阅读说明：本技术 包括可熔区段的驱动轴和用于保护这种驱动轴免受过扭矩的方法 (Drive shaft comprising a fusible section and method for protecting such a drive shaft against over-torque ) 是由 阿诺·尼古拉斯·内格里 朱利安·法比恩·帕特里克·比库利特 米歇尔·吉尔伯特·罗兰·布罗 罗曼 于 2020-02-19 设计创作，主要内容包括：本发明涉及一种飞行器涡轮发动机的驱动轴(50),该驱动轴包括：-第一部分(52)和第二部分(54),-连接装置(56),该连接装置连接所述第一部分和所述第二部分,并被构造成将扭矩从所述第二部分传递到所述第一部分,所述连接装置包括至少一个波纹管(70),至少一个波纹管包括：-第一区段(72),该第一区段的直径大于所述第一部分和所述第二部分的直径,-第二区段(74),该第二区段位于所述第一区段的侧面,所述驱动轴的特征在于,所述第一区段包括至少一个可熔区段(76),至少一个可熔区段包括至少一个通孔(78),并被构造成当施加到所述第一部分的扭矩值超过预定阈值时断裂。(The invention relates to a drive shaft (50) of an aircraft turbine engine, comprising: -a first part (52) and a second part (54), -a connecting device (56) connecting the first part and the second part and configured to transmit torque from the second part to the first part, the connecting device comprising at least one bellows (70) comprising: -a first section (72) having a diameter greater than the diameter of the first and second portions, -a second section (74) located at the side of the first section, characterized in that the first section comprises at least one fusible section (76) comprising at least one through hole (78) and configured to break when the value of the torque applied to the first portion exceeds a predetermined threshold value.)

1. A drive shaft (50) of an aircraft turbine (10), the drive shaft comprising:

a first portion (52) extending longitudinally along an axis (A) and having a first diameter (D1),

-a second portion (54) extending longitudinally along said axis (a) and having a second diameter (D2), and

-a connection device (56) connecting the first and second parts and configured to transmit torque from the second part (54) to the first part (52), the connection device (56) comprising at least one bellows (70) comprising:

-a first section (72) extending longitudinally along the axis (A) and having a diameter (D)_PS) Is larger than the first diameter and the second diameter, an

-a second section (74) extending radially with respect to the axis (A) and flanking the first section (72),

the drive shaft (50) is characterized in that the first section (72) comprises at least one fusible section (76) comprising at least one through hole (78) and configured to break when a value of torque applied to the first portion (52) exceeds a predetermined threshold.

2. The drive shaft (50) according to the preceding claim, wherein the thickness (E1, E2) of the first and second portions (52, 54) is greater than the thickness (EDS) of the second section (74) and/or the thickness (EDS) of the second section (74) is greater than the thickness (EPS) of the first section (72).

3. The drive shaft (50) according to any one of the preceding claims, wherein the first section (72) comprises a thinned portion (80) having a thickness (E)_PA) Is smaller than the thickness (E) of the first section (72)_PS) The thinned portion (80) includes the fusible section (76).

4. The drive shaft (50) according to claim 3, wherein the thinned portion (80) extends over at most 80% of the length of the first section (72).

5. The drive shaft (50) according to any one of the preceding claims, wherein the fusible section (76) comprises a plurality of through holes (78) regularly distributed around the axis (A).

6. The drive shaft (50) according to any one of the preceding claims, wherein the shape of the or each through hole (78) is circular or elliptical.

7. The drive shaft (50) according to any one of the preceding claims, wherein the or each through hole (78) is defined as follows:

wherein R is_OTextIs the outer radial distance, R, between the through hole (78) and the axis (A)_OTintIs the inner radial distance between the through-hole (78) and the axis (A), Kt is the stress concentration coefficient generated by the through-hole (78), R_PSextIs the outer radius between the first section (72) and the axis (A), and R_PSintIs the inner radius between the first section (72) and the axis (a).

