System and method for balancing a test bench turbine

Abstract

Balancing system (1) for a turbine (7) on a test bench of a turbomachine, the system comprising: - a transmitter (5) configured to rotate the turbine (7) about a downstream axis (10), - a motor (3) configured to rotate the transmitter (5) about an upstream axis (9), the terms upstream and downstream being defined relative to the transmitter (5) and a direction of transmission of the rotational movement, the transmitter (5) comprising a device (15) for adjusting a gap between the downstream axis (10) and the upstream axis (9). Figure to be published for the abstract: Figure 1

Description

Title of the invention: System and method for balancing a test bench turbine DOMAIN

[0001] The invention relates to the balancing of a test bench turbine, in particular a turbomachine test bench. STATE OF THE ART

[0002] When testing a new turbomachine, it is necessary to carry out tests on its turbine. A test campaign for a new turbomachine generally involves working on a set of several turbine configurations (seven or eight configurations for example). Each configuration corresponds to a technical design option and the aim is to identify the one that is the most efficient, the most cost-effective, or the most satisfactory in relation to a particular technical objection. All these configurations are tested on a test bench where the turbine is rotated by a drive system (or pivot of the test bench) itself rotated by a motor. For each turbine configuration, the 'drive system + turbine' assembly must be balanced. This requires the disassembly of the drive system from the test bench. This disassembly generates a significant loss of time in the progress of the tests.There is a need to perform the balancing of the 'drive system + turbine' assembly more quickly without having to dismantle the pivot assembly from the test bench. EXPOSED

[0003] An aim of the present disclosure is to propose a system for balancing a test bench turbine allowing faster balancing of the 'drive system + turbine' assembly than in the prior art.

[0004] The aim is achieved by means of a system for balancing a test bench turbine of a turbomachine, the system comprising:

[0005] - a transmitter configured to rotate the turbine around a downstream axis,

[0006] - a motor configured to rotate the transmitter around an upstream axis,

[0007] the terms upstream and downstream being defined with respect to the transmitter and a direction of transmission of the rotational movement, the transmitter comprising a device for adjusting a gap between the downstream axis and the upstream axis.

[0008] Such a system is advantageously and optionally supplemented by the following different characteristics taken alone or in combination:

[0009] - the transmitter comprises an upstream relay configured to be driven by the motor around the upstream axis, a downstream relay configured to be driven by the upstream relay around the downstream axis and configured to rotate the turbine, the adjustment device comprising a conveyor configured to adjust a position transverse to the upstream axis of a ring of the downstream relay relative to the upstream relay, the ring extending around the downstream axis, the conveyor advantageously comprising micrometric screws;

[0010] - the adjustment device comprises a mechanism separate from the conveyor, the mechanism being configured to allow the introduction of a degree of freedom between the downstream relay and the upstream relay;

[0011] - the conveyor is a first conveyor, the ring being a first ring, the mechanism being a second conveyor configured to adjust a position transverse to the upstream axis of a second ring of the downstream relay relative to the upstream relay, the second ring extending around the downstream axis, the second conveyor advantageously comprising micrometric screws;

[0012] - the mechanism is configured to allow movement transverse to the upstream axis of a second ring of the downstream relay relative to the upstream relay, the second ring extending around the downstream axis;

[0013] - the first ring and the second ring are configured to move identical manner compared to the upstream relay;

[0014] - the ring is a first ring, the mechanism being configured to allow a rotation of a second ring of the downstream relay relative to the upstream relay around any direction orthogonal to the upstream axis, the second ring extending around the downstream axis, the upstream axis passing through a center of the second ring;

[0015] - the first ring is located between the motor and the second ring; and

[0016] - the second ring is located between the motor and the first ring.

[0017] The disclosure also relates to a method for balancing a test bench turbine in which, in the presence of a transmitter configured to rotate the turbine around a downstream axis and a motor configured to rotate the transmitter around an upstream axis, a gap between the downstream axis and the upstream axis is adjusted.

