CN1127543A - Continuously variable positive planetary gear - Google Patents
Continuously variable positive planetary gear Download PDFInfo
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- CN1127543A CN1127543A CN 94192811 CN94192811A CN1127543A CN 1127543 A CN1127543 A CN 1127543A CN 94192811 CN94192811 CN 94192811 CN 94192811 A CN94192811 A CN 94192811A CN 1127543 A CN1127543 A CN 1127543A
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Abstract
The invention relates to a continuously variable positive planetary gear in which the transmission ratio can be varied via the eccentric shifting of planet wheels (21-24).
Description
The present invention relates to a kind of planetary gear of stepless change positive engagement.
The positive engagement clutch known by the prior art level has following shortcoming, and promptly they only can engage when state of rest or axle rotation synchronously.Known form of implementation has engagement sleeve and jaw clutch.Be subjected to above-mentioned restriction owing to engage possibility, at this moment the main friction clutch that adopts, realizes the moment of torsion transmission by friction in automobile making.When adopting this friction clutch, mutual rubbing surface must engage under the situation of high rotating speed on-load, and this moment, frictional engagement was carried out gradually.The shortcoming of this clutch is that wearing and tearing are big, and has further aggravated this wearing and tearing owing to frictional heat.Because as a rule, for all running statees of transmission device, it is not optimal having only single a kind of velocity ratio, thus adopt the speed changer of stepped gearing usually, to realize different velocity ratios.Whereby, compare, had a kind ofly through improving but also be not the speed changer of satisfying the demand very ideally, in addition, also have tractive force interrupts when connecting problem and gear this requirement synchronously when gear shift with the speed changer that only transmits a velocity ratio.
Ideal situation preferably under the situation that working procedure does not have tractive force to interrupt, can infinitely adapt to various transmissions this.This stepless speed variator is known so-called P.I.V. speed changer or CVT speed changer.This speed changer is based on a kind of transfer unit of power, and wherein, joining to take turns the different radius of clean-up be adjustable, can change velocity ratio thus.For regulating velocity ratio by this principle, must continuously and not have transition ground and change the radius of clean-up, consequently, the wheel that engages can not have rigid joint because their radial motion is obstructed.Therefore, all all are based upon friction by the known speed changer of prior art level and connect on the basis, as vee belt, flat belt, friction wheel and friction disk transmission device, these transmission devices have skid and be shaped on steering channel (Einlaufriefen) and require to have high impacting force and the situation of the power of adjusting under known shortcoming such as high wearing and tearing, simultaneously, its total efficiency is relatively low.
D.B.P. prospectus (DE4317478.7A1) has provided a kind of replacement form, wherein describes a kind of positive engagement speed changer as traction mechanism drive.This speed changer driving side have one group rotatably mounted and can make the planet wheel of planetary rotation, these planet wheels are arranged to can radially stepless adjustment and centered on by a haulage gear, and haulage gear will be delivered on the follower by regulating the determined velocity ratio of radial distance.The change of diameter is to cause by the above line star-wheel that has than minor diameter.For can transmitting torque in the adjustment process of bonding error in all radial positions that compensate non-chain pitch integral multiple, the suggestion planet wheel should be able on driving disc and/or the driven disc and relative driving disc and/or driven disc dallies on a direction or both direction or by locking, wherein, idle running gear shift and/or locking gear shift engages or throws off by radial force that haulage gear applied and/or by the phase control of driving disc or driven disc.Particularly planet wheel shaft can be designed to hollow shaft, this hollow shaft leans against in the shell under the spring force effect, when the radial force that acts on sprocket shaft increases, hollow shaft overcomes spring force and moves, at this moment, one lever is made the cylinder blanket swing of the clamping roller or the clamping ball of free-wheeling clutch, thereby makes above-mentioned roller or ball be pushed in the wedge slot of an interior or outer spider gear of fixing by deflection.
Task of the present invention is that a kind of stepless change positive engagement planetary gear (no haulage gear) is provided.
