WO2011053187A1 - Transmission à variation continue, variateur, limitateur de la gamme de rapports d'engrenage et satellite - Google Patents

Transmission à variation continue, variateur, limitateur de la gamme de rapports d'engrenage et satellite Download PDF

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Publication number
WO2011053187A1
WO2011053187A1 PCT/RU2010/000330 RU2010000330W WO2011053187A1 WO 2011053187 A1 WO2011053187 A1 WO 2011053187A1 RU 2010000330 W RU2010000330 W RU 2010000330W WO 2011053187 A1 WO2011053187 A1 WO 2011053187A1
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WIPO (PCT)
Prior art keywords
disks
variator
discs
satellites
gear
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PCT/RU2010/000330
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English (en)
Russian (ru)
Inventor
Владимир Михайлович ЛЕБЕДЬКОВ
Константин Владимирович ЛЕБЕДЬКОВ
Original Assignee
Lebed Kov Vladimir Mikhaylovich
Lebed Kov Konstantin Vladimirovich
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Application filed by Lebed Kov Vladimir Mikhaylovich, Lebed Kov Konstantin Vladimirovich filed Critical Lebed Kov Vladimir Mikhaylovich
Publication of WO2011053187A1 publication Critical patent/WO2011053187A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50—Gearings providing a continuous range of gear ratios
    • F16H15/52—Gearings providing a continuous range of gear ratios in which a member of uniform effective diameter mounted on a shaft may co-operate with different parts of another member

