Coupling system for coupling two components of aeronautical turbine engine, preferably coupling two turbine engine shafts

Abstract

The invention relates to a system (20) for coupling two components (22, 24) of an aeronautical turbine engine, comprising a nut (32) for clamping the two components and an anti-rotation ring (38), said anti-rotation ring comprising: a first rotational coupling member (44a) for cooperating with a first complementary rotational coupling member (44b) provided on the first component (22), forming a first rotational coupling means; a second rotary coupling member (46a) for cooperating with a second complementary rotary coupling member (46b) provided on the nut (32), forming a second rotary coupling means. The structural design of the coupling system enables the anti-rotation ring (38) to be first in a temporary axial position relative to the nut and then moved to a final coupling axial position.

Description

Technical Field

[0001] This invention relates to the field of coupling systems for connecting two components of an aircraft turbine engine (e.g., a turbojet engine or a turboprop engine).

[0002] The present invention preferably relates to a connection system for connecting two shafts of an aircraft turbine engine, such as a compressor shaft and a turbine shaft, but the present invention is not limited to this preferred application scenario.

[0003] Another application of the present invention is, for example, connecting a bearing to a turbine engine shaft. Background Technology

[0004] Connection systems for connecting aircraft turbine engine components have been widely developed in the prior art. An example of such a connection system is disclosed in document FR 2858249A1.

[0005] In some turbine engine structures, such a coupling system may include a nut for clamping two components together. This nut is threaded and can engage with the threads on one of the components to be coupled. The coupling system also includes an anti-rotation ring that engages with the nut to limit or prevent rotation of the nut relative to the components.

[0006] The installation of such a connection system typically requires first tightening the nut to its minimum tightness to establish the connection between the two components. Subsequently, just to adjust the device that enables the nut to prevent rotation to the matching position, an additional tightening operation is required on the nut; this operation is known as over-torque.

[0007] Generally, there are two ways to set the anti-rotation device on the shaft: one is to use a groove structure, but this structure requires a large over-torque during assembly; the other is to use a spline structure, but this structure is extremely expensive to manufacture.

[0008] This existing implementation has certain problems. First, applying excessive torque to the nut can generate unnecessary mechanical stress in the assembly. To reduce these stresses, the pitch or precision of the anti-rotation device (such as the spline mentioned above) can be increased, but this approach inevitably increases manufacturing costs.

[0009] Furthermore, existing implementations require a visual operating space during the installation of the connection system. However, this visual operating requirement is often not met within the compact structure of a turbine engine.

[0010] Therefore, the connection systems in the existing technology urgently need improvement. Summary of the Invention

[0011] To meet the above requirements, the primary objective of this invention is to provide a connection system for two components of an aero-turbine engine, the technical features of which are as described in claim 1.

[0012] This design allows the over-torque that may need to be applied to the nut during assembly to be kept at a moderate level, thereby reducing the mechanical stress on the assembly without increasing the pitch or precision of anti-rotation devices such as splines and / or finger-groove assemblies.

[0013] Furthermore, the design of this invention has a significant advantage: it supports blind installation of the connection system, meaning that installation can be completed without visually inspecting the mounting area within the turbine engine. This is particularly common when connecting large-diameter components (such as turbine engine shafts), making this invention highly suitable for such scenarios.

[0014] The present invention preferably includes any one or more of the following optional technical features.

[0015] Preferably, the first rotary coupling device comprises (and is preferably composed of) one or more finger-shaped protrusion-groove assemblies, the number of which is preferably less than six, more preferably less than four. The finger-shaped protrusion-groove assemblies prevent the first turbine engine component from rotating relative to the anti-rotation ring. Reducing the number of these assemblies significantly lowers manufacturing costs compared to spline couplings; however, the invention does not preclude the possibility of using spline couplings.

[0016] Preferably, the second rotary coupling device is composed of a spline, and the anti-rotation function of the nut is achieved through an anti-rotation ring. Compared to components to be coupled, such as turbine engine shafts, it is more cost-effective to manufacture spline structures on these components.

