CN101006290A - Belt-driven conical-pulley transmission, method for producing it, and motor vehicle having such a transmission - Google Patents
Belt-driven conical-pulley transmission, method for producing it, and motor vehicle having such a transmission Download PDFInfo
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- CN101006290A CN101006290A CN200580028573.4A CN200580028573A CN101006290A CN 101006290 A CN101006290 A CN 101006290A CN 200580028573 A CN200580028573 A CN 200580028573A CN 101006290 A CN101006290 A CN 101006290A
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Abstract
The invention relates to a variator 1 of conical disk twist contact device, having pairs of conical disk of the power input side and on the output side, each disk pair has an axially fixed disk 4 and an axially movable disk 5, 33. The disks are carried on shafts on respective shafts on the power input side and on the output side 3 and transmite torque via connected by a twist contact device 2, wherein optimizing at least one factor of following factors in acoustics aspect of the variator: oil type viscous or hydraulic medium, surface characteristic of contact area between the conical disk and the twist contact device, at least one geometry of the conical disk, at least one damp of the conical disk, at least one guide of the conical disk.
Description
The present invention relates to the automatic transmission of conical pulley flexible drive transmission form, for example disclosed by DE 10 2,004 015 215 and other open source literature, and relate to method that is used for its manufacturing and the Motor Vehicle of equipping it.
Automatic transmission is a specific character torque-converters (Kennungswandler) on wider meaning, its current gear ratio automatically according to the working state of current or expectation, as partial load, propelling and enviromental parameter, as temperature, air pressure, humidity of the air have level ground or infinitely change.Belong to the such characteristic torque-converters of having of it: pneumatic based on electronic, fluid power, the principle of hydrostatic pressure or based on the characteristic torque-converters of the principle of the mixing of these principles.
Automation then relate to different functions, as the starting, gear ratio is selected, the mode that gear ratio changes in the different operating state wherein for example can be regarded as each retaining level for shifting gears of gear ratio and one after the other changes, changes the saltus step of retaining level and the speed of adjusting.
Determined the degree of automation in other words, have how many functions automatically to carry out for the requirement of travelling comfort, reliability and selectable construction cost.
Usually the driver can manually intervene the operation of automation or it is limited on some individual features.
As mainly employed in Motor Vehicle is made now, automatic transmission in a narrow sense has following structure usually:
The starting unit that has a can regulate clutch form at the driving side of speed changer, the friction clutcch of wet type or dry type for example, the clutch of fluid power or fluid torque converter.
Usually be connected a bridging clutch in parallel with pump and turbine part for fluid torque converter, this bridging clutch has improved efficient and has come damped vibration by definite slip when the critical revolution by direct power transmission.
Starting unit drives a machinery, stepless or the speed change gear of level is arranged, and this speed change gear can comprise the unit that moves ahead/move backward, and main group, a zone are organized, fast block group (Splitgruppe) and/or a stepless speed variator.The gear-shift transmission group is decided to be designed to have the middle shaft type or the planetary structure of straight-tooth or helical teeth on running stability, position situation and transmission possibility.
The output block of mechanical transmission, i.e. axle or direct geared ground or drive a differential transmitting linkage indirectly by jack shaft or intergrade with constant gear ratio, this differential transmitting linkage can be used as independent transmission device and constitutes or an integrated constituent element of automatic transmission.This speed changer is suitable for the vertical and horizontal installation on Motor Vehicle in principle.
For the gear ratio of regulating mechanical transmission can be provided with hydrostatic pressure, pneumatic and/or electronic actuator.Be provided for the pressure oil of starting unit, especially hydraulic power unit according to the oil hydraulic pump of extrusion principle work, be used for the pressure oil of the lubricated and cooling hydrostatic pressure executive component and that be used for system of mechanical transmission.Can consider gear pump calmly on required pressure and delivery volume, volute pump, vane pump and reciprocating pump, the latter is generally the radial structure mode.Use gear pump and radial piston pump for this purpose in practice, wherein gear pump is because its construction cost is little and radial piston pump has advantage owing to its stress level height and controllability are good.