Definitions

  • the group of inventions relates to mechanical engineering and relates to a continuously variable transmission of vehicles with a friction variator, as well as its parts - a variator controlled by a limiter of the gear ratio and satellite range.
  • the prior art adaptive continuously variable transmission (Russian patent RU 2138710 C1), containing input and output shafts, an adaptive planetary disk friction variator, a mechanism for changing the stiffness of a characteristic.
  • the planetary friction variator can be multi-disk (Russian patent RU 2140028 C1).
  • the above analogues have a number of disadvantages: the inability to directly control the gear ratio, the low reliability of the springs or the large power take-off to create a clamp using pressurized media, the use of variator assemblies to ensure reversal, which unjustifiably increases the dimensions of the structure and its complexity as a whole, the complexity and unreliability of the mechanism adaptation, the inability to use in conjunction with high-frequency internal combustion engines.
  • the gear ratio of the variator according to RU 2140028 can be either more than 1 (in the reduction mode) or less (in the multiplication mode), while the dependence of the extreme gear ratio of the range asymptotically tends to 1, the variator can never provide a “direct stroke” under normal operating conditions so necessary for cars.
  • a gear ratio of 1 is possible either when the internal friction pair is jammed, or when the carrier is locked relative to the moving epicycle. In such cases, accidental wear of the rolling elements occurs, and the forward stroke is switched on jerkily, which is not desirable for vehicles.
  • the adaptation mechanism in this variator is designed to change the stiffness of the variator, and not to limit the range of gear ratios, so nothing will prevent the car from slipping on ice or in other road conditions with a low coefficient of adhesion of the wheels to the roadway, regardless of the stiffness of the variator.
  • a stepless transmission is known (Russian patent RU 2166138 C2), comprising a housing, input and output shafts, a planetary gear, a multi-disk planetary variator and regulation mechanism.
  • This design has the following disadvantages:
  • a continuously variable transmission (RU 2300032, publ. May 27, 2007) containing an input and output shafts, a friction variator and a reversing mechanism, and it is equipped with a planetary gearbox, the sun gear of which is fixed on the input shaft, its epicycle is fixed on the transmission case, the friction variator is made of a planetary multi-disk, forms a variation module with a planetary gearbox and includes an epicyclic mounted in the transmission case, made in the form of a package of disks with an internal cas iem, sun wheels, also embodied as disc stack with an external touch, placed on the output shaft varying unit coupled to the input shaft of the reversing mechanism, the carrier, connected to the planet carrier of the planetary gearbox and consisting of two disks connected to each other, axes with satellites placed on them in the form of intermediate disks, the carrier disks have curly slots according to the number of axes, and the axes are mounted in curly slots with the possibility of changing
  • a disadvantage of the known transmission and variator is the presence of thick-walled disks with spring sockets for coil springs in solar and epicyclic disks having a high mass and stress concentrators on the spring sockets. A large number of coil springs are required. In addition, there is a high wear of biconical satellites
  • a controlled gear range limiter which is also part of the known transmission (see ibid.), Consisting of a lever mounted on a planet carrier of a planetary multi-disk variator, two stops, each of which is mounted with the possibility of movement in a figured groove of a carrier disk, a hydraulic cylinder with working fluid that is moved between the discs of the carrier by means of its hollow coupling bolts.
  • the limiter is equipped with a lever position sensor.
  • the objective of the proposed group of inventions is to reduce the mass, dimensions, increase the service life and reduce the requirements for materials of the transmission and its parts.
  • the technical result achieved by the proposed transmission and variator is to reduce weight, reduce the number of springs and increase service life. In addition, providing a more efficient reducing kinematic variator circuit, which allows you to do without an input gear.
  • the overall dimensions of the transmission are also improved through the use of a multi-threaded gearbox that does not have internal gearing, combined with a reverse gear, also does not have internal gearing.
  • the specified variator includes an epicyclic mounted in the housing, made in the form of a package of pairwise arranged disks with an internal touch , package pairwise arranged solar disks with external contact located on the input shaft of the variator, a carrier connected to the output shaft of the variator connected to the input shaft of the reversing mechanism, and including two disks connected to each other, connected to the axis disks with satellites placed on them in the form of intermediate disks , carrier disks have figured grooves in the number of satellite axes, and satellite axes are connected with figured grooves with the possibility of changing their position and interaction by intermediate disks with solar disks and epicyclic disks, spring the terms for pressing the solar disks and epicyclic disks to the intermediate disks installed between the disks of each pair, characterized in that each of the solar disk
