CN101287931A

CN101287931A - Gear assembly and constinuously variable transmission comprising such gear assembly

Info

Publication number: CN101287931A
Application number: CNA2006800364995A
Authority: CN
Inventors: 贡纳尔·林德奎斯特
Original assignee: INFINIGEAR AB
Current assignee: INFINIGEAR AB
Priority date: 2005-09-29
Filing date: 2006-09-28
Publication date: 2008-10-15

Abstract

The present invention concerns a gear assembly, suitable for a continuously variable transmission, comprising two gear tooth devices (10, 50) making up an imaginary gear wheel with variable pitch diameter, the two gear tooth devices being radially movable and also a continuously variable transmission comprising an input shaft (1), an output shaft (2), a gear-changing shaft (3) and first gearbox shaft (4) comprising a gear assembly according to the invention, a transmission chain (5) and a second gearbox shaft (6) comprising a gear assembly according to the invention or a gear wheel (7), whereby the first gearbox shaft (4) is driven by the input shaft (1), the second gearbox shaft (6) or the gear wheel (7) is driven by the first gearbox shaft (4), and the output shaft (2) is driven by the second gearbox shaft (6) or the gear wheel (7).

Description

Gear assembly and the stepless speed variator that comprises this gear assembly

Technical field

The present invention relates to gear assembly, also relate to the stepless speed variator that comprises this gear assembly.

Background technique

Now, gear-box is the target that automotive industry reduces automobile fuel consumption work.The automatic gear-box of current tradition is than the about energy more than 10% of both hands moving gear case consumption.It is the following new solution of seeking that environmental requirement that increases and increase fuel cost force automotive industry.

Known in the past have a stepless speed variator (CVT), and this stepless speed variator makes and need not any step continuously changes the gear ratio and become possibility,, has the gear ratio of unlimited amount between minimum value and maximum value that is.This makes motor not propped up by car speed to be equipped with its best revolution operation to become possibility.

The CVT that three kinds of main types are arranged, i.e. friction type, hydraulic type and ratchet-type.Referring to, Variomatic and Multitronic CVTs for example.The subject matter of CVT is to have sizable energy loss mainly due to frictional loss in speed changer.Another problem is owing to sliding and friction makes these CVTS can not transmitting large torque and power, and these CVTS comprise flexible part.

Recently, utilization is provided with flexible cingulum and has invented a kind of new CVT on taper cone pulley, see WO 02/08638.Slide and frictional loss although in this invention, can reduce, still have big problem with flexible belt transmitting large torque and power.

US 4 878 883 shows a kind of stepless change chain transmission speed changer, and it has hydraulic system and is used on the different radii that the small gear that diameter is relative (diametrically opposed small gears) is arranged on sprocket wheel so that obtain different effective diameters.

The problem of this invention is, effective diameter and chain pitch are complementary sometimes, but between between have the effective diameter that is not complementary with the coupling chain pitch, and therefore small gear will not mesh in the recess of chain into but slippage.For this reason, will the effect instability of speed changer appear.This speed changer can only be a sense of rotation operation.

The purpose of US 2005/0148416A1 is that the pulsation that overcomes US 4878883 drives output.The speed change sprocket IVT machine of US 2005/0148416A1 has the sprocket wheel with variable-diameter, and this sprocket wheel comprises six sprockets that slidably are provided with, sprocket by can towards or away from the control unit control of central shaft motion to change effective diameter.This scheme is too complicated, and can only be a sense of rotation operation.

US 4878883 and US 2005/0148416A1 do not have can handle the structure of effective diameter than big-difference.Therefore they can not obtain high gear ratio.

Summary of the invention

The objective of the invention is to simplify and overcome the aforesaid problem that has of CVT.Essence of the present invention is the gear assembly that a formation has the reverie gear that does not wait pitch diameter, and it is applicable to stepless speed variator, and this gear assembly comprises two wheel tooth devices, but this two wheel tooth devices radial motion.

But because wheel tooth device radial motion, therefore may realize the continuous variation of the pitch diameter of reverie gear, thereby realize the continuous variation of gear ratio, and owing to have at least one to be engaged on wheel tooth in the chain, therefore can be without any sliding and almost having frictional loss ground to transmit high moment of torsion and power.Because gear assembly includes only two wheel teeth, therefore can be easier to make, and compacter, more reliable, easier maintenance and maintenance are rapider.

Preferably, wheel tooth device about mutually 180 degree in ± 20 degree scopes are directed.

According to data, in conventional gears, mainly always a wheel tooth during transmitting torque with straight-tooth gear teeth.

Two wheel tooth devices can be by driven (on input side) in case by transmit chain from input side to the outlet side transmitting torque.The wheel tooth device can be arranged on separately the spindle unit, and spindle unit is axially aligned and formed gearbox shaft (being used for for example input side of gear-box).Each is set at the wheel tooth device on separately the spindle unit, and radially is arranged in the gap of the gearbox shaft between the spindle unit of alignment toward each other.The transmission of moment of torsion during being connected in main clutch, the wheel tooth device takes place.

Also can expect allowing wheel tooth device crossover and cooperation, that is, during revolution separately, that is to say that two wheel teeth all are connected to main clutch during the peripheral part of reverie wheel.Surpass about half periphery if two wheel tooth devices all are connected in their main clutch, this is possible.Therefore two wheel tooth devices are at main clutch joint crossover.Preferably, Transmitted chains surpasses 180 degree and reaches for example 320 degree around the reverie gear.

Each wheel tooth device is driven by main clutch and/or second clutch successively.For example, main clutch is the clutch stronger than second clutch, and main clutch carries out the moment of torsion transmission.According to first embodiment of clutch drive apparatus, each wheel tooth device is substantially alternately driven by main clutch device and second clutch device.

According to second embodiment of clutch drive apparatus, also may be always by second clutch device drive gear teeth device part revolution, for example only about half of revolution, main clutch is the drive gear teeth device also, and promptly two clutches replenish mutually.

The temporary transient not wheel tooth of transmitting torque is driven by second clutch.When this wheel tooth device is engaged in the Transmitted chains, still drive by preferred more weak second clutch.Even do not have the smooth function that replaces of wheel tooth device when the pitch of the pitch diameter of reverie gear and Transmitted chains matches so yet.

Also further improve the smooth function that replaces of wheel tooth device, the gear ratio that is used for second clutch can be than the gear that is used for main clutch than higher.

The preferred mechanical means that uses is mediated and disconnecting clutch.Use the rotating cam that cooperates with pin or come solenoidoperated cluthes and its spring the stationary cam that cooperates with cam follower.Other method that can expect is to rely on hydraulics or electronics.