Oil hydraulic pump can be arranged on the arbitrary position of speed changer and on a main shaft or countershaft that is continued to drive by driver element.
Disclose stepless automatic transmission, it is made up of a starting unit, conduct move ahead/the move backward reversible transmission device of planetary pinion (Planetenwendegetriebe) of unit, an oil hydraulic pump, a stepless speed variator, a jack shaft and differential mechanism.Stepless speed variator is made up of reaching a winding contact device two awl dishes again.Each awl dish is to comprising second an awl dish that can move in the axial direction.Twine contact device these awl dishes between operation, this windings contact device for example can be propelling crawler belt (Schubgliederband), tow chain or belt.
The operating radius that twines contact device by the mobile change of the second awl dish reaches the gear ratio that changes stepless automatic transmission thus.
CVT (continuously variable transmission) needs high stress level, so that the awl dish of stepless speed variator be can be adjusted on all working point with required speed, and does not have wearing and tearing ground transmitting torque as far as possible with enough basic compaction pressure in addition.
In Motor Vehicle, the requirement of travelling comfort is very high usually, also relates to acoustic connection particularly.Especially automobile driver and occupant do not wish noisy noise in the Motor Vehicle of top grade, and these noises are that the work by the unit of Motor Vehicle forms.Yet internal-combustion engine and other unit such as speed changer produce noise, and these noises can be used as to a great extent to disturb and are felt.For example in the infinitely variable speed changer, use under the situation that connects leaf chain to cause noise, because this connection leaf chain is because the structure of its connecting plate and pin is bumped the impact that produces repetition on the awl dish of speed changer by pin in speed changer work.Acoustic effect enters (" impact ") owing to the pin as excitation source usually in the CVT speed changer.This acoustic excitation then produces resonance on the natural frequency of case of transmission (FE model (FE-Moden)) or axle (reversing mould (torsionale Moden), bending die (Biegemoden)).
Another acoustic effect is for the CVT chain, and this chain can produce vibration on section that clamps or reversion Duan Ruyi side, and this for example can prevent by slide rail.The tearing when frictional vibration that reverses for example is known as frequency from clutch and is 10Hz.When being changed to friction factor and descending of friction factor under slippage change situation, will motivate and tear.At first steel-paper friction factor is important relevant on automatic transmission.
A part task as basis of the present invention is that the acoustic effect that improves this speed changer reaches travelling comfort, especially the noise suppression sound travelling comfort of improving the Motor Vehicle that this speed changer is housed thus.Another part task as basis of the present invention is, take the suitable measure that tackles according to the strong CVT VIBRATION ANALYSIS of high frequency and the relative clarification of respective action mechanism, so that minimize or the main this vibration in the audio region of the 400-600Hz order of magnitude of inhibition as far as possible.Another part task of the present invention is that the working strength that improves parts reaches the operating life that prolongs this automatic transmission thus.Another part task of the present invention is, improves the torque transfer capability of this speed changer or the parts by speed changer can transmit bigger power.Be that another part task-this speed changer should be made economically in addition-also.
This task will by described in claims and in specification and summary the present invention of describing with reference to the accompanying drawings with and further configuration solve.
Obtained understanding by analysis to the emulation of the type of vibration mode, this vibration mode relates to and the tumbling and/or the motion of the chain of the crooked winding that interrelates in contact of corresponding mantle dish, and conclusive for vibration frequency at first is to tumble and flexural rigidity whole resisting of chain quality and mantle dish.Be appreciated that this rigidity comprise awl dish itself the tumbling of dish structure, awl dish, axle since its flexible bending and axle because the inclination of different support stiffnesses.In addition, friction factor level and friction factor variation and rotating speed and gear ratio are conclusive for frequency.