  • the springs are diaphragm springs that are installed between the disks of each pair by a packet of an even number of diaphragm springs, with the spring petals in each packet directed in opposite directions to adjacent satellites.
  • the satellites are preferably biconvex lenticular in shape.
  • each axis of the satellites is installed at each end on the arm of the corresponding pivot arm through bearing bearings, and on the other arm of the pivot arm there is a balancer with the possibility of changing its position in the corresponding figured groove made in the respective carrier disk.
  • each carrier disk consists of two washers associated with the possibility of angular displacements relative to each other, and each pivot arm is mounted on one of the washers, and the indicated curly grooves are made in the other.
  • the bearings are made in the form of sliding bearings made of carbon-carbon material, namely, a composite material in which carbon is present in two different phase states - in the form of a carbon filament, which provides strength and bearing capacity, and graphite, which provides antifriction properties of the bearing slip.
  • the reversing mechanism contains a multi-threaded boost gear and a reverse gear with common intermediate shafts.
  • the gearbox range limiter is made in the form of an annular element with an internal conical surface mounted in the housing with the possibility of axial movement and interaction with the rollers associated with the balancers.
  • a planetary multi-disk friction variator containing an epicyclic mounted in the housing, made in the form of a package of pairwise arranged disks with an internal touch, a package of pairwise arranged solar disks with an external touch located on the input shaft of the variator, a carrier connected to the output shaft of the variator and including two disks connected to each other, connected to the axis disks with the satellites placed on them in the form of intermediate disks, the carrier disks have curly grooves along the SLE satellite axes, and the axes of the satellites associated with shaped grooves with the possibility of changing their position and interaction between the intermediate discs and the solar discs and epicyclic discs, springs for pressing the solar discs and epicyclic discs to the intermediate discs installed between the discs of each pair, characterized in that each of the solar discs and epicyclic discs has a transverse Z-shaped section,
  • the springs are diaphragm springs that are installed between the disks of each pair by a packet of an even number of diaphragm springs, with the spring petals in each packet directed in opposite directions to adjacent satellites.
  • the satellites have a biconvex lenticular shape.
  • each axis of the satellites is installed at each of its ends on the arm of the pivot arm by means of bearing bearings, and on the other arm of the pivot arm there is a balancer with the possibility of changing its position in the corresponding figured groove made in the corresponding carrier disk.
  • each carrier disk consists of two washers connected with the possibility of angular displacement relative to each other, and each pivot arm is mounted on one of the washers, and the indicated curly grooves are made in the other.
  • gearbox range limiter is made in the form of an annular element with an internal conical surface mounted in the housing with the possibility of axial movement and interaction with rollers associated with balancers.
  • bearings are made in the form of plain bearings made of carbon-carbon material.
  • the limiter of the gear ratio range of the planetary multi-disk friction variator made in the form of an annular element with an internal conical surface mounted in the housing with the possibility of axial movement and interaction with rollers associated with balancers installed in the figured grooves of the carrier discs and connected by means of rotary levers with the axes of the satellites.
  • the technical result is also achieved by performing a satellite for a planetary multi-disk friction variator of a double-convex lentil shape, preferably with a directed hon.
  • FIG. 1 shows a schematic diagram of a continuously variable transmission (the reverse mechanism is not shown); in FIG. 2 is a schematic diagram of a variator; in FIG. 3 is a schematic diagram of a reversal mechanism; in FIG. 4 shows a cross section of an epicyclic disk; in FIG. 5 (a, b, c) - a biconvex satellite is shown: a - cross-section, b - front view with grooves, c - with the same groove; in FIG. 6 - contact diagram of a satellite with disks; in FIG. 7-10 shows the gear range limiter in the off state (Fig. 7 and Fig. 8) and in the on state (Fig. 9 and figure 10) in two different positions of the axles of the satellites and for the corresponding gear ratios.
  • the transmission consists of a CVT according to the gearbox and a reversal mechanism, including a step-up gearbox (multiplier) and a reverse gearbox.
