CN1802526A - Infinitely variable transmission - Google Patents
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- CN1802526A CN1802526A CN 200480006745 CN200480006745A CN1802526A CN 1802526 A CN1802526 A CN 1802526A CN 200480006745 CN200480006745 CN 200480006745 CN 200480006745 A CN200480006745 A CN 200480006745A CN 1802526 A CN1802526 A CN 1802526A
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Abstract
An IVT machine (10) comprising an input shaft (12), a drive wheel (14) on the input shaft, an output shaft (22), a ratio changing device (20) which is mounted on the output shaft, an endless belt (34) which passes over the drive wheel and in an open loop on the ratio changing device, control means for enlarging and reducing the belt loop dimension about the output shaft axis, belt guide means (26) providing a throat (30) through which the belt enters and leaves its loop on the ratio changing device, and a drive arrangement on the ratio changing device for the transmission of drive power to the output shaft and is engaged with the belt in a portion of its loop on the device and engageable with the belt on both sides of the throat in its transition across the throat during rotation of the ratio changing device.
Description
Invention field
But the present invention relates to a kind of IVT (stepless speed variator) machine of incremental operation, its expection is used for the operation of high-power and high angular velocity, and can come in enterprising action edge transmission in the other direction to realize engine braking by it.
Background of invention
Had the prior art that relates to the above-mentioned type IVT machine in a large number.The typical case of these machines is introduced in following publication: relate to US4878883, GB2062142A, GB2135743A, US4618331, US3956944, US4832660, US5984814 and US4787879 that bicycle has.What relate to CVT/IVT has WO03/042575 and a WO03/078869.Relate to band groove/fin the tapered disk connected member WO01/75333 and US4367067 arranged.What relate to speed-changing chain hook loop chain has WO94/04411 and a US5406863.
From the specification of US4878883, GB2062142A, GB2135743A, US4618331, US3956944, US4832660, US5984814 and US4787879, can see, these machines comprise the bonding apparatus that radially is provided with substantially, and it can be operated in the trapped orbit that radially separates around variable sprocket hub by sprocket tooth or with friction mode.Because the limited amount of bonding apparatus, therefore the flexible member track around them does not constitute circular arc, so their output is pulsed.Another problem relevant with these prior art machines is, therein by spring-loaded sprocket tooth or rotatable full sprocket wheel and in fixed guide operation to realize engaging part, its bonding apparatus and driver link can't be accurately synchronous, this makes these devices be only applicable to low-speed applications, for example bicycle.In the application of high speed and high moment of torsion, the machine of above-mentioned prior art is inappropriate.
Under the situation of WO03/042575 and WO03/078869, stationary problem is resolved basically, but they depend on the free wheeling sprag clutch that two-way power transmission (not allowing engine braking) can not be provided.
Under the situation of WO01/75333 and US4367067, chain exists stationary problem once more with mandatory synchronous joint of disk groove/fin.
Under the situation of WO94/04411 and US5406863, can realize mandatory joint, but the storage of ladder chain and adjusting thereof exist problem in high-speed applications.
Device in above-mentioned most of publication has all been sacrificed synchronous mandatory joint, so that can change velocity ratio with infinitesimal increment.
Brief summary of the invention
IVT machine according to the present invention comprises: input shaft; Can be transfused to the driving wheel that axle rotates; Output shaft; The rate of change device, it is co-axially mounted on also can be in company with rotation therewith on the output shaft; The endless belt, it is through driving wheel, and be positioned at support on the rate of change device rate of change configuration (formation) on band road go up the form that forms open loop; Control mechanism, it is used for making the rate of change configuration change the speed ratio of input shaft and output shaft by the band road size around the output shaft axis of amplifying and dwindle on the ratio changeable device; Tape guide mechanism, band can move thereon so that narrow orifice is provided, and band can enter and break away from it and be positioned at loop on the rate of change device by narrow orifice; And drive unit, it is located on the rate of change device to be used to transfer a driving force to output shaft, drive unit engages with a part of loop that is positioned on this device of band, engaging with band in the both sides of narrow orifice during in its transition during the rotation of rate of change device, and keeping optimum engagement with band in all ratios position on the band road on the rate of change device by narrow orifice.
Tape guide mechanism comprises two band guide wheels, and they are arranged to closely adjacent each other, and defines the band narrow orifice between them.
Machine comprises and has carried output shaft, the rate of change device, the frame of input shaft and band degree of tightness regulating device, and frame member, frame member has carried or each tape guide mechanism, and can move towards and away from the rate of change device with incremental calibration step-length with respect to frame by controller, so that comply with the band road size that changes during the rate of change, and provide and remove as requested through the band narrow orifice band of the predetermined length in the band road on the rate of change device back and forth, and when the speed ratio controlled device of the input shaft of machine and output shaft changed, drive unit was away from the chain narrow orifice.
The rate of change device can comprise a pair of frustoconical disk, it can move towards and away from ground on output shaft each other by control mechanism, wherein their conical surface faces with each other, and the supported rate of change configuration thereon of relative edge of band is provided between them.
Band can be the chain that is made of chain link, these links are crossed the connecting pin that equi-spaced apart opens and are linked together, these connecting pins are outstanding from the side of chain, and have on the conical surface that is pressed against the rate of change disk and the end face tapered complementaryly with the cone angle of the conical surface, so that it is circular making the tensioning chain loop between the disk, the width of its medium chain determines that by the gap between the disk in the low ratio position of chain that is between the disk and the cone angle of the conical surface thereof belt wheel is a sprocket wheel.
Frame member can comprise two isolated arms, its remaining part from frame member is outstanding, and all engage with configuration sliding type on one of rate of change disk, wherein leave by controller and when disk moved, arm and disk configuration can make disk move towards and away from ground each other on output shaft when frame member.
Drive unit comprises the part sprocket wheel, and its arc length is greater than the gap width at the circular chain link Lu Zailian narrow orifice place on the rate of change device.The sprocket tooth of drive unit each other separately and can move each other, to keep with the output shaft axis be the center by being connected guide mechanism on the output shaft in all ratios position in the chain loop of their center on the rate of change device.Be easily, sprocket tooth all is carried on first end of arm, wherein the tooth on the centre tooth both sides of part sprocket wheel tiltedly departs from out centre tooth in its arm updip, output shaft laterally splits, its cleaved end all is connected on the tooth godet housing coaxially, wherein the pin on second end of tooth arm can move in the groove in the godet housing transverse to the axis of output shaft, be used for guide gear towards and away from the output shaft axis and simultaneously each other towards and away from motion, so that change the arc of sprocket wheel, thereby ideally mate in any ratio position of machine and the radius of curvature of the chain loop between the disk.
In second kind of form of the present invention, drive unit can comprise a series of undercut groove of the conical surface that is arranged in each rate of change disk, its periphery from disk extends towards output shaft, their center line certain size that on its length, is spaced from each other, this size equals the distance that the axis of the chain connecting pin on the single chain link separates each other, and the bottom of groove is parallel to the conical surface of disk.
In this form of the present invention, drive unit can comprise the tooth carrier of independent fixed length, it quantitatively equals the quantity of the groove on the disk, the tooth carrier carries sprocket tooth, wherein in all ratios position of the chain between disk, the center line of each tooth is positioned on the radial line that is derived from the output shaft axis, also carry the configuration that is positioned at place, carrier end, they are arranged to have complementary angle with the cone angle of bottom portion of groove, and are bonded in the relative groove of each series on the rate of change disk.Groove quantity in each disk series is enough to make the sprocket on the interior tooth carrier of the groove in two relative series of recesses that are bonded on disk to cross the chain narrow orifice, and in during the drive unit transition is by narrow orifice, at least one tooth maintenance of drive unit each end engages with the chain on the narrow orifice both sides.
Central recess in the groove series of each disk is positioned on the radial line that is derived from the output shaft axis, what be positioned at groove on the central recess either side is crooked on the direction of part at central recess of output shaft, the distance that between their center line, keeps two connecting pin axis simultaneously, so that the tooth center line on the tooth carrier in these grooves leaves the centre tooth rotation at the low ratio from the chain loop between the disk during the rate of change of height ratio position, and during the rate of change of the low ratio position of chain, rotating towards centre tooth, so that the maintenance of any ratio position between disk is suitable for the tooth curve of the part sprocket wheel of chain annulus, keeping with the output shaft axis simultaneously is the center, and the maintenance of the center line of tooth is the center with the output shaft axis.
The bottom cutting portion of the central recess in each series is preferably identical on the both sides of groove external lateral portion on the whole length of groove, and the groove bottom cutting portion on the central recess both sides leaves the external lateral portion of the deviation in driction of central recess in groove on the edge, periphery place of disk, wherein the side-play amount of each groove undercutting becomes big successively in gradually away from those grooves of central recess, and the side-play amount of these groove undercutting is moved towards central recess on the whole length of groove.
Engage grooves configuration on the centre tooth carrier end can be horizontal configuration, it can be bonded in the groove undercutting by the external lateral portion of groove, configuration on each all the other tooth carrier ends can be outwards outstanding cylindrical first configuration, it tightly fits in the external lateral portion of groove, under horizontal configuration, be second configuration with cylindrical shank, its cross-sectional dimension is less than the width of the external lateral portion of groove, and on its free end, carry the radially outstanding configuration in the bottom cutting portion that tightly fits in groove, wherein this configuration is arranged so that it leans against the surface on the bottom portion of groove and the surface co-planar of cylindrical configuration, angle corresponding to the cone angle of the disk conical surface has been formed on the bottom of groove, when second configuration in the rate of change process when the bottom cutting portion of groove moves, it makes carrier center on it and partly rotates around first configuration through the axis of first configuration.
In a kind of modification of second kind of form of the present invention, central recess in the groove series of each disk is positioned on the radial line that is derived from the output shaft axis, what be positioned at groove on the central recess either side is crooked on the direction of part at central recess of output shaft, keep a connecting pin axial line distance simultaneously between their center line, wherein the external lateral portion of the bottom cutting portion of each groove is symmetrical on the either side of groove center line on the cross section.
In this modification of second kind of form of the present invention, drive unit can comprise the drive unit bar, it quantitatively equals the quantity of the groove in the disk series, the certain angle of end tapered inclination of bar, this angle also is provided with the groove that is parallel to the bar tapered end corresponding to the cone angle of bottom portion of groove in the opposite side of bar, engage to be used for forming between the external lateral portion of groove, thereby bar is remained in the groove, and its tapered end leans against on the bottom of groove.
The used band of this machine is the chain that is made of chain link, links is crossed connecting pin and is linked to each other, and including the configuration that inwardly is arch by the center between its connecting pin that links to each other and from common edge, wherein the arch configuration engages and locates thereon with the drive unit bar, so that driving force is passed to the drive unit bar from chain.Chain link is curved at the common direction of chain, and wherein the arch configuration stretches into the chain link from its concave edge.
Groove quantity in each disk series is enough to make the bar of the drive unit between the disk to cross the chain narrow orifice, and simultaneously during the rotation of disk, by in a period of time of narrow orifice, many bars keep engaging with chain on the narrow orifice both sides in the transition of drive unit bar.