This understanding is beat all in this respect, but because in twining the contact segmental arc-be during it is clamped in the awl dish group-vibration of chain be not described so far and with the viewpoint of holding so far, promptly in this segmental arc, be contradiction with this vibration of rubbing contact damping of awl dish.
And CVT oil was not described so far to the influence of this frictional vibration yet, so that should only be improved at high and stable in time friction factor and little wearing and tearing aspect by oil so far.
Though known, there is certain influence in the gap of tumbling in CVT awl dish (mantle dish) movably between axle and mantle dish to efficient, so far nobody described the vibration of mantle dish bending, tumble or oscillating motion.
Can require to consider to combine with definite machine configurations in order to solve described problem more than one influenced parameter and definite characteristic of for example making oil.
According to the present invention, this problem will solve by a kind of conical pulley flexible drive transmission, it is right that it has awl dish driving side and slave end, they respectively have one and decide awl dish and a mantle dish, these awl dishes respectively are arranged on a driving side and the driven side shaft and can be connected with transmitting torque by a winding contact device, wherein at least one factor of listed factor below the speed changer acoustic connection is optimized:
The medium viscosity of-oil form or hydraulic pressure,
-awl dish and the surface characteristic of twining the contact area between the contact device,
The geometrical construction of-at least one awl dish,
The damping of-at least one awl dish,
The guiding of-at least one awl dish.
Favourable in the case can be to use the oil that has the insensitive friction factor of friction velocity.Favourable in addition can be that the surface of contact between optimization awl dish and the winding contact device is for example optimized on its surface topography.
Favourable in addition can be to be provided with awl dish of optimizing at least one rigidity and/or the awl dish that at least one is damped.
Be proved to be favourable also can be, at least one awl dish that is directed at radially outer of combination in this speed changer.
The invention still further relates to the Motor Vehicle that has according to speed changer of the present invention in addition.
Below will in the mode of example the present invention be described in further detail by the accompanying drawing that summary is represented.
Accompanying drawing is represented:
Fig. 1: the partial view of a conical pulley flexible drive transmission,
Fig. 2: another form of implementation with Fig. 1 corresponding view basically,
Fig. 3 and 4: the plotted curve of friction factor relation,
Fig. 5 and 6: the summary configuration possibility of mantle dish,
Fig. 1 only illustrates the part of a conical pulley flexible drive transmission, i.e. conical pulley flexible drive transmission 1 by a driving motor, for example oil-engine driven driving side or input side part.In a conical pulley flexible drive transmission that intactly constitutes to this input side partly disposed the infinitely variable conical pulley flexible drive transmission, a slave end part that complementally constitutes, wherein these two-part are connected to each other with transmitting torque by a winding contact device that for example connects leaf chain 2 forms.This conical pulley flexible drive transmission 1 has an axle 3 at input side, in an illustrated embodiment this axle and a fixing awl dish or decide awl dish 4 and constitute integratedly.Should axially go up fixing awl dish 4 axle 3 axially on be adjacently located on the opposite of an axially movable awl dish or mantle dish 5.
In view according to Fig. 1, connect leaf chain 2 and be indicated on driving side awl dish 4, on the radially outer position on 5, this position obtains like this, move on promptly axially movable in the figure awl dish 5 the direction and this axial displacement campaign of axially movable awl dish 5 causes connecting leaf chain 2 and moving on the direction of radially outer, the gear ratio of speed changer is changed to fast to the right.
The also available known mode of axially movable awl dish 5 own is moved to the left in drawing, wherein connect leaf chain 2 and be positioned at (with label 2a indication) on the inner radial position in this position, the gear ratio of conical pulley flexible drive transmission 1 changes at a slow speed on this position.