[0018] Finally, the disclosure relates to a method for testing a plurality of turbines on a test bench, the test bench comprising a drive system configured to rotate each turbine around an axis of rotation, the method comprising the following steps:

[0019] - (E3) determination of a gap between the rotation axis and a positioning axis of a first turbine in the drive system,

[0020] - (E5) dynamic balancing of a first assembly composed of the first turbine and the drive system, dynamic balancing being achieved by adjusting a mass distribution in the first turbine,

[0021] - (E6) determination of an unbalance vector of the first set,

[0022] - (E7) modification of the balancing system as it has been presented previously respectively so as to adjust the gap between the downstream axis and the upstream axis of the balancing system equal to the gap between the rotation axis and the positioning axis of the first turbine in the drive system,

[0023] - (E9) adjustment of a mass distribution in the balancing system so as to setting an unbalance vector of a second assembly composed of the first turbine and the balancing system equal to the unbalance vector of the first assembly,

[0024] - (E10) dynamic balancing of a third assembly composed of a second turbine and the balancing system, dynamic balancing being achieved by adjusting a mass distribution in the second turbine. DESCRIPTION OF FIGURES

[0025] Other characteristics and advantages will emerge from the following description, which is purely illustrative and non-limiting, and must be read in conjunction with the attached drawings in which:

[0026] [Fig.l] is a schematic representation of a turbine balancing system;

[0027] [Fig.2], [Fig.3], [Fig.4] and [Fig.5] schematically illustrate part of a balancing system; and

[0028] [Fig.6] illustrates a method of testing a turbine on a test bench. DETAILED DESCRIPTION OF THE INVENTION Balancing system

[0029] In relation to [Fig.l], a balancing system 1 of a turbine 7 of a test bench of a turbomachine is presented.

[0030] The balancing system 1 comprises a motor 3 which drives a shaft 4 in rotation. The shaft 4 rotates around a first axis, called the upstream axis 9.

[0031] We can define planes transverse to the upstream axis and two directions y and z perpendicular to each other and perpendicular to the upstream axis. A transverse plane is parallel to the two directions y and z. We can define a direction x parallel to the upstream axis 9 so that the directions x, y and z form a direct trihedron.

[0032] The balancing system 1 comprises a transmitter 5 which is on the one hand driven in rotation by the shaft 4 and which on the other hand drives the turbine 7 in rotation. The turbine 7 is driven in rotation around a second axis, called the downstream axis 10.

[0033] The upstream axis 9 and the downstream axis 10 are close but are not necessarily identical.

[0034] The terms 'upstream' and 'downstream' are defined here in relation to the transmitter 5 and in relation to a direction of transmission of the movement from the engine 3 to the turbine 7.

[0035] The transmitter 5 comprises a device 15 for adjusting a gap between the upstream axis 9 and the downstream axis 10.

[0036] The gap between the upstream axis 9 and the downstream axis 10 may be a distance gap, that is to say that the upstream axis 9 and the downstream axis 10 are parallel to each other but they do not intersect. This distance gap may be characterized by the non-zero distance in a transverse plane between the upstream axis 9 and the downstream axis 10, or more precisely between the projections of these axes in the transverse plane.

[0037] The difference between the upstream axis 9 and the downstream axis 10 may be an angle difference, that is to say that the upstream axis 9 and the downstream axis 10 intersect at a point of intersection and that there is a non-zero angle between the axes. This non-zero angle may be characterized in a reference frame centered on the point of intersection by two components. On the one hand, there is a longitudinal component which is the angular difference between the upstream axis 9 and the downstream axis 10. On the other hand, there is a transverse component which is the angular difference between a transverse reference axis, for example an axis parallel to the direction y, passing through the point of intersection and the projection of the downstream axis 10 in the transverse plane.

[0038] Finally, the gap between the upstream axis 9 and the downstream axis 10 may be a combination of an angle gap and a distance gap, that is to say that on the one hand the upstream axis 9 and the downstream axis 10 are not parallel to each other and on the other hand they do not intersect. This gap may be characterized by a distance gap and an angle gap. The distance gap may be chosen as the smallest distance measured in a transverse plane between the upstream axis 9 and the downstream axis 10, or more precisely between the projections of these axes in the transverse plane. The angle gap may be characterized as follows: a virtual translation of the downstream axis is carried out towards the upstream axis so as to obtain a virtual downstream axis. The virtual downstream axis is parallel to the downstream axis. The translation corresponds to a translation in the transverse plane of a distance equal to the smallest distance measured in a transverse plane between the upstream axis 9 and the downstream axis 10.The translation moves from the downstream axis to the virtual downstream axis by reducing the distance to the upstream axis. The virtual downstream axis then intersects the upstream axis at a virtual intersection point. A reference frame centered on this virtual intersection point is used to decompose the angle difference into, on the one hand, a longitudinal component which is the angular difference between the upstream axis and the virtual downstream axis and, on the other hand, a transverse component which is the angular difference between the reference transverse axis passing through the virtual intersection point and the projection of the virtual downstream axis in the transverse plane.

