PLAIN SELF-CENTERING BEARING

Abstract

The present disclosure relates to a mechanical assembly of two mechanical parts rotatable relative to each other and enabling a self-centering fluid bearing to be obtained; it comprises a first part provided with a cylindrical cavity, a second part (34) having at least one cylindrical portion engaged in the cylindrical cavity of the first part, a gap separating the cylindrical portion and the wall of the cylindrical cavity so as to allow relative movement in rotation between the first part and the second part (34), and a lubricant distribution network (37, 38) configured for feeding said gap with a fluid lubricant so as to form a fluid bearing; a first surface (34s) selected from the inside surface of the cylindrical cavity of the first part and the outside surface of the cylindrical portion of the second part is provided with at least two lubricant admission orifices (39a, 39b) that are spaced apart from each other by not less than 120° about the main axis (F) of the first surface (34s), and the first surface (34s) also presents at least one circumferential groove (40a) extending circumferentially from the vicinity of a first lubricant admission orifice (39a) over at least 100° and in the direction of rotation of the second of said surfaces relative to the first surface (34s).

Claims

1. A mechanical assembly comprising a first part provided with a cylindrical cavity; a second part having at least one cylindrical portion engaged in the cylindrical cavity of the first part, a gap separating the cylindrical portion and the wall of the cylindrical cavity so as to allow relative movement in rotation between the first and second parts; and a lubricant distribution network configured for feeding said gap with a fluid lubricant so as to form a fluid bearing; wherein a first surface selected from the inside surface of the cylindrical cavity of the first part and the outside surface of the cylindrical portion of the second part is provided with at least first and second lubricant admission orifices that are spaced apart from each other by not less than 120° about a main axis of the first surface; and wherein the first surface also presents at least one first circumferential groove extending circumferentially from the vicinity of the first lubricant admission orifice over at least 100° and in the direction of relative rotation of the second of said surfaces relative to the first surface, the upstream end of the circumferential groove being disjoint from the first lubricant admission orifice in such a manner that said first lubricant admission orifice does not open out into the bottom of said circumferential groove, and a second circumferential groove extending circumferentially in the direction of relative rotation of the second of said surfaces relative to the first surface, from the vicinity of the second lubricant admission orifice over at least 100°.

2. An assembly according to claim 1, wherein the first part is a gear and the second part is a hub, said gear rotating about said hub.

3. An assembly according to claim 1, wherein the first surface is the outside surface of the cylindrical portion of the second part and the second surface is the inside surface of the cylindrical cavity of the first part.

4. An assembly according to claim 3, wherein the cylindrical portion of the second part includes a lubricant reception chamber configured to receive lubricant from a lubricant source and in fluid flow connection with the lubricant admission orifices.

5. An assembly according to claim 1, wherein the first surface includes in a first transverse plane first and second lubricant admission orifices that are diametrically opposite.

6. An assembly according to claim 1, wherein the upstream end of the circumferential groove is distant from of the first lubricant admission orifice by less than 10°.

7. An assembly according to claim 1, wherein a circumferential groove extends circumferentially from the vicinity of each lubricant admission orifice over at least 160° in the direction of relative rotation of the second of said surfaces relative to the first surface.

8. An assembly according to claim 1, wherein the angular distance between the downstream end of the circumferential groove and a second lubricant admission orifice lies in the range 5° to 20°.

9. An assembly according to claim 1, wherein the first surface also presents at least one longitudinal groove extending longitudinally from the downstream end of a circumferential groove.

10. A transmission member of an epicyclic gear train type including the mechanical assembly according to claim 1, wherein the first part of the mechanical assembly is an epicyclic gear train planet gear and the second part is a spindle of an epicyclic gear train planet carrier.

11. A turbine engine including a transmission member according to claim 10.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0042] The accompanying drawings are diagrammatic and seek above all to illustrate the principles of the invention.

[0043] In these drawings, from one figure to another, elements (or portions of an element) that are identical are identified by the same reference signs. In addition, elements (or portions of an element) that belong to different embodiments but that have analogous functions are identified in the figures by numerical references increased by 100, 200, etc.

[0044] FIG. 1 is an axial section view of an example of a turbine engine with reduction gearing.