8. The drive shaft (50) according to any one of the preceding claims, wherein the connecting means (56) comprises a plurality of bellows (70), each bellows (70) comprising:

-a first segment (72) extending longitudinally along the axis (a) and having a Diameter (DPS) greater than the first and second diameters, and

-a second section (74) extending radially with respect to the axis (A) and flanking the first section (72),

for at least one of the bellows (70), the first section (72) of the bellows (70) includes at least one fusible section (76) including at least one through hole (78) and configured to break when a value of torque applied to the first portion (52) exceeds a predetermined threshold.

9. The drive shaft (50) according to any one of the preceding claims, wherein the first portion (52) comprises a first end portion (58) comprising gear teeth (60) and adapted to be connected to a reduction gearbox (26) and a second end portion (62) connected to the connecting means (56), the second portion (54) comprises a first end portion (64) comprising splines (66) and adapted to be connected to a second drive shaft (42) and a second end portion (68) connected to the connecting means (56).

10. The drive shaft (50) according to any one of claims 1 to 9, wherein the first diameter (D1) is substantially equal to the second diameter (D2).

11. The drive shaft (50) according to any one of claims 1 to 9, wherein the first diameter (D1) is different from the second diameter (D2).

12. The drive shaft (50) according to any one of claims 1 to 11, wherein the diameter (D) of the first section (72)_PS) Is at least 1.5 times the first and second diameters (D1, D2).

13. An aircraft turbomachine (10) comprising:

-a drive shaft (50) according to any of the preceding claims,

-a reduction gearbox (26) connected to the first part (52), and

-a second drive shaft (42) connected to the second portion (54).

14. A method for protecting a drive shaft (50) of a turbine (10) according to any one of claims 1 to 12 from over-torque, the method comprising: a step of breaking the fusible section (76) when the value of the torque applied to the first portion (52) exceeds a predetermined threshold.

Technical Field

The present invention relates to a drive shaft of a turbomachine, to a turbomachine comprising such a drive shaft and to a method for protecting such a drive shaft from over-torque.

Background

The prior art includes, inter alia, patent applications US-A1-2010/111691, EP-A2-1199441 and EP-A1-3205840.

In a conventional manner, an aircraft turbomachine, such as a turbojet, comprises, from upstream to downstream along the gas flow direction, a fan, one or more compressors (for example low-pressure compressor and high-pressure compressor) arranged in series, a combustion chamber, one or more turbines (for example low-pressure turbine and high-pressure turbine), and a nozzle.

The fan generates an air flow, one part of which feeds the aforementioned components of the turbine and forms a main flow in the main duct, and the other part of which flows into a secondary duct extending around the main duct and forms a secondary air flow, which generates the main part of the thrust of the turbine. The compressor is configured to increase the pressure of air, which is then supplied to the combustion chamber. In the combustion chamber, air is mixed with fuel and burned. The combustion gases then pass through a turbine, which rotates a compressor by extracting a portion of the pressure energy from the gases exiting the combustor and converting this portion of the pressure energy into mechanical energy. The nozzles enable the exhaust gases to be ejected, thereby also generating the thrust of the turbine.

In some turbine architectures, a reduction gearbox is integrated between the low pressure turbine and the fan to enable the turbine and the fan to operate at different speeds, where the rotational speed of the turbine is higher than the rotational speed of the fan.

In particular, the rotor of the low-pressure turbine is coupled to the fan by means of a reduction gearbox, a shaft connecting the rotor of the low-pressure turbine to the reduction gearbox and a shaft connecting the reduction gearbox to the fan. The axial position of the shaft is determined in particular by the thrust bearings which ensure that the shaft is retained in the axial direction and prevent displacement of the shaft along its axis, and by the coupling of the shaft with the reduction gearbox.

It is known that turbojet engines with reduction gearboxes require flexible zones on the transmission line from the low-pressure turbine shaft to the reduction gearbox in order to isolate the vibration phenomena from the other elements of the turbojet engine. The flexible zone is typically implemented on the input shaft of the reduction gearbox.

To achieve this flexible region, it is proposed to integrate a bellows on the input shaft of the reduction gearbox. More precisely, the input shaft of the reduction gearbox is divided into two parts, which are connected to each other by a bellows.