[0039] According to a first embodiment, the transmitter 5 may comprise an upstream relay 12 configured to be driven by the motor around the upstream axis 9. The upstream relay 12 may be connected to the shaft 4 according to a connection which allows the transmission of a rotational movement. The upstream relay extends around the upstream axis 9 and rotates around this upstream axis 9.

[0040] The transmitter 5 may comprise a downstream relay 14 configured to be driven by the upstream relay 12 around the downstream axis 10. The upstream relay 12 is a part which extends around the downstream axis 10 and which rotates around this downstream axis 10. The downstream relay 14 is connected to the upstream relay 12 by a connection which allows the transmission of a rotational movement. The rotational movement is transmitted however in a possibly different direction, that is to say that the upstream axis 9 and the downstream axis 10 may be different. In other words, there is an angle difference and / or a distance difference between the upstream axis 9 and the downstream axis 10 as presented previously. The adjustment device 15 makes it possible to adjust the angle difference and / or the distance difference.

[0041] In the first embodiment, the downstream relay 14 comprises a ring 18. The ring 18 extends all around the downstream axis 10 and the ring 18 is integral with the rest of the downstream relay 14. The ring 18 extends over a length along the downstream axis 10 which is less than the length of the downstream relay 14 along the downstream axis 10. The ring 18 may in particular be a cylindrical tube along the downstream axis 10 defined by an inner cylinder with a circular section and an outer cylinder with a circular section.

[0042] In the first embodiment, the adjustment device 15 comprises a conveyor 16 configured to adjust a position transverse to the upstream axis 9 of the ring 18 relative to the upstream relay 12. In other words, the conveyor 16 makes it possible to move the ring 18 relative to the upstream relay 12 in a transverse plane perpendicular to the upstream axis 9, that is to say in the directions y and z. For example, micrometric screws 20 which radially pass through a thickness of the upstream relay 12 can come to bear against the ring 18. By screwing or unscrewing the screws, it is possible to impose a movement of the ring 18 relative to the upstream relay 12 in a direction transverse to the upstream axis 9. The micrometric screws can be four in number and distributed in two pairs of screws. The screws of the same pair can be arranged symmetrically with respect to the upstream axis 9 and both oriented in the same direction transverse to the upstream axis 9.Such a screw torque controls the position of the ring 18 in this transverse direction. The screw torques define, for example, two transverse directions perpendicular to each other.

[0043] In the example of [Fig.l], the upstream relay 12 extends radially around the relay 14 so that the micrometric screws pass through the thickness of the upstream relay 12 radially inwards and come to bear against the outside of the ring 18 of the downstream relay 14. It should be noted that the downstream relay 14 could alternatively extend around the upstream relay so that the micrometric screws would pass through the thickness of the upstream relay 12 radially outwards and come to bear against the inside of the ring 18 of the downstream relay 14.

[0044] Advantageously, the adjustment device 15 comprises a mechanism separate from the conveyor 16, the mechanism being configured to allow the introduction of a degree of freedom between the downstream relay 14 and the upstream relay 12.

[0045] According to a first option, and in relation to [Fig. 2], the downstream relay 14 comprises a second ring 23 distinct from the first ring 18. The second ring 23 extends around the downstream axis 10. The second ring 23 extends over a length along the downstream axis 14 which is less than the length of the downstream relay 14 along the downstream axis 10. The second ring 23 may in particular comprise an inner wall which is a cylinder with a circular section. According to the first option, the mechanism is configured to allow a transverse movement to the upstream axis 9 of the second ring 23 relative to the upstream relay 12.

[0046] For example, the mechanism comprises a slide system 22 which guides a translational movement of the second ring 23 relative to the upstream relay 12. The slide system 22 allows a connection with a single degree of freedom whose movement is a translation in a direction transverse to the upstream axis 9. Such a slide system can be produced when the outer wall of the second ring 23 comprises two plane faces parallel to each other and parallel to a particular transverse direction, the two faces being on either side of the downstream axis 10, and when the slide system 22 comprises two ramps each comprising a plane wall parallel to the particular transverse direction, the two walls each being arranged in contact with one of the faces to allow the second ring 23 a translational movement parallel to the particular transverse direction.In this case, it is possible to set a distance gap between the upstream axis 9 and the downstream axis 10, the gap being directed according to the particular transverse direction.