  • the transmission uses a planetary multi-plate friction variator, which is arranged as follows.
  • the variator (figure 2) contains an epicyclic mounted in the transmission housing, made in the form of a package of disks 1 with an internal touch, solar disks also made in the form of a package of solar disks 2 with an external touch, located on the input shaft 3 of the variator.
  • the carrier 4 of the variator is connected to the output shaft of the variator and consists of two disks 5 connected by coupling bolts.
  • the disks 5 of the carrier 4 of the variator are each of two washers 6 and 7 each, interconnected with the possibility of angular displacement. In this case, on one of the washers 6, the rotary levers 8 are fixed by means of bearings, and the second washer 7 has curly grooves 9.
  • each disk 5 three to six curly grooves 9 are made according to the number of axles 10 of the gears of the 11 variator.
  • the axis 10 of the satellites by means of bearings 12 are mounted on the pivot arms 8.
  • balancers 13 with the ability to change their position in the curly grooves 9 depending on the ratio of speed and torque.
  • Satellites 11 are made in the form of intermediate biconvex lenticular disks mounted on the axes 10 and interact with the solar disks 2 and disks 1 epicycle.
  • the disks 1 and 2 of the bags in this case are made with a Z-shaped cross section. Between the rear sides of the paired mounted discs 1 of the epicycle and between the rear sides of the pairwise mounted solar disks 2 installed packages of springs 14.
  • the springs 14 are made diaphragm. To unclench a pair of disks, a package of springs 14 with petals directed in different directions is required. Each package of diaphragm springs 14 creates a pressing force on two friction discs of a pair.
  • Solar and epicyclic discs 1 and 2 have a cross-section ⁇ -shape or other profile shape from a number of: unequal corner, Taurus, I-beam, channel.
  • This shape of the cross section of the disk reduces elastic deformations, which, according to the working conditions of the part, are variable, and therefore leading to fatigue wear and fracture, and thus increase the variator resource.
  • this disk shape unlike a thick-walled disk with spring sockets, is devoid of stress concentrators, which are the same spring sockets, and a strong negative influence of which was revealed during the manufacture, assembly and testing of the transmission according to JV ° 2300032.
  • a disk of this shape is close to a thin-walled flanged, and in the workpiece can be obtained by stamping or casting.
  • diagrams of stresses and deformations of such disks were constructed, and calculations of the most optimal angles of conical surfaces were made.
  • Scheme perceived loads during disk operation are shown in FIG. 4 by the example of a ⁇ -shaped disk.
  • F - clamping force provided by springs.
  • N is a normal reaction from the side of the surface of the conical disk, which provides the friction forces necessary for the operation of the variator.
  • the springs 14 creating the pressing force are made diaphragm (like the spring of the clutch basket of a car with a manual gearbox).
  • the diaphragm springs 14 do not require spring sockets in the discs 1 and 2.
  • springs have a significantly longer service life - 10 b loading cycles than Belleville springs - 10 4 loading cycles, and such springs are required much less than screw springs (up to 8 sheets per package, unlike 12 springs per package).
  • diaphragm springs make it possible to realize variable stiffness springs at the lowest cost (with the high-precision metal processing methods available today, such as laser and waterjet cutting), which avoids pinching at the maximum and minimum gear ratios of the variator.
  • the diaphragm spring package creates a more uniform downforce.
  • the diaphragm springs 14 are arranged in packages of several sheets, a multiple of 2, with each package consisting of 2 parts located supporting sides to each other. Each part has at least one leaf of springs. Packs of diaphragm springs are located between each two friction ⁇ -shaped disks 1 or 2 located on the back sides to each other.
  • Satellite disks (I satellites) have a biconvex (lentil) shape (Fig. 5).
  • the main place for variator wear is disc contact spots, and the main causes of wear are a high proportion of rolling friction, as well as drainage of friction surfaces at high frequencies under the action of centrifugal forces.
  • Biconvex (lenticular) satellites provide an increased resource for the raceway.
  • a nonlinear generatrix of the working surface of the satellite i.e. with a satellite having a convex or concave shape
  • the wear is distributed over different raceways of the solar and epicyclic disks. But the most worn will be the track corresponding to the most commonly used gear number. The rest will account for only 20% of wear. For example, take a multi-lane highway - the leftmost lane is always rolled out, as the most often used.
  • a CVT with concave disks has an increased proportion of spin friction leading to wear - and we can assume that the resource gain is not twenty, but only a few percent. While for biconvex satellites, the distribution of wear is maintained, leading to a decrease in wear per unit surface of the raceway, but the spin friction is reduced, which eats up a useful effect.