For side supports Transmitted chains at Transmitted chains, two conical plates can be set, each is arranged on the relative separately end of spindle unit of two alignment of gearbox shaft.Conical plate preferably rely on the arm separately that is connected in the gear graduation axle along the axis of gearbox shaft can be synchronously move toward one another and can be mutually synchronously mutually away from moving, wherein, arm separately is threadedly connected to the gear graduation axle by the relative orientation on the gear graduation axle.

Provide a method of the radial motion of wheel tooth device to be: to make the wheel tooth device be connected separately radial arrangement parts (a radially arranged part) movingly and locate in radial direction, thus, parts be set at gearbox shaft two alignment spindle unit relative towards the end on.For example, the wheel tooth device rely at least one controlling rod be arranged on wheel tooth device place and be arranged on the spindle unit place radially arrangement components synchronously can be radially inwards and outwards motion, this controlling rod is connected in conical plate, conical plate is connected in the gear graduation axle by arm successively, so controlling rod can be synchronized with the movement with conical plate.

Provide another method of the radial motion of wheel tooth device to be: when conical plate relied on the mutual move toward one another of transmitting gear variable-speed shaft, centrifugal force and/or conical plate radially outward promote the wheel tooth device made it slide along conical plate.In order to return the wheel tooth device, motor can be set and control motor by sensing system.Certainly expect, rely on motor that the wheel tooth device outwards and is inwards moved.

On the other hand, when the wheel tooth device should be return, because Transmitted chains is at opposite side outlet side " expansion " for example, so Transmitted chains radially advanced the wheel tooth device inwards.Also can expect, between radial arrangement parts and wheel tooth device, spring is set with equilibrium centrifugation power.Also can expect, because spring force is very high, to such an extent as to when the conical plate disjuctive movement, the wheel tooth device is return by spring.

Another method of returning the wheel tooth device is: the wheel tooth device is connected in first end of chain, and this chain enters in the central opening of conical plate, and further by the axially extended elongated hole in the each several part of axle.This chain preferably is connected in the cylinder rod that is provided with in the spindle unit elongated hole in its second opposite end.This cylinder rod is connected in the gear graduation axle then, returns the wheel tooth device during with convenient change wheel synchronously.This is to provide the radial motion of wheel tooth device simpler method than what illustrate previously.

A method that improves the gear ratio is the diameter that increases the reverie gear.If can being designed to make than long and wheel tooth device, the radial arrangement parts its further radially outward motion then can realize improving the gear ratio.In this embodiment of conical plate, the center of conical plate is processed so that provide the space for longer radial arrangement parts and this wheel tooth device.

Like this, the wheel tooth device is the longer distance of arrangement components motion radially, and therefore forms the reverie gear with larger diameter.This means gear than will therefore increasing.For support chain from start to finish, on the part of the central opening of conical plate, circular lid is set.

For the gear ratio of raising further is provided, can expect for example increasing the diameter of reverie wheel on guider by the wheel tooth parts are set, this guider is successively set on another guider.The wheel tooth device has Telescopic like this.The outward radial motion can for example obtain according to above any suggestion.Although preferably be used to the chain solution of returning, these suggestions are valuable equally for returning.When using expansion teeth gear teeth device, may obtain larger-diameter reverie gear.While is owing to the outside at conical plate increases by two distances that support between the conical plate, so Transmitted chains can be wideer.If it is identical that the width of Transmitted chains keeps, then can replace changing the angle of conical plate.

According to preferred embodiment this moment, each wheel tooth device comprises two wheel teeth that are arranged on separately on the bar, and bar interconnects by connecting rod.Preferably first wheel tooth is more outstanding than second dental transition in radial direction.

If at least the first gear ratch is by radially outward fexible bias pressure (isspring biased), thereby and can radially move inwards, second wheel tooth and its bar are pushed away by radially outward because of connecting rod simultaneously, then can obtain smooth function.

In second embodiment, the wheel tooth device comprises a wheel tooth.The wheel tooth device is vertically movable in guider, and passes through at least one spring by the radially outward fexible bias pressure in this guider.This guider is had the angle setting.When tooth will be mediated in chain, the recess of most cases lower tooth meeting collision chain or collision be the inclined-plane of guiding recess downwards.

If between the tooth collision inclined-plane, chain will force tooth to overcome elastic force and radially slide in guider inwards.Simultaneously, the wheel tooth device travels forward relative chain.Because this travels forward, tooth will move on to the inclined-plane of front and slip into the recess of front.

In the 3rd embodiment, each wheel tooth device comprises a wheel tooth, and the wheel tooth device is resiliently biased, and can move forward and backward in the angle of rotation direction.

According to first and second aspects of stepless speed variator of the present invention, this speed changer comprises input shaft, reaches output shaft, and this output shaft relies on Transmitted chains to be connected in input shaft by first gearbox shaft and second gearbox shaft.First gearbox shaft and second gearbox shaft comprise the gear assembly according to above any one embodiment, thereby first gearbox shaft is driven by input shaft, second gearbox shaft is driven by first gearbox shaft by Transmitted chains, and output shaft is driven by second gearbox shaft.

The gear graduation axle is connected in first gearbox shaft and second gearbox shaft by arm, is used for being synchronized with the movement of two wheel tooth devices of each gearbox shaft, so that reduce the pitch diameter of first gearbox shaft when increasing the pitch diameter of second gearbox shaft; Perhaps vice versa.

According to the third aspect of stepless speed variator of the present invention, this speed changer comprises input shaft, reaches output shaft, and this output shaft relies on Transmitted chains to be connected in input shaft by gearbox shaft and gear.Gearbox shaft comprises the gear assembly according to above any one embodiment, thereby gearbox shaft is driven by input shaft, and gear is driven by first gearbox shaft by Transmitted chains, and output shaft is by gear drive; Perhaps vice versa.

