WO2009051519A1 - Variateur planétaire à disques - Google Patents

Variateur planétaire à disques Download PDF

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Publication number
WO2009051519A1
WO2009051519A1 PCT/RU2008/000502 RU2008000502W WO2009051519A1 WO 2009051519 A1 WO2009051519 A1 WO 2009051519A1 RU 2008000502 W RU2008000502 W RU 2008000502W WO 2009051519 A1 WO2009051519 A1 WO 2009051519A1
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WO
WIPO (PCT)
Prior art keywords
disks
friction
variator
external
central
Prior art date
Application number
PCT/RU2008/000502
Other languages
English (en)
Russian (ru)
Inventor
Nurbei Vladimirovich Gulia
Original Assignee
Zakrytoe Aktsionernoe Obshchestvo 'kombarko'
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zakrytoe Aktsionernoe Obshchestvo 'kombarko' filed Critical Zakrytoe Aktsionernoe Obshchestvo 'kombarko'
Publication of WO2009051519A1 publication Critical patent/WO2009051519A1/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 invention relates to the field of engineering and can be used, in particular, as a motor-variator, which is widely used in various industries and technology.
  • a planetary variator comprising internal and external central friction disks, covering intermediate friction disks on the sides, a mechanism for jointly changing the gear ratio and pressure, made in the form of rotary levers carrying intermediate friction disks and mounted on a carrier (RU, JV ⁇ s 2091638).
  • the pressure parts of the mechanism for jointly changing the gear ratio and pressure are complex and, most importantly, they do not solve the problem of optimal pressing of the disks to each other due to the fact that the friction coefficient at the points of friction oil contact varies greatly. According to test data for the central internal friction discs, the value of this coefficient varies in the range of O, O15 ⁇ O, O ⁇ , and for external in the range of 0.02 ⁇ 0.08.
  • a disk planetary variator containing a housing in which a planetary gear set is installed, including central external and internal friction disks covering intermediate disks from both ends, mounted on axles with the possibility of their radial movement on the carrier, and - pressed to the intermediate disks with pressure devices, including elastic elements of axial action in contact with annular stops, and elastic elements of axial action of at least one group ntralnyh friction discs are formed integrally with the discs in the form of elastic disks with grooves on their surfaces contacting with the intermediate friction discs (RU, N ° 2,140,028).
  • the known variator has the disadvantage that when performing friction disks along with elastic elements of axial action, the form of the raceway, along which the central friction disks contact with the intermediate friction disks, is of great importance.
  • an elastic element of axial action including one made at the same time with a friction disk, bends and greatly changes the angular position of the raceway.
  • bending of the force element can lead to edge contact and damage to the friction discs.
  • the present invention is based on the task of creating a disk planetary variator, which provides reduced wear of the raceways of the friction disks and predetermined values of the pressure of the central friction disks against the intermediate disks.
  • Another difference of the claimed variator is that it has several planetary gears, and between the rows in the area of the external central friction intermediate ring stops are installed on the disks, and distance rings are installed in the area of the inner central friction disks and their elastic elements.
  • At least one end cover is installed on the housing, and between it and the nearest external central friction disk there is a sleeve with an axial movement in the housing with an annular stop on it, regulating pressure and axial the position of the base of this disk, as well as the pressure and axial position of the base of the adjacent external friction disk.
  • the difference between the embodiment of the variator with several planetary gears is that at least one end cover is installed on the housing, and between it and the external friction disk closest to this cover is placed with axial movement in the housing a sleeve with an annular stop on it, regulating pressure and axial the position of the base of this disk, as well as the pressure and axial position of the bases of other external disks connected to the said external disk through intermediate external friction disks and intermediate ring packs ry.
  • the ring stops contacting with the external central friction disks are made with several annular contact zones with these disks, and the contact zone located at a maximum distance from the variator axis contacts the disk with a minimum gear ratio of the variator, and other contact zones interact with the disk while increasing the gear ratio of the variator.
  • Another difference of the variator is that the contact zones of the ring stops with external friction disks pass one into the other smoothly, forming a convex toroidal surface on the ends of the ring stops in contact with the disks.
  • At least one longitudinal groove is made on the inner cylindrical surface of the casing, connecting the annular gap between the external and internal central friction discs through the holes in the bushings with the adjacent side cavities of the casing.
  • intermediate friction discs are mounted on rotary levers with the ability to move them.
