device of same-type also can be used to realize the present invention.Similarly, although the embodiment that illustrates adopts mechanical ball and slope device that drawbar load is provided, this function also can utilize hydraulic efficiency gear to realize in other embodiments.Well-knownly be, for example, to actuator 92 with act on one of them variator races on hydraulic piston/identical pressure of hydraulic cylinder device supply so that end load to be provided, then can realize same function in an embodiment of the present invention.

Claims

1. vehicle positive infinite variable driving device, comprise the rotation input that can be connected to rotating driver, can be connected to the rotation output of wheel, be connected between described rotation input and the described rotation output so that the change-speed box of stepless variable drive ratio to be provided, and the launch device of being arranged to optionally connect/separate described rotation input and described rotation output, described change-speed box is configured and is arranged to apply the moment of torsion that needs, and described launch device is configured and is arranged to provide the torque peak that needs, described driving device is characterised in that, described driving device comprises control setup, described control setup is sent to described change-speed box setting the moment of torsion of described needs with identical control signal, and is sent to described launch device to set the torque peak of described launch device.

2. positive infinite variable driving device according to claim 1, wherein, the structure of described change-speed box and described launch device makes the torque peak of power-transfer clutch always surpass the output torque that is applied by described change-speed box.

3. vehicle positive infinite variable driving device according to claim 1 and 2, wherein, described control signal is a hydraulic pressure.

4. according to each described positive infinite variable driving device in the aforementioned claim, wherein, described launch device comprises power-transfer clutch or drg.

5. positive infinite variable driving device according to claim 3, wherein, described hydraulic pressure is applied to the hydraulic actuator of described change-speed box, and has determined to be applied to the power of the removable torque transfer member of described change-speed box.

6. positive infinite variable driving device according to claim 3, wherein, described change-speed box have on a pair of raceway running with moment of torsion from a raceway be passed to another raceway removable roller, be attached to described roller power being applied to the hydraulic actuator of these rollers, and described hydraulic pressure is applied to described hydraulic actuator to determine described power.

7. positive infinite variable driving device according to claim 7, wherein, described change-speed box further comprise be attached in the described raceway one to transfer a torque to this raceway/from the traction force-input device that this raceway passes out, described traction force-input device is configured and is arranged to and will be applied to described raceway by the determined drawbar load of the moment of torsion of its transmission.

8. positive infinite variable driving device according to claim 7, wherein, described traction force-input device comprises first parts and second parts, and described first parts and second parts are installed into around a common rotational and are so shaped that parts cause the longitudinal travel of parts with respect to another parts with respect to the rotation of another parts.

9. change-speed box comprises: the recessed raceway of at least one pair of part annular, described raceway is common limit one substantially the variator cavities and being installed on a common variator axis of annular rotate; And at least two rollers, described roller is arranged between the described raceway with running on the recessed surface of the part annular of described raceway and thus with transmission ratio transferring power between described raceway, described roller is installed by this way, this mode allows described roller to tilt to change the degree of dip of roller axis with respect to described variator axis, thereby and the stepless change of permission transmission ratio, described change-speed box is characterised in that, one of them raceway of described change-speed box is attached to an adapter shaft by the mechanical traction force-input device, described mechanical traction force-input device not only is used for transfer torque between described adapter shaft and described variator races, also be used on described raceway, applying drawbar load power, the function of the moment of torsion that described drawbar load power is transmitted, described drawbar load power is ordered about described variator races and is engaged with described roller, to provide transferring power needed traction; And described change-speed box comprises restriction roller bevelled machinery meeting device.

10. change-speed box according to claim 9, wherein, described traction force-input device comprises first parts and second parts, and described first parts and second parts are installed into around a common rotational and are so shaped that parts cause the longitudinal travel of parts with respect to another parts with respect to the rotation of another parts.

11. change-speed box according to claim 10, wherein, described first parts of described traction force-input device comprise: at least one cam face, and described cam face is along circumferentially extending and to plane inclination radially; And at least one driven member, described driven member is advanced on described cam face and described second parts is exerted pressure.

12. according to each described change-speed box in the claim 9 to 11, wherein, described roller operationally is attached to a hydraulic piston/hydraulic cylinder device, and described mechanical meeting device is oriented to the described piston of butt limiting the stroke of described piston, and limits roller thus.

13. the method for a control vehicle positive infinite variable driving device, described positive infinite variable driving device comprises the rotation input that can be connected to rotating driver, can be connected to the rotation output of wheel, be connected between described rotation input and the described rotation output so that the change-speed box of stepless variable drive ratio to be provided, and the launch device of being arranged to optionally connect/separate described rotation input and described rotation output, described method comprises: control described change-speed box so that the reaction torque of expectation to be provided, and as one man control the torque peak of described launch device with described exercised over variator reaction torque, so that the moment of torsion that is applied to described launch device by described change-speed box is always less than the described torque peak of described launch device.

14. method according to claim 13, this method comprise identical control signal is sent to described change-speed box and described launch device.

15. according to claim 13 or the 14 described methods that are used for vehicle transmission gear, comprise by the torque peak that little by little increases exercised over variator reaction torque and described launch device and come starting of management vehicle, the described torque peak of described launch device always surpasses the moment of torsion that is applied to described launch device by described change-speed box, at least till the slip of described launch device stops, thereby until then, described driving device keeps its fastest ratio by the moment of torsion that is passed to described driving device by described launch device always.