In the third form of the present invention, the rate of change disk all can comprise the array of spaced fin, it is outwards given prominence on disc surfaces, and extend towards output shaft from disc circumference, thereby between them, define the drive unit groove, the bottom of groove is on the conical surface of disk, and when drive unit passed through narrow orifice before or after the rate of change of machine, the chain connecting pin can debouch in the groove.In all ratios position of the chain between disk, the groove between the fin is spaced apart mutually certain size on its length, and this size equals the distance of separation of the axis of adjacent chain connecting pin.
Central recess in the groove series of each disk is positioned on the radial line that is derived from the output shaft axis, what be positioned at groove on the central recess either side is crooked on the direction of part at central recess of output shaft, keeps the distance of a connecting pin axis simultaneously between their center line.
The quantity of the groove in each disk series is enough to make the chain connecting pin in the groove of two relative groove series that are bonded on disk to cross the chain narrow orifice, groove at drive unit passes through in the transition period of narrow orifice simultaneously, and at least one groove maintenance of drive unit each end engages with the chain on the narrow orifice both sides.
The side of fin can be from it the surface towards the bottom portion of groove between them and outside tapered inclination.
The laterally projecting end of chain connecting pin that is used for the machine of this form is taper, and its cone angle is corresponding to the cone angle of rate of change disk, and wherein each end all preferably has conical head, and it is sized to be matched with well in the conical socket between the fin.The head of connecting pin is slidably engaged on the end of pin, chain comprises and is positioned at adjacent pin to last outer link device, it is suitable for exposing the tapered end of pin from its head in the straight section of chain, when chain becomes bending, it can make head little by little move towards the tapered end of pin, so that promote it to enter and leave the groove of disk drive unit at chain narrow orifice place.
Rate of change disk in the of the present invention second and the 3rd form includes the outwards outstanding lug boss round output shaft on itself and its conical surface opposite surfaces, and be fixed on rate of change gear on the cylindrical rate of change gear carrier of outside thread formula, it can engage with lug boss and rotate freely thereon, and, make the rotation together of rate of change gear that the sense of rotation of disk and gear will be moved relatively with leaving towards each other and with the internal thread main body threaded joint on the machine frame spare.Machine can comprise two index gearss easily, it is fixed on journalled and connects so that on the common shaft that rotates in machine frame spare, and be meshed with the rate of change gear separately, also comprise flip flop equipment, it is used for rotating suddenly the index gears axle, to impel index gears and rate of change gear on required direction, to produce the part calibration rotation of one or more settings according to instruction from machine controller, this makes frame member carry out dividing movement toward or away from the initial chain loop between the rate of change disk as requested simultaneously, so that the chain of predetermined length is provided or therefrom removes the chain of predetermined length for the chain loop.
Flip flop equipment preferably includes machinery and triggers energy storage device, and it can rotate the axle of index gears suddenly when the device that is triggered triggers.Energy storage device can be torsion bar.The axle of index gears is a pipe fitting, an end setting of torsion bar and being fixed in the index gears pipe, and its second end is connected on the suitable gear motor, is used for applying suitable moment of torsion to bar on arbitrary sense of rotation of the index gears that controller has been selected.
In a kind of distortion of the third form of the present invention, the rate of change disk all can comprise the array of spaced fin, it is outwards given prominence to from the surface of disk, and extend towards output shaft from the periphery of disk, so that limit the groove of drive unit between them, the bottom of groove is on the conical surface of disk.
Band in this distortion is the endless belt of the flexible material of inductility, and it comprises having the laterally projecting configuration that forms complementary shape with the groove of the drive unit of disk on opposite side.
The driving wheel of this machine can be for having the pulley of flange, it comprise on the internal surface of its flange with disk on fin and the corresponding inwardly outstanding fin shape configuration of groove configuration, the guide wheel of remaining band in the machine is a roller.
In the another kind of form of machine of the present invention, the rate of change device can be the combination device for disc, and it comprises: first and second disks of overlapping and band plane side; Be in first disk and be positioned at least three straight-line grooves on the radial line that is derived from output shaft; Be in the crank slot of the equal number in second disk; The band rest pin, it is arranged in the groove of these two disks and therefrom passes, and vertically stretches out from first disk, and the loop of band is supported on the combination disk and is on these pins; And the mechanism that can operate by the machine control mechanism, it can make second disk with respect to the rotation of first integrated disc portions ground, thereby make the crank slot in second disk that the band rest pin radially inwardly or is outwards moved in the groove of first disk, with the band road size on the change pin, thus the speed ratio of change input shaft and output shaft.
The band of this machine can be the chain that has uniform-dimension between its connecting pin.
The drive unit of this machine can be in first form of the present invention the sort of.
In this specification and comprise its claim, term " band " such as in " The AmericanHeritage Dictionary of English Language " dictionary definition ground be " being used to make motion or power to be passed to continuous belts or chain on another " from a wheel or axle.
Brief description
Referring now to accompanying drawing and only introduce the embodiment of IVT machine of the present invention, in the accompanying drawings by non-limiting example:
Fig. 1 is the schematic side elevation of basic I VT machine of the present invention,
Fig. 2 is the front view of two rate of change disks of machine shown in Figure 1,
Fig. 3 is the stereogram of looking from the top of a practical embodiments of machine shown in Figure 1, has shown the low ratio position of its operation,
Fig. 4 is the view identical with Fig. 3, has shown that machine is in the height ratio position of its operation,
Fig. 5 is the front section view of the chain of machine shown in Figure 3,
Fig. 6 is the rate of change disk of machine shown in Figure 3 and the exploded perspective view of frame member,
Fig. 7 is the front section view of the rate of change device of machine shown in Figure 3,
Fig. 8 is the exploded perspective view of the drive unit of machine shown in Figure 3,
Fig. 9 is the exploded perspective view of the tooth assembly of drive unit shown in Figure 8,
Figure 10 is the schematic front view of part of the drive unit that has assembled of machine, has shown the low ratio position of machine,
Figure 11 and 12 is side views of machine shown in Figure 3, has shown low, the height ratio position of machine respectively,
Figure 13 is second embodiment's of the IVT machine of the present invention perspective view of looking from the top,
Figure 14 is the rate of change disk of machine shown in Figure 13, the rate of change gear of disk and the decomposition view of drive unit,
Figure 15 is the front section view of the rate of change device of machine shown in Figure 13,
Figure 16 is three the exploded perspective view that is used in five tooth carriers of drive unit of machine shown in Figure 13,
Figure 17 and 18 is roughly front views of the calibration flip flop equipment of machine shown in Figure 13,
Figure 19 is the partial elevation view of the disk and the drive unit of machine shown in Figure 13,
Figure 20 and 21 is the partial perspective views that are used for a kind of modification of machine shown in Figure 13 and other chain that installs,
Figure 22 is the 3rd embodiment's of the machine of the present invention stereogram of rate of change device,
Figure 23 is the perspective view of the rate of change disk of machine shown in Figure 22,
Figure 24 is a part that is used for the chain of machine shown in Figure 22,
Figure 25 and 26 is the front views of segment that are used for a kind of modification of machine shown in Figure 22,
Figure 27 to 29 is the stereograms of shorter length chain that are used for the groove modification of Figure 22 as shown in figure 25,
Figure 30 and 31 is with driving belt but not the stereogram of another modification of the rate of change disk of the machine shown in Figure 22 that chain uses,
Figure 32 and 33 is partial elevation view that are used to illustrate mathematical model of the drive unit groove of rate of change disk shown in Figure 22,
Figure 34 and 35 is the figure that are used for mathematical model shown in Figure 32 and 33.
Figure 36 be IVT machine of the present invention the 4th embodiment schematic side elevation and
Figure 37 to 39 is stereograms of parts of the rate of change device of Figure 36 machine.
Detailed description of the illustrated embodiment
In Fig. 1 and 2, schematically shown universal incremental IVT machine 10 of the present invention, it comprise have fixed drive sprocket wheel 14 from driven input shaft 12, idle running tension sprocket 16 and rate of change device 18, its middle sprocket 16 can move on the direction shown in the arrow in Fig. 1 by unshowned control mechanism or biasing mechanism.
Rate of change device 18 comprises a pair of rate of change disk 20, and it rotatably is fixed on the machine output shaft 22 and can together rotates with it.As shown in Figure 2, disk 20 has the relative butt conical surface 24, and can move towards and away from ground each other on output shaft 22 as described below, shown in the arrow among the figure.Yet concerning all embodiments of machine of the present invention, disk 20 does not have, from the last embodiment of the described machine of this specification, can see, this disk can be by the no conical surface but the disk that can carry out with disk 20 identical functions replace.
Control set part 28 can be sentenced machine output shaft 22 motions of just rotation by any suitable control mechanism in the fixed position in journalled is connected the machine frame on the direction shown in Fig. 1 arrow as suitable driving screw or hydraulic actuator device, and rate of change disk 20 is moved towards and away from ground on axle 22 as requested each other.Frame member 28 moves on both direction with very little incremental steps, and its purpose is as described below.
Rate of change device 18 also comprises part sprocket-type drive unit 32, and the tooth of this drive unit 32 can move individually, perhaps motion in groups each other.Drive unit 32 mechanical types are connected on the machine output shaft 22, or directly are connected on the conical surface 24 of rate of change disk 20, so as such as hereinafter detailed description transfer a driving force to output shaft 22.
Each rotating part of machine 10 is interconnected each other by the endless belt, and the endless belt is chain 34 in this example, shown in the dotted line among Fig. 1.Chain is shown as on the disk 20 that is among Fig. 2, and is between the low ratio and height ratio position of machine.
A key character of the present invention is, between the low ratio of machine and height ratio position and comprise in all operations position of these two positions, idler sprockets 26 the spaced distance in narrow orifice 30 places must be always less than, preferred significantly less than the track of the sub-circular chain 34 between the rate of change disk 20 diameter with respect to output shaft 22 axis.
Substantially, the operation of IVT machine 10 shown in Figure 1 is as follows: unshowned any suitable prime mover is connected on input shaft 12 and the driving sprocket wheel 14 thereof.Tension sprocket 16 leans against chain 34 on that part of being wedged by the tapered end of its connecting pin 36 of chain 34 with keeping tensioning, connecting pin 36 shows at Fig. 2 with being exaggerated, it leans against on the inclined-plane 24 of disk 20, so that the opposing chain is towards the uncontrolled radially inwardly motion of transmission machinery height ratio position.The indented joint of part sprocket-type drive unit 32 being between the adjacent connecting pin 36 of chain 34 driven any position in the chain periphery between the disk 20 of output shaft 22.
When all IVT machine parts are in the position shown in Figure 1, actuate prime mover on path shown in Figure 1 so that chain 34 moves.In doing so, machine output shaft 22 by drive unit 32 by itself and output shaft 22 mechanical coupling or be driven with the direct coupling of disk 20.
