Mechanical power transmission module

Abstract

A mechanical power transmission module (10) comprising a housing (100) and a plurality of parts forming an epicyclic gear train, one of whose inputs / outputs (101) is fixed relative to the housing, the other two inputs / outputs comprising an input (120) and an output (130, 140), power being supplied by an input shaft (110) of the module, the input shaft (110) being coupled to the output assembly (130, 140) via the input assembly (120) in a first axial position of the shaft. The input assembly (120) has a through bore (123) and the output assembly (130, 140) has means for direct coupling (142) to the through bore (123), accessible in a second position obtained by axial translation.

Description

[0001] The invention relates to a mechanical power transmission module, usable in particular for the manual manipulation of an industrial valve, in the context of an intervention by an operator on an electrically controlled actuator, also called an electric servomotor. Such a servomotor can be mounted on a complex installation valve such as a valve in the energy sector, in particular in nuclear power plants, or in the water sector, in the industrial sector such as cement works, or in the oil and gas industry sector.

[0002] The invention applies to multi-turn, quarter-turn or more generally fractional-turn servomotors and to other types of electric actuators. The power transmission module can be used in different contexts.

[0003] It is specified that if industrial valves, which are placed on fluid, liquid or gas pipes, are commonly controlled by a servomotor slaving their position to an electronic position control, it is necessary to be able, with the same device, to operate them manually, during the installation and commissioning of the electric actuator, but also each time that human intervention is necessary, and this can be in a programmed manner, or conversely urgently in the event of a difficulty on the industrial site requiring manual intervention, such as, for example, the loss of electricity supply. Setting up a manual control is nevertheless not an easy thing, because the efforts required are generally high, and it is therefore necessary to provide reduction systems.We also know that the actuator stroke can be long, which is a problem because it lengthens the intervention time if the gear reduction is present over the entire stroke.

[0004] In this context, document FR3072746_A1 discloses a method for manually controlling a valve using a handwheel using power transmission by gears located in a casing. In one configuration allowing a speed reduction, to overcome a significant reduction at the end of the valve closing stroke for example, the gears form an epicyclic train having a crown which is embedded in the casing, and in another configuration the gears ensure a transmission without speed reduction between the inlet and the outlet of the casing, which is appreciable at the start of the stroke, when the valve does not offer any particular resistance. The transition from the reduction configuration to the other configuration is carried out by the axial movement of a rod parallel to the axis and offset from it and which, depending on its position, releases the crown from the casing and immobilizes it with respect to the planet carrier.This configuration is achieved by pulling the rod out of the casing. Alternatively, the transition from one configuration to the other can be achieved by axially moving the crown for the same purposes, possibly achieved by axially moving the input flywheel and its shaft. Here too, direct coupling of the input with the output is achieved by pulling the shaft, this time the flywheel shaft, out of the casing.

[0005] Also known from another document, bearing the number WO2009027821_A1, is a power transmission mechanism comprising a casing in which gears are placed. In one configuration, the gears form an epicyclic gear train having a planet carrier which is embedded in the casing, and in another configuration offering a different speed ratio, the planet carrier is embedded in the crown of the epicyclic gear train and free relative to the casing. The transition from one to the other of the configurations is carried out either by the axial displacement of the planet carrier, or by the displacement of a ring surrounding the planet carrier and linked in rotation with it.

[0006] Another mechanism is disclosed by the same document WO2009027821_A1: In one configuration of this other mechanism, the gears form an epicyclic gear train having a planet carrier which is embedded in the housing, and in another configuration the sun planetary pinion is embedded in the crown of the epicyclic gear train and free relative to the planets. The transition from one to the other of the configurations is carried out by axial displacement of the sun. In these different implementations, an operation is carried out by action on a mechanical control element accessible either on the front face of the housing through which the power is introduced or on its side wall.

[0007] These different solutions remain complicated to use for certain operators who do not know the internal functioning of the devices offered.

[0008] We therefore need a solution that is intuitive for the operator, who is primarily interested in handling the steering wheel and does not necessarily have in mind the need to make modifications to the internal transmission chain of the system.

[0009] The invention aims to solve this problem by proposing a mechanical power transmission module comprising a casing and a plurality of mechanical parts mounted coaxially, said plurality of mechanical parts forming an epicyclic gear train, one of the inputs / outputs of which is immobilized with respect to the casing, the other two inputs / outputs of the epicyclic gear train being formed by an input assembly and an output assembly, the power being further supplied to the plurality of mechanical parts by an input shaft of the transmission module coaxial with the parts of the plurality of mechanical parts, the input shaft being coupled with the output assembly via the input assembly in a first axial position of the input shaft with respect to the casing defining a first speed ratio of the transmission module.

[0010] Thus, there is an epicyclic gear train which allows a reduction to be set up. However, the power transmission module is particular in that the input assembly comprises a central through bore, said through bore and the input shaft carrying complementary splines for coupling the input shaft with the input assembly, the input shaft, mounted sliding with respect to the casing, sliding further in the through bore to couple with the output assembly in a second position of the input shaft with respect to the casing, differing from the first position by an axial translation, in which said complementary splines are no longer engaged, and which defines a second speed ratio of the transmission module.

[0011] Thanks to this solution, it is possible to change the reduction or gear ratio between the input shaft and the output assembly by axial displacement of the input shaft since in one position the power passes through the epicyclic gear train, while it bypasses it in the second position: in fact in this second position, the input shaft is directly coupled with the output assembly. This remarkable result is obtained by the presence of a splined bore in the input assembly, thanks to the sliding nature of the input shaft and thanks to the coupling means allowing the input shaft to be coupled to the output assembly, while disengaging the input shaft from the input assembly.

[0012] The features that will be stated now are optional and advantageous.