[0017] In this embodiment, during assembly, the finger-shaped protrusion-groove assembly constituting the first connecting device is engaged first, and then the spline constituting the second connecting device is adjusted to a matching position before engagement. Since the pitch of the spline is smaller than the pitch of the groove, the angle at which the nut needs to be rotated to achieve the desired matching position of the spline, and the possible over-torque resulting therefrom, can be kept at a favorablely small level.

[0018] Preferably, when the anti-rotation ring is in a temporary axial position, a circumferential gap is formed between the first connecting member and the first complementary connecting member. Utilizing this gap, the anti-rotation ring can generate sufficient angular displacement to allow the second connecting member to align with the second complementary connecting member in the circumferential direction. This aligned position allows the anti-rotation ring to move axially from the temporary axial position to the final connected axial position.

[0019] In this solution, the aforementioned gap allows the second connector to be positioned to match the second complementary connector, where applicable. Therefore, the advantage of this design is that installation of the connection system can be completed without applying excessive torque to the nut.

[0020] It is worth noting that in the alternative solution of eliminating gaps, a moderate overtorque may need to be applied to the nut to complete the installation. Alternatively, a hybrid approach can be used, where eliminating gaps and applying overtorque to the nut are both necessary to complete the installation of the connection system, and the intensity of this overtorque can be further reduced.

[0021] Preferably, the connection system includes a resilient reset device disposed between the nut and the anti-rotation ring, for pushing the anti-rotation ring axially to the final connection axial position. This design is particularly suitable for scenarios where the installation area cannot be visually observed, and can automatically achieve the required axial movement of the anti-rotation ring. Preferably, the resilient reset device can also be used to hold the anti-rotation ring in the final installation position; of course, other components can also be used to achieve this function, which does not exceed the scope of protection of this invention.

[0022] Preferably, both the first connecting member and the first complementary connecting member are provided with inclined circumferential stop surfaces, which form a certain angle with the axial direction. This design allows a circumferential gap to be formed between the first connecting member and the first complementary connecting member when the anti-rotation ring is in the intermediate axial position. Then, when the second connecting member and the second complementary connecting member are in a matching position (e.g., by partially eliminating the circumferential gap), the elastic reset device can push the anti-rotation ring axially until it reaches the final connection position, at which point the inclined circumferential stop surfaces are in contact with each other.

[0023] Preferably, the nut and the anti-rotation ring are concentrically arranged, with the anti-rotation ring embedded inside the nut.

[0024] Another object of the present invention is to provide an aircraft turbine engine assembly comprising two components and the aforementioned coupling system for connecting the two components, wherein the two components are preferably two turbine engine shafts. Of course, this assembly can also be used in other scenarios, which does not exceed the scope of protection of the present invention.

[0025] Another object of the present invention is to provide an aircraft turbine engine that includes at least one of the above-described components. For example, the engine may be a turbojet engine or a turboprop engine.

[0026] Finally, the present invention also provides a method for installing the above-mentioned coupling system on two components of an aero-turbine engine to be coupled, the method comprising the following steps:

[0027] 1. Tighten the nut onto the first component by threading it onto the first component, thereby axially pressing the first component and the second component together;

[0028] 2. Adjust the anti-rotation ring to a temporary axial position relative to the nut, so that the first rotary coupling device is in the connected state, while keeping the second rotary coupling device in the unconnected state;

[0029] 3. After the anti-rotation ring rotates relative to the nut, move it from the temporary axial position to the final connection axial position, so that the second rotary connection device enters the connection state, while keeping the first rotary connection device in the connection state.

[0030] Other advantages and features of the present invention will be further set forth in the following non-limiting detailed description. Attached Figure Description

[0031] [Figure 1] is a longitudinal sectional view of a turbojet engine;

[0032] [Figure 2] is Figure 1 A longitudinal half-sectional view of the connection system between two components in the turbojet engine shown.