[0047] Advantageously, the mechanism comprises two slide systems which each guide a translational movement of the second ring 23 relative to the upstream relay 12 in a direction transverse to the upstream axis 9. The two directions of movement of the two slide systems can be chosen to be perpendicular to each other. When the mechanism allows the second ring 23 and relative to the upstream relay 12 a translational movement in any direction transverse to the upstream axis 9, the first ring 18 can drive the second ring 23 in movement. In this way the movement of the first ring 18, controlled by the conveyor 16, imposes the movement of the second ring 23. The first ring 18 and the second ring 23 are configured to move identically relative to the upstream relay 12.In this case, it is possible to set a distance gap between the upstream axis 9 and the downstream axis 10, the gap being directed in any transverse direction.

[0048] According to a second option, and in relation to [Fig. 3], the downstream relay 14 comprises a second ring 26 distinct from the first ring 18. The second ring 26 extends around the downstream axis 10. The second ring 26 extends over a length along the downstream axis 14 which is less than the length of the downstream relay 14 along the downstream axis 10. The second ring 26 may in particular be a cylindrical tube along the downstream axis 10 defined by an inner cylinder with a circular section and an outer cylinder with a circular section. The mechanism allowing the introduction of a degree of freedom between the downstream relay 14 and the upstream relay 12 is a second conveyor 24 configured to adjust a position transverse to the upstream axis 9 of the second ring 26 relative to the upstream relay 12. For example, micrometric screws 28 which radially pass through a thickness of the upstream relay 12 can come to bear against the ring 26. It is possible to coordinate the micrometric screws 28 associated with the second ring 26 and the micrometric screws 20 associated with the first ring 18 so that the first ring 18 and the second ring 26 move identically relative to the upstream relay 12. In this case, it is possible to adjust a distance difference between the upstream axis 9 and the downstream axis 10.

[0049] Still according to the second option, the micrometric screws 28 associated with the second ring 26 and the micrometric screws 20 associated with the first ring 18 are not coordinated so that the first ring 18 and the second ring 23 move independently of each other. In this more general case, it is possible to adjust a distance difference and / or an angle difference between the upstream axis 9 and the downstream axis 10.

[0050] According to a third option, and in relation to figures 4 and 5, the downstream relay 14 comprises a second ring 32 distinct from the first ring 18. The second ring 32 extends around the downstream axis 10. The second ring 32 extends over a length along the downstream axis 14 which is less than the length of the downstream relay 14 along the downstream axis 10. The second ring 32 may in particular be a cylindrical tube along the downstream axis 10 defined by an internal cylinder with a section. The upstream axis 9 passes through a center of the second ring 32.

[0051] The mechanism 30 is configured to allow rotation of the second ring 32 relative to the upstream relay 12 about any direction transverse to the upstream axis 9. The mechanism 30 comprises, for example, a ball joint connection system between the second ring 32 and a ring of the upstream relay 12. The second ring 32 and the ring are in contact along surfaces which are not complementary, for example one of the surfaces being flat and the other being spherical. In this case, it is possible to adjust an angle difference between the upstream axis 9 and the downstream axis 10, this angle difference being adjusted around the center of the second ring 32.

[0052] In a first example of the third option, and with reference to [Fig.4], the second ring 32 is located between the motor 3 and the first ring 18.

[0053] In a second example of the third option, and with reference to [Fig.5], the first ring 18 is located between the motor 3 and the second ring 32. It should be noted that this second example of the third option allows finer adjustment of the angle difference than in the case of the first example of the third option. Balancing process

[0054] By using a balancing system 1 as has been presented up to now, it is possible to implement a method P for balancing a test bench turbine. In relation to [Fig. 6], a method P for balancing the turbine 7 including in particular a step S2 of dynamic balancing of the turbine can be carried out on the system of the turbine 7 driven by the transmitter 5 itself driven by the engine 3. This balancing step is obtained by adjusting the mass distribution of the turbine. In particular, one or more weights, i.e. parts whose mass is precisely known, can be added to the turbine. These additions are preferably made in two separate planes of the turbine.

