Bearing bushing with radial depressions and plateau surfaces

Abstract

A bearing bushing for a charging device may include an inner jacket surface including at least two radial depressions. A respective lowest point of the at least two radial depressions may be disposed on a circle having a radius R1. A plurality of plateau surfaces may be disposed circumferentially between the at least two radial depressions and may be offset radially towards an inside of the bearing bushing. The plateau surfaces may be curved and may have a constant radius R2. A ratio between the radius R1 and the radius R2 may correspond to the relationship: R1/R2=1.001 to 1.015.

Claims

1. A bearing bushing, comprising: an inner jacket surface including at least two radial depressions, the at least two radial depressions having a respective lowest point disposed on a circle defining a first radius R1 from a center axis; a plurality of plateau surfaces disposed circumferentially between the at least two radial depressions, the plurality of plateau surfaces arranged offset radially to an inside and define a curved structure having a second radius R2 from the center axis, wherein the second radius R2 is constant and concentric to the first radius R1; at least two oil holes corresponding to the at least two radial depressions, the at least two oil holes respectively having a radial axis running through the respective lowest point of the at least two radial depressions; wherein a ratio between the first radius R1 and the second radius R2 corresponds to the following relationship: R1/R2=1.001 to 1.015; wherein the at least two radial depressions are rounded and define a third radius R3 having a center point shifted outwards from the center axis by an eccentricity E=R1R3 on the radial axis of a corresponding one of the at least two oil holes, wherein the third radius R3 is smaller than the second radius R2; and wherein the at least two radial depressions define respective ramps disposed circumferentially between the corresponding oil hole and an adjacent plateau surface of the plurality of plateau surfaces, and wherein the respective ramps are rounded and provide a non-gradual and continuous transition defined by the third radius R3 that extends from the corresponding oil hole at the first radius R1 to the adjacent plateau surface at the second radius R2.

2. The bearing bushing according to claim 1, wherein the at least two radial depressions are at least one of structured to be identical to one another and distributed evenly across a circumference of the inner jacket surface.

3. The bearing bushing according to claim 1, wherein the at least two radial depressions include three depressions arranged on a circumference of the inner jacket surface and are offset from one another by 120.

4. The bearing bushing according to claim 1, wherein a ratio of a bearing bushing width B to a bearing bushing diameter D corresponds to the following relationship: B/D=0.4 to 1.0.

5. The bearing bushing according to claim 1, wherein: the plurality of plateau surfaces includes three plateau surfaces arranged on a circumference of the inner jacket surface offset from one another by 120; and the three plateau surfaces each occupy an angular range of between 5<<60.

6. The bearing bushing according to claim 1, wherein at least one of the at least two radial depressions and the plurality of plateau surfaces arranged circumferentially therebetween have at least one of the following dimensions:
2.5 mm<R1<4.0 mm,
0.03 mm<E<0.04 mm, and
20<<35; wherein R1 is the first radius R1, E is an eccentricity from which the at least two radial depressions are shifted radially outwards, and is an angular range.

7. The bearing bushing according to claim 1, wherein the plurality of plateau surfaces respectively encompass an angular range of 20<<35 along a circumference of the inner jacket surface.

8. The bearing bushing according to claim 1, wherein the plurality of plateau surfaces cover a total angular range of between 4% and 50% of the inner jacket surface.

9. A charging device comprising: a rotor including a shaft supported via at least one bearing bushing, the at least one bearing bushing having a center axis and including: an inner jacket surface; at least two rounded radial depressions provided on a circumference of the inner jacket surface, the at least two rounded radial depression having a respective lowest point disposed on a circle defining a first radius R1 from the center axis; a plurality of oil holes corresponding in number to that of the at least two rounded radial depressions; a plurality of curved plateau surfaces disposed circumferentially between the at least two rounded radial depressions with respect to the center axis, the plurality of curved plateau surfaces arranged offset radially to an inside and defining a constant second radius R2 from the center axis, wherein the constant second radius R2 is concentric to the first radius R1; wherein a ratio between the first radius R1 and the constant second radius R2 corresponds to the following relationship: R1/R2=1.001 to 1.015; wherein the plurality of curved plateau surfaces each occupy an angular range of between 20<<35 along a circumference of the inner jacket surface; wherein the plurality of oil holes each have a radial axis disposed at the respective lowest point of a corresponding one of the at least two rounded radial depressions, the at least two rounded radial depressions defining a third radius R3 having a center point shifted radially outwards from the center axis by an eccentricity E=R1R3 on the radial axis of the plurality of oil holes; wherein the third radius R3 is smaller than the second radius R2; and wherein the at least two rounded radial depressions define respective ramps providing a non-gradual and continuous transition defined by the third radius R3 that extends from a corresponding one of the plurality of oil holes at the first radius R1 to an adjacent curved plateau surface of the plurality of curved plateau surfaces at the constant second radius R2.