[0033] [Figure 3] is a cross-sectional view of the connection system shown in Figure 2, corresponding to section III-III in Figure 2;

[0034] [Figure 4] is a partial perspective view of the clamping nut in the connection system shown in Figures 2 and 3;

[0035] [Figure 5] is a partial perspective view of the anti-rotation ring in the connection system shown in Figures 2 and 3;

[0036] [Figure 6] is a partial perspective view of the anti-rotation ring in another embodiment;

[0037] [Figure 7] is a partial perspective view of the end of the turbine engine shaft to be connected by the connection system shown in Figures 2 and 3;

[0038] [Figure 8] is a partial perspective view of the connection system shown in Figures 2 and 3;

[0039] [Figure 9] - [Figure 10], [Figure 12] are Figure 2 The connection system shown is a longitudinal half-sectional view at different consecutive stages during the installation process.

[0040] [Figure 11] is a transverse sectional view of the connection system shown in Figure 10, corresponding to section XI-XI in Figure 10;

[0041] [Figure 13] - [Figure 14] are cross-sectional views of the connection system shown in the foregoing figures at different stages of the installation method in an alternative embodiment;

[0042] [Figure 15] is a longitudinal half-sectional view similar to the connection system shown in the foregoing figures, representing another alternative embodiment;

[0043] [Figure 16] - [Figure 19] are partial cross-sectional views of the connection system at different stages of installation in another alternative embodiment;

[0044] [Figure 20] is a partial perspective view of a locking system for locking a plug onto a component of a turbojet engine, which is integrated into the connection system shown in the aforementioned figures;

[0045] [Figure 21] is an axial view of the plug shown in Figure 20;

[0046] [Figure 22] - [Figure 24] are partial perspective views of the locking system shown in Figure 20 at different stages of the installation process;

[0047] [Figure 25] is a partial cross-sectional view of the locking system in the state shown in Figure 23;

[0048] [Figure 26] is a partial cross-sectional view of the locking system in the state shown in Figure 24;

[0049] [Figure 27] is a partial cross-sectional view of the locking system after installation is complete. Detailed Implementation

[0050] Referring first to Figure 1, which illustrates an aero-turbine engine 1 according to a preferred embodiment of the present invention, this embodiment being a dual-rotor turbofan engine. Of course, the present invention can also be applied to other types of turbine engines, such as turboprop engines, without exceeding the scope of protection of the present invention.

[0051] The turbine engine 1 has an axis X around which its various components extend; this axis is referred to as the longitudinal axis of the turbine engine. Along the main flow direction 5 of the gas within the turbine engine, from upstream to downstream, are arranged a fan 3, a low-pressure compressor 4, a high-pressure compressor 6, a combustion chamber 11, a high-pressure turbine 7, and a low-pressure turbine 8.

[0052] Normally, after the air flows through the fan, it is divided into the main airflow 12a located in the center and the bypass airflow 12b surrounding it. The main airflow 12a flows through the main gas circulation passage 14a that runs through the compressors 4 and 6, the combustion chamber 11 and the turbines 7 and 8; as for the bypass airflow 12b, it flows through the bypass passage 14b that is radially fixed to the outside of the engine casing and is surrounded by the nacelle 9.

[0053] Figures 2-8 illustrate a coupling system 20 for connecting two rotating components of a turbojet engine 1. These two components are coaxial (both with the X-axis as their axis of rotation). In this embodiment, the two components are a first shaft 22 (corresponding to the low-pressure turbine shaft) and a second shaft 24 (corresponding to the low-pressure compressor shaft). Both shafts 22 and 24 are hollow structures. The upstream end of the first shaft 22 is inserted into the downstream end of the second shaft 24, achieving synchronous connection of axial translation and rotation through the coupling system 20. The two shafts 22 and 24 are coaxial and centered on the X-axis, forming a component 30 together with the coupling system 20. Multiple such components can be provided in a turbojet engine. The components to be connected can belong to different modules of the turbojet engine, including fans, compressors, combustion chambers, or turbines.

