Member For Guiding A Mobile Element In Oscillation Or Rotation

Abstract

A member for guiding an element mobile in oscillation or rotation is presented. The member has a body made of a hardened metallic material, provided with a bore for assembling the mobile element, having cavities that are distributed discontinuously in the bore and capable of acting as grease reserves, and having optional grease supply. In the bore are defined a bearing surface outside of the cavities and the grease supply, and a non-bearing surface in the cavities and the grease supply. The bore includes at least one zone with: cavities having a depth of between 2 and 5 mm, and a quantity of grease in the cavities per bearing surface of between 0.05 and 0.3 g/cm.sup.2. A mechanical system having such a member and a method for manufacturing such a member is also contemplated.

Claims

1. A member for guiding an element mobile in oscillation or rotation, comprising a body made of a hardened metallic material, provided with a bore for assembling the mobile element, comprising cavities that are distributed discontinuously in the bore and capable of acting as grease reserves, and comprising an optional greaee supply, in the bore being defined a bearing surface outside of the cavities and the grease supply, and a non-bearing surface in the cavities and the grease supply, characterised in that the bore comprises at least one zone with cavities having a depth of between 2 and 5 mm, and a grease quantity in the cavities per bearing surface of between 0.05 and 0.3 g/cm.sup.2.

2. The guiding member according to claim 1, characterised in that the quantity of grease in the cavities per bearing surface is of between 0.05 and 0.2 g/cm.sup.2.

3. The guiding member according to claim 1, characterised in that the depth of the cavities in the zone is of between 3 and 5 mm.

4. The guiding member according to claim 1, characterised in that the bore comprises a surface coating.

5. the guiding member according to claim 1, characterised in that the bore has a superficial layer treated against seizing over a diffusion depth of less than or equal to 0.6 mm, the superficial layer having a hardness greater than or equal to 500 Hv1 over a depth of between 5 and 50 μm.

6. The guiding member according to claim 1, characterised in that the metallic material of the body has a yield strength Re of between 200 and 600 MPa.

7. The guiding member according to claim 1, characterised in that the zone covers the whole bore, 360 degrees around the longitudinal axis of the body.

8. The guiding member according to claim 1, characterised in that the zone extends in the bore over an angular sector of at least 120 degrees around the longitudinal axis of the body.

9. The guiding member according to claim 1, characterised in that two zones extend in the bore, each over an angular sector of at least 120 degrees around the longitudinal axis of the body.

10. A mechanical system, comprising a guiding member according to claim 1, and an element mobile in oscillation or rotation in the bore of this guiding member.

11. A method for manufacturing a member for guiding an element mobile in oscillation or rotation, characterised in that the method comprises the following successive steps: a) manufacturing a body made of a metallic material, provided with a bore for assembling the mobile element, comprising cavities that are distributed discontinuously in the bore and capable of acting as a grease reserve, and comprising optional grease supply; in the bore being defined a bearing surface outside of the cavities and the grease supply, and a non-bearing surface in the cavities and the grease supply; the bore comprising at least one zone with cavities having a depth of between 2 and 5 mm; b) performing a hardening treatment on the bore, at least in said zone; c) applying grease in the bore, at least in said zone, with a quantity of grease in the cavities per bearing surface of between 0.05 and 0.3 g/cm.sup.2 in said zone.

12. The manufacturing method according to claim 11, characterised in that in the step of applying the grease in the bore, the quantity of grease in the cavities per bearing surface is of between 0.05 and 0.2 g/cm.sup.2.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0061] The invention will be better understood upon reading the following description which is given only by way of non-limiting example and made with reference to the appended drawings, wherein:

[0062] FIG. 1 is an axial cross-section of a mechanical system according to the invention, comprising a ring and a shaft housed in the ring.

[0063] FIG. 2 is a larger scale view of detail II in FIG. 1.

[0064] FIG. 3 is a radial cross-section of the ring along the line III-III in FIG. 1.

[0065] FIG. 4 is a cross-section similar to FIG. 1, showing a ring variant according to the invention, without grease supply means.

[0066] FIG. 5 is a view similar to FIG. 2, showing a cavity variant.

[0067] FIG. 6 is a view similar to FIG. 2, showing another cavity variant.

[0068] FIG. 7 is a view similar to FIG. 3, showing a bore variant.

[0069] FIG. 8 is a view similar to FIG. 3, showing another bore variant.

[0070] FIG. 9 is a view similar to FIG. 3, showing another bore variant.

DETAILED DESCRIPTION OF THE INVENTION

[0071] FIGS. 1 to 3 show a mechanical system according to the invention, comprising a guiding ring (1) also according to the invention, and a shaft (2) mobile in oscillation or rotation in the ring (1).