Description of drawings

With reference now to accompanying drawing, by some presently preferred embodiments the present invention is described, wherein:

Fig. 1 shows first embodiment's of CVT of the present invention plan view, but only is positioned on the CVT at dotted line place input and output axle;

Fig. 2 shows the side plan view of Fig. 1 embodiment's a part with more details;

Fig. 3 shows camshaft parts;

Fig. 4 shows the embodiment of the spindle unit that is provided with controlling rod and conical plate, and the part of conical plate is removed in the figure;

Fig. 5 shows the spindle unit that revolves the Fig. 4 that turn 90 degrees, but does not have conical plate;

Fig. 6 shows another embodiment of the spindle unit that is provided with motor and conical plate, and the part of conical plate is removed in the figure;

Fig. 7 shows the retainer that is arranged on spline part;

Fig. 8 shows the preferred embodiment of two wheel tooth devices, a part of with dashed lines attempt to represent first do not cover second that is positioned at the relative spindle unit of being arranged on of back, Fig. 8 also shows chain;

Fig. 9 a shows the alternate embodiments of wheel tooth device, part with dashed lines attempt to represent first do not cover second that is positioned at the relative spindle unit of being arranged on of back, Fig. 9 a also shows chain, and wherein, the first wheel tooth device of two positions is called I and III;

Fig. 9 b shows the first wheel tooth device of Fig. 9 a, and it is in the II place, position on the path of mediating chain;

Fig. 9 c shows selectable chain;

Figure 10 shows the plan view of the second embodiment of the present invention in being called two positions of I and II;

Figure 11 shows the side view of the second embodiment of the present invention of Figure 10 in being called two positions of I and II, sees the arrow among Figure 10; With

Figure 12 show the radial motion, another Transmitted chains of wheel tooth device and the wheel tooth device is connected the possibility that keeps a period of time simultaneously with main clutch another embodiment and

Figure 13 illustrates in greater detail second embodiment's of clutch drive apparatus the side view of part;

Figure 14 shows the housing of the clutch drive apparatus of Figure 13;

Figure 15 a there is shown the intermediate of the clutch drive apparatus of Figure 13 on the plane;

Figure 15 b there is shown the intermediate of Figure 15 a in side-looking;

Figure 16 a there is shown the cam follower of the clutch drive apparatus of Figure 13 in side-looking;

Figure 16 b there is shown the cam follower of Figure 16 a on the plane, and with the position regulation of the cam follower possibility to the intermediate of the clutch drive apparatus of Figure 13;

Figure 16 c shows the figure according to A-A among Figure 16 a;

Figure 17 shows the position regulation of the cam follower possibility to the intermediate of the clutch drive apparatus of Figure 13;

Figure 18 a there is shown the stationary cam of the clutch drive apparatus of Figure 13 on the plane;

Figure 18 b shows the plan view of the cam of Figure 18 a;

Figure 19 a shows another embodiment's of spindle unit side view;

Figure 19 b shows the spindle unit of Figure 19 a of about 90 degree of rotation;

Figure 19 c shows the planimetric map of the spindle unit of Figure 19 a;

Figure 20 illustrates in greater detail second embodiment of CVT and returns the side plan view of the part of wheel tooth device preferred path;

Figure 21 shows in detail the part that the wheel tooth device is return control;

Figure 22 shows second embodiment's of CVT of the present invention planimetric map, but has removed the input and output axle that is positioned on the CVT;

Figure 23 shows the another embodiment of wheel tooth device, radial arrangement parts and conical plate;

Figure 24 shows expansion teeth gear teeth device;

Figure 25 a shows the expansion teeth gear teeth device in maximum extension position; With

Figure 25 b shows the expansion teeth gear teeth device in maximum retraction position.

Embodiment

By some embodiments the present invention is described now.For to increase understanding, will the present invention be described in the mode of the effect of the present invention in stepless speed variator (CVT) to different parts of effect of the present invention and assembly with it.

CVT according to the present invention comprises input shaft 1; Output shaft 2; At least one gearbox shaft 4, the driving side (input side) that it is preferably used for CVT is connected in input shaft 1; Transmitted chains 5, it sees Figure 10 and Figure 11 between gearbox shaft and second gearbox shaft 6 or gear 7, thus second gearbox shaft 6 or gear 7 are driven and are connected to output shaft 2.

Gear graduation axle 3 is connected in first gearbox shaft 4 and second gearbox shaft 6 by arm 26, being synchronized with the movement of two wheel tooth devices that is used for each

gearbox shaft

4,6 is so that reduce the pitch diameter of first gearbox shaft 4 in the pitch diameter that increases by second gearbox shaft 6; Vice versa.

According to first and second embodiments, this CVT comprises two gearbox shafts, first gearbox shaft 4 and second gearbox shaft 6 (seeing Fig. 1, Fig. 2 and Figure 20, Figure 22).According to the 3rd embodiment, this CVT comprises a gearbox shaft 4 and gear 7 (seeing Figure 10 and Figure 11).

Whole three embodiments use first gearbox shaft 4 to be used for the input side of gear-box.To be described this now.Although, be to be understood that second gearbox shaft 6 is formed with the same manner, in first and second embodiments, be used to the outlet side of gear-box, therefore carry out absorbing the work of (take up) moment of torsion from first gearbox shaft 4 by Transmitted chains 5 with opposite way.

Gearbox shaft

4,6 is divided into two spindle units, see Fig. 1 and Figure 22, have and be arranged on the opposed facing radial arrangement parts 8 in each opposite end, it preferably has some guiders of planting shape, for example rhomboid, square, oval uniform section, be preferably spline, therefore following the radial arrangement parts be called spline part 8.Lining 9 preferably along spline part 8 movingly by attached, lining 9 supports integratedly or comprises wheel tooth device 10,50.Hereinafter will further describe

wheel tooth device

10,50, also referring to Fig. 8, Fig. 9, Figure 24, Figure 25 a and Figure 25 b.Two parts of wheel tooth axle 4 are by wheel tooth device 10, the 50 driven chains 5 of each several part.

In order to replace, each spindle unit can be driven by main clutch 11,66 and/or second clutch 12,67.These

clutches

11,12,66,67 can be lamella clutch.In first embodiment, first gearbox shaft 4 is two by four gear units 13, and master gear unit 13 ' " (two are used for each spindle unit) is connected to input shaft 1 four positions, sees Fig. 2 with two second gear units 13.Be used to be connected in the master gear unit 13 of main clutch 11 ' gear than less than second gear unit 13 that is used to be connected in second clutch 12 " the gear ratio; promptly, this moment is faster than the other parts rotation that connects by main clutch simultaneously by the part of the axle that second clutch connects.Input shaft 1 preferably is configured in above first gearbox shaft 4, (Fig. 1 does not illustrate) as shown in Figure 2

Because main clutch will carry out the transmission of moment of torsion, so main clutch 11 is more dynamic clutches, for example is provided with three disks.Because second clutch will mainly only drive a spindle unit, so second clutch 12 power are less, and a disk for example only is set.

Replacing by for example camshaft parts 20 realizations of rotatable cam between main clutch 11 and the second clutch 12 sees Fig. 3.Camshaft parts 20 has the cam curve 14 of free end configuration of the each several part of close gearbox shaft 4,6.Camshaft parts 20 is rotatable at least one bearing 19 that disposes in the housing of CVT or frame owing to hang by spline 15 axially movablely simultaneously.Camshaft parts 20 has axially extended pin 21, and pin can activate clutch 11,12 by the central clutch plate 23 of configuration between the clutch 11,12.