[0013] Means for coupling the output assembly with the input shaft may comprise splines carried by a central bore of the output assembly open towards the through bore and splines carried by the input shaft. This is an easy solution to implement parallel to the splines existing between the input shaft and the input assembly. The splines of the input shaft engaging the input assembly and that engaging the output assembly may be different or may be the same. In the embodiment which will be shown in the drawings, they are different, separated by a smooth section of the input shaft.

[0014] The input shaft in the first position can be pushed further into the housing than in the second position. This allows the operator to engage the reduction gear by pushing the flywheel, and engage the direct coupling by pulling it back, which is an easy and intuitive movement.

[0015] Said input assembly may constitute the planet carrier of the epicyclic gear train provided with its planets, coupled without reduction to the input shaft in the first position, the through bore being a bore of the planet carrier. This is a simple and compact version of the invention.

[0016] The output assembly may comprise a bored pinion coupled to the input assembly by external teeth and a central driver, mounted relative to each other in axial sliding connection, the driver comprising support means for undergoing axial thrust in one direction by a control rod and for undergoing axial thrust by the input shaft in the other direction and splines for, under the effect of axial thrusts, coupling and decoupling with respect to an output of the transmission module. This makes it possible to have an action on the control module coming from the part opposite the flywheel, at the other end of the worm screw, i.e. on the electric motor side. In particular, this makes it possible to establish a neutral position, by which the control rod pushes the driver which disengages from the output shaft. A push on the input shaft makes it possible to re-engage the driver on the output shaft.

[0017] In other words, the intended characteristic makes it possible to introduce an additional, axial movement, to control a mechanical actuator in translation on the axis, using support provided by a solid face. A mechanical actuator in translation can be connected to another power transmission module, for example an electric motor, coupled to the same receiver, for example a worm screw, as the output assembly of the power transmission module.

[0018] A spring can be placed between the driver and the bored pinion to prevent the driver from sliding against the bored pinion when the input shaft moves against the output assembly. This is a simple way to ensure that the parts inside the mechanism move smoothly between different positions: on the one hand, you can have a neutral position, but you can also have two different speed ratios.

[0019] A leaf spring of the transmission module may be present between the input assembly and a bearing connecting the input shaft and the housing, retains the shaft despite its weight, and cooperates with a shape carried by the input shaft to signal to an operator axially moving the input shaft that it has reached the first or second position. Such a spring can be used to keep the shaft in a stable position despite it being arranged vertically, which is a solution offered to the industrialist who uses the power transmission module and the associated servomotor. If the shaft is vertical, gravity pulls it downwards and it is necessary to maintain it, which the proposed leaf spring can do.

[0020] The input assembly can be the planet carrier of the planetary gear set, and the output assembly is the sun gear of the planetary gear set. This is a well-characterized arrangement of the planetary gear set, but other input / output arrangements are possible. The input assembly can be coupled without reduction to the input shaft in the first position. This is a simple implementation solution. The output assembly can be coupled without reduction to an output shaft of the transmission module. This is also a simple implementation solution.

[0021] The invention also relates to a use of a mechanical power transmission module as presented above and below, for the initial commissioning of an electric servomotor on a valve or gate for controlling a fluid circulating in a pipeline, or for a safety operation on said valve, the valve or gate being operated by means of a transmission shaft carrying a wheel, the input shaft being coupled to a handwheel constituting a manual control, the output assembly being coupled to a worm screw which engages the wheel.

[0022] The invention will be presented in more detail in connection with the following figures. There figure 1 shows a general view of a servomotor assembly according to the invention, seen in longitudinal section. The figure 2 shows an embodiment of a power transmission module according to the invention, in neutral position, with no gear ratio engaged. The figure 3 shows the device of the figure 1 , in an engagement configuration of a gear ratio of a factor of 3:1. The figure 4 shows the device of the figure 1 , in a configuration of engagement of a direct transmission of power, without reduction. The figure 5 shows an aspect of a power transmission module according to the figures 2 à 4 , in this case a handling assistance mechanism. The figures 6 And 7 show the handling assistance mechanism in two separate positions. The figures 8 à 10 show a second embodiment.

[0023] [ Fig. 1 ] In figure 1 a general view of an ESM servomotor assembly according to the invention is shown. The servomotor assembly comprises a flywheel 1, an electric motor 2, a worm screw and associated wheel assembly, of which the wheel 3 and the worm screw 4 are seen, as well as a clutch system 5 and a mechanical system called a through actuator 6. The wheel 3 is sized to be placed on the shaft of an industrial valve or louver (not shown). Depending on the orientation of the shaft of the valve or louver, the orientation of the ESM servomotor assembly, seen by the axis common to the electric motor 2 and the flywheel 1 as well as to the worm screw 4, can be either horizontal or vertical.

[0024] The flywheel 1 and the electric motor 2 are placed coaxially with the worm screw 4 and coupled or coupleable with respectively one and the other of its two ends. The clutch system 5 is able to decouple the electric motor 2 from the first end (on the right in the figure) of the worm screw or to couple them and the power transmission module 10 is able to carry out at least one change of speed ratio between the flywheel 1 and the worm screw 4 or to decouple these two elements, and reversibly recouple them, on the side of the second end (on the left in the figure).

[0025] The through actuator 6 is a purely mechanical system, in the embodiment presented, configured to transmit a change of configuration from the clutch system 5 to the power transmission module 10 or vice versa from the power transmission module 10 to the clutch system 5. The through actuator 6 does not transmit mechanical power, but it allows the switching from one configuration of the clutch system 5 to another or from one configuration of the power transmission module 10 to another, respectively under the control of a signal coming from the other end of the worm screw 4. The through actuator 6 is in particular constructed on the basis of a through rod 61 introduced into a through bore of the worm screw 4.The through rod 61 opens out at both ends of the worm screw 4 and it transmits, by its axial translation (i.e. longitudinal) towards the left or its translation towards the right, a command which causes a switching at the other end of the worm screw 4.

[0026] We now specify the tilting operated by the through actuator 6.