10. The charging device according to claim 9, wherein the at least one bearing bushing defines a width B and a diameter D, and wherein a ratio of the width B to the diameter D corresponds to the following relationship: B/D=0.4 to 1.0.

11. A bearing bushing, comprising: an inner jacket surface including at least two radial depressions, the at least two radial depressions having a respective lowest point disposed on a circle defined by a first radius R1 from a center axis; a plurality of curved plateau surfaces disposed circumferentially between the at least two radial depressions on the inner jacket surface, the plurality of curved plateau surfaces arranged offset radially towards the center axis and defined by a constant second radius R2 from the center axis, wherein the constant second radius R2 is concentric to the first radius R1; wherein a ratio between the first radius R1 and the constant second radius R2 corresponds to the following relationship: R1/R2=1.001 to 1.015; wherein the at least two radial depressions each include a corresponding oil hole having a radial axis running through the respective lowest point thereof, and wherein the at least two radial depressions define a third radius R3 having a center point shifted outwards from the center axis by an eccentricity E=R1R3 on the radial axis of the corresponding oil hole; wherein the third radius R3 is smaller than the constant second radius R2; and wherein the at least two radial depressions are each rounded with a non-gradual and continuous ramp defined by the third radius R3 extending between the first radius R1 and the constant second radius R2.

12. The bearing bushing according to claim 11, wherein the plurality of curved plateau surfaces each occupy an angular range of between 20<<35 along a circumference of the inner jacket surface.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The drawings show, in each case schematically:

(2) FIG. 1 shows a sectional illustration through a charging device according to the invention in the area of a shaft of a rotor of the charging device, which is supported via a bearing bushing,

(3) FIG. 2 shows a longitudinal section through the bearing bushing according to the invention.

DETAILED DESCRIPTION

(4) According to FIG. 1, a charging device 1 according to the invention, which can be embodied for example as exhaust gas turbocharger in a motor vehicle, has a rotor having a shaft 2, wherein the shaft 2 is supported via at least one bearing bushing 3, in particular in a bearing housing 4. To now be able to reduce a noise emission in response to the operation of the charging device 1 by means of the rotating rotor, as well as a friction, an inner jacket surface 5 of the bearing bushing 3 has at least two, in the shown example a total of three, depressions 6. The respectively lowest point 7 of the depressions 6 is thereby located on a circle with radius R1. Provision is made circumferentially between the individual depressions 6 for plateau surfaces 8, which are offset radially to the inside and which are curved and which have a constant radius R2. According to the invention, the following ratio applies between the radius R1 and the radius R2 applies according to the invention: R1/R21.001 to 1.015. The ratio is thereby in particular a function of the diameter (approximately R2) of the shaft 2.

(5) When further looking at FIG. 1, it can be seen that all depressions 6 are embodied so as to be rounded and identical. All depressions 6 are furthermore arranged so as to be distributed evenly across the circumference, whereby, in the case of three depressions 6, this means an arrangement of the depressions 6 so as to be offset by 120 each.

(6) The bearing bushing 3 furthermore has a number of oil holes 10, in particular of oil inlet holes 10, which corresponds to the number of the depressions 6, in each case comprising a radial axis 11, which ideally end in the lowest point 7 of the depressions 6. The rounded depressions 6 thereby have the radius R3 (loop radius) comprising a center point M1, which is shifted outwards by an eccentricity E=R1R3 on the respective radial axis 11 of the corresponding oil hole 10. The loop radius R3, that is, the radius R3 of the depressions 6, is thereby smaller than R2.

(7) Provision can further be made for the depression 6 to have a maximum depth R1 with regard to a center axis 12 (i.e. the depression does not have a constant radius with regard to the center axis). For example, the dimensions of the depression 6 can thereby be in the following ranges:
2.5 mm<R1<4.0 mm,
0.03 mm<E<0.04 mm,
20<<35.