In order to guarantee the continuous rotation of disk 20 and output shaft 22, importantly drive unit 32 passes across narrow orifice 30 when it is driven rotation by chain, and there is not any interruption in the driven motion of its circular chain simultaneously.In order to guarantee to do like this, in the drive unit 32 process paths of narrow orifice, the tooth of drive unit 32 must be before lax bending appears in the chain that leaves narrow orifice with narrow orifice 30 both sides on chain 34 ideally engage, to guarantee driving force continuity during complete 360 ° of rotations of drive unit from chain to machine output shaft 22.This narrow orifice transition of drive unit must appear in all ratios position of the chain 34 between the disk 20.
Interfering appears in any drive unit 32 that is adopted for fear of chain 34 and machine, and importantly no matter adopt any control mode, when drive unit was in narrow orifice 30 zones of the chain annulus between the disk 20, machine can prevent any rate of change.
In order to change the input shaft of machine and the velocity ratio between the output shaft from the shown in Figure 1 low ratio position of chain 34, control set part 28 moves with respect to the left side of machine frame in figure by any control mechanism that adopts for this reason.When frame member 28 motions, its entrained idler sprockets 26 is motion together also.Disk 20 is used to its any device of controlling, actuates for the projection forward of frame member 28 in this example simultaneously, thus motion each other on output shaft 22 with leaving.The outside motion of disk 20 make chain connecting pin 36, therefore also have chain with drive unit 32 together between disk towards the output shaft motion, the motion of disk simultaneously causes the diameter of the chain rail between the disk to diminish, so that change the I/O ratio of machine.Simultaneously chain tension sprocket 16 moves upward from its position shown in Figure 1 by its control mechanism or is biased, so that at the tension force that keeps during any rate of change of machine on the chain.In order to reduce the machine ratio once more, move in the right side of control set part 28 in Fig. 1, and wherein the moving direction of above-mentioned its parts changes correspondingly reverse.
Referring now to Fig. 3 to 12, introduces first embodiment of the reality of machine shown in Figure 1 in detail.
Fig. 3 and 4 has shown the machine shown in Figure 1 10 that is in its low ratio and height ratio position respectively.In this two width of cloth figure, adopt with Fig. 1 in identical label represent with Fig. 1 in identical machine part.
From Fig. 3 and 4 as seen, and from Figure 11 and 12, can more clearly see, idler sprockets 26 does not have obviously outstanding sprocket tooth, this is because they are inoperative when the power of machine transmits, and only be to be configured in shape between chain roller 38, engage slightly with chain, so that the guiding chain is come in and gone out in narrow orifice 30, and avoid with narrow orifice 30 zone in the tooth and hair of part sprocket-type drive unit give birth to and interfere.
The IVT machine is located in the frame 40 that includes two mirror image side plates 42, shown in Fig. 3 and 4.The framework side plate has all that machine input shaft 12 and output shaft and 22 journalled are connected in wherein so that axle 46 skewed slots that can move therein 44, second horizontal slot 48 and the configuration 50 of the unshowned bearing that rotates, chain tensioning idler sprockets 16, and it has and is used for chain tensioner spindle 46 at its groove 44 helical spring 52 of bias voltage upwards.
Fig. 6 has shown the rate of change device 18 that includes rate of change disk 20 assemblies, machine output shaft 22 and control set part 28.Frame member 28 comprises two side arms 53 and transverse slat spare 54, and it comes keeping arm with spaced apart relation shown in Figure 6.Plate 54 has two pairs of onwards and relatively directed arc plates 55, and wherein each has supported axle to plate at its free end, and the sprocket wheel 26 that defines one group of three narrow orifice 30 can rotate freely on this axle.Arm 53 is that mirror image is identical, and includes a pair of outwards outstanding support configuration 56, its as illustrated in fig. 3 sliding type be located in the horizontal slot 48 in the rack side plate 42, so that guide support spare 28 is with respect to the controlled motion of machine frame 40.The front end of arm 53 is shaped as shown in figure, so that provide guide rail 57 on the either side of relative intilted guide-track groove 58.
Shown in Fig. 6 and 7, rate of change disk 20 includes outwards outstanding integral boss 60, it is provided with recess 62 at contiguous its place, outer end, also comprise the keyway 64 that leads to the general triangular radial groove 66 in disk 20 back sides, and the counter weight device 68 that during rotation is used for balance device for disc 20.
As shown in Figure 6, the device of rate of change disk 20 also comprises two axle sleeves 59, on its opposite side, have groove, the bottom of its further groove certain size that is parallel to each other and is spaced from each other, it equals to define separated spacing between the guide rail 57 of the groove 58 in arm 53 front portions of frame member 28.Groove passes the gradient of the angle of axle sleeve 59 outer surfaces corresponding to groove 58.
In the rate of change device 18 that has assembled, axle sleeve 59 is located in the recess 62 in the lug boss 60 of rate of change disk 20.Axle sleeve can rotate freely on lug boss 60.The guide rail 57 that is arranged in groove 58 either sides of tilted supporter spare 28 is located at the groove of axle sleeve 59 slidably.Pass through this set, frame member can be towards and away from relatively-stationary disk 20 assemblies motion, wherein its arm 53 is by recess supports in the axle sleeve 59 and guiding, so that by disk 20 being left each other and changing the velocity ratio of machine towards ground motion and the axis that makes the flat outer surface of axle sleeve keep being orthogonal to machine output shaft 22.
Shown in Fig. 7 and 8, the machine output shaft is a two-piece type built-up shaft 22, and wherein each shaft portion is held within it and had drive unit sprocket tooth godet 78 and triangle counterweight control mechanism 80.
Shown in Fig. 8 and 9, the part sprocket tooth assembly of drive unit 32 comprises a centre tooth 82 and other two pairs of teeth 84 and 86.The part sprocket tooth by lever arm 82 ', 84 ' and 86 ' carry, as shown in Figure 9, wherein each is mirror image ground each other to the tooth in tooth 84 and 86 and lever arm thereof and is provided with on the opposite side of centre tooth arm.Near the lever arm 82 of sprocket tooth 82 ' tooth 82, carry lateral pin 88, it has the beveled end shown in Fig. 7 and 9, similar with the connecting pin 36 of chain 34, when disk when moving towards and away from ground each other on the output shaft 22, lateral pin 88 is radially outward and motion upcountry between the face 24 of disk 20, keeps simultaneously engaging with chain.Lever arm 82 ' also comprise vertical ribs 89, its between the free end of pin 88 and arm arm 82 ' opposite side on extend.Each to tooth arm 84 ' and 86 ' in all the other arms all carry lateral pin 90 at its lower end, it is anchored in the tooth armed lever and is outstanding from the both sides of tooth armed lever.
In Fig. 9 and 10, more clearly illustrated the part sprocket tooth assembly of drive unit 32.Each tooth can be made by suitable metal plate laminated together with the arm that has these teeth.
Two on tooth arm 82 ' comprise all has the outwards outstanding lugs of curve bath 100, as shown in Figures 9 and 10, it has with the connecting pin axis of chain roller 38 is the radius of curvature R 1 at center, and roller 38 in use engages with tooth 82 on the side that has lug of tooth arm, and lug is located in this tooth arm.An outstanding lug of tooth arm 84 ' include, it is oriented and leaves tooth arm 82 ' and have curve bath 102, wherein the radius of curvature R 2 of curve bath 102 is the center with the axis of the chain roller 38 of connecting pin 36, roller 38 and tooth arm 84 ' on the therefrom outstanding side of trough of belt lug engage.Tooth arm 86 ' all have outwards outstanding lug 104, it has the curved upper surface that is centrally placed on the R2, and the downside of the lug on the tooth arm 84 is supported on the lug 104.
Ratch arm 84 ' and 86 ' cross side on its institute's its whole length, all have central channel with the upper and lower of giving prominence to lug, as shown in Figure 9.The tops that are positioned at below tooth 84 and 86 of groove have fixing curved guide members 106 and 108 respectively.In the tooth assembly that has assembled, guide 108 be arranged to be snug fit at well tooth arm 84 ' on the groove 102 of lug in, wherein guide 106 be arranged in similarly tooth arm 82 ' the groove 100 of lug.
For the continuous roller 38 of part chain wheel face to be used for support chain 34 is provided between tooth 82,84 and 86, outwards open with certain radius the bottom of tooth, and this radius equals the radius of the outer surface of chain roller 38.
In order to keep continuous chain supporting surface, the chain radius between the face 24 of disk 20 in use change during, when tooth 82,84 and 86 relatively moves each other by its lever arm, tooth 84 and 86 on the outside, only have separately be in fitted key 110 and 112 and centre tooth 82 in be positioned at key 114 on each side of tooth.The upper surface of these keys all is bent to the continuous part that opens the bottom of tooth.Key 110 on the tooth 84 be slidably located on tooth arm 86 ' inside side on groove 116 in, and key 114 be arranged in similarly arm 84 ' on groove 118.
Part sprocket-type drive unit 32 is shown as in Figure 10 and 11 in the low ratio position that is in transmission machinery, wherein sprocket tooth is centered close on the radially dotted line with respect to machine output shaft 22 axis, as shown in figure 10, so that between adjacent link roller 38, engage best and lean on thereon.As mentioned above, when the machine ratio from the long radius of drive unit 32 shown in Figure 10 and 11, low ratio position change to as shown in figure 12 more minor radius, during the height ratio position, must keep tooth 82,84 and 86 this orientations with respect to chain roller and machine output shaft axis.
In the low ratio position of the tooth assembly of chain shown in Figure 10 and 11 34 and drive unit 32, tooth arm 84 ' open with 86 ' as shown in figure pins 90 by them, pin 90 is located in groove 94 and 96 and away from the groove on the diametric(al) 92, these groove 92 bootable tooth arms 82 ' radial motion, therefore and guide the motion of whole interconnection tooth assembly.
According to instruction from machine controller, from the low ratio position shown in Figure 10 and 11 of the chain 34 between the disk 20 that separates during towards height ratio position shown in Figure 12 motion, chain connecting pin 36 and tooth assembly arm 82 ' pin 88 radially inwardly move on the conical surface 24 that leans against disk by the tensioning of chain 34, make chain diminish with respect to the turning radius of output shaft axis.In the meantime, as shown in figure 10, part sprocket-type tooth arm moves downward by its pin 90 motion in groove 94 and 96, moves as illustrated in fig. 12 toward each other.At tooth assembly during towards this height ratio position of machine motion, tooth arm 84 ' and 86 ' the part that has the helical teeth that leans outward respectively in radius R 1 and the rotation of ground, R2 top, so that the radially dotted line through the tooth center is outwards opened, thereby increase the angle between them, as shown in figure 12, keeping the axis with output shaft 22 simultaneously in low ratio shown in Fig. 1,11 and 12 and all ratios position between the height ratio position is the center.The tooth arm by above-mentioned groove 94 and 96 and groove 100 and 102 motions of being controlled guaranteed that tooth 82,84 and 86 always can engage with it best between the adjacent chain roller in all ratios position of machine, and irrelevant with the speed of chain and rate of change disk 20 and array output axle 22 thereof.