[0027] When the electric motor 2, initially stopped and decoupled from the worm screw 4, starts moving under the action of a command from the motor, often received by a remote communication means, the electric motor 2 is coupled to the worm screw 4 by the clutch system 5 and a motor connection spring 62, and it pushes the through actuator 6 towards the power transmission module 10, and causes, via the through actuator 6, the decoupling of the flywheel 1 from the worm screw 4.

[0028] Conversely, when the flywheel 1 is pushed by an operator to push its shaft into the casing of the power transmission module 10, the electric motor 2 is decoupled from the worm screw 4 by the clutch system 5 because the latter is opened by the through actuator 6, the movement of which is caused by that of the shaft of the flywheel 1. Simultaneously, the worm screw 4 is coupled to the flywheel via the power transmission module 10, as will be detailed in relation to the following figures, in particular the transition from the figure 2 to the figure 3 .

[0029] [ Fig. 2 ] In figure 2 an embodiment of a power transmission module 10 according to the invention is shown.

[0030] The power transmission module 10 comprises in a casing 100, a planet carrier 120, a bored pinion 130, a part of revolution externally constituting a shaft section and comprising two internal bores (these elements will be described later) called a driver 140, a compression spring 150 and a leaf spring called a position selection leaf spring 180.

[0031] The power transmission module 10, depending on its configuration state, can receive mechanical power as input on an input shaft 110, in this case the shaft of a flywheel (the flywheel 1 of the figure 1 ), and provide power to a 160 output shaft, in this case a worm screw. These two shafts are coaxial. On the figure 2 they are decoupled which means that the rotation of the input shaft 110 which receives power is not transmitted to the output shaft 160 which is stationary.

[0032] Furthermore, a control rod 170, or rod, takes advantage of the fact that the output shaft is hollow to be introduced inside the mechanism presented, through the inside of the output shaft 160. This control rod 170 is the end of the through actuator 6 presented in figure 1 .

[0033] The casing 100 comprises on its inner face a toothed crown 101, toothed inwards, the role of which will be commented on below, an input pivot connection 102 (in this case a sliding pivot) to accommodate the input shaft 110 and an output pivot connection 103 (in this case a non-sliding pivot) to axially hold the output shaft 160.

[0034] The toothed crown 101 and the two input and output pivot links 102 and 103 are coaxial.

[0035] The input shaft 110 is in sliding pivot connection with the casing 100, the translation being limited by stops.

[0036] The portion of the input shaft 110 inside the casing 100 successively has, in order from the input pivot connection 102 towards the inside of the casing 100, first splines called first splines of the input shaft 111 (on a cylindrical section), a non-splined shaft portion 112 (another cylindrical section) and second splines called second splines of the input shaft 113 (on a third cylindrical section), then its end called the end of the input shaft 114.

[0037] The planet carrier 120 is mounted opposite the casing 100 using a bearing 121 coaxial with the input 102 and output 103 pivot connections as well as with the toothed crown 101.

[0038] The planet carrier 120 comprises one or more planets 122 which all mesh with the toothed ring 101. They have axes of rotation parallel to the axis of rotation of the planet carrier 120.

[0039] The planet carrier 120 comprises a through bore 123 coaxial with the input 102 and output 103 pivot connections as well as with the toothed ring 101 and sized to accommodate the input shaft 110 inside it. The through bore 123 comprises a splined cylindrical section called the splined portion of the planet carrier 124 and a smooth, non-splined cylindrical section, called the non-splined portion of the bore of the planet carrier 125, which is closer to the input pivot connection 102 and the flywheel than the splined portion of the planet carrier 124.

[0040] The power transmission module 10 also comprises a bored pinion 130 mounted with a pivot connection 131 (non-sliding) with respect to the casing 100 coaxially with the input shaft 110 and the output shaft 160 as well as with the planet carrier 120. This bored pinion 130 forms all or part of the sun pinion of an epicyclic gear train based on the planet carrier 120 and whose toothed crown 101 constitutes the other planetary pinion. The bored pinion 130 comprises an external gear toothing called the bored pinion toothing 132 which thus meshes with the planet(s) 122.

[0041] Thus the satellites all mesh with the bored pinion 130, on their side which faces the axis of the power transmission module 10, that is to say opposite, radially, to the toothed crown 101.

[0042] The bored pinion 130 comprises a through bore coaxial with the input shaft 110 and the through bore 123 of the planet carrier 120, this bore of the bored pinion being called the receiving bore of the driver 135.

[0043] The bored pinion 130 carries on the surface of this receiving bore of the driver 135 splines called sliding splines for coupling to the driver 133, which have a significant axial length, to allow the sliding of shorter splines, which will be presented later.

[0044] The driver 140 is a hollow cylindrical part of revolution arranged coaxially with the input shaft 110 and the through bore 123 of the planet carrier 120. It has grooves on its external surface, called external grooves of the driver 141.

[0045] The sliding splines for coupling to the driver 133 of the bored pinion 130 are engaged with the external splines of the driver 141. But the sliding splines for coupling to the driver 133 of the bored pinion 130 have a greater length, which may be double, more than double or less than double, than the external splines of the driver 141, and these interact with the part of the sliding splines for coupling to the driver 133 which is located on the side of the input pivot connection 102.

[0046] The driver 140 is also a hollow cylindrical part of revolution. However, it is not hollow from end to end, and comprises a wall 145 transverse to the axis of the power transmission module 10.

[0047] The wall 145 constitutes, on the side of the input pivot connection 102, a bottom for the bore of the driver opening on the side of the input pivot connection 102 called the direct coupling bore to the flywheel 142 and a stop for the input shaft 110 when the latter is introduced into the driver 140.

[0048] The input bore of the driver or direct coupling bore to the flywheel 142 carries on its surface splines called direct coupling splines 143, to couple the driver with the input shaft 110. These splines define a cylindrical section of the bore, which is succeeded, towards the bottom of the bore, opposite the input pivot connection 102 by a smooth cylindrical section, without splines, called the unsplined portion of the direct coupling bore 148.