Main helical spring 16 acts on the camshaft parts 20, make pin 21 make main clutch 11 mediate and overcome the elastic force of at least one second spring 17 by bar 22 application of forces that are provided with on the central clutch plate 23, as long as cam curve 14 is positioned at position, its underpart, promptly do not contact with the pin 18 that disposes in the housing of CVT or the frame.By making central clutch plate 23 towards main clutch 11, second clutch 12 is broken away from, see Fig. 2.

When cam curve 14 is positioned at its upper position, cam curve will contact with pin 18, and camshaft parts 20 with stressed towards the free end axial motion and overcome the power of main helical spring 16.Main clutch 11 breaks away from like this, and this is because at least one second spring 17 especially preferably around the equally distributed several helical springs of this clutch, makes central clutch plate 23 towards second clutch 12 application of force, makes second clutch mediate.Certainly expect relying on fluid power or electricity to change the kneading of main clutch and second clutch.

Second embodiment of clutch drive apparatus is simple, is that main clutch for example is driven from input shaft 1 with identical speed by the single gear unit 69 of each spindle unit with second clutch, sees Figure 13.Main clutch 66 is still than second clutch 67 more dynamic clutches.Preferably, second clutch 67 is also mediated and main clutch 66 will only be mediated and be used for part revolution, for example only about half of revolution.

In Figure 13-18, show second embodiment of clutch drive apparatus.It comprises the housing parts 68 that is connected in gear unit 69.Gear unit 69 relies on axle bush 70 to be configured on the spindle unit.In the inside of housing 68 is that the clutch surface of mediating with the sheet of main clutch 66 71 is set, and sees Figure 14.The clutch plate of main clutch is configured on the intermediate 72 that comprises circumferential section 73, circumferential section 73 has an inner penetration hole 74 (an inner through going hole 74), this inside penetration hole 74 is provided with spline 75 grades and is used for and the spindle unit engagement, sees Figure 15 a, 15b.

Intermediate 72 preferably is provided with two cam followers 85.These cam followers 85 can be provided with or preferably be installed on intermediate 72 integratedly.Can see that as Figure 16 a, 16b, 16c the adjacent sides at parts 86 with cam follower 85 and intermediate 72 is provided with lock rib 87.Therefore when cam follower 85 collision cams 84,, parts 86 make degree obtain adjusting by being installed on intermediate 72 at ideal position.

Being provided with a plurality of recesses 76 at circumferential section 73, is three in shown embodiment, is used for the quantity of corresponding main clutch spring 77.Another group recess 78 is arranged on circular portion 73, is three in shown embodiment, is used for second clutch spring 79.Recess 78 preferably is configured between the recess 76.Second clutch can be the lamella clutch that for example has a clutch plate, perhaps can be the clutch with a plurality of indentures 80 and the plunger 81 that matches, and indenture 80 is arranged in the clutch surface 71 of housing section 68.Such clutch more is a timing clutch.

Preferably, indenture 80 and plunger 81 all are tapers.Adjacent portion 82 act as the portion that stops of plunger 81 axial motions.This is preferably to design, so that plunger 81 can not all shift out indenture 80.

The optimal way of mediating and breaking away from clutch 66,67 has been shown in Figure 13 and Figure 18 a, 18b.Stationary cam portion 83 preferably is provided with two cams 84 of mutual 180 degree location, radial and axial displacement.Two cams 84 match with two cam followers 85 that are provided with at intermediate 72.The also mutual 180 degree location of cam follower 85 are with the radial and axial displacement of corresponding distance.Certainly expect having only a cam 84 and a cam follower 85.

When cam follower 85 power that (simultaneously) intermediate 72 will overcome main spring 79 during through cams 84 outwards towards the displacement of the outer end of spindle unit, so clutch plate will be released, promptly main clutch 66 will break away from.The length of cam 84 in rotary distance is consistent with the preferably only about half of revolution of part revolution that main clutch breaks away from.

Second clutch with indenture 80 and plunger 81 is drive shaft sub-assembly always, thus and drive gear teeth device 10,50.When the wheel tooth device will mesh into Transmitted chains 5, can need the little slippage or the displacement of second clutch 67, make the recess that wheel

tooth device

10,50 correctly enters in the Transmitted chains 5.When the entering/mesh when finishing of the wheel tooth device in the chain 5, main clutch 66 will mesh, and then pin the possible displacement of the plunger 81 in the indenture 80.Behind the only about half of revolution, main clutch 66 breaks away from, and this will give plunger 81 slips and get back to the possibility at the center of indenture 80 separately.

Wheel tooth device

10,50 is incited somebody to action subsynchronous their mutual positions of getting back to again like this, for example mutual 180 degree.

Also can expect relying on fluid power or electric control clutch 66,67.

When using the clutch drive apparatus of identical speed, the wheel tooth device must be able to be done small change in location at least backward, so that level and smooth driving is provided.Therefore preferably the elastic force unlike second clutch is stronger for the elastic force of the change in location that control gear tooth device is small.Perhaps, in the example of the second clutch 67 that uses indenture 80 and plunger 81, because the be shifted possibility of plunger 81 of the center of indenture 80 does not relatively then need the elasticity on the wheel tooth device to control.

Therefore provide simpler and compacter clutch drive apparatus, it is reduced friction, and has saved weight and the space of CVT.And the centre of the more close gearbox shaft of cam pack setting makes CVT even compacter.This embodiment also will reduce wear.

Although, if the main clutch of engagement and disengaging automotive transmission removes the clutch that helps CVT, second clutch for example must be able to break away from by the further displacement of clutch pack, if if, overcome the power of the spring of second clutch so that use slice clutch or use the clutch of band plunger and indenture and remove retainer in the plunger.

In each opposite end of the spindle unit of

gearbox shaft

4,6, conical plate 24 is attached around axle by lining 25.These plates 24 are as the side supports of Transmitted chains 5.Lining 25 is connected in gear graduation axle 3 by the arm 26 that is attached at lining regularly, sees Fig. 1, and is provided with the internal thread (not shown) at the other end around gear graduation axle 3, and gear graduation axle 3 is disposed with outside thread 27.When transmitting gear variable-speed shaft 3, arm 26 will be along the axial-movement of axle 3, and therefore along the axial-movement conical plate 24 of

gearbox shaft

4,6.

Since gear graduation axle 3 be provided with 27, two conical plates 24 of relative directed screw thread of being used for two arms 26 of

gearbox shaft

4,6 separately with

gearbox shaft

4,6 places separately with mutual synchronous relative motion or phase mutually synchronization away from motion.