This task is by realizing at the planetary gear described in the claim 1, be provided with the adjustable planet wheel of at least one diameter in this speed changer, this planet wheel and a central gear are in permanent rigid joint state, wherein, diameter between two-wheeled is than the mutual eccentric position between the decision two-wheeled, thus the rotating ratio of decision two-wheeled.If by further arrangement of the present invention, central gear is designed to the internal gear of interior engagement, then expand to most possibly under the situation of inside radius of ring gear with the coaxial planet wheel diameter of central gear being arranged to, rotating ratio is 1: 1, because the whole teeth that are positioned at inner planet wheel are meshed with the tooth of central gear.If reduce the planet wheel diameter, then to have only when the planet wheel that is positioned at inside moves on to eccentric position by coaxial position, the engagement of tooth just can be kept.Under the condition that keeps the tooth engagement, roll on the inner circumference of central gear in the outside that is positioned at inner planet wheel, that is, its not only rotation also around the rotational of central gear.Correspondingly, also central gear can be designed to have external tooth, at this moment, planet wheel is with the upward rolling of heart wheel hereinto of corresponding external tooth.Equally, have only when the relative central gear of planet wheel has a center displacement, could keep positive engagement corresponding to the diameter adjustment of planet wheel.The present invention also comprises such form of implementation, and wherein, not only the diameter of central gear is variable, and the diameter of planet wheel is also variable, that is both diameters are all variable, and the back also will be described in detail this.
Because in fact, its value is quite little the rotating speed in the scope that roughly drops on most actual techniques application, when therefore when engagement and by adjustment process, starting, the regulating error of planet wheel radial position is very little, so, in fact regulating error drops in the suitable tolerance range of system, and perhaps, regulating error can have elasticity suitable and that adjust to be compensated by the planet wheel geometry of position.For example, when rotating speed is that per second is as being 50 commentaries on classics and having under the situation of 5 planet wheels, every per second of taking turns has 250 planet wheels to be meshed with flexible element, thereby, off time of twice locking as only needing under 10 seconds the common speed conditions, during a mesh cycle, the relative movement between the planet wheel amounts to has only 1/2500, that is has only 0.4 ‰.The elastic compensating motion of the planet wheel that causes thus is very little to the loss that efficient causes, and in addition, this loss in efficiency only occurs in conditioning period and only reaches a minimum magnitude, so loss in efficiency still can be accepted.As if described in D.B.P. prospectus (DE4317478.1A1) like that, the diameter adjustment of planet wheel or gear, be performed such: planet wheel is made up of a plurality of single small-diameter wheels, detour the on the one hand star-wheel axis rotation of said steamboat, on the other hand, around himself axis along a direction rotation, and said steamboat can radially be regulated, thereby be under the eccentric position situation at the relative central gear of planet wheel, steamboat is periodically through the load curve path and a no-load path of a transmitting torque, and make, steamboat by the no-load path in the transient process of load paths, that is when positive engagement, free and shift-in central gear synchronously, but after rigid engagement and since locking rotation, steamboat is transfer function moment of torsion thereon just.Simultaneously, comprise that also per two planet wheels are arranged to this form of implementation of cascaded structure, so steamboat is in the mutual rigid engagement state directly or indirectly, and make steamboat in the process that enters the center gear teeth, can freely rotate synchronously, yet, with the counterpart positive engagement after, they rotatablely move by locking.This form of implementation is used to have the slow-speed of revolution and the very fast special use occasion of governing speed, in bicycle, also can do following variation, that is, all be provided with the support of a planet wheel file on its each, can swing, make always has a planet wheel disengagement and the engagement of the center gear teeth to throw off at every turn, thereby make those keep the planet wheel of engagement to rotate freely, and, can move radially arbitrarily.After adjustment process finished, planetary carrier was put go back to the home position again.Interrupt though this form of implementation also can produce tractive force, it only is confined under the particular condition of quick adjustment under the slow-speed of revolution or the state of rest.Under above-mentioned series connection form, can consider that also the gear teeth with single small diameter gear are designed to come to a point fully in a plane of axially staggering with the power acting surface, like this, when the gear teeth that are used for the moment of torsion transmission be to make and when having standard tooth form, the interlock meeting is easy especially by high-strength material.
According to aforementioned principles, planet wheel rolls, and needs interlock separately, belongs to this principle, by a replacement form of the present invention, can consider design of gears is become to keep permanent engagement.In this form of implementation claim 3 description is arranged, it has following feature especially: be provided with a central gear and a plurality of minor diameter planet wheel, asteroid wheel and central gear are in the permanent engagement state, and be arranged on the disk, perhaps link by force transmission mechanism and disk, planet wheel can rotate to a direction by the axis of free-wheeling clutch around himself, and can not rotate to other direction; The axis of said disk can move with respect to the central gear axis is eccentric, thereby, between disk and central gear, can be dependent on the difference of center displacement amount, rotating ratio and torque ratio are regulated.