[0055] The transmitter 5, which is configured to rotate the turbine 7 around the downstream axis 10 and which is configured to be rotated by the motor 3 around the upstream axis 9, makes it possible to adjust a gap between the downstream axis 10 and the upstream axis 9. The balancing method comprises a step S1 of adjusting a gap between the downstream axis 10 and the upstream axis 9 of the balancing system 1. This adjustment step can then be followed by the step S2 of dynamic balancing of the turbine 7. This degree of freedom which allows the adjustment of the gap between the downstream axis 10 and the upstream axis 9 makes it possible to take into account the characteristics of the test bench, and in particular the characteristics of the drive system or pivoting of the test bench, when balancing the turbine 7. It is possible to adjust the gap between the downstream axis 10 and the upstream axis 9 so as to recreate in the balancing system 1 the drive characteristics of the turbine7 by the test bench.The dynamic balancing of the turbine by the drive system then takes greater account of the characteristics of the test bench's pivot. This makes it possible to subsequently obtain on the test bench a balancing of the 'pivot + turbine' assembly without requiring the dismantling of the test bench and the associated significant loss of time.

[0056] Advantageously, such a balancing method P can be implemented in a method Q for testing a plurality of turbines on a test bench, the test bench comprising a drive system (or pivoting of the test bench) configured to rotate each of the turbines of the plurality of turbines around an axis of rotation. The method Q is described below in relation to [Fig.6].

[0057] In a first step E1, the drive system of the test bench is mounted on a standard balancing device. The drive system is therefore previously dismantled from the test bench.

[0058] In a second step E2, a standard shaft is mounted in the drive system.

[0059] In a third step E3, a difference is measured between the axis of rotation of the drive system of the test bench and the axis of positioning of the standard shaft in the test bench drive system. This deviation is typically due to defects in the fasteners provided in the drive system to accommodate and secure the master shaft or a turbine. The measured deviation corresponds to the distance between the axis of rotation of the drive system and the axis of positioning of the turbine in the drive system.

[0060] In a fourth step E4, the standard shaft is removed and the turbine is mounted in the drive system. A first assembly 'drive system + turbine' is formed. The drive system is always mounted on the standard balancing apparatus. It is possible, using the apparatus, to carry out dynamic measurements, and in particular to measure an unbalance vector of the first assembly 'turbine + test bench pivot'. The unbalance vector can in particular be given by the difference between the expected position of the center of gravity of the first assembly and the actual position of this center of gravity.

[0061] In a fifth step E5, the dynamic balancing of the first assembly is carried out by adjusting a mass distribution in the turbine. In particular, one or more weights, i.e. parts whose mass is precisely known, can be added to the turbine. These additions are preferably made in two separate planes of the turbine. Dynamic balancing consists of reducing the norm of the unbalance vector, in particular below a threshold value.

[0062] In a sixth step E6, the unbalance vector of the first “turbine + test bench pivot” assembly is determined once the balancing of step E5 has been carried out.

[0063] In a seventh step E7, the balancing system 1 is modified so as to adjust the difference between the downstream axis and the upstream axis of the balancing system equal to the difference measured in step E3, namely the difference between the axis of rotation of the drive system and the axis of positioning of the turbine in the drive system. The seventh step E7 of the method Q corresponds to the step S1 of the method P.

[0064] In an eighth step E8, the turbine is dismantled from the drive system and reassembled on the balancing system so as to form a second “turbine+balancing system” assembly. The second assembly is mounted on a standard balancing device.

[0065] In a ninth step E9, the second assembly is adjusted so that an unbalance vector of the second assembly is equal to the unbalance vector of the first assembly measured in step E6. This adjustment is carried out by adjusting a mass distribution in the balancing system. In particular, one or more weights, i.e. parts whose mass is precisely known, can be added to the balancing system. These additions are preferably made in two separate planes of the balancing system.

[0066] At the end of this ninth step E9, the balancing system is, from the point of view of the balancing of the turbine, a copy of the test bench drive system. The static fault of the drive system, corresponding to the deviation between the rotation axis of the drive system and the positioning axis of the turbine in the drive system, is transferred to the balancing system by the deviation between the downstream axis and the upstream axis. The dynamic fault of the first set corresponding to the unbalance vector of the first set is also transferred to the balancing system by the addition of the weights in the ninth step E9.