With reference to figure 1,6 and 7 as mentioned above, engage with the axle sleeve 59 of rate of change disk 20 assemblies and the frame member 28 that has a sprocket wheel 26 that defines chain narrow orifice 30 by the machine control mechanism with the step-length that increases progressively towards and away from disk 20 assemblies and entrained output shaft thereof and move.The purpose of this incremental motion is the length that accurately is controlled at the chain 34 that the chain annulus neutralization that is introduced on the sprocket wheel 26 between the disk 20 therefrom breaks away from when operation during the rate of change at machine.
In this embodiment of the present invention, as shown in figure 10, selected zip length is the length L of a chain link, and it records between the axis of adjacent connecting pin 36.The incremental motion that frame member 28 produces by machine controller will cause a chain link of chain to join in the chain annulus or therefrom break away from, to guarantee when tooth assembly passes across narrow orifice, on two inboards of the chain of chain gap in narrow orifice 30 between the chain link roller 38 with drive unit 32 tooth assemblies in each tooth synchronous fully, shown in Figure 11 and 12.As mentioned above, this enter and break away from the rate of change formula chain movement of the chain annulus between the disk 20 must be only can carry out during away from chain narrow orifice 30 at the tooth of the part sprocket-type tooth assembly of drive unit 32.The chain link gap of the tooth of chain apparatus and chain 34 this make synchronously under all design output angle speed of output shaft 22, all can realize up to 6000 rev/mins tooth and chain smoothly with perfectly engage, and do not have any interruption of moment of torsion transmission or output angle speed.
As described in the preamble of this specification, obviously competitive many known the above-mentioned type IVT depend on and use overrunning clutch or free wheeling sprag clutch to operate, and free wheeling sprag clutch has been eliminated power and transmitted two-wayly possibility by machine.Yet in above-mentioned transmission machinery of the present invention, 12 power transmits and is hindered from output shaft 22 to input shaft, makes machine fully applicable to engine braking.
Second embodiment of IVT machine of the present invention comprises fixed frame spare 120 as illustrated in fig. 13, and it has rate of change assembly 122 and indexing mechanism 124.This machine also comprises frame member 126, and it movably is connected on the frame 120, so that driving screw by first embodiment or electronic control type hydraulic pressure installation and towards and away from 122 motions of rate of change assembly.Frame member 28 among first embodiment of frame member 126 and machine is roughly the same, but does not comprise the front end of the arm 53 that has carried slant rail 57, and this is that the rate of change of assembly 122 moves through indexing mechanism 124 and carries out because in this embodiment of the present invention.The shown by reference numeral of the parts of the frame member 28 that uses in Figure 13 is used to represent identical parts and the structure among this second embodiment.
Shown in Figure 14 and 19, rate of change assembly 122 comprises two rate of change disks 128, as in Figure 19, illustrating best, it is the central line groove 132 at center that disk 128 all has on its relative conical surface 130 with the axis of spline output shaft 138, and two external grooves 134 and 136, wherein each centering groove is positioned on the both sides of central recess 132.Groove 134 curves inwardly towards its inner from its outer end, and its curvature increases towards its lower end simultaneously.As shown in figure 19, groove 136 is crooked similarly, and its curvature further enlarges than groove 134 towards its lower end simultaneously.Shown in Figure 14 and 19, groove 132 has undercutting, and has uniform T shape cross section on its length, and shown in the dotted line among Figure 19, groove 134 and 136 bottom cutting portion with the outside symmetry that forms of the opening of groove, its reason is as described below.
In this embodiment of the present invention, shown in Figure 14,16 and 19, drive unit 140 also comprises centre tooth carrier 142, the first pair tooth carrier 144 adjacent with carrier 142 except that disk groove 132,134 and 136, and second pair of external tooth carrier 146.
The chain that is used for this second embodiment's machine has kept first embodiment's chain 34, each tooth carrier comprises the sprocket tooth of three lateral alignment, it is shaped shown in Figure 14,16 and 19, and wherein each tooth to tooth carrier 144 and 146 is mirror image each other on 142 both sides of central carrier.From Figure 16, can clearly see, the same with in the foregoing description, outwards open the bottom of each sprocket tooth on the tooth carrier, so that provide bearing to support chain roller 38 on the chain link either side, all engages with roller 38 in all ratios change location of the chain of tooth between disk 128.
Tooth on each tooth carrier is fixed on the transverse arm 148, and certain size that is spaced from each other, and this size is corresponding to the gap of the lateral alignment between the roller 38 of chain 34.
The end of the transverse arm 148 of tooth carrier 142 all has horizontal rectangular configuration 150, it forms complementation with the cone angle of the face 130 of the rate of change disk of facing mutually 128 on angle, therefore and also form complementation with the bottom cutting portion of the bottom of disk groove 132, wherein configuration 150 is located in the bottom cutting portion slidably.
As shown in figure 16, tooth carrier 144 and 146 end include outwards outstanding top cylindrical configuration 152, its end is in the complementary earth tilt in bottom of disk groove wherein towards configuration 152 in use, also comprise second configuration 154, it is made of cylindrical shank, and has radially outstanding disk 156 on its free end.Cylindrical configuration 152 all has certain diameter, and it can closely be matched with groove 134 in the face of disk 128 and 136 outside slidably.The shank of configuration 154 has the diameter littler than configuration 152, its axis is downward-sloping with respect to the axis of configuration 152 simultaneously, make this axis and configuration in use be in the groove 134 of disk 128 wherein or 136 bottom quadrature, and the conical surface coplane of the outer surface of its disk 156 and configuration 152.The disk 156 of configuration 154 has certain thickness and diameter, makes it to be snug fit at well in the bottom cutting portion of groove 134 or 136.The upper surface of disk 156 makes the tooth carrier overcome the motion up or down that begins from its selected ratio position groove and is limited in the groove, and the degree of separation of disk is depended in this motion.
In the assembly of rate of change disc assembly 122 that has assembled and drive unit 140 thereof, lay respectively at tooth carrier 142, configuration 150 on 144 and 146,152 with 154 tapered end have with as first embodiment in the identical purposes of tapered end of connecting pin 36 of the described chain 34 of IVT machine, be wedged on the bottom that these configurations are in disk 128 grooves wherein, to prevent that the tooth carrier breaks away from the not controlled radial motion that when contacting with chain 34 and leave machine output shaft axis when chain crosses narrow orifice 30 between the sprocket wheel 26, and the tooth carrier inwardly or is outwards moved between disk 128, their tooth keeps accurately engaging with chain 34 simultaneously, so that it is when leaving each other on the output shaft 138 and moving, change the I/O ratio of machine, as described below towards ground at disk 128.
The same with the situation of the tooth of tooth assembly in the foregoing description of machine, when drive unit 140 by the groove that is stretched in its disk 128 134 and 136 of chain in during together with five tooth carriers 142,144 and 146 height ratios, the motion of minor sprocket radial location towards the machine output shaft, tooth carrier 144 and 146 tooth must a little up and away from tooth carrier 142 ground rotate, and move to more approaching each other, as shown in figure 13.In this embodiment of the present invention, this dish 156 top position from Figure 19 by tooth carrier configuration 154 moves to its below dotted line position and realizes.In this position, the dish 156 that groove 134 and 136 biasing bottom cutting portion make configuration 154 and tooth carrier 144 and 146 and tooth rotate slightly around the axis of its configuration 152, so that reducing of the chain rail radius between the compensation disk 128 keeps the tooth of tooth carrier ideally to engage with chain simultaneously.When the tooth of drive unit 140 passes across chain narrow orifice 30, link fashionablely on its external tooth and the narrow orifice either side simultaneously, this remains very important.When making machine get back to its low ratio, increase chain rail radial location, tooth carrier and chain be outwards motion between closed disk 128, its further groove 134 and 136 bottom cutting portion make at this moment tooth carrier 144 and 146 and tooth move in the opposite direction so that compensate the chain rail radius of this increase.
In this embodiment of machine, the circumferential spacing at the tooth center between the tooth carrier 142,144 and 146 is the twice of the L among first embodiment, i.e. 2 * L.
As the machine among the above embodiment, still importantly, only at the part sprocket tooth of drive unit 140 during away from narrow orifice 30 zones of the chain rail between the disk 128, just can cause occurring occurring in any rate of change between the disk 128, promptly chain elongates or shortens.
Shown in Figure 13,14 and 15, in this embodiment of the present invention, the rate of change disk 128 of taper includes rate of change gear 158, as shown in figure 15.Gear 158 is fixed on the outer surface of disk 128 and is spaced from by cylindrical vector 162, this cylindrical vector 162 rotatably is bonded in the recess 161 in the lug boss 160 on the disk shown in Figure 15, and can rotate freely therein.Carrier 162 has outside thread, and with ring 164 threaded joint that have internal thread, ring 164 is fixed in the sidewall of frame 120 separate spaces that held rate of change assembly 122.Screw thread on carrier 162 and the ring 164 is arranged so that during the rate of change of machine disk 128 moves the property followed ground each other towards and away from ground, and gear 158 rotates on common direction simultaneously.
As shown in figure 13, gear 158 in use is meshed with the index gears 166 of indexing mechanism 124, and by its driven rotary.The splined end driven rotary of the tubular shafts 168 that gear 166 can be rotated in unshowned bearing, and can axially motion on splined end, above-mentioned bearing are in the sidewall of rate of change assembly 122 separate spaces of frame 120.Gear 166 includes annular side plate 170, it is given prominence to from the gear teeth as illustrated in fig. 13 radially outwardly, so that provide the band toothed portion of the gear 158 in the meshing zone of gears to be clipped in wherein rotating channel, like this, to cause gear 166 to follow their motions on the splined end of axle 168 at gear during the rate of change 158 towards and away from the motion of machine frame, so that the maintenance gear engagement, and do not need wideer and heavier gear 166.
Shown in Figure 17 and 18, flip flop equipment 172 comprises two identical pawl-and-gearing devices, and they are arranged to back-to-back structure on the splined end of axle 168.In this embodiment of the present invention, each rotates ratchet 178 and has six hook tooths 180, they around the periphery of ratchet with 60 ° be spaced from each other evenly and at intervals.Trigger ratchet 182 and be shaped as shown in figure, and all can partly rotate around public pin 184, the end of ratchet 182 is fixed on flip flop equipment and is in the sidewall of frame separate space wherein, as shown in figure 13.
The control mechanism that is used for machine shown in Figure 13 comprises and is used to make frame member 126 towards and away from the driving screw of frame 120 motions or the hydraulic pressure indexing mechanism of electric operation, and unshowned triggering controller, its be used for trigger ratio change disk each other towards and away from pre-determined incremental formula dividing movement.The triggering controller is a master controller, and it has also controlled the dividing movement of frame member 126 devices.
In the operation of machine shown in Figure 13, the same with the machine in the foregoing description, when part sprocket-type device 140 was in chain narrow orifice 30 zones between the disk 128, the motion of the incremental rate of change of the chain rail 34 between disk 128 and the disk 128 was subjected to the prevention of machine control mechanism.