Also proposed in application FR-a 1-2909146 is a device for connecting two rotating shafts, comprising a straight spline formed on one of the rotating shafts and engaging with a complementary straight spline formed on the other of the rotating shafts, the device comprising a cylindrical member having greater flexibility on the other of the rotating shafts. The cylindrical member has holes, the number, arrangement and size of which are determined in such a way that the flexibility of the cylindrical member is calibrated.

In these turbine architectures, there is also a need to protect the drive shaft from over-torque due to sudden seizures in the reduction gearbox, in particular in the case of plain bearings for the planetary gears of the reduction gearbox. In fact, in the event of a sudden seizure of one of these sliding bearings, the low-pressure turbine generates a quasi-infinite torque due to its inertia and to the speed of rotation at the moment before the seizure, which can cause the breakage of the transmission line between the low-pressure turbine and the reduction gearbox.

To improve safety within the turbine, it is desirable to control the fracture area and the fracture torque of the transmission line.

It is therefore proposed in application US-a1-2017/0175753 to integrate torsionally fusible sections in the transmission line downstream of the reduction gearbox. In particular, the requirement relates to a turbomachine comprising decoupling means arranged between the reduction gearbox and the low-pressure turbine shaft, the decoupling means being adapted to decouple the reduction gearbox from the low-pressure turbine shaft in response to a determined resistance torque exerted by the reduction gearbox on the low-pressure turbine shaft being exceeded.

In application FR- A-3015570, A turbine is also proposed, having A set of uncovered counter-rotating propellers, comprising an inner casing and A radial support device of the outer casing with respect to the inner casing, the inner casing being rotationally integral with an outer casing arranged around said inner casing, the radial support device enabling the transmission of radial forces from the inner casing to the outer casing. The radial support means comprise axial uncoupling means arranged between the inner casing and the outer casing, which have recesses and enable uncoupling and thus inhibit axial deformation transmitted by the radial support means from the inner casing to the outer casing.

It is also possible to integrate a fusible section on the flexible input shaft of the reduction gearbox. However, the length of the input shaft of the reduction gearbox has a direct influence on the overall size of the turbine, and therefore this solution increases the overall size and mass of the turbine.

In particular, the present invention aims to provide a simple, economical and effective solution to these problems of the prior art.

In particular, the invention enables a fusible function to be achieved on the flexible input shaft of the reduction gearbox without increasing the overall size requirements of the turbomachine.

Disclosure of Invention

To this end, the invention relates to a drive shaft of an aircraft turbine, comprising:

a first portion extending longitudinally along an axis and having a first diameter,

-a second portion extending longitudinally along said axis and having a second diameter, an

-a connection device connecting the first and second parts and configured to transfer torque from the second part to the first part, the connection device comprising at least one bellows comprising:

-a first section extending longitudinally along the axis and having a diameter greater than the first and second diameters, an

A second section extending radially with respect to said axis and located laterally of said first section,

the drive shaft is characterized in that the first section comprises at least one fusible section comprising at least one through hole and configured to break when a torque value applied to the first portion exceeds a predetermined threshold value.

Advantageously, the fusible sections are configured such that when the value of the torque applied to the first portion of the drive shaft exceeds a predetermined threshold, only one fusible section breaks the connection means to separate the first portion from the second portion of the drive shaft.

In particular, the fusible section is realized by a through hole in the first section of the connecting device. In fact, the fusible section is configured to break at the through hole in the event of an over-torque applied to the first portion of the drive shaft to protect other elements of the drive line.

In addition, this is particularly advantageous, since oil may accumulate centrifugally at the first section and must therefore be drained, so that no oil imbalance or oil stagnation zones are created. Therefore, the through-hole also serves as a drain hole for oil.

As a result, the through hole enables oil that may accumulate at the first section to be drained and enables a desired fusible function to be performed to protect the first portion applied to the drive shaft from excessive torque.

Since the first section is subjected to torsional stress, the drilling of the through-hole into the first section involves local overstress effects, in particular at the periphery of the through-hole. This phenomenon enables the melting function to be achieved in the event of an over-torque applied to the first portion of the drive shaft.

Furthermore, this solution does not increase the axial and radial overall dimensions of the drive shaft, nor the manufacturing costs of the drive shaft.