(8) In particular the combination of the plateau surfaces 8 is hereby advantageous to improve the load-bearing capacity with the depressions 6 in the form of ramps for pressure build-up.

(9) Some possible combinations of the dimensions are listed in the table below

(10) TABLE-US-00001 plateau angle R1 [mm] R2 [mm] alpha [] sleeve diameter inner eccentricity depth Loop diameter BM42 30 R2.11 (4.22) R2.1 (4.2) 0.034 0.01 R2.077 (4.153) BM52 30 R2.61 (5.22) R2.6 (5.2) 0.034 0.01 R2.576 (5.152) BM60 25 R3.01 (6.02) R3 (6) 0.031 0.01 R2.979 (5.959) BM65 25 R3.26 (6.52) R3.25 0.031 0.01 R3.229 (6.459) (6.5) BM70 25 R3.5125 R3.5 (7) 0.038 0.0125 R3.474 (6.949) (7.025) BM79 25 R3.9625 R3.95 0.038 0.0125 R3.924 (7.849) (7.925) (7.9) BM89 25 R4.463 R4.45 0.038 0.0125 R4.424 (8.848) (8.925) (8.9)

(11) where:

(12) R1 is a radius from the center axis 12 to the lowest point 7 of a depression 6, sleeve radius,

(13) R2 is a radius of the curved plateau surfaces 8, inner diameter,

(14) R3 is a loop radius of the depressions 6,

(15) E: is the eccentricity,

(16) : is the plateau angle.

(17) It is particularly advantageous hereby that the depressions 6 transition continuously into adjacent plateau surfaces 8 and vice versa. Due to the depressions 6 according to the invention, ramps 13 are formed thereby, which serve to build up a pressure for oil for lubricating a rotor supported by the bearing bushing 1 according to the invention. Due to the continuous transition between the depressions 6 and the plateau surfaces 8, a pressure build-up in the oil can be attained, which would not be possible with a gradual transition. This results in significant advantages for the storage.

(18) Provision is thereby preferably made for a total of three curved plateau surfaces 8, which are arranged on the circumference so as to be offset by 120, and which in each case occupy an angular range of between 5<<60 (plateau angle).

(19) A ratio of a width B of the bearing bushing 3 to a diameter D thereof is preferably B/D=0.4 to 1.0 (see FIG. 2). This ratio is in particular a function of the desired bearing stability.

(20) The bearing bushing 3 itself can be arranged in the bearing housing 4 in a stationary or rotating manner, so that the invention can be realized in the case of a stationary as well as in the case of a rotating bearing bushing 3.

(21) The acoustics of the charging device 1 can be improved by means of the charging device 1 according to the invention and the bearing bushing 3, which is also in accordance with the invention, by simultaneously maintaining the bearing stability. In the case of a comparable geometry, that is, in the case of the same bearing width, the same bearing diameter and the same bearing play, the performance losses as compared to known circular cylindrical bearings are already improved significantly. Due to the improved stability characteristics, a further improvement of the friction losses is furthermore possible by decreasing the bearing surface (bearing width, bearing diameter). The friction losses can thus be reduced by means of the bearing according to the invention and in particular by means of the bearing bushing 3 according to the invention, and the efficiency as well as the transient behavior of the charging device 1 can thus be increased. The charging device 1 according to the invention can be used for example in an internal combustion engine 9, in particular in a motor vehicle.

(22) It goes without saying that the invention is to also protect the bearing bushing 3, the inner jacket surface 5 of which has at least two radial depressions 6. The respective lowest point 7 of the depressions 6 is thereby located on a circle with radius R1, whereby provision is made circumferentially between the depressions 6 for plateau surfaces 8, which are offset radially to the inside and which are curved and which have a constant radius R2. The following ratio between R1 and R2 applies thereby: 1.001R1/R21.015.

(23) All depressions 6 can thereby be embodied so as to be rounded and identical. The bearing bushing 3 has a number of oil holes 10, which corresponds to the number of the depressions 6, in each case comprising a radial axis 11, each of which ends in the lowest point 7 of the depressions 6. The rounded depressions 6 thereby have a radius R3 (loop radius) comprising a center point M1, which is shifted outwards by an eccentricity E=R1R3 on the respective radial axis 11 of the corresponding oil hole 10. A ratio of a width B of the inner bearing surface of the bearing busing 3 to a diameter D of the latter is thereby preferably: 0.4B/D1.0.