[0049] On the other side of the wall 145, the driver 140 comprises grooves directed towards the axis in its bore opening on the side of the output pivot connection 103. This bore is called the coupling bore to the worm screw 146 and the grooves are called output grooves of the driver 147.

[0050] Finally, on its periphery, the driver 140 further comprises an annular peripheral surface for lateral support 144, in a plane perpendicular to the axis, for the lateral support of a spring, and facing the side of the casing on which the input shaft 110 is located.

[0051] Facing this annular peripheral surface for lateral support 144, the bored pinion 130 comprises an annular surface for lateral support 134, in a plane perpendicular to the axis, for the lateral support of a spring, and facing the side of the casing on which the output shaft 160 is located.

[0052] The compression spring 150 is placed between the annular lateral support surface 134 of the bored pinion 130 and the lateral support surface 144 of the driver 140, which face each other.

[0053] The output shaft 160 comprises external splines called output shaft splines 161 directed towards the outside of the shaft, and it is blocked in axial translation by translation stops 162 integrated in the casing 100. The output shaft 160 is furthermore a hollow shaft comprising a bore called output shaft bore 163.

[0054] A control rod 170 is inserted into the bore of the output shaft 163, and the end of the control rod 171 comes into contact with the wall 145 of the driver, in a position called the first position of the control rod P11, pressed into the casing 100.

[0055] In figure 2 the input shaft 110 is not coupled to any of the elements contained in the casing 100, which has the consequence that if it is driven in rotation, its rotation is free and does not affect the planet carrier 120, the bored pinion 130, the driver 140 and the output shaft 160. This absence of coupling is due to the fact that in its position P2 represented in figure 2 , the input shaft 110 has its first splines 111 facing the unsplined portion of the planet carrier bore 125 and its second splines 113 facing the unsplined portion of the direct coupling bore 148. The splined portion of the planet carrier 124 and the direct coupling splines 143 face the unsplined portion 112 of the input shaft. The length of this unsplined portion was chosen to ensure the absence of coupling in the P2 position.

[0056] As represented in figure 2 , in this neutral position, on the one hand, the control rod 170 has retracted into the casing 100 (this is the first position of the control rod P11), and the end of the control rod 171 has moved the driver 140 to the left, which has had the consequence of disengaging the output splines of the driver 147 from the splines of the output shaft 161.

[0057] On the other hand, the first splines of the input shaft 111 are on the side of the input pivot connection 102 with respect to the splined portion of the planet carrier 124 and are not engaged with it. Finally, the second splines of the input shaft 113 are on the side of the output pivot connection 103 with respect to the direct coupling splines 143, without interacting with them. On the other hand, it is the non-splined shaft portion 112 which faces its right both the splined portion of the planet carrier 124 and the direct coupling splines 143.

[0058] These relative positions of the splines guarantee the free rotation of the input shaft 110: it is not linked to the planet carrier 120, nor to the driver 140.

[0059] There is also free rotation of the worm screw, i.e. the output shaft 160, since it is not connected to the driver 140.

[0060] In the configuration of the figure 2 , the compression spring 150 is compressed, and it is ready to assist in a relative axial displacement of the driver 140 with respect to the bored pinion 130.

[0061] [ Fig. 3 ] There figure 3 shows the result of the translation T1 (denoted first translation) of the input shaft 110 towards the inside of the casing 100 thanks to the input connection 102 which has been said to be a sliding pivot connection. The input shaft 110 is brought to a stop towards the inside, within the framework of the connection 102. The stop is ensured by the casing 100 or any other element connected to the casing, as will be seen in figures 5 à 7 .

[0062] This translation is aided by the compression spring 150, which relaxes and pushes the driver 140 towards the part of the mechanism opposite the input link 102. At the end of this translation, the input shaft 110 is in a position referred to as the first position of the input shaft P1: the input shaft 110 is pushed into the casing 100. The driver 140 has also moved towards the output link 103, and it has pushed the control rod 170 towards the outside of the casing.

[0063] In this situation represented in the figure 3 , the first splines of the input shaft 111 are engaged with the splined portion of the planet carrier 124, because the input shaft 110 has progressed in the housing, while the planet carrier 120 has not moved.

[0064] The second splines of the input shaft 113 do not interact with the direct coupling splines 143, however, because the latter always face the non-splined portion 112 of the input shaft 110. More precisely, the second splines of the input shaft 113 and the direct coupling splines 143 have followed the same movement towards the right of the mechanism, and as in figure 2 , are not in contact.

[0065] The input shaft 110 therefore drives the planet carrier 120 in rotation, which via the satellites 122 drives the bored pinion 130 in rotation.

[0066] With regard to the bored pinion 130, the sliding splines for coupling to the driver 133 are always engaged with the external splines of the driver 141. As has been seen, the sliding splines for coupling to the driver 133 of the bored pinion 130 have a length greater than the external splines of the driver 141, and these interact this time with the part of the sliding splines for coupling to the driver 133 which is located on the side of the output pivot connection 103, because due to the progression of the input shaft 110 in the casing 100 and in the direct coupling bore to the flywheel 142, the end of the input shaft 114 has pushed the wall 145 and the driver 140 has moved towards the output pivot connection 103.

[0067] The bored pinion 130 therefore drives the driver 140 in rotation, due to the maintenance of the engagement of the splines which have just been mentioned.

[0068] As mentioned, the end of the input shaft 114 has pushed the driver 140, by pressing on the wall 145, towards the output pivot connection 103 and due to this movement, the output splines of the driver 147 and the splines of the output shaft 161 are in interaction with each other and a rotation of the driver 140 necessarily causes a rotation of the output shaft 160, that is to say the worm screw.

[0069] The driver 140 therefore drives the output shaft 160 in rotation.