If planet wheel is bearing in respectively radially on the bearing, bearing, for example pass through guiding device, can occupy different radial positions, preferably spring-loaded or by bearing radially press and the center gear teeth on planet wheel remain engagement, thereby planet wheel whenever turns around and occupies different radial positions periodically, makes them roll across on the circumference that gear or chain or other haulage gear twine jointly.If what related in this moment is that planet wheel is supporting to rotation on free-wheeling clutch, then on all eccentric axial location the most close minor axis to the whole load of that steamboat transmission of position, and all other small gears are by above-mentioned steamboat rotary driving, its peripheral velocity is greater than the peripheral velocity of active steamboat, that is, be the maintenance engagement, the necessary edge idle running of other driven steamboat direction is added the rotation around himself axis.In the present embodiment, do not exist from the synchronous rotation problem of zero load after entering engagement.
Using planetary a wheel or a planet wheel of formation and having under the situation of directional clutch, preferentially select mechanical type unidirectional (idle running) clutch for use, particularly clamping element formula free-wheeling clutch or pallet free-wheeling clutch are perhaps selected viscous hydraulic type or electromechanical type clutch for use.
Clutch clamping element formula free-wheeling clutch accurately is subjected to the restriction in working life, and the rated torque Mzul of this clutch is 10
8Drop to 50% under the secondary stress loop condition.For this free-wheeling clutch being applied to can cause all at revolution how existence one determines the problem of its size in the transmission of periodicity clutch process.If free-wheeling clutch is by the raising speed transmission, rated torque then descends, but because rotating speed rises, so stress-number of cycles increases, under the gearing down situation, situation is opposite.To this in lifetime 10
8This situation of secondary stress circuit free-wheeling clutch (as in transmission for vehicles) is vital to determining dimensions.Therefore, when adopting planetary gear of the present invention, special circumstances are stipulated: freewheel changes by one or more cylindrical gears groups or planetary gear set or the form of implementation by other drive technology with respect to the rotating speed of planet wheel.This change of this rotating speed as along rotating speed rising direction raising speed, has reduced to be present in the order of magnitude of the moment in the free-wheeling clutch, but has not increased clutch frequency or stress-number of cycles.Therefore, though select high transmission ratio under high rotating speed and low torque condition, stress-number of cycles does not increase, this be because, each clutch process takes place once when just in time each changes at follower, rather than occur in the single gear of planet wheel or planet wheel each when changeing.
On the contrary in another solution, that is under the situation of using latch clutch, durability is restricted hardly, in addition, this clutch low price, the shortcoming that the clutch accuracy reduces (8 ° to 10 °) recently remedies by hereinbefore described transmission.In addition, the angle error of clutch process has only caused the variation of the loading transfer point between two planet wheels, and does not cause functional defective.The moment of torsion sudden change that at this moment, might produce can be suppressed by the resilient member in the free-wheeling clutch locking device.In addition, in the form of implementation of a preferred use pallet free-wheeling clutch, adjusting that should the regulation speed ratio is not carried out in infinitesimal level, and should when sudden change, always select such velocity ratio, be that they mainly cause rotation in the planet wheel, the ratchet or the surface width of latch clutch passed in this rotation, so just no longer produce the load sudden change.Velocity ratio is to carry out under enough little locking angle by stepless this change to accurate step-less adjustment, so shortcoming is increased the weight of.
By further design of the present invention, the gear one by one or the planet wheel of planet wheel are coupled with spring force, and/or are supported on the bearing radially on their free-wheeling clutch, this radially bearing preferably along the nonlinear curve path movement.
By further design of the present invention, central gear and/or planet wheel or planet wheel are contained on driving disc and/or the driven disc, and its advantage is: guiding device, the articulated mounting that can be provided for single gear of planetary pinion or planet wheel on each dish.Planetary single gear or planet wheel preferably are hinged on a driving disc or the driven disc by a lever or crank respectively.
Like this, the moment of torsion transmission is undertaken by relevant lever or crank.Along with moment of torsion is passed to central gear from the single gear or the planet wheel of planet wheel, each gear forms the movement locus by principle determined, the relation of these movement locus and effective mid point, different effective radiuses and different tangential components in the load curve path, have been caused, this causes the nonuniformity of velocity ratio, its value can reach 1.5 or bigger under the WITH HIGH-ECCENTRIC situation, thereby has significantly damaged the smooth operation of transmission device.
By further design of the present invention, the nonuniformity of moment of torsion transmission or velocity ratio can be compensated at least in part by one-period property controlling device.This point can realize with different modes.