The torque that is provided by a unshowned driving motor imports the driving side part of the conical pulley flexible drive transmission shown in Fig. 1 by a gear 6 that is bearing on the axle 3, this gear 6 is bearing on the axle 3 by the rolling bearing of ball bearing 7 forms of a bearing radial force and axial force, and this ball bearing is fixed on the axle 3 by a back-up ring 8 and a spindle nut 9.Between gear 6 and axially movable awl dish 5, be provided with a torque sensor 10, this torque sensor disposed one be provided with the support plate 11 of axial restraint and the support plate configuration 13 of an axially movable support plate 12.Between two support plates 11,12, be provided with some rolling elements, for example shown in the rolling element of ball 14 forms.
The torque that imports by gear 6 cause fixing in the axial direction support plate 11 with axial on a rotation angle between the support plate 12 movably, this will cause an axial displacement of support plate 12, exactly owing to some starting inclined planes that are arranged on this support plate, ball 14 ascending motions reach and are used for support plate axial dipole field each other thus on these inclined-planes.
Be provided with a piston/cylinder unit 17 in order to produce impacting force, by this impacting force the awl dish 4 of axial restraint loaded a normal force with the leaf chain 2 that is connected between the axially movable awl dish 5, this piston/cylinder unit has two pressure chambers 18,19.First pressure chamber 18 is used for changing the loading that connects leaf chain 2 according to gear ratio, and second pressure chamber 19 is used for increasing with interrelating or reduce impacting force with the pressure chamber 15 according to torque control of torque sensor 10, connection leaf chain 2 between the awl dish is to 4,5 is loaded by this impacting force.
For to these pressure chamber's supply pressure media, axle 3 is provided with three passages 20, is fed in these pressure chambers by these passages from the pressure medium of a unshowned pump.Can and be input to circulation loop again by axle 3 outflows by passage 21 pressure mediums of discharging side.
As obvious by Fig. 1, conical pulley flexible drive transmission 1 has a noise damping device 23 respectively in the zone at these supporting positions of axle 3 epicone dishes 5.This noise damping device can have an annular solid and a damping lining or only be made up of a damping lining for this reason.
Employed label is also at the feature that can contrast in other accompanying drawing among Fig. 1.These accompanying drawings should be considered as the unit in this respect.For the sake of clarity, in other accompanying drawing, only use and exceed the label beyond the label among Fig. 1.
In Fig. 2, the center-aisle of present three passages 20 constitutes with the form of relative Fig. 1 remodeling; As can be seen, the hole 24 that constitutes central passage 20 is done shortlyer than the center hole among Fig. 1 significantly, and this hole 24 processes from the side shown in the right side of Fig. 1 and 2 as blind hole.This blind hole is cost height and the exigent precision of work in-process on making.Its manufacture cost reaches and increases in requirement aspect the course of working reliability and the super direct ratio of its length ground in the case.Therefore the shortening in this hole brings favorable influence to manufacture cost.
In the bottom section in this hole 24, branch out a transverse holes 25, wherein also can have a plurality of transverse holes to be arranged on the circumference with distributing.This transverse holes 25 is configured to radial hole in the illustrated case, but it also can other angle be made into inclined hole.Axle 3 surface is passed in hole 25 on a position, this position and working state, promptly for example irrespectively be arranged in a zone with the gear ratio that adjusts, and this zone is all the time by 5 coverings of mantle dish.
By making axle 3 be done shortly in the axial direction in the overlay area that transverse holes 25 is arranged on mantle dish 5, can save structure space thus.What the shortening by axle 3 also can obtain loading in addition reduces.
Here, the outlet of passage or transverse holes 25 for example can be set in the zone of the turning groove 26 adjacent with the centering face 22 of axle.When with mantle dish 5 axially movably but do not have the toothing 27 be connected with axle 3 for example because transmitting torque when being subjected to high load, work is particularly advantageous like this with relatively rotating.