  • the technical result of the invention is that, due to the differences of the variator noted above, the friction discs are pressed against each other optimally, there are no edge contacts during skews and wear of the friction discs contact zones with each other and ring stops is reduced. This provides high efficiency and durability of the variator.
  • FIG. 1 depicts a general structural diagram of a variator with one planetary row (longitudinal section);
  • FIG. 2 is a view A-A of FIG. 1;
  • FIG. 3 depicts a general structural diagram of a variator with two planetary gears (longitudinal section);
  • FIG. 4 the implementation of the clamp stop to the external Central friction discs;
  • FIG. 5 is the same as FIG. 4, another option
  • FIG. 6 - the implementation of the contact zones of the Central external friction discs with intermediate disks for various gear ratios of the variator; 7 is the same as FIG. 6, another option.
  • the disk planetary variator contains a leading (high-speed) central shaft 1 (Fig. 1-3), which in this case is the shaft of an electric motor, combined with the variator in one unit - the variator motor.
  • a sleeve 2 is mounted on the shaft 1 with the possibility of limited axial movement and transmission of torque (at the key), on which, using the stops 3 and the nut 4, as well as the shaped key 5, the central internal friction discs 6 are pressed, pressed against the intermediate friction discs 7 with elastic elements of axial action, made in the form of Belleville springs 8, abutting against the sides of the stops 3.
  • the disks used are mounted on the sleeve 2 with the possibility of their axial movement within the permissible axial elasticity of the springs 8.
  • the external central friction wheels 9, simultaneously playing the role of axial action of force elements - disc springs in contact with the intermediate friction discs 7 are planted in case 10 with the help of sleeves 1 1 and 12 with stops 13 on them, and between the outer Central friction discs 9 may be a closed or open ring 14, which determines the axial distance between the bases of the outer Central friction discs 9 (however, the presence of the ring 14 is possible, but not necessary )
  • the extreme (in Fig. 1) part of the sleeve 12 is in contact with the end cover 15 of the housing 10, and thus, the base of the disks 9 are sandwiched between the cover 15, the stop 13 of the sleeve 11, the stop 13 of the sleeve 12 and the body 10.
  • the cover 15 is attached to the body 10 , for example, using bolts 16 located at the ends of the cover 15 and the housing 10 around the circumference.
  • the bushings 11 and 12 are in contact with the external central friction discs 9 with their stops 13, while the annular contact zones 17 of the stop 13 with the external central friction disk 9 (Fig. 4) can be either one or several, lagging from each other, as in radial and axial position. Contact zones can also be combined into one curved toroidal zone 18 (Fig. 5).
  • the variator gear ratio changes, the intermediate friction disks 7 radially move, which causes elastic angular displacement in the longitudinal radial planes (deflection) of the outer central friction disks 9 (shown by a dashed line).
  • the choice of the parameters of the Belleville springs 8 and round plates is based on the fact that the pressing force of the external central friction disks 9 to the intermediate friction disks 7 progressively increases with an increase in the gear ratio of the variator compared to the force pressing internal friction discs 6 to them.
  • the central inner friction discs 6 are in contact with the intermediate friction discs 7 along raceways on the central inner friction discs 6, which may have both a conical and convex toroidal surface.
  • the intermediate friction discs 7 sit on the axles 20 with the possibility of some axial movement, and the axles 20 in the bearings 21 mounted on the pivoting levers 22, which in turn are rigidly fixed (for example, using pins 23) on the axis 24, or made with it at the same time (Fig. 1, 2).
  • Axis 24 is set to rotate in carrier 25, and thus the variator mechanism forms a single-friction friction gear, where the external central friction disks 9 act as the epicyclic, the internal central friction disks 6 act as the sun wheel, and the intermediate friction disks 7 on the 20-axis bearings 21 of the rotary levers 22 - satellites, and the carrier 25 - the planetary gear carrier.
  • Swing arms 22 are provided with counterweights 26 of increased or reduced weight to increase or decrease the imbalance of the swing arms 22 (Fig. 2).
  • axles 27 are pivotally fixed, connected with a mechanism for changing their radial position, for example, with rods 28 of cylinders 29, into which fluid (oil, air, etc.) is supplied under pressure through O-rings-collectors 30, a channel system in the output shaft 31 and the carrier 25 connected to it, as well as the pipe 32.
  • the rods 28 are returned to their original position when the pressure decreases, for example, a spring .33.
  • the number of cylinders 29 is equal to the number of counterweights 26, and therefore the number of pivoting levers 22.
  • FIG. Figure 3 shows a structural diagram of a variator with two planetary friction planetary gear sets, and, according to the same principle, variators with any rational number of planetary rows can be constructed, for example, up to 5.
  • the difference between a scheme with two or more planetary rows and a scheme with one row consists of only in the presence of intermediate stops 34 between adjacent external central friction discs 9 of the first and second or subsequent planetary rows, both contact zones of which are made similar to working the surfaces of the stops 13, and are combined in one stop 34 and are made on its two end surfaces.