By first form of implementation, compensation is undertaken by a kind of radius compensation, wherein, selection has the intermediate value that is essentially constant, minimum value or the maximum value of identical transfer function integration, and transfer function is that the ratio of the angular velocity of the driving wheel that passes through with corner and follower determines relevantly.
By further design of the present invention, the nonuniformity of moment of torsion transmission or velocity ratio can compensate by the elastic device relevant with power and/or by balancing mass.Elastic device can be that hydraulic type, pneumatic type or other are mechanical.
The adjusting of relative eccentric ratio causes at least one axial-movement in the diaxon.To make its motion in order power being passed on the fixed axle, must to establish a flexible shaft or universal coupling or other hinge.In a preferred form of implementation, relative movement is not to move but rotation, axle for adjustment process at moving movement on the circular orbit rolls on a gear train this moment, at this moment, a wheel stops at axis of movement central authorities and second wheel that is next wheel and stops on the gear, and this gear is concentric with the circular orbit mid point, and the axle that moves at conditioning period rolls on this circular orbit.
By this measure and for avoiding imbalance to add balancing mass, can carry out the very high adjusting of frequency.
The possibility of this quick adjustment also can be utilized and eliminate above-mentioned nonuniformity.Under the effective radius situation that diminishes on phase cycling ground, eccentricity is reduced at this moment, and under the radius situation that phase place enlarges, it is big that eccentricity becomes.Reach method in this way, available simple geometric realizes uniformity.
In a particularly preferred form of implementation, moment of torsion transmission between driving link that is designed to disk, wheel or axle respectively and corresponding driven member by a period of time pole realize, wherein, toggle link bending Motion Compensation that be controlled or that be subjected to the elastic force effect nonuniformity of moment of torsion and the fluctuation of speed.
By further design of the present invention, the tracks of toggle link is a circle on the load curve path, this circle particularly by slide block, cam, more piece buckle chain and/or conduct radially the connecting rod guiding device of bearing make.For the amplitude that compensates geometric relevant with the eccentricity periodic motion that said fluctuation selects is a time constant.
Said unidirectional (idle running) clutch is by speedup or gearing down, with a rotation speed operation different with said planet wheel.In addition, the planet wheel guiding device makes the backlash of relative central gear and/or impacting force temporarily remain constant.
Especially, for the nonuniformity of compensation torque transmission or consider and be adjusted to desirable velocity ratio that rotating ratio can be designed to level two or more parallel connections or series connection, at this moment, the phase place of these grades is preferably chosen like this, can make the nonuniformity compensation mutually basically of each single level.Especially, two-stage has a common eccentric disc, and has the driving disc or the driven disc of the out of phase that is used to compensate nonuniformity, and/or the said planetary gear one by one on these two kinds of dishes or the gear quantity of planet wheel equate.
By further design of the present invention, with differential speed variator that driven shaft links to each other in, the planetary gear of at least two groups is entered as and can makes the nonuniformity of moment of torsion and rotating speed compensate basically.
At last, a plurality of planet wheel levels and reverse and/or convertible unidirectional (idle running) clutch link, or with can link via the axle of an inversion axis or axle control in the same way.
The advantage of described planetary gear is: it can be regulated under state of rest and load, and it is fricton-tight and be positive engagement, low noise and compact structure, and, it not only efficient height but also life-span long.Its cost is lower than four stage change-over gear case or three grades of automatic clutches, and the latter is as having the Gear Planet Transmission robot device of multi-disc friction clutch.Do not have stationary problem completely, do not need these devices of portable coupling or friction clutch yet.
Extensive by planetary gear application of the present invention, to all the engine-driven automobiles that can imagine, assist the transmission of unit from bicycle up to machine-building.By designing a kind of transmission line, with the axle that a cylindrical gears component is two mutual counter-rotatings that moves through of engine shaft, an axle upper planet wheel speed changer can be controlled to be relative rotation speed and can and then access a desired speed discrepancy therein.This speed discrepancy further is delivered on the driving wheel of differential transmitting linkage, so when speed discrepancy is 0, just no longer need to start clutch.A kind of vehicle with this speed changer can stop reversing automatically, and can not have under any small speed with colliding and travel.Have only because the caused undesirable motion of the fluctuation of speed in the planetary transmission must be by the relatively jaw clutch disconnection of controlling device or positive engagement, said jaw clutch is the state of rest safety installations that is used between the driving shaft of the reciprocal commentaries on classics of two-phase, because undesirable wriggling process also can not stop with break.
