OIL LINE GUTTER FOR A TURBOMACHINE
The sectorized oil channeling gutter in turbomachines addresses oil spray issues by gradual oil evacuation, enhancing gearbox efficiency and assembly ease.
Patent Information
- Authority / Receiving Office
- FR · FR
- Patent Type
- Patents
- Current Assignee / Owner
- SAFRAN TRANSMISSION SYST
- Filing Date
- 2022-05-24
- Publication Date
- 2026-05-29
AI Technical Summary
Existing oil channels in turbomachines experience oil spray due to high-velocity ejection, leading to disruptions in the gearbox's dynamic behavior and efficiency.
A sectorized oil channeling gutter with radially offset edges to gradually evacuate oil, minimizing splashes and preventing oil from falling back onto the gearbox.
The solution effectively reduces oil splashes and maintains gearbox efficiency by preventing oil accumulation and degradation, while facilitating assembly.
Smart Images
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Abstract
Description
Title of the invention: OIL CHANNEL GUTTER FOR A TURBOMACHINE Technical field of the invention
[0001] The present invention relates in particular to an oil channel trough for a turbomachine, and to a turbomachine comprising such a trough. Technical background
[0002] A turbofan conventionally comprises an air inlet with a shrouded fan, the outlet airflow of which splits into a primary flow entering a primary stream of the gas generator and a secondary flow exiting in a secondary stream around the gas generator. The gas generator conventionally comprises, from upstream to downstream in the direction of gas flow, at least one compressor, one combustion chamber, and at least one turbine.
[0003] In the case of a geared turbomachine, the fan shaft is driven by a turbine shaft via an epicyclic gear reducer. The reducer allows the rotational speed of the fan shaft to be reduced relative to that of the turbine shaft. The reducer is conventionally housed in an enclosure (commonly called an "oil enclosure") positioned axially between the fan and the compressor.
[0004] As its name indicates, an epicyclic gear reducer comprises an epicyclic gear train including at least one sun gear, one crown gear, some satellites, and one satellite carrier. Depending on the requirements, such an epicyclic gear reducer can be configured in various ways.
[0005] In the remainder of this application, we will focus more specifically on the configuration commonly referred to as "planetary". More precisely, in such a configuration, the gearbox has a solar element fixed to the turbine shaft, a ring fixed to the blower shaft and a fixed planet carrier.
[0006] The bearings and gears of the epicyclic gear reducer are abundantly lubricated with oil, in particular to minimize wear on the contact surfaces of these different parts, and thus maximize the efficiency and lifespan of the reducer.
[0007] The oil is generally injected into the reducer via various nozzles, then ejected to the periphery of the ring under the effect of centrifugal force.
[0008] It is known from documents FR3084407A1 and FR3081513A1, in the name of the applicant, to install an oil channel around the crown, in particular to guide the ejected oil and thus facilitate its removal from the enclosure for reuse after appropriate treatment. The channels proposed in the The aforementioned documents are monolithic and extend continuously around the crown.
[0009] However, engine manufacturers have observed that such oil channels need improvement. Indeed, the oil ejected at high velocity impacts the oil film circulating in the channel, and the various impacts generate oil spray that splashes onto the different parts of the gearbox, particularly the moving parts. Such oil spray disrupts the dynamic behavior of the gearbox, to the detriment of its efficiency.
[0010] The objective of the present invention is therefore to provide a simple, effective and economical solution to address the aforementioned disadvantages. Summary of the invention
[0011] The invention thus proposes an oil channeling gutter for a turbomachine reducer, the gutter having axis X and the reducer comprising a rotating ring about the axis X and attached to a blower shaft of the turbomachine, the gutter being intended to be arranged around oil ejection means formed in the ring; characterized in that the gutter is sectorized and comprises a first series of curved primary sectors arranged around the X axis, each primary sector being circumferentially delimited by a front edge and a rear edge defined along a circumferential direction D around the X axis, the circumferentially adjacent front and rear edges of two successive primary sectors being radially offset from each other, so that the front edge is radially offset inwards relative to the rear edge, so as to form between them a primary oil evacuation opening outside the gutter.