  • the elastic elements - Belleville springs 8 of the first and subsequent planetary rows are here separated by distance rings 14.
  • the variator is a lubricant, preferably a special variator, increasing the coefficient of friction between the friction discs.
  • Devices for filling, monitoring and draining oil are not shown in the drawing.
  • the ring 14 and the bushings 11 and 12 can be made with radial holes, and longitudinal grooves 35 are made in the housing 10 on its inner cylindrical surface, passing under the sleeve 12, the ring 14 and the disks 9.
  • the disk planetary variator operates (Fig. 1, 2) as follows.
  • the operation of the device begins with a minimum gear ratio, which is usually about 1.3, that is, the rotational speed of the shaft 31 is this number of times less than the rotational speed of the driving central shaft 1, in this case the motor shaft, combined with the variator in one unit - the variator motor .
  • the torque from the driving central shaft 1 through a key, or other connection for transmitting torque is transmitted to the sleeve 2, which is mounted on the driving central shaft 1 with limited axial movement, and from the sleeve 2 to the stops 3 and central internal friction discs 6 connected by a key 5 with a sleeve 2 with the possibility of axial movement on it during operation of the device within the elasticity of Belleville springs 8.
  • the central internal friction discs 6 are pressed against the intermediate friction discs 7 on both sides by cup springs 8, which abut their bases in the sides on the stops 3, pressed against each other by the nut 4 on the sleeve 2, and during rotation, they transmit torque to the intermediate friction discs 7, mounted on the axis 20, mounted with axial movement in bearings 21, mounted on the pivoting levers 22, in turn, mounted on an axis 24, mounted rotatably on the carrier 25.
  • the fluid is supplied to the cylinders 29 through the pipe 32, the manifolds 30 and the channel system in the output shaft 31.
  • the central internal friction discs 6 move axially along the sleeve 2 with the transmission of torque.
  • the intermediate friction disks 7 are also in frictional contact with the external central friction disks 9, which at the same time play the role of external friction disks and axial force elements — disk springs.
  • External central friction discs 9 are sandwiched between the stops 13 of the bushings 11 and 12, and, if present, through the ring 14, and transmit torque (reactive) to the housing 10 due to friction.
  • the outer central friction discs 9 Due to the fact that the axial size of the ring 14 is less than the axial distance between the bases of the outer central friction discs 9, freely touching the intermediate friction discs 7 at their periphery, where their thickness is minimal, and even more so in the absence of ring 14, the outer central friction discs 9 are always pressed against intermediate friction discs 7 through the elastic deformation of the first, and thus transmit a force that generates friction torque.
  • the clamp of the outer central friction discs 9 to the intermediate friction discs 7 increases as the intermediate friction discs 7 are tapered between the outer central friction discs 9 with an increase in the elastic deformation of the latter, like disc springs.
  • the raceway 19 of the toroidal shape on the external Central friction discs 9 in the process of deformation comes into contact with intermediate friction discs 7 (6, 7, contact zones circled) all in new places, making the wear of the raceways more uniform.
  • the external central friction discs 9 are fixed on the housing 10 in a certain axial position in the carrier 25, which is fixed rigidly in the axial direction in the housing 10, in a state where the pressure of the external central friction discs 9 to the intermediate friction disks 7 is almost the same on both sides, and the intermediate friction discs 7 are not subject to bending.
  • the intermediate friction discs 7 set the central inner friction discs 6 pressed to them in the same position, moving axially the central inner friction discs b together with cup springs 8, stops 3 and the sleeve 2 along the drive central shaft 1 and in the carrier 25. Since the clamping of the external central friction discs 9 to the intermediate friction discs 7 to optimize the pressure should progressively increase with increasing gear ratio, the axial stiffness of the outer central GOVERNMENTAL friction discs 9 should also increase, which is achieved by performing the step of stops 13 (FIG. 4) or toroidal (Fig. 5) forms.
  • the stops 13 when sliding the intermediate friction discs 7 between the discs are moved apart in the raceway zone, bend and touch the stops 13 all in new zones, approaching the periphery of the outer central friction discs 9, which progressively increases their rigidity and pressure force to the intermediate friction discs 7.
  • This clamp is much less than the maximum clamp of the external central friction discs 9 to the intermediate friction discs 7 and is significantly less dangerous from the point of view of wear of the raceways.
  • Lubrication of the contact zones of the central internal friction discs 6 and the external central friction discs 9 with the intermediate friction discs 7 is carried out by the penetration of oil through the holes in the bushings 11 and 12, if any, as well as the groove 36, into the annular gap between the external central friction discs 9 and spraying its intermediate friction discs 7 during rotation drove 25.
  • the most successfully declared planetary disk variator is industrially applicable in various industries and equipment, mainly as a motor variator.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