  • the main advantage of the biconvex shape of the satellite is a decrease in the size of the contact spot by about 15%, but more significantly, the decrease is primarily in the more elongated direction of the spot - the circumferential direction of the working disks. Such a change slightly reduces the transmitted force at each contact spot by 2-3%, but increases the resource of the working fluid by 15-20%.
  • the effect of drying the working spots is essential. If this happens, dry friction appears with a transition to the super-slip effect, and very rapid wear occurs, at some the moment the throughput power rapidly drops to 0. This is due to the fact that the rotating disks (solar disks and satellites), throw off the oil from themselves by the action of centrifugal forces. To prevent this, directed hon - micro roughnesses and risks must be applied to the surface of the disks, which during rotation will play the role of a centripetal pump, which prevents the oil from flying out under the action of centrifugal forces. Accordingly, the direction of the grooves (grooves) of the hone should be opposite to the rotation of the disks. In this case, the variator becomes irreversible, i.e. It can work only in one direction, but acquires the ability to work in the field of high frequencies, which reduces weight and dimensions.
  • variators of this type were the very high load from centrifugal forces, with a rotational speed of the input shaft of 6000 rpm, the carrier speed is more than 4000 rpm, and thus the load from centrifugal forces significantly exceeds the load from torque, which itself in itself exceeds the permissible for a different type of rolling bearings other than needle ones. This was the reason for the development of the transmission according to patent N ° 2300032.
  • plain bearings are available that can withstand loads of more than 25 MPa at linear speeds of more than 15 m / s, which allows the variator to be implemented according to the gearbox.
  • the proposed variator according to the gear circuit is more high-frequency at the same speed of the output link, and therefore lighter and more compact, because with equal transmitted power the transmitted torque is less, the higher the frequency. Namely, the required total area of contact spots, and therefore the number of working bodies of the variator, depends on the transmitted moment, and therefore the dimensions and mass.
  • the variation module can include only the variator itself and the input gear. But for most existing ICEs and electric motors, an input gearbox is not required, in this case the variation module includes only a variator, as in the proposed transmission.
  • the reversal mechanism (Fig. 3) includes an output gearbox and a reverse gearbox. With a variator made according to the gear circuit, the output gear is step-up, i.e. animator.
  • the output shaft 15 of the variator and the input shaft 16 of the reversing mechanism are connected by a spline connection.
  • the input shaft 3 of the variator is the input shaft of the transmission, and the output shaft 17 of the reversing mechanism is its output shaft.
  • the reversal is carried out using spurious gears, which reduces the overall dimensions in comparison with a reverse gear with internal gearing.
  • the step-up gearbox and reverse gearbox are multi-threaded with common intermediate shafts.
  • only one of the flows is implemented for the reverse gear, since according to the conditions of use during reverse operation, the transmitted power is much less.
  • a gear 18 of a multi-threaded gearbox is connected to the input shaft 16 of the reversing mechanism, which transmits torque to the gears 19, connected to the intermediate shafts 20, on which gears 21 and Gears 22 are also mounted.
  • the gears 21 transmit torque to the gear 23, and gears 22 transmitting torque to the gears 24 through spurious gears 25.
  • Gears 23 and gears 24 can be connected to the output shaft 26 via a synchronizer 27, thereby you can choose forward or reverse.
  • the multi-threaded scheme allows reducing the load on the gears and bearings, thereby reducing the requirements for the properties of materials, and allowing the use of more technologically advanced and cheaper materials, i.e. reduce the cost of the product.
  • Switching the direction of rotation is done by switching the synchronizer when the clutch is switched off with the car engine.
  • the clutch may be disk, but more promising is the use of fluid coupling or torque converter.
  • Translation of the synchronizer between the “forward”, “neutral” and “reverse” positions can be carried out manually, using the translation mechanism. However, for safety reasons, it is preferable to use an electrically controlled drive, with protection against switching with the clutch engaged or at high engine speeds (with hydraulic clutch).
  • the proposed gear range limiter is a conical ring element 28 installed in the variator housing with an inner conical surface and a set of rollers 29.
  • the rollers 29 are connected to the variator balancers 13 (or are part of them) and can rotate on their own axes.