[0045] FIG. 2 is a theoretical diagram of the transmission member.

[0046] FIG. 3 is a perspective view of a spindle.

[0047] FIG. 4A is a section view on plane IVA of FIG. 3.

[0048] FIG. 4B is a section view on plane IVB of FIG. 3.

[0049] FIGS. 5A and 5B show lubricant feed in the planes IVA and IVB respectively while the spindle is centered.

[0050] FIGS. 6A and 6B show lubricant feed in the planes IVA and IVB while the spindle is off-center.

[0051] FIG. 7 is a section view showing a second embodiment.

[0052] FIGS. 8A and 8B are section views in two different planes showing a third embodiment.

DETAILED DESCRIPTION

[0053] In order to make the invention more concrete, an example transmission member is described in detail below with reference to the accompanying drawings. It should be recalled that the invention is not limited to this example.

[0054] FIG. 1 shows a bypass turbojet with reduction gearing as described in the introduction and including a transmission member 3 of the invention.

[0055] This transmission member 3 comprises an epicyclic gear train 30 analogous to that described in the introduction with reference to FIG. 2.

[0056] It should be observed in particular that in this example the ring 31 is secured to the casing 60 via flexible shrouds 61, the planet carrier 35 is coupled to the fan shaft 2a to drive the fan 2 via a connection that is stiff, and the sun gear 32 is coupled flexibly to a fluted end 10a of the low pressure shaft 10.

[0057] In this example of the invention, and as can be seen more clearly in FIGS. 3, 4A, and 4B, each of the spindles 34 of the planet gears 33 has an oil reception chamber 37 in fluid-flow connection with the gap 36 forming the smooth bearing via channels 38 that pass through the spindle 34 and open out via injection orifices 39a-39d referred to as oil admission orifices.

[0058] The spindle 34 has first and second oil admission orifices 39a and 39b situated diametrically opposite in a first radial plane IVA extending close to a first end of the spindle 34; it also has third and fourth oil admission orifices 39c and 39d situated diametrically opposite in a second radial plane IVB extending in the proximity of the second end of the spindle 34. The third and fourth orifices 39c and 39d are arranged so as to be offset by 90° relative to the first and second orifices 39a and 39b, i.e. the straight line connecting together the third and fourth orifices 39c and 39d is orthogonal to the straight line connecting together the first and second orifices 39a and 39b. The orifices 39a-39d are thus provided respectively at 0°, 90°, 180°, and 270° around the axis F of the spindle 34.

[0059] Each orifice 39a-39d opens out in the surface of the spindle 34. Circumferential grooves 40a-40d are also provided in the surface of the spindle 34. Each circumferential groove 40a-40d extends from the immediate vicinity of an oil admission orifice 39a-39d in the same radial plane as that orifice: more precisely, the upstream end of a circumferential groove 40a is arranged immediately downstream from the corresponding orifice 39a, with less than 5° of difference therefrom, but nevertheless without the orifice 29a opening out directly into the groove 40a. In this reduction gearing, the gear 33 revolves clockwise about the spindle 34: the upstream end of the circumferential groove 40a is thus arranged immediately after the orifice 29a in the clockwise direction.

[0060] The circumferential groove 40a-40d associated with a given orifice 39a-39d extends to a zone situated upstream from the other orifice 39b, 39a, 39d, 39c in the same radial plane IVA or IVB: more precisely, its upstream end is arranged in the range 10° to 15° further upstream than said other orifice 39b, 39a, 39d, 39c, i.e. specifically in the range 10° to 15° traveled in the anticlockwise direction. Each circumferential groove 40a-40d thus extends over about 160°.

[0061] Furthermore, each circumferential groove 40a-40d is extended at its downstream end by a longitudinal groove: the longitudinal grooves 41a and 41b extend longitudinally from the circumferential grooves 40a and 40b towards the plane IVB, but without reaching it; the longitudinal grooves 41c and 41d extend longitudinally from the circumferential grooves 40c and 40d towards the plane IVA, but without reaching it.

[0062] The transmission member 3 also has an oil distributor 50 for distributing lubricating oil from an oil feed 64 provided in the stator to the bearings 36 of the planet gears 33.