[0070] And furthermore, the driver 140, because it has moved towards the output pivot connection 103, has pushed, by its solid wall 140, the control rod 170 towards the output pivot connection. The control rod 170 is found moved towards the outside of the casing 100, in a second position of the control rod P12.

[0071] [ Fig. 4 ] We will now discuss the consequence of a translation of the input shaft 110 towards the outside of the casing 100 from the configuration of the figure 3 , as represented in figure 4 . This translation is noted second translation T2 The input shaft 110 is brought to a stop towards the outside, within the framework of the input connection 102 which was said to be a sliding pivot connection. The stop is ensured by the casing 100. At the end of this translation, the input shaft 110 is in a position qualified as second position of the input shaft P2, which is that which had been presented in figure 2 .

[0072] This translation has the effect of releasing the first splines of the input shaft 111 from the splined portion of the planet carrier 124. It is recalled that the planet carrier 120 is immobilized in axial translation and it therefore does not move backward when the input shaft 110 moves backward.

[0073] The translation also has the effect of engaging the second splines of the input shaft 113 with the direct coupling splines 143 of the driver 140.

[0074] The compression spring 150 in fact maintains the driver 140 in the position it occupied in figure 3 , and the external splines of the driver 141 remain engaged with the same portion of sliding splines coupling to the driver 133, without relative sliding of the driver 140 with respect to the bored pinion 130. For the same reason, due to the opposition of the compression spring 150, the splines of the output shaft 161 remain engaged with the output splines of the driver 147.

[0075] Thus, thanks to the compression spring 150, the second splines of the input shaft 113 engage with the direct coupling splines 143 of the driver 140, the driver 140 having remained stationary, while the input shaft moves back into the position it had occupied in the configuration of the figure 2 , in which the driver was offset towards the inside of the casing, away from the output, and decoupled from the output shaft, which is not the case in figure 4 .

[0076] This results in figure 4 , that a rotation of the input shaft 110 around its axis directly drives the rotation of the driver 140 without the torque being transmitted via the planet carrier 120 and the bored pinion 130. And the driver 140 then drives the output shaft 160 in rotation.

[0077] We will now discuss a new configuration change, which can be the triggering of the servomotor's electric motor. From the configuration of the figure 4 in which the control rod is in its second position P12, a push on the control rod 170 towards the inside of the casing moves the driver 140, by pressing the end of the control rod 170 on the wall 145, towards the input pivot connection 102, against the spring 150 which offers resistance but is then nevertheless compressed.

[0078] The translation has the effect of disengaging the second splines of the input shaft 113 from the direct coupling splines 143 of the driver 140. In fact, the input shaft 110 is in abutment and does not move back - it is therefore not driven in translation by the driver 140, and the direct coupling splines 143 therefore disengage from the splines 113, and are found at right angles to the non-splined portion 112.

[0079] The external splines of the driver 141 remain engaged with the sliding splines coupling to the driver 133, but with relative sliding of the driver 140 with respect to the bored pinion 130. The output splines of the driver 147 disengage from the splines of the output shaft 161, since the output shaft 160 is not movable in translation with respect to the casing 100.

[0080] We find the configuration of the figure 2 , with the control rod 170 in its first position P11, that is to say pressed into the casing 100.

[0081] [ Fig. 5 ] There figure 5 shows an aspect of the mounting of the input shaft 110 with respect to the casing 100. The input shaft 110 is articulated with respect to the casing 100 by means of a ball bearing constituting an essential element of the input pivot connection 102. The input shaft 110 also carries on its circumference a peripheral rib forming, in section, a lug called a positioning lug 115. This lug is in contact with a leaf spring referred to as a position selection leaf spring 180. The leaf of this spring is bent to offer two stable positions to the input shaft 110 by offering two housings offset along the axis of the input shaft 110 to accommodate the positioning lug 115 in two offset positions corresponding respectively to the engagement of the first splines of the input shaft 111 with the splined portion of the planet carrier 124 and the engagement of the direct coupling splines 143 with the second splines of the input shaft 113.The position selection leaf spring 180 and the positioning lug 115 cooperate together and also have an additional function, which can also be considered as their main function: they allow the weight of the flywheel 1, when the axis is placed vertically, to be supported so that the flywheel 1 and its shaft (input shaft 110) do not move due to gravity. This function is not used if the shaft is placed horizontally, but the choice of orientation is up to the manufacturer who uses the system.

[0082] There figure 5 shows the system with the input shaft 110 pulled out of the housing 100, and the locating pin 115 consequently placed in the housing closest to the ball bearing of the input pivot link 102, or first positioning indication space 181.

[0083] [ Fig. 6 ] There figure 6 shows the system with the input shaft 110 pushed into the housing 100, and the positioning lug 115 consequently placed in the housing closest to the planet carrier 120 or second positioning indication space 182.

[0084] [ Fig. 7 ] There figure 7 shows the system with the input shaft 110 in an intermediate position between the two functional positions presented previously: we see that the blade of the position selection leaf spring 180 is constrained by the presence of the positioning lug 115 in this intermediate position in which no housing is provided to accommodate the positioning lug 115: the result is that the position is unstable, or uncomfortable for the operator who operates the steering wheel 1 (whose axis is the input shaft 110), and understands from the feedback of forces that he perceives when operating the steering wheel 1, that he has not yet reached the functional position that he is looking for.Consequently, the operator continues to move the steering wheel 1 until he perceives that it is in a more stable or better received position, which is the case when the positioning lug 115 reaches either the first positioning indication space 181 or the second positioning indication space 182 (depending on the direction in which the steering wheel is moved).

[0085] The steering wheel is often operated by hand, but in some implementations it is planned to be operated by an electric or pneumatic motor, to which it is then connected by a socket. The operation is then faster. All the components of the mechanism are sized to withstand a high rotation speed. The system is mounted on bearings.

[0086] The invention takes other forms, within the scope of the claims.