Expand planetary gear and the member consumption that increases and expense expenditure are lower by described mode, this be because, in the design of planetary gear, needed planetary stage can constitute all-in-one-piece, so, a lot of members, as axle, bearing, disk, casing and lubrication etc., can be from repeatedly utilizing.
In addition, can directly utilize mechanical gyrator (Schwungkreisel) like this, the size that drives motor may need only consider that the continuous rating of stable state determines, and refluxes and can guide by gyrator for all unsteady state power flows and power.Therefore, concerning the urban transit system vehicle, utmost point fuel saving, and improving road horsepower and raising, reduce emission of harmful substances in the time of manoeuvring performance.
In described form, planetary transmission is at present only at a direction transmitting torque and power, and this is because unidirectional (idle running) clutch is in negative side carry-over moment not.Yet,, wish that power flow all can transmit at both direction, so can consider to install additional corresponding annex in a lot of applications.In a possible form of implementation, free-wheeling clutch can be transferred in the other direction for this reason.In another form of implementation, with the second level and the in parallel or setting of connecting of free-wheeling clutch in the other direction.The velocity ratio that suitably is adjusted in the two-stage can avoid motion to be obstructed.
Embodiments of the invention as shown in drawings.Among the figure:
Fig. 1 a to d be respectively a kind of plan view with first form of implementation of planetary gear of internal gear type central gear (a, c) and side view (b, d);
Fig. 2 a, b are another form of implementation of planetary gear, and this planetary gear has an external tooth type central gear;
Fig. 3 is the variation and relevant peripheral force of load curve path effective radius;
Fig. 4 is for by each gear of planet wheel shown in Figure 2 and the central gear schematic representation that rolls of interworking mutually;
Fig. 5 is the toggle link geometric representation in the rod gear, the motion on a guiding circle of this toggle link;
Fig. 6 is one at driven disc with radially be equipped with the form of implementation of toggle link between bearing, and this is each gear of bearing support planet wheel radially;
Fig. 7 is and the corresponding schematic representation of Fig. 5, has wherein considered eccentricity;
Fig. 8 a, b are another form of implementation of planetary gear, are used for bicycle here.
Fig. 9 a, b are the perspective view of above-mentioned form of implementation;
Figure 10 a, b are respectively the perspective view and the plan view of a driven disc, and this driven disc has tangential bearing and is used for the moment of torsion transmission;
Figure 11 a, b are perspective view and the plan view with central unit of three radial supports;
Figure 12 a, b are the cylindrical gears group of driving mechanism;
Figure 13 has the system of vehicle transmission circuit conceptual scheme that a planet wheel speed changer does not have clutch;
Figure 14 is the sectional view of speed changer, and this device has the periodic adjustment device, is used to compensate nonuniformity;
Figure 15 a, b are respectively the diagrammatic top view of a speed changer, and this device has a central unit, and this central unit has three bearings at diverse location.
Driving wheel 20 is a central wheel of internal teeth among Fig. 1, and each planet wheel 21 to 24 keeps engagement and the running of relative central gear with central gear.These single gears 21 to 24 are radially moving on the bearing, and bearing radially shown in Fig. 1 c, d, is set out through occupying different radial positions after the revolution prejudicially by the concentric position shown in Fig. 1 a.By these single gears 21 to 24 are bearing in the free-wheeling clutch with its rotation relevantly, nearest that gear (being 22 here) of the most close radial position transmits whole load in all eccentric axial location.Remaining gear is gear 24 especially, is had a peripheral velocity by transmission, and this peripheral velocity is greater than the peripheral velocity of the gear 22 that is used as driving wheel.Transmission moves through with bar 25 and is delivered on the driven disc 29 in 28.Gear 21 to 24 meshes with the ring gear maintenance of central gear 20 when rotating all the time, therefore, and no longer synchronous after the starting of unloaded path.Each gear in the gear 21 to 24 is in the time of free-wheeling clutch lockup state, that is in the load curve path, be in time of transmitted load, the time that occupies short radius position with relevant gear is equally long, up to by following closely and take over to the further approaching gear in the center of driven disc 29.Like this, this gear is following closely born the driving task, and gear is compared therewith, and it is bigger than the peripheral velocity of this gear that the peripheral velocity of that gear that goes before then becomes.