When changing machine ratio up or down in machine operation and by the instruction that independently triggers controller, the electronic equipment of controller applies suitable moment of torsion with actuate motor 176 to torsion bar 174 on selected any direction, and actuates this torsion bar 174.Be triggered simultaneously ratchet 182 of axle 168 keeps locking and can't rotate, and ratchet 182 is locked into the ratchet cover plate 178 can't rotate on either direction, as shown in figure 17.
Need overcome and act on any triggering ratchet 182 that the bias voltage of the torsion bar 176 on the ratchet 178 operates via axle 168 and on one of them direction of arrow shown in Figure 17, be triggered, so that discharge torsion bar 174 energy stored on the hook tooth that engages.When discharging, ratchet 178 rotation rapidly on required direction at once, so that axle 168, gear 166 and the rotation of gear 158 incremental, so that disk 128 is moved toward or away from ground as requested each other.Ratchet trigger ratchet 182 by gravity towards ratchet 178 bias voltages, and suppose that ratchet shown in Figure 180 rotates in the counterclockwise direction, d/d so hook tooth 180 will make the head of ratchet move downward on ratchet, so as with next indented joint, as shown in figure 18.For the ratchet 182 of resetting effectively, can between the trigger arm that projects upwards of ratchet, spring be set and be attached thereto, so that make arm bias voltage toward each other.For gear 158 is rotated in the opposite direction, the rotation of motor 176 controlled devices is so that apply torque load to ratchet 178 in the opposite direction.
The above method that adopts mechanical device (torsion bar 174) to be used as triggering energy storage device makes and does not need high-power electric or hydraulic accumulation energy device expensive more and complexity to realize identical purpose.
Obviously, the same with machine among first embodiment, must synchronously make frame member 126 toward or away from the motion of rate of change assembly 122 incremental ground with the operation of indexing mechanism 124, thereby chain is entered and break away from chain rail between the disk 128.In this embodiment of the present invention, this by with first embodiment's machine in the very identical mode of the motion of frame member 28 realize.Be used to make the driving screw or the electronically controlled hydraulic control of frame member 126 motions to be actuated, this master controller may command and actuate indexing mechanism 124 by master controller.
In Figure 19, shown to be used for calculating the groove 134 of disk 128 and 136 the necessary variable of center line, be introduced by simple mathematical model now.
Point P, G, K, M, N and O are positioned on the same driving sprocket wheel radius SR (line AG), and all separate angle of release θ each other with respect to the some A of machine output shaft center, and it is corresponding to the zip length L on this driving radius SR.By make X-axis flatly through the some A and make Y-axis vertically through the some A, when having provided driving radius SR and zip length L, just can calculate the X of a H and Q, the Y coordinate, as described below:
L
2=2SR
2-2SRSRcos (θ), by drawing for θ solves an equation:
Therefore, mid point to the equivalence of putting A of the zip length L at some Q place drives radius R E perpendicular to line KM, therefore is calculated as follows:
Therefore, the X of some Q, the Y coordinate is as follows:
X:QE＝RE·sin(k·θ) (C)
Y:AE＝RE·cos(k·θ) (D)
Wherein, k is an integer multiple, and the number of the zip length of Y-axis, k=2 are in this case left in expression.
Therefore put the X of H, the Y coordinate is as follows:
X:HF＝RE·sin(k·θ) (E)
Y:AF＝RE·cos(k·θ) (F)
Wherein, k is an integer multiple, and the number of the zip length of Y-axis, k=4 are in this case left in expression.
A to F combines with equation, just can draw in the whole ratio ranges of machine to be used for X, and one group of universal equation of Y coordinate, as follows:
Wherein, k is an integer multiple, and the zip length number of Y-axis is left in expression.
The X of point I and J (being respectively the center line of the inner and outer portions of groove when SR changes), the Y coordinate can be by determining that easily it differs from one another between sprocket tooth in conjunction with their fixed relationships with respect to a H and line HA.
Above-mentioned meeting causes the inner and outer portions of groove 134 and 136 to have two unequal center lines, shown in the below bottom cutting portion that the dotted line of the groove among Figure 19 is represented.
In second embodiment's shown in Figure 13 of a machine of the present invention modification, chain 34 and band tooth driver 140 are engaged 186 replacements of drive unit bar by crooked chain pitch chain 184 shown in Figure 20 and 21 and trough of belt chain.Shown in these two figure, chain 184 is made of the crooked link plate 188 that pivotally is linked together by connecting pin 190, and connecting pin 190 has the interval roller 192 that can rotate between link plate 188.
The downside of link plate 188 is rounded, has formed the bar bonding bearing configuration 194 of central dome, and it can the most clearly be seen on center link plate 188 shown in Figure 20.
The end 195 of drive unit bar 186 is tapers, so that form complementation with the conical lower portion of the groove 132,134 of rate of change disk 128 and 136 and stride thereon, place, end at contiguous bar is provided with groove 196, and it is in narrow of the outside of groove 132 to 136.Four in five bars 186 of machine drive device in Figure 20 and 21, have only been shown.
When using with chain 184, groove 132,134 and 136 outer, interior bottom cutting portion is modified on the both sides of groove center line is symmetrical, requires to make the mathematical model of above-mentioned groove center line to be suitable for the axis that comes balancing lever 186 with the similar mode of the calculating of Figure 19 mid point I and the J position of rising a little with respect to the axis of adjacent connecting pin 190 when bar engages with chain link configuration 194 to this improvement of groove.In this case, the center line of groove can be separated one section distance between the connecting pin axis that is in the single chain link each other.
Except above modification, machine shown in Figure 13 remains unchanged.Yet, use chain 184 and driveshaft 186 to provide the chain of simplifying to engage design as the machine drive device, wherein eliminated the moment of torsion that is applied on tooth carrier 142,144 and 146.
Provide following example that incremental chain movement during the rate of change of machine of the present invention is described:
Suppose zip length L=12.7 millimeter, the circular chain rail between the disk 20 need change its length by the zip length from the zip length of height ratio chain link HRL=20 to its low ratio chain link LRL=40, therefore, and θ
HRL=360 °/20=18 ° (chain link is with respect to the angle of input shaft axis, the girth of HRL=20), θ
LRL=360 °/40=9 ° (chain link is with respect to the angle of input shaft axis, the girth of LRL=40).
Utilize equation A
SR can be calculated as follows:
Following table provides the value from the zip length RL of HRL=20 to LRL=40 on the circumference of disk 20, and corresponding θ and rate of change percentage calculation are as follows:
Rate of change %=100/RL (J)
The displacement DD of the respective circular disks 20 of each disk is relevant with the cone angle of chain connecting pin 36 (Fig. 5 and 15), and is calculated as follows:
DD＝SRC·tan(α) (K)
Wherein, SRC is the variation of the SR of continuous zip length.
If suppose to be used for the helical pitch LS=4.4 millimeter/commentaries on classics of rate of change gear 158, adjust the required rotation ASR of nut so and will be constant:
ASR＝360*DD/LS＝60° (L)
As shown in the table:
| RL | Rate of change | θ | SR | SRC | DD | ASR | |
| Chain link | ％ | Degree | Millimeter | | Millimeter | Degree | |
| 20 | 5.0 | 18.0 | 40.6 | 2.0 | 0.7 | 60 | |
| 21 | 4.8 | 17.1 | 42.6 | 2.0 | 0.7 | 60 | |
| 22 | 4.5 | 16.4 | 44.6 | 2.0 | 0.7 | 60 | |
| 23 | 4.3 | 15.7 | 46.6 | 2.0 | 0.7 | 60 | |
| 24 | 4.2 | 15.0 | 48.6 | 2.0 | 0.7 | 60 | |
| 25 | 4.0 | 14.4 | 50.7 | 2.0 | 0.7 | 60 | |
| 26 | 3.8 | 13.8 | 52.7 | 2.0 | 0.7 | 60 | |
| 27 | 3.7 | 13.3 | 54.7 | 2.0 | 0.7 | 60 | |
| 28 | 3.6 | 12.9 | 56.7 | 2.0 | 0.7 | 60 | |
| 29 | 3.4 | 12.4 | 58.7 | 2.0 | 0.7 | 60 | |
| 30 | 3.3 | 12.0 | 60.7 | 2.0 | 0.7 | 60 | |
| 31 | 3.2 | 11.6 | 62.8 | 2.0 | 0.7 | 60 | |
| 32 | 3.1 | 11.3 | 64.8 | 2.0 | 0.7 | 60 | |
| 33 | 3.0 | 10.9 | 66.8 | 2.0 | 0.7 | 60 | |
| 34 | 2.9 | 10.6 | 68.8 | 2.0 | 0.7 | 60 | |
| 35 | 2.9 | 10.3 | 70.8 | 2.0 | 0.7 | 60 | |
| 36 | 2.8 | 10.0 | 72.9 | 2.0 | 0.7 | 60 | |
| 37 | 2.7 | 9.7 | 74.9 | 2.0 | 0.7 | 60 | |
| 38 | 2.6 | 9.5 | 76.9 | 2.0 | 0.7 | 60 | |
| 39 | 2.6 | 9.2 | 78.9 | 2.0 | 0.7 | 60 | |
| 40 | 2.5 | 9.0 | 80.9 | 2.0 | 0.7 | 60 |
Can notice that constant ASR is an approximative value, this is because if L greater than SR, then should be similar to incorrect.
For control change correctly, the speed of supposing disk 128 and output shaft 138 is 3000 rev/mins or 50 revolutions per seconds or 20 commentaries on classics/milliseconds.Suppose that the transition region of not carrying out conversion on the narrow orifice 30 has constituted 60 °.So, the formula of used time of conversion ST is: ST=[(360-60)/360] 20 milliseconds=16 milliseconds, in a period of time like this, disk need move 0.7 millimeter, or rate of change gear 158 needs to rotate 60 °, and this depends on employed control system and mechanism.Average disk speed calculation is as follows:
0.7 millimeter/16 milliseconds=43.75 mm/second.
In a second embodiment, its motion is synchronous corresponding to control and the rate of change gear 158 of the control set part 126 of SRC, but can postpone as described below or shift to an earlier date.
No matter when machine of the present invention raises to height ratio (SR reduces), the motion of control set part 28 all can postpone and stretch, this be because the idler sprockets 26 at narrow orifice 30 places when the chain path on the disk 120 reaches 2 millimeters further away from each other transmission device still can work, in the time of after conversion, also can adjusting, this will simplify control greatly, because the endurance is not as so important under disk 120 motion conditions.
No matter when machine of the present invention is adjusted downward to low ratio (SR increase), the motion of control set 126 need take place before the motion of disk 120, to prevent the collision between idler sprockets 26 and the part sprocket-type drive unit 32, but similarly, as described above, this endurance is not too important, and can simplify control.
Be used under the situation of motor vehicle at IVT machine of the present invention, utilize the high torsional performance of the forced engagement of IVT, and by directly being connected output shaft on the wheel of motor vehicle through differential mechanism, just can further simplify control, in this case, therefore the maximum (top) speed of output shaft will be in about 1300 rev/mins (the highest wheel speeds, rev/min), therefore further increase conversion time.