In one embodiment, be attached at pivotally around axletree 60

gearbox shaft

4,6 each part at least one controlling rod 28 preferably in the lining 25 of conical plate 24, for example in groove 29, be connected to conical plate 24 by pin 30, and for example be connected to spline parts 8 movable linings 9, see Fig. 2, Fig. 4 and Fig. 5 along the spindle unit end by pin 61.Preferably dispose two controlling rods 28, each is positioned at each sidepiece of the part of

gearbox shaft

4,6.

When conical plate 24 during towards the motion of the free end of

gearbox shaft

4,6, lining 9 will along spline 8 towards the central motion of

gearbox shaft

4,6, return.Therefore each

wheel tooth device

10,50 also will be return.

When conical plate 24 during towards the motion of relative conical plate, lining 9 will be along spline 8 towards the peripolesis of

gearbox shaft

4,6, outstanding.Being synchronized with the movement so also will being being synchronized with the movement of

wheel tooth device

10,50 of each

gearbox shaft

4,6 of conical plate 24.

See Fig. 6, in a second embodiment, when conical plate passed through the mutual move toward one another of transmitting gear variable-speed shaft,

wheel tooth device

10,50 slided and outwards moves by the conical plate of centrifugal force along band supporting element 58.In order to return the wheel tooth device, motor 59 disposes controlling rod 62 and controls by the sensing system (not shown).Certainly expect by motor 59 motion

wheel tooth device

10,50 outwards and inwards.This produces simpler spindle unit.

See Figure 12, also can expect configuration spring 65 between radial arrangement parts 8 and

wheel tooth device

10,50, with equilibrium centrifugation power.When conical plate 24 during by the mutual move toward one another of transmitting gear variable-speed shaft 3,

wheel tooth device

10,50 will outwards move slidably along conical plate.

On the other hand, when

wheel tooth device

10,50 should be return, because chain 5 for example outlet side expansion in the opposite end, therefore chain 5 will force

wheel tooth device

10,50 radially inwards, that is, second gearbox shaft 6 will increase its pitch diameter, and perhaps gear 7 is away from 4 motions of first gearbox shaft.Can expect that also elastic force is very high, to such an extent as to when conical plate 24 motions separate, make that by spring 65

wheel tooth device

10,50 is return.

In Figure 19 a, 19b, 19c, show the another embodiment of spindle unit.Spindle unit is depicted as does not have its conical plate.Along the axis of spindle unit be provided with elongated, be preferably columniform hole 88.Radial arrangement parts 8 extend across the most of of end diameter and preferably extend equidistantly from the center.Radially arrangement components 8 another mode of returning the wheel tooth device of sliding is first end that the wheel tooth device is connected in chain 89, and this chain 89 will enter radial arrangement parts 8 centers and further by the elongated hole 88 in the spindle unit.Preferably, second end of chain 89 is connected in the cylindrical bar 90 of configuration in the elongated hole 88, sees Figure 20.

Cylindrical bar 90 is connected in gear graduation axle 3 successively, so that have being synchronized with the movement of wheel tooth device, sees Figure 20, Figure 21 and Figure 22.Bar 90 is connected in first end 91 of first connecting rod 92.Second end 93 of first connecting rod 92 is connected in the synchronizing shaft 94 of configuration in the carriage 95 at the pedestal place.Synchronizing shaft 94 is by 3 controls of gear graduation axle.By transmitting gear variable-speed shaft 3, arm 26 is synchronized with the movement.

Bar 96 is connected in arm 26 separately at its first end 97, and its second end 98 is connected in second end 99 of second connecting rod 100.First end 101 of second connecting rod 100 is connected in synchronizing shaft 94.When arm 26 motion, synchronizing shaft 94 will move, so first connecting rod 92 also will move, and make bar 90 88 li of elongated hole inwards or outside moving.Bar 90 activates chain 89, thus and actuation gear tooth device 10,50.The length difference of first connecting rod 92 and second connecting rod 100 is corresponding with the stroke distances difference of arm 26 and

wheel tooth device

10,50 respectively.

Radial arrangement parts 8 advantage longer than the embodiment who illustrates previously be, lining 9 can be designed to make its further radially outward carrier wheel tooth device.In Figure 23, the conical plate 24 that shows lining 9 and be fit to.In this embodiment of conical plate 24, the center 102 of conical plate 24 is processed, so that provide the space for longer radial arrangement parts 8 and this lining 9.

Like this, lining 9 is the longer distance of arrangement components 8 motions radially, thereby forms the reverie gear with larger diameter.This means gear than will therefore increasing.For comprehensive support chain 5, circular lid 103 is configured on the part of central opening 102 of conical plate 24.

Thereby further extending the diameter of reverie gear and another mode that can expect of increase gear ratio is the lining 9 that disposes between radial arrangement parts 8 and

wheel tooth device

10,50 more than, make the lining 9 of winning ' radially arrangement components 8 slips, and some plant the guiding element of shapes this first lining 9 ' also be provided with, second lining 9 " slides along this guiding element, sees Figure 24 and 25a, Figure 25 b.Therefore

wheel tooth device

10,50 is set at second lining, 9 " linings.To have Telescopic like this.Certainly can expect disposing lining if desired more than two.

The outside radial motion of

wheel tooth device

10,50 can for example for example push away by conical plate 24 radially outwards according to above any one suggestion and realize.Returning of

wheel tooth device

10,50 can for example be carried out according to above any one described suggestion, although preferably use chain 89 solutions to be used to return.Owing to increase by two distances that support between the conical plate 24, so Transmitted chains 5 can be wideer.If it is identical that the width of Transmitted chains 5 keeps, then can be instead, the angle of conical plate is changed.

First embodiment according to clutch drive apparatus, two

wheel tooth devices

10,50 are spent in ± 20 scopes of spending by mutual orientation 180, this be because, whether be driven according to them by main clutch 11 or second clutch 12, and will and have different rotation rates by driven, see Fig. 8.Perhaps, except driving during second clutch drives transmission alternately by main clutch, they will be driven by different clutches, vice versa, perhaps, see Figure 12,

wheel tooth device

10,50 can all drive a period of time by main clutch 11 simultaneously, for example, spend as 90 corresponding to the part of angle of rotation.

Therefore two

wheel tooth devices

10,50 form the diameter corresponding to the reverie gear, and this diameter will be according to whether return still outstanding the change by gear graduation axle 3 wheel tooth devices 10,50.Like this, can continuously change gear by the diameter that continuously changes the reverie gear of making by two

wheel tooth devices

10,50.

According to first embodiment,

wheel tooth device

10,50 replaces substantially, and a spindle unit of gearbox shaft 4 is driven by main clutch 11, and when operation, and

wheel tooth device

10,50 is engaged on chain 5 in the chain 5.At this moment, another

wheel tooth device

10,50 on the relative parts of gearbox shaft 4 is driven by second clutch 12, and main

gear teeth device

10,50 about 180 degree that distance drives are directed (according to the present diameter and the selected chain pitch of two wheel tooth devices 10,50).