By the form of implementation corresponding to Fig. 2, driving wheel 30 is an external gear, and at this moment, each planet wheel 31 to 34 reaches power or moment of torsion on the driven disc 35 by means of lever 36 to 39 with being rigidly connected.Therefore each cylindrical gears carries out the raising speed transmission to 40 with 41 rotating speeds with each relevant gear, make those must the smaller moment of transmission with respect to the fixing free-wheeling clutches of relevant radially bearing 42 with gear 41, thereby obtains a degree of regulation that has improved.Relative driven disc 35 off-centre of representing among Fig. 2 a initiatively to move in turn are not quite inclined to one side, the extreme eccentric position of expression among Fig. 2 b, when pressing the position of Fig. 2 b, velocity ratio Yue Keda 1: 6, at this moment, lever 36 to 39 is correspondingly swung, even so that guarantee to have off-centre also can mesh rigidly at each gear 31 to 34 and 30 of driving wheels.
As shown in Figure 3, along the variation of load line path 44 effective radiuses 43, identical with the variation of the tangential component 45 of driving force 46 between driving disc 47 and driven disc 48.Each gear is represented with 49.
Fig. 4 represents (to move on to dotted line position from solid line position) when the driving disc position change is very little, the intensity of variation of each gear 49 radial positions.
Fig. 5 will contrast Fig. 6, and among Fig. 6, the angle lever 50 that the straight lever 36 to 39 among Fig. 2 has been had toggle link 51 substitutes.These toggle links 51 move leading on the circle 52, they on leading circle by simply radially bearing (not drawing among Fig. 6) guiding.By the compensating motion of toggle link 51, the time pole 50 can be bent into different angles at diverse location, make between driving wheel 30 and driven disc 35 velocity ratio that has a constant along whole load line.As seen from Figure 7, toggle link 51 is how by different bendings, that is the different amount between each lever arm part realize compensation.
Fig. 8 and Fig. 9 (a, b two figure are respectively arranged) have represented to be used for the special form of implementation of the present invention on the bicycle chainwheel 54, and this sprocket wheel is hinged on the radially bearing of each gear 56 by crank.These single gears 56 keep engagement with central gear 57, move relative to the off-centre of gear ring 54 by central gear 57 to change velocity ratio.
Figure 10 a, b are depicted as a driven disc 58, and this disk is driven by driving wheel 59 by tangential bearing 60.The diagonal angle bearing of compensation circle 62 is represented with 61.
Figure 11 a, b are depicted as a central unit with three radial struts, and three planet wheels 63 among the figure on radial struts 64 keep permanent engagement with center driving wheel 62.By the rotating speed of variable speed drive 65 raising free-wheeling clutches 66, with the moment of torsion minimum that guarantees that this place produces.
Under the situation of pressing form of implementation shown in Figure 12 a, the b, the cylindrical gears 67 by is separately realized the moment of torsion transmission of diaxons 68, and two cylindrical gearss 67 are contained on the diaxon 68.Diaxon or cylindrical gears are kept by the axial support 69 of single-revolution.
Figure 13 shows that the transmission line scheme that has a planet speed changer and do not have a kind of vehicle of clutch.Wherein, one drives axle 72 and the axle 73 of the axle 70 of motor 71 by two reverses of gear train driving always, is connected in the planetary gear 74 between axle 70 and the driven shaft 72, its speed discrepancy can be adjusted to desirable value.The velocity ratio that axle is 70 and 73 is assumed to 1: 1.25 in the illustrated case.Diaxon 72 and 73 motion input differential transmitting linkage 75 make driven shaft 76 to be adjusted to differential values 0 that when turning round rapidly promptly the velocity ratio of planet wheel speed changer is changed to 1.25.Other numerical example such as following table:
N
IdlingN
Forward gear 1N
Forward gear 2N
Reverse gear800 3,000 6,000 2,000 1 800 3,000 6,000 2,000 2 1,000 6,000 10,000 2,000 3-1000-3,750 7,500 2500 driven shaft 0 2,250 2500-500 planet wheel speed changes of motor, 1.25 2.00 1.67 1 device velocity ratios
Figure 14 represents to have the planetary transmission of the so-called IVT speed changer of an integrated type planetary gear set.Have among Figure 14: driving shaft 77, one planet gear drives 78, have free-wheeling clutch 79 and driven planet wheel 81 of idle running transmission device 80.One operating handle 82 acts on the balance staff of regulating device (VerstelLung) 83.Change velocity ratios by handling eccentric disc 84, this is used to compensate the nonuniformity eccentric disc, connects together with the control gear 85 of one-period property.
Figure 15 a and b are depicted as by the planetary gear of Figure 14 situation at different eccentric positions.