In the 3rd embodiment of IVT machine of the present invention, the rate of change disk 128 of the frustoconical in second embodiment's the machine and chain 34 are by the disk shown in Figure 23 and 24 198 and improve chain 34 replacements.
As shown in figure 24, the free end of the connecting pin 36 of above-mentioned machine embodiment's chain 34 has head 206, and its slightly tapered outer surface 208 towards pin is inside taper.The cone angle of pin 206 side is corresponding to the cone angle of the sidewall of disk groove 204, and their length is corresponding to the degree of depth of groove.
In this embodiment of the present invention, drive unit 32 in 204 the foregoing descriptions of fin 202 and groove and 140 purposes.When disk 198 rotations, the pin 206 that is in a part of endless chain 34 between the disk is in the groove 204, and be directed carrying out rate of change motion therein, when crossing chain rail narrow orifice 30, only easily skid off from groove 204 in the chain outlet port of narrow orifice in order, and new pin head enters into a series of guide recess of the chain inlet of leading to narrow orifice 30 once more, can not collide with fin 202.
Yet this improvement chain 34 can cause bigger pin 206 angle, makes the pin head to engage smoothly with fin 202, and this can cause unbalanced lateral force in the band fin part on disk 198.
In this embodiment's of machine of the present invention high speed and high torque applications, the groove 204 in the disk 198 has step-like shape of cross section as shown in figure 25.Groove 204 is divided into the tapered top that makes progress, and the cone angle of its sidewall is at the cone angle that is far smaller than the groove 204 the disk 184 shown in Figure 23 when the median plane of process groove is measured.The bottom of recess sidewall has parallel side, and with the bottom quadrature of groove, this bottom is positioned on the conical surface level of disk.The height of the parallel side wall of fin 202 and groove 204 part begins to be decreased to very slightly near the height of the height ratio orbital position the machine output shaft hole 210 from the big chain rail radius shown in Figure 26 of disc circumference, as shown in figure 23.
Shown in Figure 27 to 29, chain 34 with the foregoing description is identical basically to be used for the chain 212 of disk groove 204 shown in Figure 25, and difference is its improved combination outside links device 214.
In use, during along straight line path, the high end face 224 on inclined-plane 220 is close together in pairs, as shown in figure 28 at chain 212.When chain entered curved path shown in Figure 29, the guiding connecting pin will the position from Figure 28 moves to the position among Figure 29, so as it with the pin of following in its back between relative rotation.Identical relative rotation occurs between the paired inclined-plane 220 on the pin, and the inclined-plane on the chain link 218 will make the tapered end 208 of pin 36 expose fewly from pin head 222 to arch on the inclined-plane of chain link 220.Show in Figure 25 and 26 in chainlet radius, height ratio position and its long radius of the chain rail between the disk 184, the exposing respectively of pin length between the low ratio position.The degree that pin 36 exposes from pin head 222 is shown as in the drawings and has been exaggerated a lot, sells the greatest practical extent of exposing in practice and can change about 0.1 millimeter.
This improvement chain makes the sidewall of groove compare with the recess sidewall among above-mentioned Figure 23 to have littler cone angle, so that the tractive force between the tapering part of raising chain pin head 222 and groove shown in Figure 25 204, also reduce the interactional actual component between pin head 222 and the recess sidewall simultaneously, so that promote the pin head to enter and leave disk groove 204.
In another modification of rate of change disk, drive unit and the chain of machine shown in Figure 13 of the present invention, disk 128 and chain 34 are replaced by disk 226 shown in Figure 30 and 31 and endless belt 228.
As shown in figure 30, disk 226 has the drive unit of fin 229 and groove 230 on its conical surface 231, and this is similar to the disk 198 shown in Figure 22 and 23.Yet the groove of disk 226 does not comprise tapered sidewalls, and rounded on the upper surface of fin.
In this modification of the present invention, can make by the flexible material of any suitable inductility with 228, but preferably constitute by the flat metal chain link or the similar rigid material chain that are embedded in the flexible material with suitable stiffness.Chain link can be arranged to suitable shape, so that strengthen having with disk groove 230 transverse teeth 231 of complementary shape.Though not shown in Figure 31, be with 228 obviously also to need to be provided with sprocket hole, merge by its guiding so that make it to join with idle pulley 26, drive unit 14 and the tension sprocket at narrow orifice 30 places.Perhaps, comprise that the driving sprocket wheel 14 of the machine of disk 226 can be the plane pulley, it has the side flange that comprises outstanding radial teeth, makes pulley can have and the closely similar outward appearance of device for disc shown in Figure 31 when engaging with 228.Tension sprocket 16 and idler sprockets 26 can be only for having the plane pulley of flange, all these make and needn't the hole be set in 228 being with.
In this specification, first embodiment's introduction of having only IVT machine of the present invention is for having disk Equilibrator 68.Yet other embodiment also can require balance more or less, and it will be provided with any of multiple mode known in the balance rotating body field.
Figure 32 to 34 has shown and the groove 204 that comes calculating ratio variation disk 198 by following mathematical model and the relevant variable of sidewall cone angle of fin 202.The center line of groove 204 can adopt above equation G and H to calculate.
Point B, D, E, F and G all are on the same driving radius SR (line AG), and with respect to an A (center of tapered disk 198) open-angle θ, it is corresponding to the zip length L that drives on the radius SR, shown in figure 32.By making X-axis flatly through some A with make Y-axis vertically through a some A, when having provided driving radius SR and zip length L, just can calculate the X of a B, the Y coordinate, i.e. groove central point Xg, Yg, as described below:
L
2=2SR
2-2SRSRcos (θ), by drawing for θ solves an equation:
Therefore, the X of some B, the Y coordinate is as follows:
Xg:BC＝SR·sin(k·θ) (J)
Yg:AC＝SR·cos(k·θ) (K)
Wherein, k is an integer multiple, and the number of the zip length of Y-axis is left in expression, therefore at a k=3 of B place.I to K combines with equation, just can draw the one group of universal equation that is used for the X-Y coordinate, and is as follows:
Wherein, k is an integer multiple, and the zip length number of Y-axis is left in expression, and L is a zip length, and SR is current driving radius.For central recess, obvious k=0.
Below provide and be used to calculate the mathematical model of when chain pin head 206 engages and breaks away from tapered disk, selling the angle φ of the groove 204 that enters and leave tapered disk 198.Chain 34 girths around tapered disk are calculated as the summation around all zip length L of tapered disk at driving radius SR place, therefore, leave relation between the corresponding angle of swing β of the straight length LinDis of chain of tapered disk and disk 198 as shown in the formula described:
More than relate to central recess AM, and only by adding that kL just can extend in the continuous recess 204, wherein k defines as described above and shows in Figure 33.Like this, equation N has caused following result:
After disk 198 rotates through angle β, as shown in figure 33, the new X of the central point of groove 204, Y coordinate Xn, Yn can calculate by the rotation that centers on the Z axle on equation L and M, as shown in the formula:
Xn＝Xg·cos(β)+Yg·sin(β) (P)
Yn＝-Xg·cos(β)+Yg·cos(β) (Q)
And, can draw by using equation L and M:
When chain pin breaks away from disk 198 after tapered disk has rotated angle beta, the X of chain pin, Y coordinate Xp, Yp is calculated as follows:
To be Xp provided by the length of the chain that does not contact with tapered disk 198 the X coordinate, therefore represented by LinDis in equation 0.The Y coordinate obviously equals SR, therefore:
Yp＝SR (U)
In order to find along the Xn of groove 204 center lines, the Yn coordinate, its near pin coordinate (Xp, Yp) distance D min needs to change the SR among equation R and the S, hereinafter referred to as SRg, SR among equation T and the U should keep constant simultaneously, realizes minimum value up to following equation:
Dmin＝[(Xn-Xp)
2+(Yn-Yp)
2]
0.5 (U)
As example, Figure 33 and 34 has shown to have coordinate by some H (Xn, Yn), k=2 wherein, corresponding chain pin head 206 are in a N place and have coordinate that (Xp, Yp), wherein N is positioned on the horizontal line MP, and from X-axis one segment distance SR, wherein MN=LinDis+2 * L is arranged.
Be updated among the equation U and draw:
Equation V can differentiate with respect to SRg, and setting equals zero and finds the solution SRg, perhaps can come iterative computation to go out Dmin at the different value of SRg, up to finding minimum value.
Figure 34 represented at the relevant above variable of a J place and disc face 200, and some J is perpendicular to the point of X-Y plane under a H.
In order to calculate entering angle φ (cone angle on chamfer angle on the groove side and the chain pin head 206), can notice for utilize said method calculate minimum range Dmin for, SRg will be always greater than SR, and this is because chain is leaving tapered disk (seeing Figure 33 and 35).As can be known, chain pin contacts in radius with disk from the spirit or scope of the present invention that claims limit.
DiskDis＝(SRg-SR)·tan(α) (W)
Wherein α is the cone angle of tapered disk face.
Therefore, can utilize equation W to calculate the entering angle φ of chamfering as described below:
More than calculate the DiskDis that obviously need be applied to less than the disk depth of groove.Also need to be recycled and reused for all SR values (all ratios of incremental CVT) and all k values (institute is fluted).The maximum value φ that in above calculating, obtains need be applied to the fluted and chain pin head 206 that matches.
Should be noted that in order to illustrate to be in-groove on the X-axis that need carry out following work: making the X coordinate among the equation L is negative value, and equation T is changed into Xp=β L/ φ-kL.Should also be noted that this equation only Xp on the occasion of the time be only correct, therefore, only chain pin break away from Xp=0 or at the Y-axis place be only when contacting with tapered disk correct.
Figure 36 to 39 has shown the modification referring to figs. 1 to first embodiment of 12 described IVT machines of the present invention.In this modification of the present invention, the taper rate of change disk 20 of rate of change device 18 is replaced by a combination device for disc 232.In addition, it is identical that the remaining part of machine keeps, and have and label identical shown in Fig. 1 to 12.The operation of these two kinds of machines is substantially the same.
Shown in Figure 36 to 39, combination device for disc 232 comprises two overlapping disks 234 and 236.In this embodiment, disk 234 has six radial grooves 238, array output axle 22, and the part sprocket-type assembly of machine first embodiment's its tooth godet 78 and drive unit 32.Disk 234 is fixed on the joining tooth godet 78.Disk 236 has six curve baths 240, and it is located on the disk, with respect to the groove in the disk 234 238 as shown in the figure.Disk 236 can partly rotate and by thereon with respect to disk 234.
The head 242 of the rest pin 244 of disk 234 and 236 by double end chain 34 keeps together, and as shown in figure 39, these heads 242 pass the groove 238 and 240 in disk 234 and 236 respectively.In Figure 37 and 38, upper pin 244 is passed the centre tooth of part sprocket wheel of drive unit 32 and fixed thereon, so that the pin 88 that plays a part in the machine with first embodiment is identical.