Thus, the bellows enables flexibility for overall dynamics and misalignment.

According to the invention, the overtorque is the torque applied to the first part, the torque value exceeding a predetermined threshold.

The first and second portions may be tubular in shape. The first diameter, i.e., the diameter of the first portion, may be substantially equal to the second diameter, i.e., the diameter of the second portion. Alternatively, the first and second diameters may be different from each other.

The thickness of the first portion and the second portion may be greater than the thickness of the second section. The thickness of the second section may be greater than the thickness of the first section.

The first section may be annular in shape. The diameter of the first section may be at least 1.5 times the first diameter and the second diameter.

The first section may include a thinned portion having a thickness less than a thickness of the first section. In particular, the thinned portion may include a fusible section.

The thinned portion may extend over at most 80% of the length of the first section.

The fusible section may be annular in shape. Alternatively, the fusible section may extend over at least one corner sector of the first section.

The fusible section may include a plurality of through holes. The through holes may be regularly distributed on the fusible sections about the axis.

The shape of the or each through hole may be circular or elliptical.

The or each through-hole may be defined as:

[ mathematical formula 1]

Wherein R is_OTextIs the outer radial distance, R, between the through hole and the axis_OTintIs the inner radial distance between the through hole and the axis, Kt is the stress concentration coefficient generated by the through hole, R_PSextIs the outer radius between the first section and the axis, and R_PSintIs the inner radius between the first section and the axis.

In particular, a via is a hole adapted to perform a fusible function, the dimensions of which conform to the above equation.

The thickness of the first section, the number and size of the through holes may be calibrated to optimize the oil drainage and fusible function of the first section.

The connection means may comprise a plurality of bellows. Each bellows may include:

-a first section extending longitudinally along the axis and having a diameter greater than the first and second diameters, an

-a second section extending radially with respect to said axis and flanking said first section.

For at least one of the bellows, referred to as the first bellows, a first section of the bellows may include at least one fusible section, the at least one fusible section including at least one through hole and being configured to break when a value of torque applied to the first portion exceeds a predetermined threshold. Through holes adapted to perform a fusible function may also be used as oil drain holes.

For other bellows, referred to as second bellows, the first section of the bellows may comprise at least one oil drain hole. The oil discharge hole is not suitable for exerting the fusible function of the through hole.

In particular, the first section of each bellows may comprise at least one fusible section comprising at least one through hole and configured to break when a value of torque applied to the first portion exceeds a predetermined threshold.

The first portion may comprise a first end portion comprising gear teeth and adapted to be connected to a reduction gearbox, and a second end portion connected to said connecting means.

The second portion may comprise a first end portion comprising splines and adapted to be connected to a second drive shaft, and a second end portion connected to said connecting means.

The invention also relates to an aircraft turbine comprising:

-a drive shaft according to the invention,

-a reduction gearbox connected to said first part, an

-a second drive shaft connected to the second part.

This solution thus makes it possible to ensure the uncoupling function at over-torque, to protect the transmission line in the event of sudden jamming of the reduction gearbox connected to the drive shaft, while being compatible with the flexible zone at the inlet of the reduction gearbox and ensuring the drainage of the oil that may accumulate in the flexible zone.

The invention also relates to a method for protecting a drive shaft of a turbomachine according to the invention from over-torque, comprising the step of breaking the fusible section when the value of the torque applied to the first portion exceeds a predetermined threshold value.

Drawings

The invention will be better understood and other details, features and advantages thereof will become more apparent from the following description, given by way of non-limiting example, with reference to the accompanying drawings, in which:

figure 1 is a schematic view in semi-axial section of a turbomachine according to the invention,

figure 2 is a schematic view in axial section of a part of a turbine according to the invention,

figure 3 is a schematic view in axial section of a drive shaft according to the invention,

figures 4a-4d figures 4a, 4b, 4c and 4d are perspective views of a part of a drive shaft according to an embodiment of the invention,

fig. 5a schematically shows a part of a drive shaft according to section a-a of fig. 4a, an

Fig. 5B schematically shows a part of the drive shaft according to section B-B of fig. 4 c.