Claims (23)
1. can be stepless or the planetary gear of quasi-stepless speed change positive engagement, it comprises the adjustable planet wheel of at least one diameter, this planet wheel and a central gear are in permanent rigid joint state, wherein these two the mutual diameter ratios of wheel determine the mutual eccentric position of these two wheels, and determine the rotating ratio of these two wheels thus.
2. according to the said planetary gear of claim 1, it is characterized in that, planet wheel is made up of a plurality of single small-diameter wheels, steamboat is designed to the star-wheel rotational that can detour on the one hand, on the other hand, only can be by a directed oncoming clutch in one direction around himself rotational, said steamboat, be under the eccentric position situation at relative central gear, periodically through the load diagram path and a no-load path of a transmitting torque, and, steamboat when carrying out the transition to load paths by the no-load path, that is will with the moment of central gear rigid engagement, free synchronization ground motion, but after rigid engagement and rotation are prevented from, beginning transfer function moment of torsion thereon.
3. continuously variable positive engagement planetary gear, it comprises a central gear and a plurality of minor diameter planet wheel, minor diameter planet wheel and central gear are in forever the outer gearing state and are contained on the disk, perhaps link by force transmission mechanism and disk, wherein, planet wheel can be by unidirectional (idle running) clutch around himself axis to a direction rotation but locked to the rotation of another direction, and the axis of said disk moves with respect to the central gear axis is eccentric, is adjusted into different rotating ratios and torque ratio thereby can be dependent on center displacement between disk and central gear.
4. according to any described planetary gear in the claim 1 to 3, it is characterized in that: said steamboat or planet wheel are gears, and wherein, said central gear preferred design becomes the external gear of internal gear or outer gearing.
5. according to any described planetary gear in the claim 2 to 4, its special sheet is: said directed oncoming clutch is the mechanical type overrunning clutch, particularly clamping element formula free-wheeling clutch, or pallet free-wheeling clutch, or viscous hydraulic type or electromechanical type clutch.
6. according to any described planetary gear in the claim 1 to 5, it is characterized in that: said unidirectional (idle running) clutch directly control the circular movement of said planet wheel and do not control that its rotation and/or said planet wheel can be used on initiatively and between the follower hinge or other Force transmission parts replace.
7. according to any described planetary gear in the claim 3 to 6, it is characterized in that: said each gear or planet wheel and other small diameter gear are in the rigid engagement state, wherein, said small gear or planet wheel are arranged on to be installed on radially and bear on the free-wheeling clutch of less moment of torsion on the bearing.
8. according to any described planetary gear in the claim 1 to 7, it is characterized in that: the wheel one by one of said planetary pinion or planet wheel is spring loaded and/or is arranged at its unidirectional (idle running) clutch on bearing radially, this radially bearing be preferably on the nonlinear curved path and move.
9. according to any described planetary gear in the claim 1 to 8, it is characterized in that said central gear and/or planetary pinion or planet wheel are arranged on a driving disc and/or the driven disc.
10. planetary gear according to claim 9 is characterized in that; Said planetary wheel one by one or planet wheel can be hinged on driving disc or the driven disc by a lever or a crank respectively.
11., it is characterized in that according to any described planetary gear in the claim 1 to 10: the nonuniformity of moment of torsion transmission by by the variation of the action radius that load line determined/or effectively the variation of tangential component compensated at least in part by means of one-period property controlling device.
12. planetary gear according to claim 11, it is characterized in that a compensation device, use under this compensation device situation, transient state, the even velocity ratio that causes by the eccentricity of adjusting, be to have identical transfer function integration and be essentially constant intermediate value minimum value or maximum value, this transfer function is by the decision of the ratio of driving shaft angular velocity relevant with corner and driven shaft angular velocity.
13., it is characterized in that: the flexibly compensation that the nonuniformity of velocity ratio or moment of torsion transmission is relevant with power basically and/or be compensated by balancing mass according to claim 11 or 12 described planetary gears.
14. according to any described planetary gear in the claim 11 to 13, it is characterized in that: said moment of torsion transmits the variation that the eccentric axis ground offsetting that has a gear in gear or the planet wheel at least maybe can be adjusted this eccentricity, at this moment, rotation can change eccentricity under the situation of movable axis not.
15. according to any described planetary gear in the claim 10 to 14, it is characterized in that: the moment of torsion transmission between driving link that is designed to disk, gear or axle and corresponding driven member is carried out via toggle, the bending campaign of toggle link that periodically be controlled or spring-loaded at this moment, the nonuniformity of compensation torque or velocity ratio.
16. planetary gear according to claim 13 is characterized in that: the tracks of said toggle link is a circle at least on the load line path, and this circle is particularly made by slide block, cam, more piece words pitch chain and/or connecting rod guiding device.