Le dispositif de l'invention comprend un boîtier (10) dans lequel on a monté une rangée planétaire comprenant des disques de friction internes et externes (9) et (6) qui entourent des deux extrémités des disques de friction intermédiaires (7) montés à demeure sur des axes (20) de manière à pouvoir se déplacer sur un coulisseau (25). Ces disques (6) et (9) sont comprimés contre les disques de friction intermédiaires (7) par des dispositifs de compression (8). Les pistes de roulement sur les disques de friction centraux (6) et (9), en contact avec la surface des disques de friction intermédiaires (7), sont toroïdaux et convexes, et la zone de contact des éléments souples (8) à action axiale avec des butées annulaires (3) est disposée dans leur partie annulaire périphérique. Les butées annulaires (3) ont la possibilité de se déplacer dans le sens axial à l'intérieur du corps (10).
PCT/RU2008/000502 2007-10-19 2008-08-01 Variateur planétaire à disques WO2009051519A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
RU2007138710 2007-10-19
RU2007138710/11A RU2350805C1 (ru) 2007-10-19 2007-10-19 Дисковый планетарный вариатор

Publications (1)

Publication Number Publication Date
WO2009051519A1 true WO2009051519A1 (fr) 2009-04-23

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Application Number Title Priority Date Filing Date
PCT/RU2008/000502 WO2009051519A1 (fr) 2007-10-19 2008-08-01 Variateur planétaire à disques

Country Status (2)

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RU (1) RU2350805C1 (fr)
WO (1) WO2009051519A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB393170A (en) * 1932-10-24 1933-06-01 Giuseppe Colucci Variable speed gearing
RU2140028C1 (ru) * 1998-05-26 1999-10-20 Гулиа Нурбей Владимирович Многодисковый планетарный вариатор
WO2000070241A1 (fr) * 1999-05-14 2000-11-23 Ferenc, Martin Transmission a variation continue et variantes

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB393170A (en) * 1932-10-24 1933-06-01 Giuseppe Colucci Variable speed gearing
RU2140028C1 (ru) * 1998-05-26 1999-10-20 Гулиа Нурбей Владимирович Многодисковый планетарный вариатор
WO2000070241A1 (fr) * 1999-05-14 2000-11-23 Ferenc, Martin Transmission a variation continue et variantes

Also Published As

Publication number Publication date
RU2350805C1 (ru) 2009-03-27

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