[0087] In particular, the presence of a sliding connection between the driver 140 and the bored pinion 130 is not essential to the realization of the invention in its greatest generality. The bored pinion 130 and the driver 140 can be replaced by a single part constituting a bored sun pinion, which then does not participate in decoupling the flywheel 1 from the worm screw 4 according to the above principles.

[0088] Furthermore, it is possible to position the splines so that direct coupling is achieved by pushing the flywheel and transmission by the epicyclic gear train by pulling the flywheel. For this, a single section carrying splines can be provided on the input shaft 110, which in one position engages the planet carrier, and in the other position engages the driver. This is compatible with the establishment of a sliding connection between the driver and the bored pinion, by means of the displacement of the support points of the spring 150.

[0089] Furthermore, it is not essential that the direct coupling between the input shaft and the driver be made in a bore of the driver: the latter may, in a variant, carry external splines on a small diameter which enters a bore made in the shaft, which would in turn carry internal splines engaging the external splines of the driver. Or the coupling between the input shaft and the driver may be made using various forms of dog clutch.

[0090] Also, one can consider placing a reduction stage between the input shaft and the planet carrier.

[0091] [ Fig. 8 ] In figure 8 a second embodiment of a power transmission module 10 according to the invention is shown.

[0092] As in the first embodiment, the power transmission module 10 comprises, in a casing 600, a planet carrier 620, a bored pinion, a part having overall symmetry of revolution, externally constituting a shaft section and comprising two internal bores (these elements will be described later) called a driver 640 and a compression spring 650.

[0093] As in the first embodiment, the power transmission module 10, depending on its configuration state, can receive mechanical power as input on an input shaft 610, the flywheel shaft, and provide power on an output shaft 660, in this case a worm screw. These two shafts are coaxial. On the figure 8 they are decoupled which means that the rotation of the input shaft 610 which receives power is not transmitted to the output shaft 660 which is stationary (or vice versa). Thus, the gearbox is in neutral.

[0094] Furthermore, as in the first embodiment, a control rod 670, or rod, takes advantage of the fact that the output shaft is hollow to be introduced inside the mechanism presented, through the inside of the output shaft 660. This control rod 670 is the end of the through actuator 6 presented in figure 1 .

[0095] The casing 600 comprises, as in the first embodiment, on its inner face a toothed crown 601, toothed inwards, an input pivot connection 602 (a sliding pivot) to accommodate the input shaft 610 and an output pivot connection 603 (a non-sliding pivot) to axially hold the output shaft 660. The toothed crown 601 and the two input and output pivot connections 602 and 603 are coaxial. The input shaft 610 is in sliding pivot connection with the casing 600, the translation being limited by stops in both directions.

[0096] The portion of the input shaft 610 inside the casing 600 successively carries, in order from the input pivot connection 602 towards the inside of the casing 100, a non-splined portion 612, a first externally splined sliding gear called the first sliding gear 691, and a second externally splined sliding gear called the second sliding gear 692, then its end called the end of the input shaft 614. The two sliding gears 691 and 692 are pushed relative to each other along the shaft in opposite directions by a compression spring 693 mounted around the shaft 610 and pressed at its two ends against the two sliding gears respectively.Their longitudinal movements relative to the shaft 610 are limited, for the first sliding gear 691 by a stop in the direction of the flywheel and carried by the shaft, and for the second 692 by a stop in the direction of the end of the input shaft 614, this second stop also being carried by the shaft (these two stops are constituted by shoulders of the shaft, the sliding gears being mounted in a narrowed section of the latter). The spring 693 is furthermore chosen to, in the absence of opposing force or obstacle, push the two sliding gears into stop simultaneously.

[0097] As in the first embodiment, the planet carrier 620 is mounted opposite the casing 600 using a bearing 621 coaxial with the input 602 and output 603 pivot links as well as with the toothed ring 601. The planet carrier 620 comprises one or more satellites 622 which all mesh with the toothed ring 601. They have axes of rotation parallel to the axis of rotation of the planet carrier 620.

[0098] As in the first embodiment, the planet carrier 620 comprises a through bore 623 coaxial with the input and output pivot connections as well as with the toothed crown.

[0099] The bore 623 is sized to accommodate inside it the input shaft 610 with its sliding gears, or in any case the first sliding gear 691. The through bore 623 comprises a splined cylindrical section called the splined portion of the planet carrier 624, which is adapted to form a connection with the splines of the sliding gear, which are complementary.

[0100] As in the first embodiment, the power transmission module 10 also comprises a bored pinion (already mentioned) 630 mounted with a pivot connection 631 (non-sliding) with respect to the casing 600 coaxially with the input shaft 610 and the output shaft 660 as well as with the planet carrier 620. This bored pinion 630 forms all or part of the sun pinion of an epicyclic gear train based on the planet carrier 620 and whose toothed crown 601 constitutes the other planetary pinion. The bored pinion 630 comprises an external gear toothing called the bored pinion toothing 632 which thus meshes with the planet gear(s) 622. Thus the planet gears mesh with the bored pinion 630. As in the first embodiment, the bored pinion 630 comprises a through bore coaxial with the input shaft 610 and the through bore 623 of the planet carrier 620, this bore of the bored pinion being called the receiving bore of the driver 635.The bored pinion 630 carries on the surface of this receiving bore of the driver 635 splines called sliding splines for coupling to the driver 633, which have a significant axial length, to allow the sliding of shorter splines, of the external surface of the driver.

[0101] As in the first embodiment, the driver 640 is a hollow cylindrical part of revolution arranged coaxially with the input shaft 610 and the through bore 623 of the planet carrier 620. It carries splines on its external surface, called external splines of the driver 641. The sliding splines for coupling to the driver 633 of the bored pinion 630 are engaged with the external splines of the driver 641. But the sliding splines for coupling to the driver 633 of the bored pinion 630 have a length greater than the external splines of the driver 641, and these interact, in the configuration of the figure 8 , with the part of the sliding splines coupling to the driver 633 which is located on the side of the input pivot connection 602.