When chain 5 is left in drive

gear teeth device

10,50 operation, rely on cam axial region 20 that 12 change takes place from main clutch 11 to second clutch, as mentioned above.Second clutch 12 is to move than main clutch 11 higher rotational speeies, therefore, to increase its rotational speed from drive the wheel tooth device of changing into by the second clutch driving 10,50 by main clutch, thereby faster than another

wheel tooth device

10,50 operations, therefore " flee from " another

wheel tooth device

10,50 that has changed over chain 5 this moment and driven fast by main clutch 11.

The second

wheel tooth device

10,50 is temporarily with higher speed operation, the retainer 31 that is provided with on it collides wall 56 on the spline parts 8 that are connected in another wheel tooth device 10,50.Retainer 31 so that make the gear-box smooth running, and forms the adjustment limit preferably by spring 57 bias voltages, sees Fig. 7.The power of the force rate second clutch 12 of spring 57 is bigger.Thereby the second

wheel tooth device

10,50 temporarily enters it and is engaged on this position in the chain 5 once more.

This circulation is continuously carried out, and like this, two

wheel tooth devices

10,50 are with driven chain 5.The steady engagement of wheel tooth device is possible, because it is driven by more weak second clutch 12.Another factor is, second clutch is than the faster drive

gear teeth device

10,50 of meshed gears tooth device, therefore before it begins chain 5, provides certain transmission time and is used for 10,50 engagements of the second wheel tooth device and advances chain 5.

Wheel tooth device

10,50 can be engaged in the recess 37 of chain 5, and does not influence the driving of chain 5, and another

wheel tooth device

10,50 that the driving of chain 5 is connected in main clutch 11 influences.After this, when

tooth

32,33 or 51 was engaged in the chain 5 safely, this

wheel tooth device

10,50 was seen Fig. 8, Fig. 9 a, Fig. 9 b or Fig. 9 c by alternately beginning chain 5 to main clutch 11.

As selectively, see Figure 12,

wheel tooth device

10,50 can all drive a period of time by main clutch 11 simultaneously, corresponding to the angle of rotation partial distance.This is possible, if two

wheel tooth devices

10,50 are connected in the only about half of periphery of their main clutch 11 above the reverie wheel.Therefore two

wheel tooth devices

10,50 have crossover in main clutch 11 joints.

This realization this point, cam axial region 20 is provided with cam curve, Design of cam curves for make main clutch 11 be engaged more than about 180 the degree.Also can realize by control electronics or fluid clutch device.

When using second embodiment of clutch drive apparatus, main clutch and second clutch from input shaft 1 by the single gear unit 49 of for example each spindle unit with identical speed driving, see Figure 13 and Figure 22.Main clutch 66 still is than second clutch 67 more dynamic clutches.Preferably, second clutch 67 is engaged always, and 68 a part of revolutions of engagement of main clutch, for example only about half of revolution.

Therefore, when wheel tooth device not during transmitting torque,

wheel tooth device

10,50 is driven by more weak second clutch 67, enters once more and is engaged in the Transmitted chains 5 up to it.Then main clutch 66 also begins drive

gear teeth device

10,50, is engaged in the chain 5 once more and begins up to relative wheel tooth device to be driven by its main clutch 66.Till that time, 10,50 in the first wheel tooth device is driven by its second clutch 67.

The preferred embodiment of wheel tooth device 10 comprises two

teeth

32,33 that are provided with by on connecting rod 36 interconnective each

bar

34,35, sees Fig. 8.(visible on travel direction) first tooth 32 is more outstanding than second tooth 33 in radial direction.First bar 34 is by spring (not shown) radially outward bias voltage, and As mentioned above being coupled to each other.

When wheel tooth device 10 during with chain 5 engagements, first tooth 32 is engaged on 37 li of the chain recesses of chain.If during the chain 5 between first tooth, the 32 collision chain recesses 37, see Fig. 8, on preferred planar surface 38, tooth 32 is radially pushed inward, and because 37 li of chain recesses are given prominence to and be engaged on to connecting rod 36, the second teeth 33 radially outwards.

Therefore, provide the steady and safe engagement of wheel tooth device 10 in chain 5.Phase mutual edge distance between two

teeth

32 and 33 is preferably pitch only about half of of chain 5.

Second embodiment of wheel tooth device 50 comprises a wheel tooth 51, preferably has hypotenuse, sees Fig. 9 a and Fig. 9 b.In Fig. 9 a, the first wheel tooth device 50 and its lining 9 are partly cut away in the figure, so that do not cover second wheel tooth device 50 and its lining 9 that disposes on the relative spline parts 8 of relative spindle unit.The first wheel tooth device 50 is also shown in two position I and the III.

Wheel tooth device 50 length direction in guiding element 52 is removable, and by at least one spring 53 radially outward fexible bias pressure in this guiding element 52.Guiding element 52 is disposed at spline parts 8 angularly.When tooth 51 will be engaged on 51 li on chain, tooth 51 recess 37 of collision chain 5 or collision in most cases be the inclined-plane 54 of guiding recess 37 downwards.

There is edge 55 separately downwards between two inclined-planes 54 of guiding recess 37.Therefore, tooth 51 is before this edge 55 or slide into recess 37 afterwards.However, still exist tooth 51 just in time to collide at the edge possibility at 55 top, see position I.If this thing happens, chain 5 will overcome the elastic force application of force makes tooth 51 radially slip into guiding element 52 inwards, sees Fig. 9 b.Simultaneously, wheel tooth device 50 will travel forward with chain 5.

Because this wheel tooth device 50 is than the bigger distance of chain 5 motion, so it will travel forward sooner than chain 5, and tooth 51 is removed inclined-plane 54 that moves to the front and the recess 37 that slides into the front.Wheel tooth device 50 is pushed into the retainer 31 of another wheel tooth device 50, and spring 57 is compressed.Second clutch 12 slides simultaneously.Therefore it is possible forwards adjusting.Thereby 50 engagements of wheel tooth device are in chain 5, and the driving to chain 5 is taken in preparation.

The 3rd embodiment of wheel tooth device also is the (not shown) that can expect.It is included in a wheel tooth that is provided with on the bar.This bar in the angle of rotation direction by fexible bias pressure forward and backward.Here provide wheel tooth and slided into possibility in the nearest recess that is engaged on chain.Preferably, chain is provided with the inclined-plane that tilts in the recess between the recess.