But in many cases, the load of toothing 27 is not the design criteria of a key, and the outlet in hole 25 can be set in the zone of this toothing, as shown in Figure 2 thus.Obtain an advantage in the turning groove 26 in the following manner by transverse holes 25 being arranged on replace in the toothing 27 to be arranged on, a bigger drag torque is promptly arranged, the flexural stress in the edge fiber is reduced by it.When the crucial fiber that is subjected to transverse holes 25 interference was maintained on the roughly the same radius, the face rotary inertia on this position was bigger in addition.Obtain obviously reducing of stress in the key area around the outlet of the transverse holes 25 between the tooth of toothing 27 thus.The supply of hydraulic fluid is identical in Fig. 1 and 2, because pressure chamber 15 and 19 forms connection each other and mantle dish 5 has some attachment holes 28, these attachment holes make the zone of toothing 27 be connected with pressure chamber 19.Mantle dish 5 is indicated in the position on its outermost left side in these figure, and this position is corresponding to starting gear ratio or low gear (Underdrive).If mantle dish 5 moves on the direction of deciding awl dish 4 to the right now, then the part of cavity or chamber 29 always is positioned in the outlet of transverse holes or passage 25, so that also can guarantee required liquid stream supply as among Fig. 1 all the time.Also obtain two transition statuses for pressure chamber 16 as among Fig. 1, these transition statuses are relevant with the axial position of mantle dish 5.Shown in the position in control hole 30 expose, make thus with it form is connected, by a stopper 31 axially the passages 20 of sealing reach and form pressure chamber's 16 decompressions that are connected or only have external pressure by a unshowned passage and it.If now mantle dish 5 moves towards the direction of decide awl dish 4, then it will move on these control holes 30, wherein, from certain stroke chamber 29 be positioned at control hole 30 outlet above.But have a high pressure relevant with torque in chamber 29, this high pressure also enters in the pressure chamber 16 by control hole 30 and passage 20 then, makes the there also add high pressure thus.Realized two transition statuses in this way, these transition statuses and gear ratio are controlled impacting force relatively.
Be provided with a belleville spring 32 among this external Fig. 2, it makes mantle dish 5 move on on the predetermined axial position under speed changer 1 pressure-less state, can regulate speed changer 1 gear ratio thus, this gear ratio can prevent excessive load, for example when the Motor Vehicle trailer.
Two plotted curves shown in Fig. 3, they illustrate change curve relevant with contact pressure, the friction factor relative sliding velocity.Here reach in expression Sliding velocity on the abscissa and on y coordinate, represent friction factor.Dotted line is counted as reference value and represents a friction factor, and it for example can be on about μ=0.12.As appreciable by these two figure, friction factor is the function of Sliding velocity, and wherein this friction factor is tending towards along with the increase of Sliding velocity descending.
As mentioned above, the friction factor that for example descends along with the growth of Sliding velocity in clutch will cause tearing and causing thus the decline of travelling comfort.Therefore try hard to make the decline of friction factor on whole speed to keep as much as possible little.
Curve shown in Fig. 3 appear at chain some swing casting dies and awl dishes and their coefficient surface of contact between point of contact on.Chain twines contact device in other words and both loads by torque to be passed on traffic direction in the case, also mainly loads by impacting force on transverse to the direction of traffic direction.Here this impacting force should be selected like this, and torque promptly to be passed can be delivered on another awl dish group with enough reliability antiskids with changeing.
The dispersion width of the friction factor that the respective distance representative of these curves on the y coordinate direction is relevant with impacting force or contact pressure.Contact pressure that the line here is corresponding low and the top corresponding high respectively contact pressure of line.
By according to existing form of implementation upper curve figure, so far with can see significantly according to comparison lower curve figure, the invention process form: at first each is diminished by discrete areas of two curve limits, obtains friction factor thus and diminishes with the contact pressure that has just applied or the dependence of impacting force.In other words, insensitive according to the variation of the relative contact pressure of form of implementation of the present invention (lower curve figure).