[0072] The ring (1) comprises a tubular body (10) centred on a longitudinal axis (X10). The body (10) has an outer cylindrical surface (11) and an inner cylindrical surface forming a bore (12) for receiving the shaft (2). The body (10) is made of a metallic material receiving a hardening treatment, for example nitriding, cementation or soaking. Preferably, the body (10) is made of steel having a yield strength Re of between 200 and 600 MPa.

[0073] The body (10) comprises cavities (20) that are distributed in the bore (12) and capable of acting as a grease reserve (30). The cavities (20) are discontinuously distributed in the bore (12), i.e. they do not communicate with each other. Preferably, the cavities (20) are regularly distributed in the bore (12), around and/or along the axis (X10).

[0074] The cavities (20) can be of any shape. For example, the cavities (20) can have a circular radial cross-section, with a diameter (D20), and a rectangular axial cross-section, with a depth (P20). In practice, the depth (P20) is measured at the bottom of the cavity (20), at the point farthest from the surface of the bore (12).

[0075] The body (10) also comprises means (26) for supplying grease (30) to the bore (12). For example, the supply means (26) comprise an annular groove (27) formed on the outer surface (11), an annular groove (28) formed in the bore (12), and at least one orifice (29) passing through the body (10) between the grooves (27, 28). The annular grooves (27, 28) are formed around the axis (X10). Preferably, the supply means (26) comprise several orifices (29) distributed around the axis (X10), of which there are two, three, four or more orifices (29). The means (26) and more specifically the groove (28) are not connected to the cavities (20).

[0076] Alternatively, the supply means (26) can have no outer groove (27). Indeed, tests have shown that the inner groove (28) is sufficient to ensure the supply of grease (30) into the bore (12).

[0077] In the bore (12), a bearing surface (14) is defined outside the cavities (20) and the supply means (26), and a non-bearing surface (16) is defined in the cavities (20) and the supply means (26).

[0078] According to the invention, the bore (12) comprises at least one zone (40) with: [0079] a depth (P20) of cavities (20) of between 2 and 5 mm, and [0080] a ratio of the amount of grease (30) in the cavities (20) divided by the bearing surface (14) of between 0.05 and 0.2 g/cm.sup.2.

[0081] The grease (30) contained in the supply means (26) is not taken into account in the calculation of the grease (30)/bearing surface (14) ratio.

[0082] Tests carried out by the Applicant have shown that, in the case of an articulation operating in oscillation or in rotation, the grease (30) comprised in the inner groove (28) does not have an effect on the lubrication of the bore (12) since this groove (28) is not connected to the cavities (20). Furthermore, this groove (28) contributes to increasing the contact pressure between the shaft (2) and the ring (1) by reducing the bearing surface (14).

[0083] These tests have been carried out under the following conditions: [0084] Rings (1) of inner diameter 80 mm/outside diameter 95 mm/length 60 mm [0085] Pressure=50 MPa [0086] PV: 0.21 MPa.Math.m/s [0087] Initial lubrication only. [0088] Comparison between rings (1) with and without inner lubrication groove (28). [0089]

[0090] The service life of the rings (1) without an inner lubrication groove (28) is twice as long as the rings (1) with an inner lubrication groove (28).

[0091] The results obtained are contrary to certain publications of the state of the art, claiming that all the grease (30) contained in a ring (1) is “effective”, including the grease (30) contained in the inner and outer grooves (27, 28).

[0092] Preferably, the depth (P20) of the cavities (20) in the zone (40) is of between 3 and 5 mm. More preferably, the depth (P20) is equal to 4 mm.

[0093] In the example of FIGS. 1 to 3, the zone (40) covers the whole bore (12), 360 degrees around the axis (X10) of the body (10). In other words, the whole bore (12) is provided with cavities (20) having a depth (P20) of between 2 and 5 mm.

[0094] Preferably, the bore (12) has a surface layer (50) treated against seizing over a diffusion depth (P50) less than or equal to 0.6 mm, the surface layer (50) having a hardness greater than or equal to 500 Hv1 over a depth (P52) of between 5 and 50 μm.

[0095] Two test runs were carried out by varying certain parameters, such as the dimensions of the ring (1), the dimensions of the cavities (20), and the material of the shaft (2).

[0096] For the first test run, Table 1 presents the test conditions used for this run, while Tables 2 and 3 present different series of tests and the results obtained.