[0012] Such a gutter allows the ejected oil to be gradually evacuated while channeling (or guiding) the oil towards the suction inlet(s). The gradual evacuation of the oil prevents the gutter from becoming clogged and minimizes the amount of oil circulating within it, thereby significantly reducing the intensity of the splashes resulting from the various impacts of the ejected oil with the oil circulating in the gutter, and preventing the oil circulating in the gutter from falling back onto the gearbox by gravity. The gradual evacuation of the oil thus prevents degradation of the gearbox's dynamic behavior, and consequently improves its efficiency.
[0013] The sectorization of the gutter also makes it easier to assemble.
[0014] The gutter according to the invention may comprise one or more of the following features, taken individually or in combination with each other: - the first series extends around the X-axis in a first angular range of 180°; - the radial offset between the front edge and the rear edge is between 2 and 30 mm; - the circumferentially adjacent front and rear edges of two successive primary sectors overlap; - the gutter comprises a second series of curved secondary sectors arranged around the X axis, each secondary sector being circumferentially delimited by a front edge and a rear edge defined along the circumferential direction D around the X axis, the circumferentially adjacent front and rear edges of two circumferentially successive secondary sectors being radially offset from each other, so that the front edge is radially offset outwards relative to the rear edge, so as to form between them a secondary oil evacuation opening outside the gutter; - the second series extends in a second angular range of 180° around the X axis; - each primary sector includes an oil flow path whose opening is oriented radially towards the X axis, the oil flow path being delimited by a bottom wall and two side walls; - the side walls move closer together to form a narrowing; - each primary sector includes a flange for fixing to a turbomachine housing, the flange extending outwards from the bottom wall.
[0015] The present invention also relates to an X-axis turbomachine comprising an epicyclic gear reducer and a reducer lubrication circuit which includes an oil channel trough as described above, the reducer comprising a rotating ring about the X-axis, the ring being integral with a blower shaft centered on the X-axis, the trough being arranged around oil ejection means formed in the ring.
[0016] In a particular embodiment, the lubrication circuit of the reducer may include an oil suction port disposed at 6 o'clock by analogy to the face of a clock. Brief description of the figures
[0017] The invention will be better understood and other details, features and advantages of the invention will become more apparent upon reading the following description, given by way of non-limiting example and with reference to the accompanying drawings in which:
[0018] [Fig-1] [Fig.1] is a schematic axial half-section view of a turbomachine including a gutter according to the invention;
[0019] [Fig.2] [Fig.2] is a schematic cross-sectional view of a gutter according to a first method of implementation;
[0020] [Fig.3] [Fig.3] is a schematic cross-sectional view of a gutter according to a second embodiment;
[0021] [Fig.4] [Fig.4] is a schematic cross-sectional view of a gutter according to a third embodiment;
[0022] [Fig. 5] [Fig. 5] is a perspective view of a gutter according to a fourth mode of realization;
[0023] [Fig.6] [Fig.6] is a detail view of [Fig.5];
[0024] [Fig.7] [Fig.7] is a detail view of [Fig.6];
[0025] [Fig.8] [Fig.8] is a detail view of [Fig.7] showing the oil drainage (symbolized by the four arrows) via an opening;
[0026] [Fig.9] [Fig.9] is a view of a first example of an embodiment of the section of a gutter sector;
[0027] [Fig. 10] [Fig. 10] is a view of a second example embodiment of the section of a gutter sector;
[0028] [Fig. 11] [Fig. 11] is a view of a third embodiment of the section of a section of the gutter. Detailed description of the invention
[0029] Figure 1 shows a partial representation of a geared turbomachine 1, which conventionally comprises, from upstream to downstream in the direction of gas flow, a shrouded blower 2 and a gas generator 3 comprising at least one compressor, one combustion chamber, and at least one turbine.
[0030] As illustrated in [Fig.1], the airflow generated by the blower 2 is divided, by an inter-vein structure 4 of the turbomachine 1, into a primary flow which enters a primary vein 5 of the gas generator 3 and into a secondary flow which flows in a secondary vein 6 around the gas generator 3, the secondary flow participating predominantly in the thrust supplied by the turbomachine 1.
[0031] As illustrated in [Fig.1], the blower 2 comprises a blower shaft 7 which carries blades 8 and which is driven in rotation by a turbine shaft 9 via an epicyclic gear reducer 10.
