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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
  • F16C25/06—Ball or roller bearings
  • F16C25/08—Ball or roller bearings self-adjusting
  • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
  • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
  • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
  • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
  • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
  • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/30—Parts of ball or roller bearings
  • F16C33/58—Raceways; Race rings
  • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
  • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
  • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
  • F16C35/063—Fixing them on the shaft
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
  • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
  • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
  • F16C35/067—Fixing them in a housing
• • 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
  • F16H1/00—Toothed gearings for conveying rotary motion
  • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
  • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
  • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
  • F16H1/14—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising conical gears only
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2380/00—Electrical apparatus
  • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
• • 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
  • F16H57/00—General details of gearing
  • F16H57/02—Gearboxes; Mounting gearing therein
  • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
  • F16H57/022—Adjustment of gear shafts or bearings
  • F16H2057/0221—Axial adjustment

Definitions

• the present invention relates to speed reducers or multipliers.
• the present invention relates to the pre-loading of bearings for gearbox or speed multiplier as well as the mounting of the speed reducer or multiplier.
• reducer will be used later to designate both a reducer and a speed multiplier.
• Figure 1 partially and schematically illustrates a gearbox of the prior art provided with a shaft 1, a spiral gear 2, two bearings 3 to 4 conical rollers arranged in a mounting said "O".
• the bearings 3 comprise a radially inner ring 5 and a radially outer ring 6.
• Two circlips 7 and 8 make it possible to immobilize the bearings axially.
• an interface formed of a wedging system 9 comprising shims is installed between the bearings 3.
• the implementation of a pre-load in the bearings is carried out by arranging an interface formed by a lock nut 12 between the bearings 3 and varying the tightening of it.
• the invention thus aims to solve all or part of the problems posed by the prior art.
• the invention aims to reduce the assembly time, avoid a loss of pre-load bearings throughout the life of the machine and find a solution that can be used for different machines.
• a speed reducer comprising a shaft extending along a longitudinal axis, two bearings arranged around the shaft, the two bearings each comprising a radially outer ring, a radially inner ring and rolling elements arranged between the radially outer and inner rings, the gearbox comprising a pre-load system positioned in the gap between the two bearings, this pre-load system comprising:
• At least one elastically deformable element interposed between the two spacer elements, configured to be able to occupy a first prestressed state and a second at least partially relaxed state
• the pre-load system being arranged in such a way that the transition from the first state to the second state of the at least one elastically deformable element results in a unidirectional rotation displacement of each spacer element relative to the other, and by effect of wedge generates a pre-load in the bearings.
• support is meant as much a contact as a support with or without interposition of a ring-type element or other element inserted.
• each spacer element can be supported only with the radially outer ring of the associated bearing. As a variant, each spacer element can only bear against the radially inner ring of the associated bearing.
• Each spacer element advantageously has an outer bearing surface against one of the bearings and an inner face, opposite to the outer face, in contact with the at least one elastically deformable element, the inner face having at least one housing for said elastically deformable element such that it exerts, during the transition from the first state to the second state, a substantially tangential force on the inner face.
• the inner face has at least one relief, being for example at least partially helical, of substantially complementary shape to the inner face of the other spacer element except the housing of said at least one elastically deformable element.
• the relief, such as the helical shape, of the inner face of each spacer element makes it possible to create an axial force by a wedge effect during the transition from the first state to the second state of said at least one elastically deformable element.
• Such a shape makes it possible to cause axial displacement of the spacer elements away from each other during the passage from the first to the second state, in order to generate axial prestress in the bearings.
• each spacer element may be notched or not.
• the inner face of each spacer element may have a coefficient of friction of between 0.05 and 0.6, preferably between 0.1 and 0.5, better still between 0.1 and 0.3.
• the coefficient of friction is preferably the strongest possible.
• the challenge for the spacer is to have a helicoid angle sufficient to allow sufficient axial travel necessary for mounting and play catch and, paradoxically, small enough to withstand external axial forces without moving and minimize the stiffness of elastic elements.
• the two spacer elements are identical.
• Said at least one elastically deformable element is for example a spring, selected from the group consisting of the compression springs, the tension springs and the torsion springs, preferably a compression spring.