In use, this modification of machine is operated in the mode identical with Fig. 3 to 12, unique difference is, disk 236 rotates with respect to disk 234 with the controller that is used for this purpose by actuating any suitable mechanism, rather than machine controller makes disk 20 move towards and away from ground each other in the mode of rate of change by the trough of belt arm on the frame member 28.
Above embodiment is intended to illustrate the preferred embodiments of the present invention.Although specifically do not propose in this article, yet those of ordinary skill in the art can visualize some increase, deletion or modification to above embodiment, these all can not break away from the spirit or scope of the present invention that claims limit.
Claims (40)
1. an IVT machine (10) comprising:
Input shaft (12),
The driving wheel (14) that can be rotated by described input shaft (12),
Output shaft (22),
Rate of change device (20), it is co-axially mounted on that described output shaft (22) is gone up and can be in company with rotation therewith,
Endless belt (34), it is through described driving wheel (14), and be positioned at support on the described rate of change device (20) the rate of change configuration (24) of loop of described band (34) go up the form that forms open loop and
Control mechanism, it is used for making described rate of change configuration (24) change the speed ratio of described input shaft (12) and output shaft (22) by amplifying and dwindling the loop size around the described band (34) of output shaft (22) axis on the described rate of change device (20)
It is characterized in that described machine also comprises:
Tape guide mechanism (26), described band (34) can be gone up motion so that narrow orifice (30) is provided at described guide mechanism (26), and described band (34) can enter and break away from it and be positioned at loop on the described rate of change device (20) by described narrow orifice (30),
Drive unit (32), it is located at described rate of change device (20) and goes up to be used to transfer a driving force to described output shaft (22), described drive unit (32) engages with a part of loop that is positioned on the described device (20) of described band (34), engaging with described band (34) in the both sides of described narrow orifice during in its transition during the rotation of described rate of change device (20), and keeping optimum engagement with described band (34) in all ratios position of described band (34) loop on described rate of change device (20) by described narrow orifice (30).
2. IVT machine according to claim 1 is characterized in that, the guide mechanism of described band (34) comprises the guide wheel (26) of two bands (34), and they are arranged to closely adjacent each other, and defines described band narrow orifice (30) between them.
3. according to each described IVT machine in claim 1 or 2, it is characterized in that, described machine comprises and has carried described output shaft (22), rate of change device (20), the frame (40) of input shaft (12) and band degree of tightness regulating device (16), and frame member (28), described frame member (28) has carried described or each tape guide mechanism (26), and can move towards and away from described rate of change device (20) with incremental calibration step-length with respect to described frame (40) by described controller, so that comply with the loop size of the band (34) that changes during the rate of change, and provide and remove as requested through described band narrow orifice (30) band (34) of the predetermined length in band (34) loop on described rate of change device (20) back and forth, and when the speed ratio of the described input shaft (12) of described machine and output shaft (22) was changed by described controller, described drive unit (32) was away from described chain narrow orifice (30).
4. each described IVT machine in requiring according to aforesaid right, it is characterized in that, described rate of change device (20) comprises a pair of frustoconical disk (20), it can move towards and away from ground on described output shaft each other by described control mechanism, wherein their conical surface (24) faces with each other, and the supported rate of change configuration (24) thereon of relative edge of described band (34) is provided between them.
5. each described IVT machine in requiring according to aforesaid right, it is characterized in that, described band is the chain (34) that is made of chain link, these links are crossed the connecting pin (36) that equi-spaced apart opens and are linked together, these connecting pins are outstanding from the side of described chain (34), and have on the conical surface (24) that is pressed against described rate of change disk (20) and the end face tapered complementaryly with the cone angle of the described conical surface, so that it is circular making tensioning chain (34) loop between the described disk (20), the width of wherein said chain (34) is determined by the cone angle of the gap between the disk in the low ratio position that is in the chain (34) between the described disk (20) and the conical surface (24) thereof, described belt wheel (14,16,26) be sprocket wheel.
6. IVT machine according to claim 5, it is characterized in that, described frame member (28) comprises two isolated arms (53), its remaining part from described frame member (28) is outstanding, and all engage with configuration (59) sliding type on one of described rate of change disk (20), wherein leave by described controller and when described disk (20) moved, described arm (53) and described disk configuration (59) can make described disk (20) move towards and away from ground each other on described output shaft (22) when described frame member (28).
7. IVT machine according to claim 6 is characterized in that, described drive unit (32) comprises the part sprocket wheel, the gap width that its arc length is located at described chain narrow orifice (30) greater than circular chain (34) loop on the described rate of change device (20).
8. according to the IVT machine of claim described 7, it is characterized in that, the sprocket tooth (82 of described drive unit (32), 84,86) each other separately and can move each other, to keep with described output shaft (22) axis be the center by being connected guide mechanism (78) on the described output shaft in all ratios position in the chain loop of their center on described rate of change device (20).
9. IVT machine according to claim 8, it is characterized in that, described sprocket tooth (82,84,86) all be carried on arm (82 ', 84 ', 86 ') first end on, tooth (84,86) on the centre tooth of wherein said part sprocket wheel (82) both sides tiltedly departs from out described centre tooth (82) in its arm (84 ', 86 ') updip, described output shaft (22) laterally splits, its cleaved end all is connected on the tooth godet housing (78) coaxially, wherein said tooth arm (82 ', 84 ', 86 ') second end on pin (90) can be transverse to the axis of output shaft (22) groove (92 in described godet housing (78), 94,96) motion is used for guide gear (82 in, 84,86) towards and away from described output shaft (22) axis and simultaneously each other towards and away from motion so that change the arc of described sprocket wheel (32), thereby ideally mate in the radius of curvature of any ratio position of described machine and chain (34) loop between the described disk (20).
10. IVT machine according to claim 5, it is characterized in that, described drive unit (140) comprises a series of undercut groove (132 of the conical surface (130) that is arranged in each described rate of change disk (128), 134,136), its periphery from described disk extends towards output shaft (138), their center line certain size that on its length, is spaced from each other, this size equals the distance that the axis of the chain connecting pin (36) on the single chain link separates each other, described groove (132,134,136) bottom is parallel to the conical surface (130) of described disk.
11. IVT machine according to claim 10, it is characterized in that, described drive unit (140) comprises the tooth carrier (142 of independent fixed length, 144,146), it quantitatively equals the groove (132 on the described disk (128), 134,136) quantity, described tooth carrier carries sprocket tooth, wherein in all ratios position of the described chain (34) between described disk (128), the center line of each tooth is positioned on the radial line that is derived from output shaft (138) axis, also carry the configuration (150 that is positioned at place, described carrier (142,144,146) end, 152,154), they are arranged to and described groove (132,134,136) Di Bu cone angle has complementary angle, and be bonded in the relative groove (132,134,136) of each series on the rate of change disk (128).
12. IVT machine according to claim 11, it is characterized in that, groove (132 in each disk (128) series, 134,136) quantity is enough to make the groove (132 in two relative series of recesses that are bonded on described disk (128), 134,136) Nei tooth carrier (142,144,146) sprocket on is crossed described chain narrow orifice (30), and in during described drive unit (32) transition is by described narrow orifice, at least one tooth maintenance of described drive unit (32) each end engages with the chain (34) on described narrow orifice (30) both sides.
13. according to each described IVT machine in the claim 10 to 12, it is characterized in that, the groove (132 of each disk (128), 134,136) central recess in the series (132) is positioned on the radial line that is derived from output shaft (138) axis, be positioned at the groove (134 on described central recess (132) either side, 136) the part towards output shaft (138) is crooked on the direction of central recess (132), the distance that between their center line, keeps two connecting pins (36) axis simultaneously, so that the tooth carrier (142 in these grooves, 144,146) the tooth center line on leaves described centre tooth rotation at the low ratio from the chain loop (34) between the disk (128) during the rate of change of height ratio position, and during the rate of change of the low ratio position of chain (34) towards described centre tooth rotation, so that the maintenance of any ratio position between described disk (128) is suitable for the tooth curve of the part sprocket wheel (140) of chain (34) annulus, keeping with output shaft (138) axis simultaneously is the center, and the maintenance of the center line of described tooth is the center with output shaft (138) axis.
14. IVT machine according to claim 13, it is characterized in that, the bottom cutting portion of the described central recess (132) in each series is identical on the both sides of groove external lateral portion on the whole length of described groove (132), and the groove on central recess (132) both sides (134,136) bottom cutting portion leaves the deviation in driction of central recess (132) in described groove (134 on the edge, periphery place of disk (128), 136) external lateral portion, each groove (134 wherein, 136) side-play amount of undercutting is gradually away from those grooves (134 of central recess (132), 136) become big in successively, the side-play amount of these groove undercutting is moved towards central recess (132) on the whole length of described groove.
15. IVT machine according to claim 14, it is characterized in that, engage grooves configuration on described centre tooth carrier (142) end can be horizontal configuration (150), it can be bonded on by the external lateral portion of described groove (132) in the groove undercutting, each all the other tooth carriers (144,146) configuration on the end (152,154) can be outwards outstanding cylindrical first configuration (152), it tightly fits in described groove (134,136) in the external lateral portion, it under described horizontal configuration (150) second configuration (154) with cylindrical shank, its cross-sectional dimension is less than described groove (134, the width of external lateral portion 136), and on its free end, carry and tightly fit in described groove (134,136) the radially outstanding configuration (156) in the bottom cutting portion, wherein this configuration is arranged so that it leans against the surface on the bottom portion of groove and the surface co-planar of described cylindrical configuration (152), described groove (134, angle corresponding to the cone angle of the conical surface of described disk (128) (130) has been formed on bottom 136), when second configuration in the rate of change process along described groove (134, when bottom cutting portion 136) moves, it makes described carrier (144,146) partly rotate around described first configuration through the axis of described first configuration (152) around it.
16. IVT machine according to claim 10, it is characterized in that, the groove (132 of each disk (128), 134,136) central recess in the series (132) is positioned on the radial line that is derived from output shaft (138) axis, the part towards output shaft (138) that is positioned at the groove on described central recess (132) either side is crooked on the direction of central recess (132), the distance that between their center line, keeps a connecting pin (36) axis simultaneously, each groove (132 wherein, 134, the external lateral portion of bottom cutting portion 136) is symmetrical on the either side of groove (132,134,136) center line on cross section.
17. IVT machine according to claim 16, it is characterized in that, described drive unit (32) comprises drive unit bar (186), it quantitatively equals the quantity of the groove (132,134,136) in disk (128) series, the certain angle of end tapered inclination of described bar, this angle is corresponding to the cone angle of described groove (132,134,136) bottom, in the opposite side of bar (186), also be provided with the groove (196) that is parallel to the bar tapered end, engage with the external lateral portion of described groove (132,134,136) being used for, thereby described bar (186) is remained on groove (132,134,136) in, and its tapered end leans against on the bottom of described groove.