[0032] The turbomachine 1 is defined along a longitudinal axis X which corresponds in particular to the axis of rotation of the blower and turbine shafts 7, 9.
[0033] As indicated above, the epicyclic gear reducer 10 is here of the "planetary" type and hereafter referred to as reducer 10. The reducer 10 allows the rotational speed of the blower shaft 7 to be reduced relative to that of the turbine shaft 9.
[0034] More specifically, the reducer 10 comprises a central solar element 11 fixed to the turbine shaft 9 and a ring gear 12 fixed to the blower shaft 7, the solar element 11 and the ring gear 12 being movable about the X-axis. The reducer 10 also comprises a fixed (or immobile) satellite carrier 13 which carries several satellites 14 distributed around the X axis, each satellite 14 being meshed with both the solar 11 and the corona 12.
[0035] The ring 12 can be mobile in rotation around the axis X in a clockwise or counterclockwise direction of rotation, depending in particular on the direction of rotation of the turbine shaft 9.
[0036] By convention in this application, the terms "upstream" and "downstream" are defined with respect to the direction of gas flow in the turbomachine 1.
[0037] Furthermore, by convention in the present application, "axial" or "axially" means any direction parallel to the X axis of the turbomachine 1 or the gutter 18, "radial" or "radially" means any direction perpendicular to the X axis of the turbomachine 1 or the gutter 18, and "circumferentially" means any direction relative to the circumference of the turbomachine 1 or the gutter 18 (as opposed to the radial and axial directions explained above).
[0038] Finally, by convention in the present application, the terms "internal", "external", "inside" and "outside" are defined radially with respect to the X axis of the turbomachine 1 or the gutter 18.
[0039] As illustrated in [Fig.1], the reducer 10 is housed and lubricated in an annular enclosure 15 around the X axis, the enclosure 15 being pressurized and arranged axially between the blower 2 and the compressor.
[0040] More specifically, to lubricate the gearbox 10, the turbomachine 1 includes a lubrication circuit 16 which has one or more oil injection nozzles inside the gearbox 10. The injected oil is centrifuged outwards to lubricate the various moving parts (in particular the bearings and gears) of the gearbox 10, and then ejected from the gearbox 10 via oil ejection means 17 formed in the ring 12. The oil ejection means 17 are, for example, in the form of orifices formed in the ring 12. The lubrication circuit 16 further includes a fixed oil channel 18 which is arranged around the oil ejection means 17, this channel 18 allowing the oil to be channeled or guided towards one or more suction ports 19 preferably arranged at 6 o'clock by analogy to the face of a clock.The suction inlet(s) 19 are not necessarily at 6 o'clock, by analogy with the face of a clock.
[0041] The gutter 18 has an X axis and in other words is also defined along the X axis.
[0042] According to the invention, the gutter 18 is sectorized and comprises a first series 20 (or row) of curved primary sectors 21 arranged around the axis X. Each primary sector 21 is circumferentially delimited by a front edge 22 and a rear edge 23 defined along a circumferential direction D around the axis X. The circumferentially adjacent front and rear edges 22, 23 of two primary sectors 21 successive are radially offset from one another, so that the front edge 22 is radially offset inwards from the rear edge 23, so as to form between them a primary opening 24 for oil evacuation outside the gutter 18.
[0043] In other words, the front edge 22 of a primary sector 21 is radially offset inwards relative to the rear edge 23 of a primary sector 21 which precedes it along the circumferential direction D of the gutter 18, so as to form between them a primary opening 24 for oil evacuation outside the gutter 18.
[0044] Such a gutter 18 allows the ejected oil to be gradually evacuated while channeling (or guiding) the oil towards the suction inlet(s) 19. The gradual evacuation of the oil helps to clear blockages in the gutter and minimize the amount of oil circulating within it, thereby significantly reducing the intensity of the splashes resulting from the various impacts of the ejected oil with the oil circulating in the gutter, and preventing the oil circulating in the gutter from falling back onto the gearbox by gravity. The gradual evacuation of the oil thus prevents any degradation of the gearbox's dynamic behavior, and consequently improves its efficiency.
[0045] The sectorization of the gutter 18 also makes it easier to assemble.