Detailed Description

Fig. 1 shows an aircraft turbine 10, such as a turbojet engine with dual flow and dual bodies. The turbine 10 includes, from upstream to downstream, a fan 12, a low pressure compressor 14, a high pressure compressor 16, an annular combustor (not shown), a high pressure turbine (not shown), and a low pressure turbine (not shown) according to the flow direction of the gas flow in the turbine indicated by arrow F.

The rotor of the high-pressure compressor 16 and the rotor of the high-pressure turbine are connected by a high-pressure shaft 18 and form a high-pressure body therewith. Similarly, the rotor of the low-pressure compressor 14 and the rotor of the low-pressure turbine are connected by and form a low-pressure body with a low-pressure shaft 20. The high-pressure shaft 18 and the low-pressure shaft 20 extend along a longitudinal axis a of the turbine 10.

Fan 12 includes blades 22 connected to a fan shaft 24. Fan shaft 24 may be rotatably connected to low pressure shaft 20 by way of a reduction gearbox 26, for example of the epicyclic gear type. The reduction gearbox 26 is coupled to the low pressure shaft 20 by splines driving the planet wheels and to the fan shaft 24 attached to the planet carrier. Typically, the planet wheels, whose rotation axis coincides with the rotation axis of the turbine, drive a series of planet pinions or planet gears, which are evenly distributed around the circumference of the reduction gearbox 26. The planet gears also rotate about the axis of the turbine by meshing with the internal teeth of a ring gear, which is attached to the stator of the turbine. Each of the planet gears is free to rotate about the satellite axis connected to the satellite carrier by a bearing (ball or roller bearing) which may be sliding or have rolling elements. Since the pinions of the planet gears cooperate with the teeth of the ring gear, such that rotation of the planet gears about their planet gear axes causes rotation of the planet carrier about the turbine axis and hence rotation of the fan shaft 24 connected to the planet carrier, which is at a lower rotational speed than the low pressure shaft 20.

The turbine 10 may also include a fan casing (not shown) that extends around the blades 22 and defines an air inlet duct for the gas flow F. One part of this air enters an inner annular flow duct 28, called primary duct, for the primary flow, while another part feeds an outer annular flow duct 30, called secondary duct, for the secondary flow. The main flow conduit 28 passes through the low pressure compressor 14, the high pressure compressor 16, the combustor, and the high and low pressure turbines. The secondary conduit 30 surrounds the compressor casing (not shown) and the turbine casing (not shown) and joins the primary conduit 28 at a nozzle (not shown) of the turbine 10.

The high pressure shaft 18, the low pressure shaft 20, and the fan shaft 24 are centrally located and guided for rotation about axis a by bearings, such as roller bearings. For example, the fan shaft 24 is supported by an upstream bearing 32, here a roller bearing, and a downstream bearing 34, here a ball bearing; the high pressure shaft 18 is supported by an upstream bearing 36, here a ball bearing, and a downstream bearing 38, here a roller bearing; and the low pressure shaft 20 is supported by a bearing 40, here a ball bearing.

FIG. 2 shows a portion of turbine 10 more precisely.

The turbine includes a drive shaft 50 connected at one end to the reduction gearbox 26 and at the other end to the second drive shaft 42. The second drive shaft 42 is connected to the low pressure shaft 20.

The drive shaft 50 extends longitudinally along an axis a. The drive shaft 50 includes a first tubular shaped portion 52 extending longitudinally along axis a and having a first diameter D1, and a second tubular shaped portion 54 extending longitudinally along axis a and having a second diameter D2. Thus, the first portion 52 and the second portion 54 are coaxial. The first diameter D1 may be between 70mm to 250mm, such as between 90mm to 120 mm. The second diameter D2 may be between 70mm and 200mm, for example between 90mm and 120 mm. In particular, the first diameter D1 may be substantially equal to the second diameter D2.

More specifically, fig. 3 shows the drive shaft 50.

Because the first portion 52 has a tubular shape, the first outer diameter D1ext is defined as the outer diameter of the first portion 52, and the first inner diameter D1int is defined as the inner diameter of the first portion 52. The first diameter D1 corresponds to an average value between the first outer diameter D1ext and the first inner diameter D1 int.