Most time,

tooth

32,33 or 51 need be with respect to contacting with chain 5 on the position of chain direction or small position change forward or backward.When

tooth

32,33 or 51 need move backward, it will be driven by more weak second clutch 12, thereby clutch slip is engaged on 5 li on chain up to wheel tooth device 10,50.If tooth need travel forward, the second

wheel tooth device

10,50 will be promoted by chain 5, and by second clutch 12 drivings, make the spring 57 of 31 li of retainers on the spline parts 8 be connected in main

gear teeth device

10,50 by mild compression at least, see Fig. 8, the second wheel tooth device meshes in the chain recess 37 of front simultaneously.

When an engagement in

tooth

32,33 or the tooth 51 was in chain 5, the driving of

wheel tooth device

10,50 can be changed into main clutch 11 from second clutch 12, thus chain 5.Simultaneously, can change into by second clutch 12 drivings and with chain 5 and break away from by another

wheel tooth device

10,50 of main clutch 11 chains 5, and the fact owing to being driven by second clutch 12 begins wheel tooth device 10, the 50 quicker operations that chain drives than this moment.

In a preferred embodiment, chain 5 is preferably made by a plurality of bolts, this bolt is connected with sidepiece 41 by connecting rod 40, see Fig. 2, recess 37 is formed between the bolt, and As mentioned above, bolt is preferably made flat in inside, thereby forms the flat 38 between the chain recess 37 when using the wheel tooth device 10 of preferred embodiment.Sidepiece 41 has and the corresponding outside 42 that tilts of the inclination of conical plate 24.Certainly chain 5 also can otherwise design, but preferably has certain device that guide

gear

32,33 is engaged on 5 li on chain.

According to the second and the 3rd embodiment of wheel tooth device 50, chain 5 is provided with inclined-plane 54, and when the wheel tooth device 10 with preferred embodiment used, inclined-plane 54 tilted in the recess 37 between the recess 37 rather than flat 38.

In Fig. 9 c, show another embodiment of chain 5, here, recess 37 is arranged between the connecting rod 40, and inclined-plane 54 and edge 55 are configured in connecting rod 40 places.

In one embodiment, the wheel tooth device is partly cooperated to pass through main clutch 11 chains 5, and chain 5 preferably can surpass 180 degree around the reverie gear, for example reach 320 degree, sees Figure 12.This realizes by at least one (being two in an illustrated embodiment) tension pulley 63.If only use a tension pulley, preferably it has the diameter (do not look out) bigger than two tension pulleys shown in Figure 12 63.

In this embodiment, Transmitted chains 5 preferably is provided with the bolt 64 of circular cross-section and the outside connecting rod 40 of turning-in a little, makes chain 5 steadily follow the circumference of one or more tension pulleys 63.In this embodiment, connecting rod 40 is provided with the outstanding inwards part that constitutes inclined-plane 54 and edge 55, thereby chain recess 37 is arranged between the projection of connecting rod 40.

In first embodiment according to CVT of the present invention, outlet side comprises second gearbox shaft 6.It is driven by chain 5, and the first

wheel tooth device

10,50 is engaged on 5 li on chain, and the

wheel tooth device

10,50 by being connected in main clutch 11 is from chain 5 and further to output shaft 2 transferring power.Second gearbox shaft 6 to be working with first gearbox shaft, 4 corresponding modes, thereby and

wheel tooth device

10,50 in the mode identical with the above alternately from chain 5 to output shaft 2 transferring power.

See Fig. 1, gear graduation axle 3 is provided with the screw thread 27 that is used for two

gearbox shafts

4,6, but is used for two

axles

4,6 in relative direction.Therefore when gear graduation axle 3 rotates, be connected in each arm of 4,6 26 and be synchronized with the movement.

Like this, conical plate 24 is mutually away from motion, and correspondingly, gearing 10,50 is return in any one described mode and is formed on the reverie gear that an axle reduces pitch diameter, conical plate 24 motion opposite to each other mutually simultaneously, and correspondingly wheel

tooth device

10,50 is outstanding in any one described mode, is formed on the reverie gear of another increase pitch diameter.Chain 5 will be extended always like this.

In second embodiment according to CVT of the present invention, outlet side comprises second gearbox shaft 6, sees Figure 22.It is driven by

chain

5, and 10,50 engagements of the first wheel tooth device are in chain 5, the

wheel tooth device

10,50 by being connected in main clutch 66 from chain 5 further to outlet side 2 transferring power.Second gearbox shaft 6 is to work with first gearbox shaft, 4 corresponding modes, and

wheel tooth device

10,50 drives second clutch 67 always, and drives about revolution half, also drives main clutch 66 like this.

In the 3rd embodiment according to CVT of the present invention, outlet side comprises gear 7, sees Figure 10 and Figure 11.If pitch diameter and chain pitch coupling makes tooth 43 engagements of gear 7 in chain 5 and need not any controlling device, if but for example diameter be five equilibrium, then this is possible.

For " diameter " that makes chain 5 not rely on two

wheel tooth devices

10,50 of gearbox shaft 4 keeps elongation, gear is installed in slide part 44 movably.Slide part 44 is removable along at least one guiding element 45 (being preferably two), and each is arranged on each sidepiece of gear 7, sees position I and position II among Figure 10 and Figure 11.Slide part 44 is connected in gear graduation axle 3 by the nut 48 that attaches to slide part 44 securely with feed gear's axis 46 and helical gear device 47.Therefore, the transformation of the gear of gear graduation axle 3 promptly changes the rotation of being transmitted and change into feed gear's axis 46 by helical gear device 47.Preferably, gear graduation axle 3 and feed gear's axis 46 arranged perpendicular.

Feed gear's axis 46 preferably has the screw thread 49 that advances that along with the change of gearbox shaft 4 diameters routing motion needs, and makes chain 5 balance and fully elongation well.Nut 48 has a cylindrical recess with the short internal thread (not shown) of band, and this internal thread can be followed the advancing outside thread 49 of feed gear's axis 46 and move.The rotation of gear 7 by directly or with any easily, the suitable manner (not shown) passes to output shaft 2.Certainly, if desired, can expect using gear that is used for input side and the gearbox shaft 4 that is used for outlet side.

Based on first and second embodiments, also be possible according to the 4th embodiment of CVT of the present invention.When existing the pitch diameter that is complementary with chain pitch to make that distance between two

wheel tooth devices

10,50 is 180 when spending in one of

gearbox shaft

4,6, described gearbox shaft can move and need not any clutch variation.Main clutch 11 meshes incessantly by retraction pin 18, makes pin 18 not interact with cam axial region 20.Like this, automobile is with identical speed run duration, and during for example expressway drove, the mechanical wear of parts reduced.This feature of the 3rd embodiment can be by for example program control (not shown).

Tumbler gear can be used on the output shaft 2 in a conventional manner.