Can be seen also that by Fig. 3 the curve among the lower curve figure more flatly extends, and obtains thus: the coherence of friction factor and Sliding velocity diminishes.Can reach the more stable properties of friction factor by this smooth negative gradient of friction factor relative sliding velocity.In the case when these curve approximations from the top down or oppositely move abreast than when their change problems on its slope littler because the change of any slope represents the coherence of friction factor and Sliding velocity bigger.
Change curve that determine so clearly, the friction factor relative sliding velocity shown in lower curve figure among Fig. 3 and relative contact pressure can produce the inhibition to vibration, and this vibration is to inspire by the friction factor variation that steel-steel between band or chain and the awl dish contacts.By using a kind of corresponding oil to change and directly to overcome this vibration in the place that vibration occurs by a kind of like this friction factor.
Plotted curve among Fig. 4 is set up as the plotted curve among Fig. 3 basically, but the former is provided with the coherence that illustrates with employed oil, but the coherence with the surface characteristics value is shown.The explanation that the explanation of making in conjunction with Fig. 3 reaches about improving is equally applicable to Fig. 4, that is to say, the lower curve chart is understood the major improvement of situation.
The upper curve of Fig. 4 illustrates a situation on the polished surface, and the lower curve figure of this figure is illustrated in the coherence according to friction factor and Sliding velocity and contact pressure under the situation of surface characteristics value of the present invention.These surface characteristics values for example can produce by a kind of polishing processing, and wherein friction parameter has correct change curve and it can be held on long working time.For example on smooth surface, the noise phenomenon can be occurred immediately, and how also noise can be do not occurred during in best situation under the state of rough surface.This improvement of noise properties aspect also can realize by the reduction of impacting force or contact pressure.
Test by simulation calculation and measurement shows, can active influence be arranged to vibration characteristics and noise properties by the tumble raising of rigidity of axial movable awl dish or mantle dish, wherein this situation especially-but not exclusive ground-the be suitable for mantle dish of slave end.Always obtain, the resistance to flexure of raising-by it can reduce the awl dish, especially slave end awl dish group opens-can reduce noise is produced the vibration amplitude that significant relationship is arranged.Similarly effect can reach by the damping that improves on this position.
Fig. 5 and 6 respectively schematically shows the profile of a mantle dish, and wherein each figure only illustrates upper half part of rotational symmetric profile.
Fig. 5 with the embodiment of summary a) to e) reinforced structure of awl dish itself respectively is shown.Here each summary is represented the part of slave end, axially movable awl dish or mantle dish 33 among Fig. 5 and 6, and wherein similarly configuration also can be transferred on the mantle dish 5 of driving side.
In order to strengthen mantle dish 33 in the axial direction, also can be provided with one and strengthen bulge loop 35, as shown in Fig. 5 c at radially outer.Fig. 5 d represents also to be provided with another and strengthens bulge loop 36 except that the reinforcement bulge loop 35 that is arranged on radially outer, the latter is set at radially inner and also can be used as two separating devices between the pressure chamber thus when needed.
Strengthen bulge loop 35 and 36 and be used as parts or annulus separately and illustrate in Fig. 5 c and 5d, their need be connected with mantle dish 33.Fig. 5 e illustrates and will strengthen the possibility that bulge loop 35 and/or reinforcement bulge loop 36 and mantle dish constitute integratedly, and wherein available favourable mode is considered a kind of configuration that meets processing.
Shown in Fig. 5 f and the 5g with the reinforced structure of the connection of awl dish on axle.Here the wheel hub 37 that is mantle dish 33 at first on the one hand is connected by a stiffening ring 38 with the part that the radially outward of mantle dish 33 is stretched, so that can reduce the distortion in this zone at least, be provided with strengthening rib 34 in addition, these strengthening rib are connected with stiffening ring 38 and are connected with the wheel hub 37 of mantle dish 33 on the other hand on the one hand.
Fig. 6 a to 6e illustrates the damping possibility in principle that is used for axial movable awl dish of slave end or mantle dish 33, but they also can be used for drive-side shaft to movable awl dish or mantle dish 5.