TABLE-US-00001 TABLE 1 Bench Large Oscillation Test Bench Law of Motion Sinusoidal axis oscillation Oscillation amplitude 90° Grease (type) Extreme Pressure Grease Lubrication Initial Only (no supply means (26) provided in the ring (1)) Ring material (1) Steel (Re < 600 MPa) Shaft material (2) 16NC6 Cemented Soaked Stop criterion COF > 0.35 T° > 100° C. Wear > 0.5 mm

TABLE-US-00002 TABLE 2 Quantity of Performance: grease/ number of Test conditions bearing cycles P PV surface completed Cavity (MPa) (MPa .Math. m/s) (g/cm.sup.2) until seizing depth Ring 100 0.1 0.039 15000 4 Inner Ø 100 0.1 0.039 20000 3 30 mm 100 0.1 0.051 50000 4 Length 100 0.1 0.1 83000 3 20 mm 100 0.1 0.133 92000 4 100 0.1 0.166 97000 5 100 0.1 0.2 95000 6 100 0.1 0.2 120000 4 100 0.1 0.3 90000 5.5 100 0.1 0.3 99000 4 100 0.1 0.391 35000 4

[0097] The results of tests carried out on larger ring dimensions are given in Table 3 below.

TABLE-US-00003 TABLE 3 Quantity of Performance: grease/ number of Test conditions bearing cycles P PV surface completed Cavity (MPa) (MPa .Math. m/s) (g/cm.sup.2) until seizing depth Ring 50 0.21 0.036 70000 2 mm Inner Ø 50 0.21 0.057 110000 3 mm 80 mm 50 0.21 0.091 164000 4 mm Length 50 0.21 0.144 300000 4 mm 60 mm

[0098] For the second test run, Table 4 presents the test conditions used for this run, while Table 5 presents a series of tests and the results obtained.

TABLE-US-00004 TABLE 4 Bench Large Oscillation Test Bench Law of Motion Sinusoidal axis oscillation Oscillation amplitude 90° Grease (type) Extreme Pressure Grease Lubrication Initial Only (no supply means (26) provided in the ring (1)) Ring material (1) Steel (Re < 600 MPa) Shaft material (2) 42CD4 QT + HF soaking with hard Cr coating (soaked and coated steel) Stop criterion COF > 0.35 T° > 100° C. Wear > 0.5 mm

TABLE-US-00005 TABLE 5 Quantity of Performance: grease/ number of Test conditions bearing cycles P PV surface completed Cavity (MPa) (MPa .Math. m/s) (g/cm.sup.2) until seizing depth Ring 100 0.1 0.039 27000 4 Inner Ø 100 0.1 0.039 39500 3 30 mm 100 0.1 0.051 84000 4 Length 100 0.1 0.133 135000 4 20 mm 100 0.1 0.2 144300 6 100 0.1 0.2 180000 4 100 0.1 0.3 140000 4 100 0.1 0.391 55000 4

[0099] According to the results of the two test runs, it is noted that the performances, which correspond to the number of cycles before seizing, are maximum for a quantity of grease per bearing surface of between 0.05 g/cm.sup.2 and 0.3 g/cm.sup.2, and most particularly between 0.05 g/cm.sup.2 and 0.2 g/cm.sup.2.

[0100] Other embodiments of a guiding member (1) according to the invention are shown in FIGS. 4 to 9. Certain constituent elements of the member (1) are comparable to those of the first embodiment described above and, with the aim of simplification, have the same numerical references.

[0101] FIG. 4 shows a guiding member (1) comprising cavities (20) but with no grease supply means (30). In the bore (12), the bearing surface (14) is defined outside of the cavities (20) and the non-bearing surface (16) is defined in the cavities (20).

[0102] FIG. 5 shows a cavity (20) having a diameter (D20) less than the depth (P20).

[0103] FIG. 6 shows a cavity (20) having a diameter (D20) greater than the depth (P20).

[0104] FIG. 7 shows a bore (12) comprising a zone (42) extending over an angular sector of 120 degrees around the longitudinal axis (X10). The bore (12) is provided with cavities (20) having a depth (P20) of between 2 and 5 mm only in this zone (42). Outside of the zone (42), the bore (12) has no cavities acting as a grease reserve (30).

[0105] FIG. 8 shows a bore (12) comprising a zone (42) extending over an angular sector of 180 degrees around the longitudinal axis (X10). The bore (12) is provided with cavities (20) having a depth (P20) of between 2 and 5 mm only in this zone (42). Outside of the zone (42), the bore (12) is provided with cavities (22) acting as a grease reserve (30) and having a depth of less than 2 mm, for example 1 mm. These cavities (22) are not taken into account for the calculation of the grease (30)/bearing surface (14) ratio in the zone (42).

[0106] FIG. 9 shows a bore (12) comprising two zones (44, 46) each extending over an angular sector of 120 degrees around the longitudinal axis (X10). The zones (44, 46) are located opposite each other on either side of the axis (X10).

[0107] Moreover, the guiding member (1) can be shaped differently from FIGS. 1 to 9 without moving away from the scope of the invention defined in the claims. Furthermore, the technical characteristics of the different embodiments and variations mentioned above can be combined in their entirety or only in part. Thus, the guiding member (1) can be adapted in terms of cost, functionalities and performance.