[0046] The circumferential direction D of the gutter 18 around the axis X can have a clockwise or counterclockwise direction around the axis X.
[0047] The number of primary sectors 21 is variable and depends in particular on the size of the turbomachine 1 and the requirements of the specification concerning the dynamic behavior of the reducer 10. The oil evacuation is all the more efficient as the number of openings 24 over a given angular range is large.
[0048] The first series 20 of primary sectors 21 can extend all around the ring 12. Such an embodiment is preferred when the rotation speed of the ring 12 is high, and in other words when the oil flows over the primary sectors 21 mainly under the action of its velocity.
[0049] The first series 20 of primary sectors 21 can also extend only within a first given angular range, for example a range of 180°. Such an embodiment is preferred when the rotational speed of the ring 12 is lower, and in other words, when the oil flows mainly over the primary sectors 21 under the action of gravity G. The primary sectors 21 then allow the oil to be evacuated and guided under the action of gravity G.
[0050] Advantageously, the first angular range corresponds to an angular range in which the direction of the ejected oil and the direction of gravity G are in the same direction. For example, when the crown 12 rotates clockwise and the circumferential direction D of the gutter 18 is clockwise, the first angular range can be between 12 o'clock and 6 o'clock by analogy with the dial of a clock. Conversely, when the crown 12 is mobile in a counterclockwise direction of rotation and the circumferential direction D of the gutter 18 has a counterclockwise direction, the first angular range can be between 6 o'clock and 12 o'clock by analogy to the dial of a clock.
[0051] The circumferentially adjacent front and rear edges 22, 23 of two successive primary sectors 21 can overlap, in particular to optimize the guidance of the oil.
[0052] The radial offset (or radial clearance) between the front edge 22 and the rear edge 23 is between 2 and 30 mm. The value of the radial offset depends in particular on the quantity of oil to be evacuated via the primary opening 24.
[0053] The gutter 18 may include a second series 25 (or row) of curved secondary sectors 26 arranged around the axis X. In the same way as a primary sector 21, each secondary sector 26 is circumferentially delimited by a front edge 27 and a rear edge 28 defined along the circumferential direction D of the gutter 18. The circumferentially adjacent front and rear edges 27, 28 of two successive secondary sectors 26 are radially offset from each other, so that the front edge 27 is radially offset outwards from the rear edge 28, so as to form between them a secondary opening 29 for oil discharge outside the gutter 18.
[0054] In other words, the front edge 27 of a secondary sector 26 is radially offset outwards relative to the rear edge 28 of a secondary sector 26 which precedes it along the circumferential direction D of the gutter 18, so as to form between them a secondary opening 29 for oil evacuation outside the gutter 18.
[0055] The number of secondary sectors 26 is variable and depends in particular on the size of the turbomachine 1 and the requirements of the specification concerning the dynamic behavior of the reducer 10. The oil evacuation is all the more efficient as the number of openings 29 over a given angular range is large.
[0056] Advantageously, the second series 25 of secondary sectors 26 is complementary to the first series 20 of primary sectors 21 around the axis X.
[0057] Advantageously, the second series 25 extends over a second given angular range, for example a range of 180°. The secondary sectors 26 allow the oil to be evacuated and guided under the action of gravity G over the second range which is preferably complementary to the first range.
[0058] Advantageously, the second angular range corresponds to an angular range in which the direction of the ejected oil and the direction of gravity G are opposite. For example, when the ring 12 rotates clockwise and the circumferential direction D of the trough 18 is clockwise, the second angular range can be between 6 o'clock and 12 o'clock by analogy with clock face. Conversely, when the crown 12 is mobile in a counterclockwise direction of rotation and the circumferential direction D of the gutter 18 has a counterclockwise direction, the first angular range can be between 12 o'clock and 6 o'clock by analogy to the dial of a clock.
[0059] The circumferentially adjacent front and rear edges 27, 28 of two successive secondary sectors 26 can overlap, in particular to improve the guidance of the oil.
[0060] The radial offset (or radial play) between the front edge 27 and the rear edge 28 is between 5 and 40 mm. The value of the radial offset depends in particular on the quantity of oil to be evacuated via the secondary opening 29.