[0067] The steps presented above are ideally implemented using the first turbine of the test campaign. After the ninth step, the following turbines in the test campaign can be balanced, and in particular dynamically, on the balancing system. Each dynamic balancing of a following turbine corresponds to a tenth step E10 of the Q method. This tenth step E10 corresponds to step S2 of the P method. There is no longer any need for the test bench drive system to balance them. This saves a lot of time and effort during the test campaign, because it is not necessary to assemble and disassemble the drive system several times with respect to its test bench.

Claims

Claims

1. Balancing system (1) for a turbine (7) of a test bench of a turbomachine, the system comprising: - a transmitter (5) configured to rotate the turbine (7) around a downstream axis (10), - a motor (3) configured to rotate the transmitter (5) around an upstream axis (9), the terms upstream and downstream being defined relative to the transmitter (5) and a direction of transmission of the rotational movement, the transmitter (5) comprising a device (15) for adjusting a gap between the downstream axis (10) and the upstream axis (9).

2. System according to claim 1 wherein the transmitter (5) comprises an upstream relay (12) configured to be driven by the motor around the upstream axis, a downstream relay (14) configured to be driven by the upstream relay (12) around the downstream axis and configured to drive the turbine in rotation, the adjustment device (15) comprising a conveyor (16) configured to adjust a position transverse to the upstream axis of a ring (18) of the downstream relay (14) relative to the upstream relay (12), the ring (18) extending around the downstream axis, the conveyor (16) advantageously comprising micrometric screws (20).

3. A system according to claim 2 wherein the adjustment device comprises a mechanism separate from the conveyor (16), the mechanism being configured to allow the introduction of a degree of freedom between the downstream relay (14) and the upstream relay (12).

4. System according to claim 3 in which the conveyor (16) is a first conveyor, the ring (18) being a first ring, the mechanism being a second conveyor (24) configured to adjust a position transverse to the upstream axis of a second ring (26) of the downstream relay (14) relative to the upstream relay (12), the second ring (26) extending around the downstream axis, the second conveyor (24) advantageously comprising micrometric screws (28).

5. System according to claim 3 in which the mechanism is configured to allow a transverse displacement to the upstream axis of a second ring (26) of the downstream relay (14) relative to the upstream relay (12), the second ring (26) extending around the downstream axis.

6. A system according to any one of claims 4 or 5 wherein the first ring (18) and the second ring (26) are configured to move identically relative to the upstream relay (12).

7. The system of claim 3 wherein the ring (18) is a first ring, the mechanism being configured to allow rotation of a second ring (32) of the downstream relay (14) relative to the upstream relay (12) about any direction orthogonal to the upstream axis, the second ring (32) extending about the downstream axis, the upstream axis passing through a center of the second ring (32).

8. The system of claim 7 wherein the first ring (18) is located between the motor and the second ring (32).

9. The system of claim 7 wherein the second ring (32) is located between the motor and the first ring (18).

10. Method for balancing a test bench turbine (7) in which, in the presence of a transmitter (5) configured to rotate the turbine (7) around a downstream axis (10) and a motor (3) configured to rotate the transmitter (5) around an upstream axis (9), a gap between the downstream axis (10) and the upstream axis (9) is adjusted.

11. A method of testing a plurality of turbines on a test bench, the test bench comprising a drive system configured to rotate each turbine about an axis of rotation, the method comprising the following steps: - (E3) determining a gap between the axis of rotation and a positioning axis of a first turbine in the drive system, - (E5) dynamically balancing a first assembly composed of the first turbine and the drive system, the dynamic balancing being obtained by adjusting a mass distribution in the first turbine, - (E6) determining an unbalance vector of the first assembly, - (E7) modifying a balancing system according to any one of claims 1 to 9 so as to set the gap between the downstream axis and the upstream axis of the balancing system equal to the gap between the axis of rotation and the positioning axis of the first turbine in the drive system,- (E9) adjusting a mass distribution in the balancing system so as to set an unbalance vector of a second assembly composed of the first turbine and the balancing system equal to the unbalance vector of the first assembly, - (E10) dynamic balancing of a third assembly composed of a second turbine and the balancing system, the dynamic balancing being obtained by adjusting a mass distribution in the second turbine.

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