According to the invention, the terms "inner" and "outer" are defined with respect to the axis a, the "inner" being radially closer to the axis a and the "outer" being radially further from the axis a.

The thickness E1 of the first portion 52 corresponds to the difference between the first outer diameter D1ext and the first inner diameter D1 int. The thickness E1 may be between 2mm to 6 mm.

The first inner diameter D1int and the first outer diameter D1ext of the first portion 52 may vary along the axis a. In other words, the thickness E1 of the first portion 52 may vary along the axis a.

Similarly, because the second portion 54 is tubular in shape, the second outer diameter D2ext is defined as the outer diameter of the second portion 54, and the second inner diameter D2int is defined as the inner diameter of the second portion 54. The second diameter D2 is an average of the second outer diameter D2ext and the second inner diameter D2 int.

The thickness E2 of the second portion 54 corresponds to the difference between the second outer diameter D2ext and the second inner diameter D2 int. The thickness E2 may be between 2mm to 6 mm.

The second inner diameter D2int and the second outer diameter D2ext of the second portion 54 may vary along the axis a. In other words, the thickness E2 of the second portion 54 may vary along the axis a.

The drive shaft 50 also includes a coupling device 56 that couples the first portion 52 to the second portion 54 and is configured to transfer torque from the second portion 54 to the first portion 52. Specifically, the connection device 56 is configured to transfer the torsional torque from the second portion 54 to the first portion 52. The torsional torque is transferred from the low pressure turbine to the low pressure shaft 20, then to the drive shaft 50, then to the reduction gearbox 26, then to the fan shaft 24, and finally to the blades 22.

First portion 52 may include a first end 58 adapted to be connected to reduction gearbox 26. The first end 58 includes, for example, gear teeth 60. The first portion 52 may include a second end 62 connected to the connection device 56.

The second portion 54 may include a first end 64 adapted to be connected to the second drive shaft 42. The first end portion 64 includes, for example, splines 66. The second portion 54 may include a second end 68 connected to the connection device 56.

In particular, the drive shaft 50 is a unitary piece, i.e., the first portion 52, the second portion 54 and the connecting means 56 are unitary.

The connection means 56 comprise one or more bellows 70. For example, in fig. 2, the connection device 56 includes two bellows 70, while in fig. 3, the connection device 56 includes four bellows 70.

The bellows 70 includes a first section 72 extending longitudinally along the axis a. The first section 72 is annular in shape. Diameter D of first section 72_PSLarger than the first diameter D1 and the second diameter D2. Diameter D_PSMay be at least 1.5 times the first diameter D1 and the second diameter D2. Diameter D_PSMay be between 120mm and 400mm, for example between 140mm and 250 mm.

The bellows 70 enables flexibility to the overall dynamics and misalignment. Flexibility is defined by: the need for global dynamics; the installation of the bellows in the turbine, i.e. the overall dimensions of the bellows; and a method for producing the bellows, i.e. whether the bellows is a one-piece component or is obtained by forming, welding or internal machining of the shaft.

Outer diameter D_PSextIs defined as the outer diameter of the first section 72 and the inner diameter D_PSintIs defined as the inner diameter of the first section 72. Diameter D_PSIs the outer diameter D_PSextAnd an inner diameter D_PSintAverage value of (a).

Inner diameter D_PSintThe ratio with respect to the first inner diameter D1int may be 1 to 4. E.g. inner diameter D_PSintMay be between 1 and 2 times the first inner diameter D1 int.

Thickness E of first segment 72_PSIs the outer diameter D_PSextAnd an inner diameter D_PSintThe difference between them. Thickness E_PSAnd may be between 2mm and 6 mm. Thickness E of first segment 72_PSMay vary along axis a.

Thickness E1 of first portion 52 may be greater than thickness E of first section 72_PS. Thickness E2 of second portion 54 may be greater than thickness E of first section 72_PS。

The thickness is a function of the torque transmitted by the drive shaft and the need for flexibility in the overall dynamics according to the requirements of the turbine.