[0061] Advantageously, the primary sectors 21 and / or secondary sectors 26 are curved with a concavity turned or oriented with the interior. The primary sectors 21 and / or secondary sectors 26 are, for example, each in the form of an arc of a circle.
[0062] Each primary sector 21 (or each secondary sector 26) may include an oil flow path 30 whose opening 31 is oriented radially towards the X axis (or the interior), the oil flow path 30 being delimited by a bottom wall 32 and two side walls 33. The opening 31 is then placed around and opposite the oil ejection means 17 of the ring 12.
[0063] The side walls 32 can move closer together so as to form a narrowing 34.
[0064] Each primary sector 21 (or each secondary sector 26) can be fixed to a housing 36 (for example an inlet housing) via a flange 35, the flange 35 extending outwards from the bottom wall 32. The flange 35 can be attached to the sector 21, 26 or be formed as a single piece with the sector 21, 26.
[0065] According to the embodiments illustrated in the figures, the direction of the circumferential direction D of the gutter 18 corresponds to the direction of rotation of the crown 12.
[0066] As indicated by the arrow in figures 2 to 8, the crown 12 is here mobile in rotation in a clockwise direction, the circumferential direction D of the gutter 18 thus having a clockwise direction.
[0067] According to the first embodiment of the gutter 18, which is illustrated in [Fig. 2], the gutter 18 comprises a first series 20 of primary sectors 21 and a second series 25 of secondary sectors 26. As illustrated by the dashed arrows, the oil flows in the gutter 18 primarily under the action of gravity G. The first series 20 comprises three primary sectors 21 extending from 12 o'clock to 6 o'clock, analogous to the face of a clock. The second series 25 also comprises three secondary sectors 26 extending from 6 o'clock to 12 o'clock, analogous to the face of a clock. The circumferentially adjacent front and rear edges 22, 23 of two successive primary sectors 21 overlap. Similarly, the front edges and rear 27, 28 circumferentially adjacent of two successive secondary sectors 26 overlap.
[0068] According to the second embodiment of the gutter 18, which is illustrated in [Fig. 3], the gutter 18 comprises only a first series 20 of primary sectors 21. As illustrated by the dashed arrows, the oil flows in the gutter 18 primarily under the action of its velocity. The first series 20 comprises six primary sectors 21 distributed regularly around the X-axis. The circumferentially adjacent front and rear edges 22, 23 of two successive primary sectors 21 overlap.
[0069] According to the third embodiment of the gutter 18, which is illustrated in [Fig. 4], the gutter 18 comprises only a first series 20 of primary sectors 21. As illustrated by the dashed arrows, the oil flows in the gutter 18 primarily under the action of gravity G. The first series 20 comprises three primary sectors 21 extending from 12 o'clock to 6 o'clock, by analogy with the face of a clock. The circumferentially adjacent front and rear edges 22, 23 of two successive primary sectors 21 overlap.
[0070] According to the fourth concrete embodiment of the gutter 18, which is illustrated in Figures 5 to 8, the gutter 18 comprises only a first series 20 of primary sectors 21. The oil flows in the gutter 18 primarily under the action of gravity G. The first series 20 comprises three primary sectors 21 extending from 12 o'clock to 4 o'clock, by analogy with the face of a clock. The circumferentially adjacent front and rear edges 22, 23 of two successive primary sectors 21 are joined. As illustrated in [Fig.8], the oil symbolized by the four arrows is evacuated outside the gutter 18 via the primary opening 24. On the exposed angular portion (the angular portion which does not include sectors), the oil is ejected onto the walls defining the enclosure 15, then converges towards the suction port(s) 19. The absence of sectors here prevents oil from falling by gravity onto the reducer 10.
[0071] As illustrated in [Fig.8], each primary sector 21 comprises an oil flow path 30 whose opening 31 is oriented radially towards the X axis (or the interior), the oil flow path 30 being delimited by a bottom wall 32 and two side walls 33. The opening 31 is then positioned around and opposite the oil ejection means 17 of the ring 12. More precisely, each primary sector 21 has a U-shaped cross-section, the side walls 33 being perpendicular to the bottom wall 32. Each primary sector 21 finally comprises a mounting flange 35 to a housing 36 (here an inlet housing), the flange 35 projecting outwards from the bottom wall 32.
