EP3365572A1

EP3365572A1 - Speed reducer and method of assembling such a reducer

Info

Publication number: EP3365572A1
Application number: EP16782240.2A
Authority: EP
Inventors: Pascal PONT
Original assignee: Moteurs Leroy Somer SA
Current assignee: Moteurs Leroy Somer SA
Priority date: 2015-10-20
Filing date: 2016-10-18
Publication date: 2018-08-29
Also published as: FR3042562A1; CN108138842A; US10371201B2; WO2017067905A1; US20190078614A1; FR3042562B1

Abstract

The present invention relates to a speed reducer comprising a shaft (11) extending along a longitudinal axis, two rolling bearings (16, 17) arranged around the shaft (11), the two rolling bearings (16, 17) each comprising a radially outer ring (19), a radially inner ring (18) and rolling elements (20) arranged between the radially outer and inner rings (19, 18), characterized in that it comprises a preload system positioned in the space between the two rolling bearings (16, 17), this preload system comprising: - two spacer elements (40) each one resting against one of the rings (18; 19) of the rolling bearings (16, 17), - at least one elastically deformable element (41) interposed between the two spacing elements (40), and configured to be able to occupy a preloaded first state and an least partially relaxed second state, the preload system being arranged in such a way that the transition of the said at least one elastically deformable element (41) from the first state to the second state causes a unidirectional rotational movement of each spacer element (40) with respect to the other so as to use a wedge effect to generate preload in the rolling bearings (16, 17).

Description

SPEED REDUCER AND METHOD FOR MOUNTING A TEL

GEAR

The present invention relates to speed reducers or multipliers. In particular, 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.

The term "reducer" will be used later to designate both a reducer and a speed multiplier.

It is sometimes necessary, in a reducer, to have pre-loaded bearings. The pre-load must then be homogeneous and constant throughout the life of the machine.

Among the pre-load bearing techniques, it is known, when mounting a gearbox, to impose a stalling value in order to pre-load the bearings. For example, 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. To preload the bearings 3, an interface formed of a wedging system 9 comprising shims is installed between the bearings 3.

In the example of the prior art illustrated in FIG. 2, 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.

Thus, according to these two known embodiments, it is necessary to mount, in one of the rings of the bearings, a preload or preload by wedging.

These solutions create several problems.

First, a specific interface for each reducer torque is required. In a complete range, it is thus necessary to have interface parts between the motors and gearboxes. Thus, the number of references is relatively important for a complete range of motors and gearboxes. In addition, the implementation of the interface requires measuring zero clearance parts, calculate the calibration to be performed and statistically determine the values to obtain a single calibration. Thus, editing is based on statistics, without providing certainty. In addition, the adjustment is machine by machine. It is indeed necessary to make a calibration case by case, for each machine produced, which generates a waste of time during assembly. Finally, as and when the use of the machine, the preload initially planned tends to decrease with the wear of the various parts.

The invention thus aims to solve all or part of the problems posed by the prior art. In particular, 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.

It achieves this through 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:

two spacer elements respectively in abutment with one of the bearing rings,

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.

By "support" is meant as much a contact as a support with or without interposition of a ring-type element or other element inserted.

Thanks to the invention, there is an automatic preload linked to at least partial expansion of said at least one elastically deformable element. The assembly time is thus reduced. When the mechanical parts come to wear, the action of the elastically deformable element (s) tends to maintain the precharge defined at the assembly of the machines. The noise generated by the appearance of a game in the bearing is reduced and the loss of preload is reduced or absent. 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.

Advantageously, 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.

The inner face of 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.

In a particular embodiment, 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. When 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. When the bearings are in an O - configuration, each spacer element bears only with the radially outer ring of the associated bearing. When 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:

installing the pre-load system according to the invention and the bearings around the shaft so as to put said at least one elastically deformable element in the first constrained state,

axially locking the assembly of the bearings and of the precharging system, by means of axial locking elements, so as to pass said at least one elastically deformable element in the second state at least partially expanded, to generate a pre-load in the bearings.

The invention may be better understood on reading the following detailed description of a non-limiting embodiment of the invention and with reference to the appended drawing, in which:

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, and

- Figure 7 represents in isolation the pre-charge system.

FIG. 3 illustrates a speed reducer 10 according to the invention comprising a shaft 11 extending along a longitudinal axis X. In the example illustrated, 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. In the example of Figure 3, 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. In particular, the axial locking element 25 could consist of a nut present on the shaft.