  • the conical ring element 28 has the ability to move along the axis of the variator and is located coaxially with the axis of rotation of the variator. In the process, the rollers 29 move along the guide lines of the cone or along circles of a smaller radius, since the cone limits only the maximum distance from the center or approaching it.
  • the cone prevents the movement of the rollers 29 in a circle above a predetermined radius, but does not prevent them from moving to any smaller circle - thereby the rollers 29 move away from the cone and a gap is formed.
  • a conical ring element 28 installed in a predetermined position limits the gear ratio range to a desired value, however, direct contact of the working surfaces occurs only when this gear ratio is reached, at lower gear ratios there is a gap that reduces wear and increases the service life of the site.
  • the conical ring element 28 in this case is driven by a linear actuator with a hydraulic or electromechanical drive and is equipped with a feedback system that allows you to control the position of the conical ring element 28, and hence the limit of the gear ratio range.
  • the proposed gearbox range limiter directly limits the gearbox ranges to the largest values, which does not allow the car wheel to develop maximum speed with a poor coefficient of adhesion of the wheel to the roadway and begin to slip.
  • crankcase type lubrication system while oil is fed to the rubbing surfaces using an electric oil pump and by means of nozzles mounted on the central shaft of the variator, as well as on the transmission case.
  • Oil supply using an electric oil pump is the most efficient scheme, which allows not only to supply a sufficient amount of lubricants regardless of the engine speed, but also to avoid dry starting at the start, which is the main cause of wear of any mechanical systems with an oil pump driven by the main shaft .
  • a continuously variable transmission operates as follows. Rotation from the engine is transmitted to the input shaft 3 of the friction variator, which transfers the force to the solar disks 1. From the solar disks, the force is transmitted to the satellites 11, which, starting from the epicycles 2, transmit the force on the axis 10 of the satellites 11. The axes 10 of the satellites 11 transmit the force to the carrier 4 by means of rockers and balancers 13. In this case, under the influence of centrifugal forces and forces from torque, the balancers 13 tend to take an equilibrium position that ensures the position of the axes 10 of the satellites 11, and the satellites 11 themselves, in which the exact ratio is optimal. The solar disks 1 and the epicyclic disks 2 are pressed by the springs 14.
  • the frictional contact is provided by viscous fluid friction forces in a fluid with a high traction coefficient used as a lubricant
  • the compressive forces are provided by the springs 14, and each spring 14 creates a compressive force of two friction drive arranged in pairs.
  • the gear ratio depends on the position of the bearings 12 of the axles 10 of the satellites 11, which, in turn, is determined by the ratio of centrifugal force and torque.
  • the axis 10 of the satellites tends to take the equilibrium position that at a given moment corresponds to the engine speed and the speed of the car, depending on the load of the car and road conditions.
  • the axles 10 of the satellites 11 are in the center of the possible range gear ratios determined by a curly groove 9 at the equilibrium point with zero centrifugal force and force from the torque.
  • gear ratios close to 1 Larger gear ratios are used mainly during acceleration, lower gear ratios are used for high-speed or very economical modes, which means rarely. Thus, the most used mode can be placed by selecting numbers gearboxes almost to the center of the gear ratio, where the pinch is minimized, which means that the efficiency is highest.
  • the range of gear variator ratios is from 4.17 to 0.81.
  • the proposed gear ratio limiter directly limits the range of gear ratios to the largest values, which does not allow the car wheel to develop a maximum speed with a poor coefficient of adhesion of the wheel to the roadway and begin to slip.
  • Torque from the output shaft 15 of the variator is transmitted to the input shaft 16 of the combined multiplier and reverse gear.
  • a gear 18 is connected to the input shaft 16, which transmits torque to the gears 19 of the intermediate shafts 20.
  • torque is transmitted to the gears 21 of the second stage of the multiplier and gears 22 of the second stage of the reverse gear.
  • the gears 21 of the second stage of the multiplier transmit torque to the output gear 23 of the multiplier, which can be connected to the synchronizer 27 the output shaft 26.
  • the gears 22 of the second stage of the reverse gear transmit torque to the spurious gears 25, providing reversal of the direction of motion and transmitting torque to the output gear 24 of the reverse gear, which may be connected via the synchronizer 27 to the output shaft 26.
  • the position of the synchronizer 27 determines whether the output shaft 26 is connected to the output gear 23 of the multiplier or to the output gear 24 of the reverse gear, or whether none of them is in position "Neutral".
  • the multiplier and reverse gear have a common first stage (16, 18, 19, 20), but different second stages.