[0102] As in the first embodiment, the driver 640 is a cylindrical part having overall symmetry of revolution, and hollow, comprising a wall 645 transverse to the axis of the power transmission module 10.

[0103] The wall 645 constitutes, on the side of the input pivot connection 602, a bottom for the bore of the driver opening on the side of the input pivot connection 602 called the direct coupling bore to the flywheel 642.

[0104] The input bore of the driver or direct coupling bore to the flywheel 642 carries on its surface splines called direct coupling splines 643, to couple the driver with the input shaft 610, by the second sliding gear 692. These splines define a cylindrical section of the bore, which is followed, towards the inlet of the bore, towards the input pivot connection 602, by a smooth cylindrical section, without splines.

[0105] As in the first embodiment on the other side of the wall 645, the driver comprises splines directed towards the axis in its bore opening on the side of the output pivot connection. This bore is used for coupling to the worm screw and the splines are output splines of the driver 647.

[0106] As in the first embodiment, the driver 640 comprises on its periphery an annular peripheral surface for lateral support in a plane perpendicular to the axis, for the lateral support of a spring, and facing the side of the casing on which the input shaft 610 is located.

[0107] Facing this annular peripheral surface for lateral support 644, the planet carrier 620 comprises an annular surface for lateral support, in a plane perpendicular to the axis, for the lateral support of a spring, and facing the side of the casing on which the output shaft is located. This is an assembly equivalent to the assembly shown in the first embodiment (the two assemblies are interchangeable): the compression spring 650, instead of resting on the bored pinion, rests on the planet carrier 620, which is longitudinally fixed with respect to the casing, like the bored pinion. Resting on one or the other therefore has the same effect and amounts to resting on the casing. The compression spring 650 is thus placed here between the planet carrier 620 and the driver 640, which face each other, but it mainly governs the sliding of the driver 640 with respect to the bored pinion 630 along the sliding splines.

[0108] As in the first embodiment, the output shaft 660 comprises external splines and is blocked in axial translation by translation stops 662 integrated in the casing 600. The output shaft 660 is furthermore a hollow shaft comprising a bore called the output shaft bore 663. A control rod 670 is inserted into the bore of the output shaft 663, and the end of the control rod 671 approaches the wall 645 of the driver, in a position called the first position of the control rod P11, pressed into the casing 600, shown in FIG. figure 8 .

[0109] An elongated spacer 699 is mounted through the wall 645, perpendicular to it and fixed in sliding connection with an axis parallel to the shaft 610. It constitutes a stop with clearance for the shaft 610 and for the rod 670, and makes it possible to transfer a thrust from the shaft 610 to the rod 670 and vice versa, without moving the driver 640.

[0110] In figure 8 the input shaft 610 is coupled in its position P2 to the planet carrier 125 by the first sliding gear 691.

[0111] As represented in figure 8 , in this neutral position, on the one hand, the control rod 670 has retracted into the casing 600 (this is the first position of the control rod P11), and the end of the control rod 671 has moved the driver 640 to the left, which has had the consequence of disengaging the output splines of the driver 647 from the splines of the output shaft 661.

[0112] On the other hand, the first sliding gear 691 is engaged to the grooved portion of the planet carrier 624 or is not, then being offset in the direction of the second sliding gear, 692, then compressing the spring 693, due to an angular offset between the grooves 624 of the planet carrier and those of the first sliding gear 691.

[0113] And the second sliding gear 692 is engaged to the direct coupling splines 643 or is not, then being offset in the direction of the first sliding gear, 691, then compressing the spring 693, due to an angular offset between the splines 643 of the driver and those of the second sliding gear 692.

[0114] Possibly, one of the two shifters is engaged, the other not, depending on the gear ratio that was engaged when shifting into neutral.

[0115] There is also free rotation of the worm screw, i.e. the output shaft 660, with respect to the input shaft since the worm screw is not connected to the driver 640.

[0116] In the configuration of the figure 8 , the compression spring 650 is compressed, and it is ready to assist in a relative axial displacement of the driver 640 with respect to the bored pinion 630. But it is kept compressed by the rod 670 which forces the spacer 699 towards the flywheel until the end of its travel, as well as the driver on which it presses via the spacer 699. The driver therefore compresses the spring 650.

[0117] [ Fig. 9 ] We will now consider the transition from the configuration of the figure 8 (one or the other of the two players being engaged), towards the figure 9 , by translation T1 of the flywheel and its shaft towards the inside of the casing.

[0118] This passage is done in two stages, the first stage involving the spacer 699, which nevertheless remains optional in the invention.

[0119] The initial effect of the translation T1 (denoted first translation) of the input shaft 610 towards the inside of the casing 600 thanks to the input connection 602 which has been said to be a sliding pivot connection is as follows.

[0120] This translation requires an effort from the operator who presses on the shaft 610, which in turn presses on the spacer 699 which meets the rod 670. The operator then counters the resistance provided by the rod 670. Then, the spacer reaching the end of its travel, he moves the driver.

[0121] It is aided by the compression spring 650, which naturally tends to push the driver 640 toward the part of the mechanism opposite the input link 602. Rapidly during this translation, the input shaft 610 is in a position referred to as the first position of the input shaft P1: the input shaft 610 is pressed into the casing 100. The driver 640 has also moved toward the output link 603, and the spacer 699 has moved toward the output link relative to the driver 640, because the input shaft has pressed against it, and it is only after having made this relative movement with respect to the driver that it has been able to drive the latter toward the output shaft, in which it has been aided by the spring 650.

[0122] In addition, the spacer 699 immediately pushed the control rod 670 in the direction of the outside of the casing. The control rod 670 is moved towards the outside of the casing 600, in a second position of the control rod P12. The engine is disengaged as a result, and the safety of the operator handling the steering wheel is ensured.