Fig. 6 a at first illustrates wheel hub 37 and is divided into each layer, and wherein this lamination group compresses and play thus damping function by the compaction pressure that is applied by hydraulic medium.
Among Fig. 6 b additionally this reinforcement bulge loop 35 be configured to the lamination group, this cap rock group again by compaction pressure compacted.According to Fig. 6 c, be positioned at radially inner reinforcement bulge loop 36 and also can be configured to the lamination group, wherein this reinforcement bulge loop 36 also can be used as the separation structure between the different pressures chamber.Conversion ground, wheel hub 37 also can be divided into each layer in according to the form of implementation of Fig. 6 c.
Respectively show spring 39 in Fig. 6 d and 6e, these springs 39 have improved friction between each layer cylindrical body by additional radial compaction, have side by side improved damping function thus.In Fig. 6 e, also wheel hub 37 can be configured to the lamination group.
Express another kind of solution in Fig. 6 f and 6g, it is: the direction of tumbling that changes the mantle dish.When the mantle dish normally by its inner radial zone or under by the situation of its wheel hub 37 guiding the radially exterior domain of this mantle dish tumbling and demonstrating maximum deflection on the direction.In order to tackle this problem, the mantle dish is externally led so that this mantle dish with exterior domain radially by touching outside on the guide mechanism 40 and can not departing from there thus.Deflection then can appear in the radially inner region of mantle dish 33, also can take described measure to this.But should note in the case: avoid mantle dish 33 tumbling or clamping between these guide mechanisms.
The reference number table
2 connecting plate type chains, 22 centering faces
Inside position, the footpath of 2a connecting plate type chain 23 noise damping units
3 axle 24 (center) holes
4 decide awl coils 25 transverse holes
5 mantle dishes, 26 turning grooves
6 gears, 27 toothings
7 ball bearings, 28 attachment holes
8 back-up rings, 29 empty chamber/chambeies
9 spindle nuts, 30 control holes
10 torque sensors, 31 stoppers
Support plate 32 belleville springs of 11 axial restraints
12 axially movable support plate 33 mantle dishes (slave end)
13 support plate configurations, 34 strengthening rib
14 balls 35 are strengthened bulge loop (outward)
15 first pressure chambers 36 strengthen bulge loop (interior)
16 second pressure chambers, 37 wheel hubs
17 pistons-/piston-cylinder unit 38 stiffening rings
18 first pressure chambers, 39 springs
19 second pressure chambers, 40 outer guiding
20 (3) passages (feeding)
Claims (7)
1. conical pulley flexible drive transmission (1), has driving side and slave end awl dish is right, they respectively have one and decide awl dish (4) and a mantle dish (5,33), these awl dishes are separately positioned on a driving side and a driven side shaft (3) and go up and can be connected with transmitting torque by a winding contact device (2), wherein at least one factor in the listed factor below the optimization of speed changer acoustic connection:
The medium viscosity of-oil form or hydraulic pressure,
-awl dish and the surface characteristic of twining the contact area between the contact device,
The geometrical construction of-at least one awl dish,
The damping of-at least one awl dish,
The guiding of-at least one awl dish.
2. according to the conical pulley flexible drive transmission of claim 1, it is characterized in that: use the oil that has the insensitive friction factor of friction velocity.
3. according to the conical pulley flexible drive transmission of claim 1 or 2, it is characterized in that: have the optimization surface of contact between awl dish and winding contact device.
4. according to one conical pulley flexible drive transmission in the claim 1 to 3, it is characterized in that: have awl dish optimised at least one rigidity.
5. according to one conical pulley flexible drive transmission in the claim 1 to 4, it is characterized in that: have at least one damped awl dish.
6. according to one conical pulley flexible drive transmission in the claim 1 to 5, it is characterized in that: have at least one outside diametrically awl dish that is directed to.