[0072] Figures 9 to 11 illustrate different examples of embodiments of the section of a sector 21, 26 of gutter 18, these examples can in particular be applied to the methods of realization of figures 2 to 4.
[0073] According to the first embodiment illustrated in [Fig. 9], the sector 21, 26 has a U-shaped profile with an opening 31 oriented towards the X-axis (or the interior). The side walls 33 flare out from the bottom wall 32 over a first portion, then are parallel over a second portion.
[0074] According to the second embodiment illustrated in [Fig. 10], the sector 21, 26 has a C-shaped profile with an opening 31 oriented towards the X-axis (or inwards). The side walls 33 approach each other slightly to form a narrowing 34. The sector 21, 26 further includes a shouldered fixing flange 35 projecting outwards from the bottom wall 32.
[0075] According to the third embodiment illustrated in [Fig. 11], the sector 21, 26 has a T-shaped profile with an opening 31 oriented towards the X-axis (or inwards). The lateral walls 33 approach each other to form a narrowing 34. More precisely, the lateral walls 33 comprise first and second parallel portions, the second portions forming the narrowing 34. The first and second portions of a lateral wall 33 are connected via an axial wall.
Claims
Demands
1. Oil channel trough (18) for a turbomachine (1) reducer (10), the trough having axis (X) and the reducer comprising a ring (12) movable in rotation about the axis (X) and integral with a blower shaft (7) of the turbomachine, the trough (18) being intended to be arranged around oil ejection means (17) formed in the ring (12);characterized in that the gutter (18) is sectorized and comprises a first series (20) of curved primary sectors (21) arranged around the axis (X), each primary sector (21) being circumferentially delimited by a front edge (22) and a rear edge (23) defined along a circumferential direction (D) around the axis (X), the circumferentially adjacent front and rear edges (22, 23) of two successive primary sectors (21) being radially offset from each other, so that the front edge (22) is radially offset inwards relative to the rear edge (23), so as to form between them a primary opening (24) for oil evacuation outside the gutter (18), the circumferentially adjacent front and rear edges (22, 23) of two successive primary sectors (21) overlapping.;
2. Gutter (18) according to claim 1, wherein the first series (20) extends around the axis (X) in a first angular range of 180°.
3. Gutter (18) according to claim 1 or 2, characterized in that the radial offset between the front edge (22) and the rear edge (23) is between 2 and 30 mm.
4. Gutter (18) according to any one of claims 1 to 3, comprising a second series (25) of curved secondary sectors (26) arranged around the axis (X), each secondary sector (26) being circumferentially delimited by a front edge (27) and a rear edge (28) defined along the circumferential direction (D) around the axis (X), the circumferentially adjacent front and rear edges (27, 28) of two circumferentially successive secondary sectors (26) being radially offset from each other, so that the front edge (27) is radially offset outwards from the rear edge (28), so as to form between them a secondary opening (29) for oil drainage outside the gutter (18).
5. Gutter (18) according to claim 4, wherein the second series (25) extends in a second angular range of 180° around the (X) axis.
6. Gutter (18) according to any one of claims 1 to 5, characterized in that each primary sector (21) comprises an oil flow channel (30) whose opening (31) is oriented radially towards the axis (X), the oil flow channel (30) being delimited by a bottom wall (32) and two side walls (33).
7. Gutter (18) according to claim 6, characterized in that the side walls (33) approach each other so as to form a narrowing (34).
8. Gutter (18) according to any one of claims 6 or 7, characterized in that each primary sector (21) comprises a flange (35) for attachment to a turbomachine housing, the flange (35) extending outwards from the bottom wall (32).
9. Turbomachine (1) of axis (X) comprising an epicyclic gear reducer (10) and a reducer lubrication circuit (16) comprising an oil channel trough (18) according to any one of claims 1 to 8, the reducer (10) comprising a ring (12) rotatable about the axis (X), the ring (12) being integral with a blower shaft (7) centered on the axis (X), the trough (18) being arranged around oil ejection means (17) formed in the ring (12).
10. Turbomachine (1) according to the preceding claim, characterized in that the lubrication circuit (16) of the reducer comprises an oil suction port (19) disposed at 6 o'clock by analogy to the face of a clock.