• said the least a resiliently deformable element is a compression spring
• the transition from the first state to the second state consists of at least partial spring expansion, the first state being a compressed state.
• the number of elastically deformable elements may be greater than one, preferably between two and eight, more preferably equal to four, the elements preferably being distributed regularly around the axis of rotation between the spacer elements. .
• the gearbox advantageously comprises a transmission
• the transmission may comprise a gear, preferably spiroconic, the shaft advantageously carrying a bevel gear.
• the gear can be of any other type.
• the bearings can be tapered rollers or any other type of bearings.
• the two bearings may consist of tapered roller bearings according to a so-called "X" mounting, respectively a so-called “O” mounting, the radially inner and outer rings then having an increasing thickness, respectively decreasing axially.
• X tapered roller bearing
• O so-called "O” mounting
• each spacer element bears only with the radially outer ring of the associated bearing.
• the mounting of the bearings is an X-mount
• each spacer element bears only against the radially inner ring of the associated bearing.
• the gearbox advantageously comprises at least one axial locking element disposed against each bearing so as to prevent any axial displacement of said bearing away from the other bearing, each axial locking element may comprise at least one shoulder formed on the shaft, a notched nut and / or circlip or other.
• the invention also relates to a method of mounting a gear as defined above, comprising the following steps:
• FIGS. 1 and 2 previously described, are schematic and partial sections of gearbox according to the prior art
• FIG. 3 is a diagrammatic and partial sectional view of an exemplary reducer according to the invention.
• FIG. 4 is an exploded perspective schematic view of the reducer of FIG. 3;
• FIG. 5 represents, in isolation, a spacer element
• FIG. 6 partially represents the reducer of FIG. 3 during its assembly
• FIG. 3 illustrates a speed reducer 10 according to the invention comprising a shaft 11 extending along a longitudinal axis X.
• the shaft carries a conical pinion 13 at one end and a gear wheel. cylindrical 15 at another end, in a manner known per se.
• the gearbox 10 further comprises bearings 16 and 17 disposed around the shaft 11.
• Each bearing 16 or 17 comprises a radially inner ring 18 and a radially outer ring 19 as well as rollers 20 of conical type in the illustrated example.
• the mounting of the bearings is "X" but it could be other without departing from the scope of the invention.
• the gearbox 10 comprises axial locking elements 25 disposed against each bearing 16 and 17 so as to block any axial displacement of a bearing away from the other bearing.
• the axial locking element 25 comprises in this example a circlip, but it could be otherwise without departing from the scope of the invention.
• the axial locking element 25 could consist of a nut present on the shaft.
• a flat washer 26 and a screw 27 are provided, as shown in FIG. 3.
• a notch washer 51 and a locknut 52 are provided as visible in Figure 3, but this device can easily be replaced by a shim and a circlip.
• the gearbox 10 comprises two spacer elements 40, in this example identical, arranged substantially symmetrically with respect to each other, each spacer element 40 being in abutment against one of the rings of the bearing which is adjacent to it. Between the spacer elements 40 are interposed elastically deformable elements 41, four in number in the illustrated example. Each spacer element 40 bears, in this example in contact, only with the outer ring 19.
• each spacer element 40 has an axially outer or an outer face 45 and, on the opposite side, an axially inner or an inner face 46, opposite the inner face 46 of the Another spacer element 40.
• the outer face 45 bears on the bearing 16 or 17 closest and substantially smooth in the example shown.
• the inner face 46 of each spacer element 40 has at least one relief 49, in particular of helical shape with a housing 50 provided for each elastically deformable element 41.
• the elastically deformable elements 41 are able to occupy a first constrained state.
• the first state corresponds to a compressed state of the spring.
• the elastically deformable element 41 is able to occupy also a second state, at least partially relaxed.
• the elastically deformable element 41 due to the shape of the inner face 46 of each spacer element, exerts a tangential force, which creates a unidirectional displacement in rotation of each element d spacer 40 relative to each other. This rotation generates a wedge effect axial displacement of the spacer elements 40 away from each other and thus a pre-load in the bearings 16 and 17, exerting a stress on the ring with which each element d spacer 40 comes to rest.
• the preload can be generated by means of eccentric provided between the two spacer elements 40, provided with torsion springs in order to make up the games generated by wear.
• the number and type of elastically deformable elements 41 may be different without departing from the scope of the invention.
• the elastically deformable member 41 may consist of a torsion spring or a tension spring.
• each spacer element 40 may be notched.
• the two spacer elements 40 may be identical or different.
• the inner shape 46 of the spacer members 40 may be different from a helical ramp.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Support Of The Bearing (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=54848785

Family Applications (1)

Country Status (5)

Families Citing this family (2)

Family Cites Families (19)

• 2015
  • 2015-10-20 FR FR1559987A patent/FR3042562B1/fr active Active
• 2016
  • 2016-10-18 US US15/768,906 patent/US10371201B2/en active Active
  • 2016-10-18 EP EP16782240.2A patent/EP3365572A1/de not_active Withdrawn
  • 2016-10-18 WO PCT/EP2016/074934 patent/WO2017067905A1/fr unknown
  • 2016-10-18 CN CN201680060957.2A patent/CN108138842A/zh active Pending

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