Abstract

Le groupe d'inventions se rapporte aux constructions mécaniques et concerne une transmission à variation continue destinés aux moyens de transport dotés d'un variateur à frottement. La transmission à variation continue comprend des arbres d'entrée et de sortie (26), un variateur planétaire à frottement à disques multiples, un mécanisme d'inversion et un limitateur piloté de la gamme de rapports d'engrenage. Le variateur comprend un épicycle qui est monté sur le corps du dispositif et se présente comme un ensemble de disques (1) disposés deux par deux et se touchant par leur côté interne; un ensemble de disques solaires (2) disposés deux par deux et se touchant par leur côté externe; un porte-satellites relié à l'arbre de sortie du variateur et comprenant deux disques qui sont reliés aux disques de l'axe et comportant des satellites se présentant comme des disques intermédiaires. Les disques solaires sont disposés sur l'arbre de sortie du variateur relié à l'arbre d'entrée du mécanisme d'inversion; les disques du porte-satellites comportent des rainures profilées dont le nombre est fonction du nombre d'axes de satellites. Les axes de satellites sont reliés aux rainures profilées qui permettent d'en modifier leur position et d'assurer l'interaction avec les disques intermédiaires, les disques solaires et les disques de l'épicycle. Chacun des disques solaires et de l'épicycle a une section transversale correspondant à une forme sélectionnée parmi les formes en « Z », un coin inégal, en « T », en « I » ou en « U ». Les satellites ont une forme convexo-convexe en haricot. Le mécanisme d'inversion comprend un engrenage de réduction de hausse à canaux multiples et un engrenage de réduction générale inverse avec des arbres intermédiaires. Le limitateur piloté de la gamme de rapports d'engrenage se présente comme un élément annulaire possédant une surface interne conique qui est monté dans le corps de manière à pouvoir se déplacer axialement de façon à interagir avec des rouleaux relié à des poids.
PCT/RU2010/000330 2009-10-26 2010-06-16 Transmission à variation continue, variateur, limitateur de la gamme de rapports d'engrenage et satellite WO2011053187A1 (fr)

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RU2009139302/11A RU2399814C1 (ru) 2009-10-26 2009-10-26 Бесступенчатая трансмиссия, вариатор, ограничитель диапазона передаточных чисел и сателлит
RU2009139302 2009-10-26

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CN102562973A (zh) * 2011-06-03 2012-07-11 郭克亚 一种摩擦行星式无级变速器传动机构
CN110266176A (zh) * 2019-04-30 2019-09-20 苏州博安捷机器人科技有限公司 一种磁传动二级变速器

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RU2763619C1 (ru) * 2021-09-26 2021-12-30 Федеральное государственное бюджетное образовательное учреждение высшего образования Северо-Кавказский горно-металлургический институт (государственный технологический университет) Базовый вариатор широкодиапазонной трансмиссии

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EP0459234A1 (fr) * 1990-06-01 1991-12-04 Casarotto, Giorgio Variateur épicycloidal à disques incorporant un combinateur épicycloidal
RU1772006C (ru) * 1991-01-22 1992-10-30 Горьковский Автомобильный Завод Бесступенчата трансмисси
RU2300032C1 (ru) * 2006-02-15 2007-05-27 Константин Владимирович Лебедьков Бесступенчатая трансмиссия, механизм реверсирования, модуль варьирования и управляемый ограничитель диапазона передаточных чисел

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US2841019A (en) * 1953-12-18 1958-07-01 Beier Alice Infinitely variable friction disk power transmission
EP0459234A1 (fr) * 1990-06-01 1991-12-04 Casarotto, Giorgio Variateur épicycloidal à disques incorporant un combinateur épicycloidal
RU1772006C (ru) * 1991-01-22 1992-10-30 Горьковский Автомобильный Завод Бесступенчата трансмисси
RU2300032C1 (ru) * 2006-02-15 2007-05-27 Константин Владимирович Лебедьков Бесступенчатая трансмиссия, механизм реверсирования, модуль варьирования и управляемый ограничитель диапазона передаточных чисел

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102562973A (zh) * 2011-06-03 2012-07-11 郭克亚 一种摩擦行星式无级变速器传动机构
CN102562973B (zh) * 2011-06-03 2014-04-16 郭克亚 一种摩擦行星式无级变速器传动机构
CN110266176A (zh) * 2019-04-30 2019-09-20 苏州博安捷机器人科技有限公司 一种磁传动二级变速器

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