18. according to claim 16 or 17 described IVT machines, it is characterized in that, described band is the chain (184) that is made of chain link (188), described links is crossed connecting pin (190) and is linked to each other, and including the configuration (194) that inwardly is arch by the center between its connecting pin (190) that links to each other and from common edge, wherein said arch configuration (194) engages and locates thereon with drive unit bar (186), so that driving force is passed to drive unit bar (186) from chain (184).
19. IVT machine according to claim 18 is characterized in that, described chain link (188) is curved at the common direction of chain (184), and wherein said arch configuration (194) stretches into the described chain link (188) from its concave edge.
20. according to each described IVT machine in the claim 16 to 19, it is characterized in that, groove (132 in each disk (128) series, 134,136) quantity is enough to make the bar (186) of the drive unit (32) between the disk (128) to cross described chain narrow orifice (30), simultaneously during the rotation of disk (128), by in a period of time of narrow orifice (30), many bars (186) keep engaging with chain (184) on described narrow orifice (30) both sides in drive unit bar (186) transition.
21. IVT machine according to claim 5, it is characterized in that, described rate of change disk (198) includes array of spaced fin (202), its surface from disk (198) (200) is gone up outwards outstanding, and extend towards output shaft (138) from the periphery of disk, thereby between them, define drive unit groove (204), the bottom of described groove is on the conical surface (200) of disk (198), during the rotation of described disk (198), when drive unit (32) passed through described narrow orifice (30) before or after the rate of change of described machine, described connecting pin (36) can debouch in the described groove.
22. IVT machine according to claim 21, it is characterized in that, in all ratios position of the chain between described disk (198), groove (204) between the described fin (202) spaced apart mutually certain size on its length, this size equals the distance of separation of the axis of adjacent chain connecting pin (36).
23. according to the IVT machine described in claim 21 or 22, it is characterized in that, central recess (204) in the groove of each disk (204) series is positioned on the radial line that is derived from output shaft (138) axis, the part towards output shaft (138) that is positioned at the groove (204) on central recess (204) either side is crooked on the direction of central recess (204), keeps the distance of a connecting pin (36) axis simultaneously between their center line.
24. according to each described IVT machine in the claim 21 to 23, it is characterized in that, the quantity of the groove (204) in each disk (128) series is enough to make the chain connecting pin (36) in the groove (204) of two relative groove series that are bonded on disk (198) to cross described chain narrow orifice (30), simultaneously at the groove (204) of drive unit (32) by in the transition period of narrow orifice (30), at least one groove (204) of described drive unit (32) each end keeps engaging with chain (184) on described narrow orifice (30) both sides.
25. according to each described IVT machine in the claim 21 to 24, it is characterized in that, the side of described fin (202) can be from it the surface towards the groove between them (204) bottom and outside tapered inclination.
26. according to each described IVT machine in the claim 21 to 25, it is characterized in that, the laterally projecting end of described chain connecting pin (36) is taper, its cone angle is corresponding to the cone angle (200) of rate of change disk (198), wherein each end all has a conical head (206), and it is sized to be matched with well in the conical socket (204) between the fin (202).
27. IVT machine according to claim 26, it is characterized in that, the head (222) of described connecting pin (36) is slidably engaged on the end of described pin (36), described chain (212) comprises and is positioned at adjacent pin (36) to last outer link device (214), it is suitable for exposing the tapered end (208) of pin (36) from its head (222) in the straight section of chain (212), when chain (212) when becoming bending, it can make head (222) little by little move towards the tapered end (208) of pin (36), so that promote it to locate to enter and leave disk drive unit groove (204) at chain narrow orifice (30).
28. according to each described IVT machine in the claim 10 to 27, it is characterized in that, described rate of change disk (198) includes the outwards outstanding lug boss (160) round output shaft (138) on itself and its conical surface (200) opposite surfaces, and be fixed on rate of change gear (158) on the cylindrical rate of change gear carrier of outside thread formula (162), it can engage with lug boss (160) and rotate freely thereon, and with internal thread main body (164) threaded joint on the described machine frame spare (120), make the rotation together of described rate of change gear (158) that the disk (128,198) and the sense of rotation of gear (158) will be moved relatively with leaving towards each other and.
29. IVT machine according to claim 28, it is characterized in that, described machine comprises two index gearss (166), it is fixed on, and journalled connects so that on the common shaft (168) that rotates in machine frame spare (120), and be meshed with rate of change gear (158) separately, also comprise flip flop equipment (172), it is used for rotating suddenly index gears axle (168), to impel index gears (166) and rate of change gear (158) on required direction, to produce the part calibration rotation of one or more settings according to instruction from machine controller, this makes frame member (126) as requested and toward or away from rate of change disk (128 simultaneously, 198) the initial chain (34 between, 184,212) loop carries out dividing movement, so that be chain (34,184,212) loop provides the chain of predetermined length or therefrom removes the chain of predetermined length.
30. IVT machine according to claim 29 is characterized in that, described flip flop equipment (172) comprises that machinery triggers energy storage device (174), and it can rotate the axle (168) of described index gears (166) suddenly when being triggered by described flip flop equipment (172).
31. IVT machine according to claim 30 is characterized in that, described energy storage device is torsion bar (174).
32. IVT machine according to claim 31, it is characterized in that, the axle (168) of described index gears (166) is a pipe fitting, one end setting of described torsion bar (174) and being fixed in the index gears pipe (168), and its second end is connected on the suitable gear motor (176), is used for applying suitable moment of torsion to described bar on arbitrary sense of rotation of the index gears (166) that controller has been selected.
33. IVT machine according to claim 4, it is characterized in that, described rate of change disk (226) includes array of spaced fin (228), its surface from disk (226) (231) is gone up outwards outstanding, and extend towards output shaft (138) from the periphery of disk, so that limit the groove (230) of drive unit (32) between them, the bottom of described groove is on the conical surface of disk (231).
34. IVT machine according to claim 33, it is characterized in that, described band is the endless belt (228) of the flexible material of inductility, and it comprises having the laterally projecting configuration (231) that forms complementary shape with the groove (230) of the drive unit (32) of described disk (226) on opposite side.
35. IVT machine according to claim 34, it is characterized in that, described machine drive wheel (14) is for having the pulley of flange, it comprise on the internal surface of its flange with disk (226) on fin (229) and the corresponding fin shape configuration of inwardly giving prominence to of groove (230) configuration, the guide wheel (26) of remaining band (34) in the machine is a roller.
36. IVT machine according to claim 3 is characterized in that, described rate of change device (20) for the combination disk (232) device, it comprises: overlapping and the band plane side first disk (234) and second disk (236); Be in first disk (234) and be positioned at least three straight-line grooves (238) on the radial line that is derived from output shaft (22); Be in the crank slot (240) of the equal number in second disk (236); Band rest pin (224), it is positioned in the groove (238,240) of these two disks and therefrom passes, and vertically stretches out from first disk (234), and the loop of band (34) is supported in described combination disk (232) and goes up and be on these pins; And the mechanism that can operate by the machine control mechanism, it can make second disk (236) partly rotate with respect to first disk (234), thereby make the crank slot (240) in second disk (236) that band rest pin (244) radially inwardly or is outwards moved in the groove (238) of first disk (234), with the loop size of the band (34) on the change pin (244), thus the speed ratio of change input shaft (12) and output shaft (22).
37. IVT machine according to claim 36 is characterized in that, described band is chain (34), and it has uniform size between its connecting pin.
38. according to the described IVT machine of claim 37, it is characterized in that, described drive unit (32) comprises the sprocket wheel of the part chain (34) with certain arc length, the gap width that described arc length is located at chain narrow orifice (30) greater than the chain loop on the described rate of change device.
39. according to the described IVT machine of claim 38, it is characterized in that, the sprocket tooth (82 of described drive unit (32), 84,86) each other separately and can move each other, to keep with described output shaft (22) axis be the center by being connected guide mechanism (78) on the described output shaft (22) in all positions in chain (34) loop of their center on described rate of change device (232).
40. according to the described IVT machine of claim 39, it is characterized in that, described sprocket tooth (82,84,86) all be carried on arm (82 ', 84 ', 86 ') first end on, tooth (84 on the centre tooth of wherein said part sprocket wheel (82) both sides, 86) its arm (84 ', 86 ') updip tiltedly departs from out described centre tooth (82), described output shaft (22) laterally splits, its cleaved end all is connected on the tooth godet housing (78) coaxially, wherein said tooth arm (82 ', 84 ', 86 ') second end on pin (90) can be transverse to the axis of output shaft (22) groove (92 in described godet housing (78), 94,96) motion in, be used for guide gear (82,84,86) towards and away from described output shaft (22) axis and simultaneously each other towards and away from motion, so that change described narrow orifice (30) that described sprocket wheel (32) locates arc to described chain loop, wherein said machine control mechanism makes chain guide mechanism (26) that described narrow orifice (30) locates towards and away from described machine output shaft (22) axial-movement simultaneously, simultaneously during the rate of change of described machine, the chain incremental of predetermined length is replenished on the described rate of change device combination disk (232), perhaps therefrom removes the chain (34) of predetermined length, described drive unit this moment (32) is away from described chain narrow orifice (30).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ZA200307933 | 2003-10-13 | ||
| ZA2003/7933 | 2003-10-13 | ||
| ZA2003/9224 | 2003-11-27 |
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| CN1802526A true CN1802526A (en) | 2006-07-12 |
| CN100564945C CN100564945C (en) | 2009-12-02 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2004800067453A Expired - Fee Related CN100564945C (en) | 2003-10-13 | 2004-03-05 | Stepless speed variator |
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| CN102076996A (en) * | 2008-04-25 | 2011-05-25 | 瓦里博克斯Ip股份有限公司 | Incremental variable transmission |
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| CN102076996A (en) * | 2008-04-25 | 2011-05-25 | 瓦里博克斯Ip股份有限公司 | Incremental variable transmission |
| CN102076996B (en) * | 2008-04-25 | 2014-10-15 | 瓦里博克斯Ip股份有限公司 | Incremental variable transmission |
| CN104633031A (en) * | 2015-03-03 | 2015-05-20 | 南通市通州区三槐机械制造有限公司 | Continuous operation and intermittent operation interexchange mechanism |
| CN104633031B (en) * | 2015-03-03 | 2017-02-01 | 南通市通州区三槐机械制造有限公司 | Continuous operation and intermittent operation interexchange mechanism |
| CN107120401A (en) * | 2017-05-17 | 2017-09-01 | 李良杰 | It is driven disc type buncher |
| CN109139835A (en) * | 2018-08-20 | 2019-01-04 | 山东斯兰德环保科技有限公司 | A kind of ball chain transmission mechanism |
| CN109139835B (en) * | 2018-08-20 | 2020-06-02 | 金剑 | Ball chain transmission mechanism |
| CN110654959A (en) * | 2019-10-31 | 2020-01-07 | 苏州吾德电梯有限公司 | Power transmission structure of household platform elevator |
| CN112158620A (en) * | 2020-09-22 | 2021-01-01 | 福建恒安集团有限公司 | Servo conveying mechanism after folding baby pull-ups |
Also Published As
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|---|---|
| CN100564945C (en) | 2009-12-02 |
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