To maintain the cylindrical gearwheel 15, a flat washer 26 and a screw 27 are provided, as shown in FIG. 3. To maintain the ring radially Inside the bearing 17, 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. In the illustrated example, close to the axial locking elements 25, there are provided support blocks 29 and adjustment wedges 30, as can be seen in particular in FIG. 4.

In the space between the bearings 16 and 17, 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.

As can be seen more clearly in FIGS. 5 to 7, 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. In the case of an elastically deformable element 41 constituted by a compression spring, as illustrated, 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. During the transition from the first state to the second state, 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 invention is of course not limited to the example just described. In particular, one or more intermediate piece (s) may be interposed (s) between the two spacer elements 40 without departing from the scope of the invention.

Similarly, 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. For example, the elastically deformable member 41 may consist of a torsion spring or a tension spring.

The inner face 46 of 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.

Claims

1. Speed reducer (10) comprising a shaft (11) extending along a longitudinal axis (X), two bearings (16, 17) arranged around the shaft (11), the two bearings (16, 17). each comprising a radially outer ring (19), a radially inner ring (18) and rolling elements (20) arranged between the radially outer and inner rings (19, 18), characterized in that it comprises a system of pre-charge positioned in the gap between the two bearings (16, 17), said pre-load system comprising:

two spacer elements (40) bearing each with one of the rings

(18; 19) bearings (16, 17),

at least one elastically deformable element (41) interposed between the two spacer elements (40), configured to be able to occupy a first prestressed state and a second at least partially relaxed state,

the pre-charge system being arranged such that the transition from the first state to the second state of said at least one elastically deformable element (41) causes a unidirectional displacement in rotation of each spacer element (40) relative to the other, so as to generate a wedge pre-charge in the bearings (16, 17).

2. Gearbox according to claim 1, each spacer element (40) being supported only with the radially outer ring (19) of the associated bearing.

3. Gear unit according to claim 1, each spacer element (40) being only bearing against the radially inner ring (18) of the associated bearing.

4. Gear unit according to any one of the preceding claims, each spacer element (40) having an outer face (45) bearing against one of the bearings and an inner face (46), opposite to the outer face, in contact with said at least one elastically deformable element (41), the inner face (46) having at least one housing (50) for said elastically deformable element (41) as it exerts, during the transition from the first state to the second state, a tangential force on the inner face (46).

5. Reducer according to claim 4, the inner face (46) being at least partially helical, substantially complementary shape to that of the other element spacer (40) except the housing (50) of said at least one resiliently deformable member (41).

6. Gear unit according to claim 4 or 5, the inner face (46) of each spacer element (40) forming a smooth or toothed surface.

7. Gear unit according to any one of claims 4 to 6, characterized in that at least the inner face (46) of each spacer element (40) is made of a material such as steel and presents a coefficient of friction of between 0.05 and 0.6, preferably between 0.1 and 0.3.

8. Gear unit according to any one of the preceding claims, the two spacer elements (40) being identical.

9. Gear unit according to any one of the preceding claims, said at least one elastically deformable element (41) being a spring selected from the group consisting of compression springs, tension springs and torsion springs.

10. Gearbox according to claim 9, said at least one elastically deformable element (41) being a compression spring.

11. Reducer according to any one of the preceding claims, the number of elastically deformable elements (41) being greater than one, preferably between two and eight, more preferably equal to four, distributed, in particular regularly, between the spacer elements (40).

12. Gear unit according to any one of the preceding claims, comprising a transmission, the transmission comprising a gear.

13. Gear unit according to claim 12, the gear being spiroconic, the shaft carrying a bevel gear.

14. Gear unit according to any one of the preceding claims, the two bearings (16, 17) consisting of tapered bearings in a so-called X-shaped arrangement, respectively a so-called O-fitting, the radially inner and outer rings having an increasing thickness, respectively decreasing axially.

15. Gear unit according to any one of the preceding claims, comprising at least one axial locking element (25) disposed against each bearing so as to prevent axial displacement of said bearing away from the other bearing, each axial locking element ( 25) having at least one shoulder formed on the shaft, a notched nut and / or a circlip or other type of axial locking element.

16. A method of mounting a gear unit according to any one of claims 1 to 15, comprising the following steps:

mounting the pre-load system and the bearings (16, 17) around the shaft (11) so as to put said at least one elastically deformable element (41) in the first constrained state,

axially locking the assembly of the bearings (16, 17) and the precharge system, using axial locking elements (25), so as to pass said at least one elastically deformable element (41) in the second state at least partially relaxed, to generate a pre-load in the bearings (16, 17).