[0054] This invention is particularly suitable for connecting large-diameter components, where the connection area is often poorly visible or even completely inaccessible. Figure 2 illustrates this situation, showing the connection system 20 in its fully installed state, with the two shafts 22 and 24 already connected.

[0055] The connecting system 20 first includes a nut 32 for clamping the two shafts. This nut, centered at X, has a first thread 34a (i.e., nut thread) that mates with a second thread 34b (i.e., first component thread) on the outer surface of the first shaft 22. As shown in Figures 2 and 8, when the connecting system 20 is installed, the downstream end of the nut 32 applies an axial force to the second shaft 24 (specifically, its internal shoulder). This axial force pushes the second shaft 24 downstream, causing it to fit tightly against the external shoulder of the first shaft 22, as shown in Figure 2. An axial washer 36 is optionally placed between the two shaft shoulders. The axial tightening force of the nut must be sufficient to achieve a stable and reliable connection between the two shafts 22 and 24.

[0056] The coupling system 20 also includes an anti-rotation ring 38 for limiting or preventing the nut 32 from rotating relative to the first shaft 22 after the coupling system 20 is installed in place.

[0057] The anti-rotation ring 38 is at least partially embedded inside the nut 32 with X as its center, and is movable relative to the nut between different axial positions. (See attached...) Figure 2 and 8 In the indicated state, the anti-rotation ring 38 is in its downstream position relative to the nut 32, which corresponds to the final engagement state of the shaft connection. The anti-rotation ring 38 is fixed by the engagement of its carrying ring 40 (or similar limiting element) with the corresponding groove 42a, which is machined on the upstream side of the first thread 34a on the inner surface of the nut 32.

[0058] When the anti-rotation ring 38 is in the final connected position, the anti-rotation ring can be axially fixed relative to the nut 32 by means of the ring 40 or other translational stop system that matches the anti-rotation ring. In this position, both the first rotary coupling device and the second rotary coupling device are in an effective connected state.

[0059] The first rotary coupling device comprises a first rotary coupling member 44a disposed at the downstream end of the anti-rotation ring 38 and a first complementary rotary coupling member 44b disposed at the upstream end of the first shaft 22. In this embodiment, the device is preferably a finger-shaped protrusion-groove assembly, with the finger-shaped protrusion 44a preferably disposed on the anti-rotation ring 38 and the groove 44b disposed on the first shaft 22; however, the reverse arrangement can also be used. This groove 44b is also referred to as the first groove 44b.

[0060] The number of finger-shaped protrusion-groove components is preferably less than four, for example, three, or two as shown in the figure. When the number of components is two, the two finger-shaped protrusions 44a are preferably distributed with opposite diameters, and the grooves 44b corresponding to the upstream end of the first shaft 22 are also distributed with opposite diameters, and the grooves open axially upstream.

[0061] As shown in Figures 2, 5 and 8, the finger-shaped protrusion 44a located at the downstream end of the anti-rotation ring 38 extends both axially downstream and radially inward; or as shown in Figure 6, the alternative extends only axially downstream.

[0062] The second rotary coupling device consists of a second rotary coupling member 46a disposed on the outer surface of the anti-rotation ring 38 and a second complementary rotary coupling member 46b disposed on the inner surface of the nut 32. In this embodiment, the device is preferably composed of mutually mating splines 46a and 46b, specifically two concentric annular splines. Each annular spline 46a and 46b can be a complete 360° ring, or it can only cover corner segments less than 360°, or it can be composed of multiple circumferentially spaced corner segments. The number of teeth in each spline is relatively large, for example, more than twenty, thirty, or forty. The number of teeth in the two splines is preferably the same, and the number of teeth is strictly more than the number of grooves and finger-like protrusions.

[0063] Each spline has a conventional toothed structure and extends radially. Specifically, spline 46a extends radially outward and spline 46b extends radially inward.

[0064] A significant feature of this invention is that the first spline 46a is located upstream of the finger-like protrusion 44a, and the two are axially offset from each other. Preferably, the spline 46a and the finger-like protrusion 44a have no overlapping area in the axial direction.