17. any described planetary gear according in the claim 9 to 16 is characterized in that: be the selected geometry of the nonuniformity of compensation torque transmission or velocity ratio, the width of cloth of the periodic motion that it is relevant with eccentricity temporarily remains constant.
18. according to any described planetary gear in the claim 1 to 17, it is characterized in that: said free-wheeling clutch is by speedup or gearing down, with a rotation speed operation different with the rotating speed of said planetary pinion or planet wheel, and/or the guide device of said planet tooth or planet wheel to make the backlash of relative central gear and/or impacting force be time constant.
19. according to any described planetary gear in the claim 1 to 18, it is characterized in that: the compensation of transformation of speed between actuator and driven member and/or moment of torsion nonuniformity realizes by two or more levels, at this moment, the phase place of particularly said level is chosen and should be made the nonuniformity of said level compensate mutually basically.
20. planetary gear according to claim 19, it is characterized in that: two levels have a common eccentric disc, and driving disc and driven disc with the out of phase that is used for the compensation torque nonuniformity, and/or the number of said planet wheels on this two dish equates.
21. any described planetary gear according in the claim 1 to 20 is characterized in that: with the joining differential biography device of driven shaft in, the planetary transmission of at least two levels is entered as and can makes the moment of torsion nonuniformity be compensated basically.
22. any described planetary gear according in the claim 1 to 21 is characterized in that, a plurality of planet wheel levels with reverse and/or convertible unidirectional (idle running) clutch links to each other or with can link to each other via the axle of an inversion axis or axle control in the same way.
23. according to any described planetary gear in the claim 1 to 22, it is characterized in that: the distribution of the motion of driving link should make a reversing shaft and a footpath lead to a planet wheel gear by the adjustable axle of planetary gear, thereby the driven shaft of said planet wheel gear (the 3rd) can be a regulation range stepless speed regulation that has enlarged by linking to each other with driving shaft.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP4324123.9 | 1993-07-19 | ||
| DE19934324123 DE4324123A1 (en) | 1993-05-26 | 1993-07-19 | Infinitely variable transmission with positive torque transmission |
| DE19934329441 DE4329441A1 (en) | 1993-05-26 | 1993-09-01 | Continuously variable transmission with positive torque transmission |
| DEP4329441.3 | 1993-09-01 | ||
| DEP4340374.3 | 1993-11-26 | ||
| DEP4343145.3 | 1993-12-17 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1127543A true CN1127543A (en) | 1996-07-24 |
Family
ID=25927798
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 94192811 Pending CN1127543A (en) | 1993-07-19 | 1994-05-10 | Continuously variable positive planetary gear |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1127543A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103527735A (en) * | 2013-11-04 | 2014-01-22 | 苏州建莱机械工程技术有限公司 | Planet intermittent synchronizing mechanism |
| CN105317959A (en) * | 2014-08-01 | 2016-02-10 | 本田技研工业株式会社 | Continuously variable mechanism |
| CN106461037A (en) * | 2014-05-05 | 2017-02-22 | 鲁汶大学 | Continuously variable planetary transmission |
| IT201900014907A1 (en) * | 2019-08-21 | 2021-02-21 | Edoardo Facchini | MOTION TRANSMISSION DEVICE |
| CN114270074A (en) * | 2019-09-05 | 2022-04-01 | 池田昌幸 | Gear speed change device |
-
1994
- 1994-05-10 CN CN 94192811 patent/CN1127543A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103527735A (en) * | 2013-11-04 | 2014-01-22 | 苏州建莱机械工程技术有限公司 | Planet intermittent synchronizing mechanism |
| CN103527735B (en) * | 2013-11-04 | 2017-02-08 | 苏州建莱机械工程技术有限公司 | Planet intermittent synchronizing mechanism |
| CN106461037A (en) * | 2014-05-05 | 2017-02-22 | 鲁汶大学 | Continuously variable planetary transmission |
| CN105317959A (en) * | 2014-08-01 | 2016-02-10 | 本田技研工业株式会社 | Continuously variable mechanism |
| IT201900014907A1 (en) * | 2019-08-21 | 2021-02-21 | Edoardo Facchini | MOTION TRANSMISSION DEVICE |
| CN114270074A (en) * | 2019-09-05 | 2022-04-01 | 池田昌幸 | Gear speed change device |
| CN114270074B (en) * | 2019-09-05 | 2024-02-20 | 池田昌幸 | Gear speed variator |
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