7. Motor Vehicle is characterized in that: have according to one speed changer in the above claim.
Applications Claiming Priority (13)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102004040826.2 | 2004-08-24 | ||
| DE102004040826 | 2004-08-24 | ||
| DE102004041715 | 2004-08-28 | ||
| DE102004041715.6 | 2004-08-28 | ||
| DE102004042883 | 2004-09-04 | ||
| DE102004042883.2 | 2004-09-04 | ||
| DE102004043536 | 2004-09-09 | ||
| DE102004043536.7 | 2004-09-09 | ||
| DE102004044190.1 | 2004-09-14 | ||
| DE102004044190 | 2004-09-14 | ||
| DE102004046213.5 | 2004-09-22 | ||
| DE102004046213 | 2004-09-22 | ||
| PCT/DE2005/001414 WO2006021183A2 (en) | 2004-08-24 | 2005-08-11 | Spherical disk-shaped enveloping gear system, method for the production thereof, and vehicle comprising such a gear system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101006290A true CN101006290A (en) | 2007-07-25 |
| CN101006290B CN101006290B (en) | 2012-06-27 |
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Family Applications (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800285819A Expired - Fee Related CN100532884C (en) | 2004-08-24 | 2005-08-11 | Belt-driven conical-pulley transmission, method for producing it, and motor vehicle having such a transmission |
| CN 200580028575 Pending CN101006291A (en) | 2004-08-24 | 2005-08-11 | Belt-driven conical-pulley transmission, method for producing it, and motor vehicle having such a transmission |
| CN2005800285734A Expired - Fee Related CN101006290B (en) | 2004-08-24 | 2005-08-11 | Belt-driven conical-pulley transmission, method for producing it, and motor vehicle having such a transmission |
Family Applications Before (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800285819A Expired - Fee Related CN100532884C (en) | 2004-08-24 | 2005-08-11 | Belt-driven conical-pulley transmission, method for producing it, and motor vehicle having such a transmission |
| CN 200580028575 Pending CN101006291A (en) | 2004-08-24 | 2005-08-11 | Belt-driven conical-pulley transmission, method for producing it, and motor vehicle having such a transmission |
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| CN (3) | CN100532884C (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102498319A (en) * | 2009-09-16 | 2012-06-13 | 威伯科有限公司 | Contacting module for a transmission controller, transmission control module, and method for the production thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE112011100935A5 (en) * | 2010-03-18 | 2013-01-24 | Schaeffler Technologies AG & Co. KG | Cone-plate sheet metal part |
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| US5750477A (en) * | 1995-07-10 | 1998-05-12 | The Lubrizol Corporation | Lubricant compositions to reduce noise in a push belt continuous variable transmission |
| JP3709973B2 (en) * | 2000-03-31 | 2005-10-26 | 本田技研工業株式会社 | Belt-type transmission |
| CN2522676Y (en) * | 2002-01-19 | 2002-11-27 | 刘亚军 | Dynamic pressure balancing mechanism of moving conic-disc oil cylinder of stepless speed variator |
| DE10226861B4 (en) * | 2002-06-15 | 2012-11-08 | Zf Friedrichshafen Ag | Continuously variable belt drive |
-
2005
- 2005-08-11 CN CNB2005800285819A patent/CN100532884C/en not_active Expired - Fee Related
- 2005-08-11 CN CN 200580028575 patent/CN101006291A/en active Pending
- 2005-08-11 CN CN2005800285734A patent/CN101006290B/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102498319A (en) * | 2009-09-16 | 2012-06-13 | 威伯科有限公司 | Contacting module for a transmission controller, transmission control module, and method for the production thereof |
| CN102498319B (en) * | 2009-09-16 | 2014-10-29 | 威伯科有限公司 | Contacting module for a transmission controller, transmission control module, and method for the production thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100532884C (en) | 2009-08-26 |
| CN101006290B (en) | 2012-06-27 |
| CN101006292A (en) | 2007-07-25 |
| CN101006291A (en) | 2007-07-25 |
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