The stepless speed variator of gear assembly of the present invention and this gear assembly of use is not subjected to shown and described embodiment's restriction, but the various modifications of parts within the scope of the appended claims,, variation and to substitute be also can further developing of can expecting.

Claims

1. a gear assembly is formed the reverie gear with variable pitch diameter, and this gear assembly is suitable for stepless speed variator, it is characterized in that, this gear assembly comprises two wheel tooth devices (10,50), and described two wheel tooth devices (10,50) can move radially.

2. gear assembly according to claim 1 is characterized in that, mutual 180 degree of described two wheel tooth devices (10,50) ± 20 degree are directed.

3. gear assembly according to claim 1 and 2, it is characterized in that, described wheel tooth device (10,50) is connected each radial arrangement parts (8) movably in radial direction and locates, described radial arrangement parts (8) be configured in gearbox shaft (4,6) two alignment spindle unit relative towards the end on.

4. gear assembly according to claim 3, it is characterized in that, two conical plates (24) are set, and each conical plate (24) is arranged on the place, each relative end of parts of two alignment of described gearbox shaft (4,6), so that at its side supports Transmitted chains (5).

5. gear assembly according to claim 4, it is characterized in that, described conical plate (24) can be synchronized with the movement in opposite directions mutually by each arm (26) and can be mutually away from being synchronized with the movement, and the relative orientation that described arm (26) is gone up setting by gear graduation axle (3) is threadedly connected to gear graduation axle (3).

6. gear assembly according to claim 5 is characterized in that, described wheel tooth device (10,50) by described conical plate (24) but mutual move toward one another and radially outward is synchronized with the movement.

7. gear assembly according to claim 5, it is characterized in that, described wheel tooth device (10,50) can radially be synchronized with the movement inwards by the chain (89) of configuration in the wheel tooth device (10,50) and by the connecting rod (92,100) that is connected in arm (26), and described arm (26) can be synchronized with the movement by gear graduation axle (3).

8. gear assembly according to claim 5, it is characterized in that, described wheel tooth device (10,50) by at least one controlling rod (28) radially arrangement components (8) can radially be synchronized with the movement inwards and outwards, described controlling rod (28) is configured in wheel tooth device (10,50) and locates and be configured in the spindle unit place, described controlling rod is connected in conical plate (24), described conical plate (24) is connected in gear graduation axle (3) successively by arm (26), and therefore described controlling rod can be synchronized with the movement with described conical plate (24).

9. according to any one the described gear assembly in the aforementioned claim, it is characterized in that described two wheel tooth devices (10,50) substantially alternately are engaged on Transmitted chains (5) lining.

10. according to any one the described gear assembly in the aforementioned claim, it is characterized in that, each wheel tooth device (10,50) drives at least a portion revolution by main clutch (11,66), and drives at least a portion revolution by second clutch (12,67).

11. any one the described gear assembly according among the claim 1-9 is characterized in that, each wheel tooth device (10,50) drives at least a portion revolution by main clutch (66), and is driven by second clutch (67) always.

12., it is characterized in that described clutch (11,66,12,67) drives the spindle unit that disposes wheel tooth device (10,50) on it according to claim 10 or 11 described gear assemblies.

13. gear assembly according to claim 10 is characterized in that, rotating cam (14,20) is cooperated with pin (18), so as control main clutch (11) and second clutch (12) with and spring (16,17).

14., it is characterized in that at least one stationary cam (84) is cooperated with at least one cam follower (85) according to claim 10 or 11 described gear assemblies, so as control main clutch (66) and second clutch (67) with and spring (77,79).

15. any one the described gear assembly according in the aforementioned claim is characterized in that, wheel tooth device (10) comprises two wheel teeth (32,33) that each bar (34,35) upward is provided with, and described bar interconnects by connecting rod (36).

16. gear assembly according to claim 15 is characterized in that, first wheel tooth (32) is more outstanding in radial direction than second wheel tooth (33).

17. gear assembly according to claim 15, it is characterized in that, the at least the first gear ratch (34) is by the radially outward fexible bias pressure, thereby radially can promote inwards, and second wheel tooth (33) and its bar (35) then because connecting rod (36) but the radially outward motion.

18. gear assembly according to claim 1 and 2, it is characterized in that, described wheel tooth device (50) comprises a wheel tooth (51), wheel tooth device (50) length direction in guiding element (52) is movable, and in this guiding element (52) by at least one spring (53) radially outward fexible bias pressure.

19. gear assembly according to claim 1 and 2 is characterized in that, described wheel tooth device comprises a wheel tooth, and described wheel tooth device is resiliently biased and can be forward and motion backward in the angle of rotation direction.

20. stepless speed variator, comprise input shaft (1) and the take-off lever (2) that is connected in input shaft (1) by the first gear-box bar (4) and second gearbox shaft (6) by Transmitted chains (5), it is characterized in that, each described first and second gearbox shaft (4,6) comprises according to any one the gear assembly in the aforementioned claim, thereby described first gearbox shaft (4) is driven by input shaft, described second gearbox shaft (6) is driven by first gearbox shaft (4) by Transmitted chains (5), and output shaft (2) is driven by second gearbox shaft (6).

21. stepless speed variator according to claim 20, it is characterized in that, gear graduation axle (3) is connected in described first gearbox shaft (4) and described second gearbox shaft (6) by arm (26), being synchronized with the movement of two wheel tooth devices that is used for each gearbox shaft (4,6), so that reduce the pitch diameter of first gearbox shaft (4), increase the pitch diameter of second gearbox shaft (6) simultaneously; Perhaps vice versa.

22. stepless speed variator, comprise input shaft (1) and the take-off lever (2) that is connected in input shaft (1) by gearbox shaft (4) and gear (7) by Transmitted chains (5), it is characterized in that, gearbox shaft (4) comprises according to any one the gear assembly in the aforementioned claim, thereby gearbox shaft (4) is driven by input shaft, gear (7) is driven by first gearbox shaft (4) by Transmitted chains (5), and output shaft (2) is driven by gear (7); Perhaps vice versa.

23. stepless speed variator according to claim 22, it is characterized in that described gear (7) is installed movably so that make Transmitted chains (5) not rely on the pitch diameter of the reverie gear that is formed by two the wheel tooth devices (10,50) in the gearbox shaft (4) and kept being extended.

24. according to claim 22 or 23 described stepless speed variators, it is characterized in that, gear graduation axle (3) is connected in gearbox shaft (4) by arm (26), be used for being synchronized with the movement of two wheel tooth devices, and be connected in gear (7), be used for being synchronized with the movement of gear (7),, increase the distance between gearbox shaft (4) and the gear (7) simultaneously so that reduce the pitch diameter of gearbox shaft (4); Perhaps vice versa.