[0065] Figures 9-12 show in detail the installation steps of the coupling system 20 on the two shafts 22 and 24.

[0066] The first step involves installing the connecting system 20 onto the first shaft 22, with the nut 32 fitted onto the upstream end of the shaft. The nut 32 is then tightened using the first thread 34a and the second thread 34b. The purpose of tightening is to apply force to the second shaft 24 via the downstream end of the nut, axially pressing the first shaft 22 and the second shaft 24 together. The tightening torque applied to the nut 32 must reach the minimum torque value required to ensure a stable connection between the two shafts. This step is illustrated in Figure 9. During this process, the anti-rotation ring 38 remains in the upstream non-working position (i.e., the non-connected position). The anti-rotation ring is axially fixed relative to the nut 32 by the engagement of the retaining ring 40 with another groove 42b on the inner surface of the nut (located upstream of groove 42a).

[0067] The second step, as shown in Figures 10 and 11, involves rotating the anti-rotation ring 38 about axis X relative to the fixed nut 32 while simultaneously translating it downstream. The purpose of rotating the anti-rotation ring is to align the finger-shaped protrusion 44a with the groove 44b, and then axially inserting the finger-shaped protrusion into the same groove. This axial movement brings the anti-rotation ring 38 to a temporary axial position relative to the nut, at which point the first rotary coupling devices 44a and 44b are engaged. However, due to the misalignment of splines 46a and 46b (as shown in Figure 11, the tooth gaps between the first spline 46a and the other ring of the second spline 46b are not aligned, and vice versa), the axial movement of the anti-rotation ring 38 is typically hindered at this point. Therefore, when the anti-rotation ring 38 is in the temporary axial position, the second rotary coupling devices 46a and 46b remain in a non-engaged state.

[0068] In this step, rotational and translational forces can be applied to the anti-rotation ring 38 simultaneously, which is especially suitable for blind installation scenarios where it is not possible to directly observe inside a turbojet engine.

[0069] To achieve a matching position for splines 46a and 46b, as shown in Figure 3, nut 32 needs to be tightened again relative to the second shaft 22. Apply a moderate overtorque to the nut until splines 46a and 46b are properly matched. The steps for applying overtorque to nut 32 are shown in Figure 12.

[0070] Because the pitch of the spline is smaller than that of the groove, the nut needs to be turned to achieve the desired matching position between the splines, and the resulting over-torque can be kept at a small, favorable level.

[0071] Subsequently, the anti-rotation ring 38 is moved axially relative to the nut 32 again, from the temporary axial position to the final connection axial position, so that splines 46a and 46b are mated and connected, as shown in Figure 2. Similarly, especially in the blind assembly scenario of turbojet engines, the rotation of the nut 32 and the translation of the anti-rotation ring 38 can be performed simultaneously.

[0072] After this step is completed, the second rotary coupling devices 46a and 46b enter the coupling state due to the spline engagement. At the same time, as the anti-rotation ring 38 moves further axially relative to the nut 32, the finger-shaped protrusion 44a further inserts into the corresponding groove 44b, and the first rotary coupling devices 44a and 44b remain in the coupling state.

[0073] During movement, the retaining ring 40 engages with the groove 42a to axially lock the anti-rotation ring 38. This ensures the entire connection system 20 remains stably in the installed state, guaranteeing reliable connection of the two shafts 22 and 24 in both translational and rotational directions, and preventing the nut 32 from loosening.

[0074] Figures 13 and 14 illustrate an alternative implementation, the advantage of which is that the installation of the coupling system 20 can be completed without applying over-torque to the nut.

[0075] This alternative has many of the same technical features as the embodiments shown in Figures 2-12, and the parts with the same numbers in the figures represent the same or similar structures.