The bellows 70 also includes a second section 74 extending radially with respect to the axis a and flanking the first section 72. The second section 74 corresponds to a shoulder of the first section 72.

Thickness E of second section 74_DSAnd may be between 2mm and 6 mm. Thickness E of second section 74_DSMay vary radially with respect to axis a.

Thickness E1 of first portion 52 may be greater than thickness E of second section 74_DS. E.g. thickness E_DSMay be between 70% and 80% of the thickness E1.

Thickness E2 of second portion 54 may be greater than thickness E of second section 74_DS. E.g. thickness E_DSMay be between 70% and 80% of the thickness E2.

Thickness E of second section 74_DSMay be greater than the thickness E of the first section 72_PS. E.g. thickness E_PSMay be between the thickness E_DSBetween 70% and 80%. In other words, the thickness E_PSMay be between 49% and 64% of thickness E1 or thickness E2.

Fig. 4a, 4b, 4c and 4d show different embodiments of the bellows 70.

The first section 72 includes at least one fusible section 76. The fusible section 76 is configured to break when the amount of torque applied to the first portion 52 exceeds a predetermined threshold. In other words, the fusible section 76 is configured to separate the first portion 52 from the second portion 54 when an over-torque is applied to the first portion 52.

The predetermined threshold may be between 25000Nm and 100000 Nm.

In particular, the drive shaft 50 is sized to transmit maximum torque during normal operation and to break when an over-torque in the range of 5% to 15% above the rated maximum torque is encountered. For example, over-torque may be caused by a jam in the reduction gearbox 26.

The predetermined threshold depends on the thrust of the turbine, the choice of the reduction ratio of the reduction gearbox 26, the rotation speed of the turbine and the capacity of the fusible section to ensure the transmission of the rated torque is reached, while ensuring the instantaneous breakage at the over-torque value (taking into account the dimensional allowance).

The fusible section 76 may extend over at least one corner sector of the first section 72. In other words, only a portion of the first section 72 may form the fusible section 76. The fusible sections 76 may be formed over a plurality of angular sectors of the first section 72, for example, evenly distributed about the axis a.

As shown in fig. 4a-4d, the fusible section 76 may be annular in shape. In other words, the first section 72 may include a fusible section 76 that completely surrounds the axis a. Thus, the entire first section 72 may form the fusible section 76.

The fusible section 76 includes one or more through holes 78.

The through holes 78 may be formed on the angular sector of the fusible section 76 about the axis a, or may be evenly distributed on the fusible section 76 relative to the axis a.

The shape of the through-hole 78 may be circular or elliptical. For example, in fig. 4a and 4c, the shape of the through-hole 78 is circular, while in fig. 4b and 4d, the shape of the through-hole 78 is elliptical. The oval shape of the through hole enables to reduce the cross section between two consecutive holes without increasing the axial overall dimension requirement, thus optimizing the setting of the sectional torque. Of course, the through-hole 78 may also be polygonal or any other shape.

The through-hole 78 also enables oil that may have accumulated at the first section 72 to be drained.

Optionally, the first section 72 may include a thinned portion 80 having a thickness less than the thickness E of the first section 72_PS. For example, the thickness E of the thinned portion 80_PAMay be between the thickness E of the first section 72_PSBetween 70% and 80%. Thickness E of thinned portion 80_PACan be between 1mm andbetween 5 mm. Thickness E of thinned portion 80_PAMay vary along axis a.

In particular, thinned portion 80 may include fusible section 76. The thinned portion 80 can extend no more than 80% of the length of the first section 72, i.e., no more than 80% of the dimension of the first section 72 along the axis a. Preferably, the thinned portion 80 extends at least 50% of the length of the first section 72. Advantageously, this makes it possible not to weaken the first section 72, while making it possible to have on said first section 72 a fusible section 76 configured to break the drive shaft 50 into two distinct portions when the value of the torque applied to the first portion 52 exceeds a predetermined threshold.