[0063] Such oil distributors are known: in this example, the distributor may be analogous to that described in the French patent application filed under the No. 13/58581. Under such circumstances, the distributor is not described again in detail. It suffices to know that it comprises a rotary portion that is driven to rotate together with the planet carrier 35, that recovers oil from the stator, and that transfers it to the oil reception chambers 37 of the spindles 34 via connection ducts.

[0064] The operation of the balancing system of this fluid bearing is described below with reference to FIGS. 5A, 5B, 6A, and 6B. In FIGS. 5A and 5B, the gear 33 is correctly centered around its spindle 34. As a result, no pinching zone appears in the gap 36: the distance between the surface 34s of the spindle 34 and the inside surface of the central cavity in the gear 33 is constant all around the spindle 34. Under such conditions, oil spreads equally in the channels 38 so that the oil flow rate 42a-42d as injected via the orifices 39a-39d are equal.

[0065] Oil thus escapes from each orifice 39a-39d and spreads uniformly in the circumferential grooves 40a-40d and in the longitudinal grooves 41a-41d in such a manner that the centering of the gear 33 is unaffected.

[0066] FIGS. 6A and 6B show the situation in which the gear 33 is off-center relative to the spindle 34: the gear 33 is located too far to the right relative to the spindle 34, such that a pinch zone P is present on the left of the spindle 34. Because of this pinching, the section of the passage at the outlet from the orifice 39a is reduced, thereby reducing the oil flow rate 42a escaping from this orifice 39a. Under such circumstances, since the flow rate at which oil enters into the oil reception chamber 37 is constant, the oil flow rates 42b-42d escaping from the other orifices 39b-39d increase. More particularly, the oil flow rate increases mainly through the orifice situated opposite from the pinch zone P, specifically the orifice 39b, insofar as the other two orifices 39c and 39d are also subjected to a small reduction in their through sections caused by the gear 33 being off-center. Consequently, the oil flow rate 42b from the orifice 39b increases significantly, and a larger quantity of oil is delivered by the circumferential groove 40b and the longitudinal groove 41b into the zone M situated immediately upstream from the pinch zone P. As a result, an increased quantity of oil is applied to the inside surface of the gear 33 as it passes through the upstream zone M immediately before reaching the pinch zone P, thereby reducing any risk of friction. In addition, the greater quantity of oil present in this zone makes it possible to enlarge the pinch zone P, thereby tending to recenter the gear 33 about the spindle 34.

[0067] FIG. 7 shows a variant embodiment in which the spindle 134 has three oil admission orifices 139a, 139b, and 139c in a given radial plane, instead of two. These three orifices 139a-139c are situated equally around the axis A, i.e. they are situated every 120°. In analogous manner to the above example, the spindle 134 may have three other oil admission orifices situated in a second radial plane and phase-offset by 60° relative to the orifices 139a-139c in the first radial plane.

[0068] In a manner analogous to the first example, circumferential grooves 140a-140c are provided in the surface of the spindle 34 and they extend to a zone situated upstream from the orifice in the clockwise direction. Furthermore, in analogous manner, each circumferential groove 140a-140c is extended at its downstream end by a longitudinal groove 141a-141c.

[0069] FIG. 8 shows a third embodiment in which the stationary part is a bearing surface 233 within which a shaft 234 rotates. In such an example, since the stationary part is the outer part, the lubricant distribution network is provided within this part. In spite of this difference, the lubricant distribution network is entirely analogous to that of the first example: the inside surface of the cavity of the bearing surface 233 is thus provided with two oil admission orifices 239a and 239b in a first radial plane, and two oil admission orifices 239c, 239d in a second radial plane at a phase shift of 90°; each of these orifices 239a-d is followed by a circumferential groove 240a-d and by a longitudinal groove 241a-d.

[0070] The embodiments described in the present disclosure are given by way of non-limiting illustration and a person skilled in the art can easily, in the light of this disclosure modify these embodiments or envisage others while remaining within the ambit of the invention.

[0071] Furthermore, the various characteristics of these embodiments may be used singly or they may be combined with one another. When combined, these characteristics may be combined as described above, or in other ways, the invention not being limited to the specific combinations described in the present disclosure. In particular, unless specified to the contrary, any characteristic described with reference to any one embodiment may be applied in analogous manner to any other embodiment.