[0076] In the alternative shown in Figures 13 and 14, when the anti-rotation ring 38 is in a temporary axial position, there is a circumferential gap 48 between each finger protrusion 44a and its corresponding groove 44b. By partially or completely eliminating this gap 48, sufficient angular displacement can be generated between the anti-rotation ring 38 and the fixed nut 32, thereby achieving a matching position of the splines 46a, 46b in the circumferential direction. After this operation, the state of the coupling system 20 is shown in Figure 14. It should be noted that the circumferential direction extending around the X-axis is consistent with the tangential direction.

[0077] As mentioned earlier, after splines 46a and 46b are positioned to match, the anti-rotation ring 38 can be moved axially from the temporary axial position to the final connection axial position.

[0078] It is worth noting that a hybrid approach can also be adopted, which involves rotating the anti-rotation ring 38 to eliminate the aforementioned gap 48, while simultaneously applying a slight over-torque to the nut 32 to achieve the matching positions of splines 46a and 46b.

[0079] Figure 15 illustrates an alternative embodiment in which an elastic reset device is provided, for example, one or more springs 50 are axially disposed between the nut 32 and the anti-rotation ring 38. The springs 50 can push the anti-rotation ring 38 axially downstream relative to the nut 32, providing the necessary axial force for the anti-rotation ring 38 to move from its upstream position to a temporary axial position, and then from the temporary axial position to its final connected axial position.

[0080] This design also keeps the anti-rotation ring 38 stably in the final connection axial position, thus eliminating the need for an anti-rotation ring stop component.

[0081] Figures 16-19 illustrate the state of the connection system 20 at different installation stages in another alternative embodiment, in which each finger-shaped protrusion 44a and its corresponding groove 44b are provided with an inclined circumferential stop surface, which forms an angle with the axial direction. That is, both stop surfaces 52a and 52b form a non-zero angle with the axial direction parallel to the axis X.

[0082] Figure 16 shows the inclined circumferential stop surfaces 52a and 52b. They are parallel or substantially parallel to each other, and are the side surface 68 of the finger-shaped protrusion 44a and the groove 44b, respectively. The circumferential stop surface 52b of the groove 44b is inclined, causing it to expand circumferentially in the axial upstream direction; conversely, the circumferential stop surface 52a of the finger-shaped protrusion 44a is inclined, causing it to contract circumferentially in the axial downstream direction.

[0083] The state shown in Figure 16 corresponds to that in Figure 9, where the finger-shaped protrusion 44a is not yet aligned with the corresponding groove 44b. When the operator or spring 50 drives the anti-rotation ring 38 to rotate and achieve the aligned position, the finger-shaped protrusion 44a will partially insert into the groove 44b, as shown in Figure 17. The axial insertion operation stops here due to the obstruction between the splines. Subsequently, the circumferential gap 48 between the inclined circumferential stop surfaces 52a and 52b can be partially or completely eliminated by rotating the anti-rotation ring 38, allowing the same splines to achieve the aligned position (this aligned position is not shown in Figures 16-19), as shown in Figure 18. After the splines achieve the aligned position, the anti-rotation ring 38 moves axially to the final connected axial position under the action of spring 50. As shown in Figure 19, the anti-rotation ring 38 reaches the position when the circumferential stop surfaces 52a and 52b are in contact (preferably surface contact).

[0084] Because the contact surfaces 52a and 52b are inclined, the finger-shaped protrusions 44a that stop on the side of the groove 44b exert an inclined force on the shaft 22, which includes a circumferential component. The direction of this circumferential component can drive the second shaft 22 to rotate, thereby further tightening the nut 38 relative to the shaft.

[0085] The assembly 30 shown in Figure 20 includes not only the coupling system 20 for connecting the two shafts 22 and 24, but also a locking system 120 for locking the plug 60 onto the first shaft 22. The plug 60 is mounted on the upstream end of the first shaft 22, located at or near the first rotary couplings 44a and 44b. The plug 60 is used to seal the X-centered hollow cavity 66 inside the first shaft 22. The plug 60 needs to withstand significant loads, especially pressure loads, therefore the locking system 120 must be able to withstand these loads.