Thinned portion 80 can be formed on at least one corner sector of fusible section 76, and thus on at least one corner sector of first section 72. In other words, only a portion of the fusible section 76 may include the thinned portion 80. Thinned portions 80 may be formed over a plurality of angular sectors of first section 72, for example, evenly distributed about axis a. Thinned portion 80 may be annular. Accordingly, the fusible section 76 may include a thinned portion 80 that completely surrounds the axis a.

Fig. 5a and 5b show different embodiments of the first section 72.

In fig. 5a, the thickness of the first section 72 is constant.

In fig. 5b, the first section 72 includes a thinned portion 80. The inner diameter of the thinned portion 80 is greater than the inner diameter D of the first section 72_PSintAnd the outer diameter of the thinned portion 80 is less than the outer diameter D of the first section 72_PSext. In other words, the first section 72 is thinned from the inside and from the outside with respect to the axis a. Of course, the first section 72 may be thinned only from the inside or from the outside relative to the axis a.

The through-hole 78 may be defined according to the following equation:

[ mathematical formula 2]

Wherein R is_OTextIs a Chinese character' tongThe outer radial distance, R, between the bore 78 and the axis A_OTintIs the inner radial distance between the through-hole 78 and the axis A, Kt is the stress concentration coefficient produced by the through-hole 78, R_PSextIs the outer radius between the first section 72 and the axis A, and R_PSintIs the inner radius between the first section 72 and the axis a.

The outer radial distance refers to the radial distance of the through-hole 78 relative to the axis a at the outside of the fusible section 76, and thus refers to the radial distance of the through-hole 78 furthest from the axis a. The inner radial distance refers to the radial distance of the through-hole 78 relative to the axis a at the inner side of the fusible section 76, and thus refers to the radial distance of the through-hole 78 closest to the axis a.

The coefficient Kt depends on the drive shaft geometry, the number of through holes 78, and the number of through holes 78 in the fusible section 76. As a non-limiting example, the coefficient Kt may be between 1.2 and 5.

The through-hole 78 as defined above may be adapted to perform a fusible function.

In particular, the fusible section 76 is not locally thickened at the through hole 78 from the inside or the outside with respect to the axis a. The fusible section 76 either has a constant thickness or includes thinned portions 80 from the inside and/or outside relative to the axis a. Thus, the thickness of the fusible section 76 does not increase around the through hole 78. This enables the through-hole 78 to be adapted to perform a fusible function.

When the connection means comprises a plurality of bellows 70, as particularly shown in fig. 3, each bellows 70 may comprise a first section 72 and a second section 74.

For at least one of the bellows 70, referred to as a first bellows, the first section 72 of the bellows 70 may include a fusible section 76 that includes one or more through holes 78 and is configured to break when a value of torque applied to the first portion 52 exceeds a predetermined threshold. In other words, at least one of the bellows 70 may include a fusible section 76 on the first section 72 thereof, and thus include at least one through hole 78 adapted to perform a fusible function. In particular, only one of the bellows 70 may include a fusible section 76 having at least one through hole 78 adapted to perform a fusible function on the first section 72 thereof. The through-holes 78 in the first bellows also serve as a drain for the accumulated oil.

For other bellows, referred to as second bellows, the first section 72 of these bellows does not include a fusible section 76, nor a through hole 78 adapted to function as fusible. The second bellows may include one or more oil drain holes configured to drain oil accumulated at the first section of the bellows. These discharge holes are not suitable for exerting the fusible function of the through-hole 78.

Alternatively, the first section 72 of each of the plurality of bellows 70, i.e., the first and second bellows, may include a fusible section 76 that includes at least one through hole 78 and is configured to break when an over-torque is applied to the first portion 52. In other words, all the bellows comprise holes suitable to perform a fusible function, which also enable the drainage of the oil accumulated at the first section of each bellows.

The invention also relates to a method for protecting a drive shaft 50 as described above from excessive torque.

The method includes the step of rupturing the fusible section 76 when the amount of torque applied to the first portion 52 exceeds a predetermined threshold. In other words, the method includes the step of breaking the drive shaft 50 into two separate portions, a first portion 52 and a second portion 54, when an over-torque is applied to the first portion 52 of the drive shaft 50.

Advantageously, this makes it possible to protect the transmission line from high torques applied to one of the elements of the transmission line.