[0086] In the embodiment shown in Figure 20, the locking system 120 for locking the plug 60 and the connecting system 20 for connecting the two shafts are combined in the assembly 30. The two share some components, making the overall structure more compact and effectively reducing the weight and manufacturing cost of the assembly.

[0087] Referring again to Figure 20, the locking system 120 includes the aforementioned anti-rotation ring 38, which here additionally functions as a locking plug 60. Therefore, in the following description, the anti-rotation ring 38 is also referred to as a locking ring.

[0088] As previously described, the locking ring 38 is provided with a protruding component consisting of finger-shaped protrusions 44a. When the locking ring 38 is in the aforementioned final connection axial position (i.e., the locked position), the finger-shaped protrusions 44a are respectively embedded in the first groove of the first shaft 22 (i.e., the aforementioned first groove 44b). Of course, the protruding component 44a and the first groove 44b may also adopt other shapes, which does not exceed the protection scope of the present invention.

[0089] A notable feature of this embodiment is that the plug 60 has one or more fixed finger-like protrusions 62, the number of which preferably matches the number of the first grooves 44b, and their distribution positions correspond to each other. Therefore, the plug body 64 has two fixed finger-like protrusions 62 with opposite diameters. The outer diameter of the plug body 64 is approximately equal to the inner diameter of the hollow cavity 66 in the shaft 22, preferably maintaining a small installation gap during assembly. Furthermore, the fixed finger-like protrusions 62 extend radially outward from the plug body 64.

[0090] Each fixed finger-like protrusion 62 is inserted into a second groove of the first shaft 22, the second groove being in the form of a second groove 144b, which opens circumferentially within the first groove 44b. The size of each second groove 144b is much smaller than that of the first groove 44b in which its opening is located, for example, it may be simply a circumferential indentation structure.

[0091] More precisely, each second circumferential groove 144b is machined on one of the two sides 68 of the first groove 44b through which it opens. Figure 20 In the preferred embodiment shown, each second circumferential groove 144b ( Figure 20 Only one of the two grooves 144b is visible in the middle, both of which are formed at the axial bottom of their associated first groove 44b.

[0092] Therefore, when the locking ring 38 is in the locked position at the upstream end of the first shaft 22, each finger protrusion 44a at least partially covers a second groove 144b that receives the plug-fixing finger protrusion 62 in the circumferential direction. More precisely, each finger protrusion 44a covers the bottom of the second groove 144b that receives the fixing finger protrusion 62 in the circumferential direction.

[0093] Through this overlapping structure, each finger-like protrusion 44a is accompanied by a second groove 144b in the circumferential direction, but the two elements do not need to contact each other. If a circumferential gap exists, its value is preferably kept small enough to prevent the fixed finger-like protrusion 62 from completely dislodging from the second groove 144b.

[0094] Figure 21 The image shown is an axial view of plug 60, and its installation method will be combined with... Figures 22 to 27 Please provide an explanation.

[0095] The first step, as shown in Figures 22, 23 and 25, is to insert the plug 60 axially into the hollow cavity 66 of the first shaft 22, so that each fixed finger-shaped protrusion 62 of the plug is inserted axially downstream into the corresponding first groove 44b of the first shaft 22 until it reaches the axial bottom of the groove.

[0096] The second step involves rotating the plug 60 about its central axis X, causing each fixed finger-like protrusion 62 to engage with its corresponding second groove 144b. Because the second groove 144b is shallow, the rotation angle of the plug remains moderate. Figures 24 and 26 show the locking system 120 after this step.

[0097] The final step, as shown in Figure 27, involves axially moving the locking ring 38 to the locked position. This causes each finger-shaped protrusion 44a to be inserted into the corresponding first groove 44b of the first shaft 22, until the finger-shaped protrusion 44a at least partially covers the second groove 144b that accommodates the fixed finger-shaped protrusion 62 in the circumferential direction.

[0098] Various modifications can be made to this invention by those skilled in the art; these modifications are merely non-limiting examples, and the scope of protection of this invention is defined by the appended claims. In particular, technical features in different embodiments and their alternatives can be substituted for and / or combined with each other.

Claims

1. A connection system (20) for connecting two components (22, 24) of an aircraft turbine engine, comprising a nut (32) for clamping the two components (22, 24) together, the nut (32) having a nut thread (34a) for engaging with a first component thread (34b) provided on a first component (22) of the two components (22, 24); further comprising an anti-rotation ring (38) for limiting or preventing rotation of the nut (32) relative to the first component (22), characterized in that, The anti-rotation ring (38) includes: The first rotary connecting member (44a) is used to cooperate with the first complementary rotary connecting member (44b) disposed on the first component (22) to form a first rotary connecting device; The second rotary connecting member (46a) is used to cooperate with the second complementary rotary connecting member (46b) provided on the nut (32) to form a second rotary connecting device; The connection system is configured such that the anti-rotation loop (38) is capable of: At a temporary axial position relative to the nut (32), the first rotary coupling device (44a, 44b) is in a connected state, and the second rotary coupling device (46a, 46b) is in a non-connected state. After the anti-rotation ring (38) rotates relative to the nut (32), it moves from the temporary axial position to the final connection axial position. At this time, the second rotary connection device (46a, 46b) is in the connection state, and the first rotary connection device (44a, 44b) remains in the connection state.

2. The connection system according to claim 1, characterized in that, The first rotary coupling device (44a, 44b) includes one or more finger-shaped protrusion-groove assemblies, preferably fewer than six, more preferably fewer than four.

3. The connection system according to claim 1 or 2, characterized in that, The second rotary coupling device (46a, 46b) is composed of splines.

4. The connection system according to any one of the preceding claims, characterized in that, When the anti-rotation ring (38) is in a temporary axial position, a circumferential gap (48) is formed between the first connecting member (44a) and the first complementary connecting member (44b). By eliminating this gap, the anti-rotation ring (38) can generate sufficient angular displacement to match the second connecting member (46a) with the second complementary connecting member (46b) in the circumferential direction. This matching position allows the anti-rotation ring (38) to move axially from the temporary axial position to the final connecting axial position.

5. The connection system according to any one of the preceding claims, characterized in that, It includes an elastic reset device (50) disposed between the nut (32) and the anti-rotation ring (38) for pushing the anti-rotation ring (38) axially to the final connection axial position.

6. The connection system according to any one of the preceding claims, characterized in that, Both the first connecting member (44a) and the first complementary connecting member (44b) are provided with inclined circumferential stop surfaces (52a, 52b), which are at a certain angle to the axial direction.

7. The connection system according to any one of the preceding claims, characterized in that, The nut (32) and the anti-rotation ring (38) are concentrically arranged, and the anti-rotation ring (38) is embedded inside the nut (32).

8. An aircraft turbine engine assembly (30) comprising two components (22, 24) and a coupling system (20) according to any one of the preceding claims, the coupling system (20) being used to connect the two components (22, 24), wherein the two components are two turbine engine shafts.

9. An aircraft turbine engine (1) comprising at least one component (30) according to claim 8.

10. A method for installing the coupling system (20) according to any one of claims 1-7 on two components (22, 24) of an aircraft turbine engine to be coupled, characterized in that, Includes the following steps: By tightening the nut (32) onto the first component (22) through the nut thread and the first component thread (34a, 34b), the first component (22) and the second component (24) are axially pressed together; Adjust the anti-rotation ring (38) to a temporary axial position relative to the nut (32) so that the first rotary coupling device (44a, 44b) is in the connected state, while keeping the second rotary coupling device (46a, 46b) in the unconnected state. After the anti-rotation ring (38) rotates relative to the nut (32), the anti-rotation ring (38) is moved relative to the nut (32) from the temporary axial position to the final connection axial position, so that the second rotary connection device (46a, 46b) enters the connection state, while keeping the first rotary connection device (44a, 44b) in the connection state.

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