[0123] The driver has not yet engaged the output shaft (worm) 660. A small rotation may be necessary for the complementary splines 647 and 661 to engage, and there may therefore be resistance at this stage. However, the motor is already disengaged thanks to the input shaft pressing on the spacer 699 and the movement of the latter which has enabled the control rod 670 to be pushed.

[0124] Furthermore, the first sliding gear 691 has disengaged from the splined portion of the planet carrier 624 (if it was engaged there), because the input shaft 610 has progressed in the casing, whereas the planet carrier 620 has not moved, and the sliding gear 691 is in abutment on the shaft 610 in the direction of the flywheel (the movement of the shaft in the opposite direction to the flywheel therefore drives it in an identical movement).

[0125] The 650 spring has partially relaxed.

[0126] [ Fig. 9 ] There figure 9 shows the final result of the translation T1 (noted first translation) of the input shaft 610 towards the inside of the casing, after if necessary a small relative rotation of the driver and the output shaft, the spring 650 relaxing completely.

[0127] The input shaft 610 rotates the driver 640.

[0128] The driver 640 has moved towards the worm screw. The driver and the spacer 699 have, after a transient relative displacement, returned to their relative positions with respect to each other of the figure 8 , due to the resistance provided by the rod 670 and the pressure provided by the spring 650. The transient movement of the spacer 699 is represented by the two arrows in its rectangle, in the drawing.

[0129] The rotation of the two shafts, input and output, is therefore in direct coupling (speed ratio equal to 1). The input shaft 610 therefore drives the output shaft 660 in rotation, without gear reduction or reduction.

[0130] [ Fig. 10 ] We will now discuss the consequence of a translation of the input shaft 610 towards the outside of the casing 600 from the configuration of the figure 9 , as represented in figure 10 This translation is noted as the second translation T2.

[0131] The input shaft 610 is brought outward, as part of the input link 602 which has been said to be a sliding pivot link.

[0132] Initially, the translation also has the effect of releasing the second sliding gear 692 from the direct coupling splines 643 of the driver 640.

[0133] The compression spring 650 in fact maintains the driver 640 in the position it occupied in figure 9 The splines of the output shaft 661 remain engaged with the output splines of the driver 647. But the second sliding gear is taken towards the flywheel by the stop which it meets in the direction of the end of the shaft on which it is mounted.

[0134] On the other hand, the first sliding gear 691 may have difficulty engaging the splines of the planet carrier, if an angular offset constitutes a hindrance. In such a situation, the sliding gear moves by compressing the spring 693. The fact that it slides on the shaft 610 makes it possible to accommodate this difficulty, which is resolved as soon as a rotation is applied to the flywheel, thanks to the relaxation of the spring 693 which promotes the engagement of the splines of the planet carrier and the first sliding gear 691. Knowing that the planet carrier 620 is immobilized in axial translation and it therefore does not move back when the input shaft 610 moves back.

[0135] This results in figure 10 , that a rotation of the input shaft 610 around its axis causes the rotation of the driver 640, the torque being transmitted via the planet carrier 620, the satellites and the bored pinion 630 with therefore a non-unitary speed ratio.

[0136] At the end of this translation T2, the input shaft 610 is in a position described as the second position of the input shaft P2, which is that, or similar to that, which had been presented in figure 8 .

[0137] We will now discuss a new configuration change, which can be the triggering of the servomotor's electric motor. From the configuration of the figure 9 or the configuration of the figure 10 in which the control rod is in its second position P12, a push on the control rod 670 towards the inside of the casing moves the driver 640, by pressing the end of the control rod 670 on the spacer 699 which, once at the end of its travel, drives the wall 645 and therefore the entire driver, towards the input pivot connection 602, against the spring 650 which is then progressively compressed.

[0138] The translation therefore has the effect of releasing the splines 647 from the driver and 661 from the worm screw (the output shaft).

[0139] From the configuration of the figure 9 the translation may have the effect of engaging the first sliding gear 691 with the splines of the planet carrier. The first sliding gear 691 may also, alternatively, move back towards the worm along the shaft by compressing the spring 693, if the engagement of the splines is not easy due to angular misalignment, but the spring 693 forces the first sliding gear 691 to engage with the planet carrier as soon as such possible angular misalignment is overcome, which occurs if the steering wheel is turned.

[0140] Likewise from the configuration of the figure 10 the translation may have the effect of engaging the second sliding gear 692 with the direct coupling splines 643. Indeed, the input shaft 110 is in abutment and does not move back - the second sliding gear 692 may move back along the shaft towards the flywheel by compressing the spring 693, if the engagement of the splines is not easy due to angular misalignment, but the spring 693 forces the second sliding gear 692 to engage with the driver as soon as such a possible angular misalignment is overcome, which occurs if the flywheel is turned.

[0141] In all cases we find the configuration of the figure 8 , with the control rod 670 in its first position P11, that is to say pushed into the casing 600. The sliding gears thus make it possible to overcome difficulties in engaging splined shafts and complementary splined bores, which can occur when the splines are not very fine. Thus, it is possible to choose an embodiment without a sliding gear, but with very fine splines.

[0142] And the optional 699 sliding spacer allows the electric motor to be disengaged before engaging the manual control, when changing the configuration of the figure 8 (neutral) to the configuration of the figure 9 (direct coupling - speed ratio equal to 1). ESM servomotor assembly 1 flywheel 2 electric motor 21 electric motor rotor 3 wheel 4 worm screw 5 clutch release system 6 through actuator 61 actuating rod 62 motor connection spring 10 power transmission module 100, 600 housing 101, 601 ring gear 102, 602 input pivot link 103, 603 output pivot link 110, 610 input shaft 111 first splines of the input shaft 691 first sliding gear or input sliding gear, splined sliding gear 112 non-splined shaft portion 113 second splines of the input shaft 692 second sliding gear or output sliding gear, splined sliding gear 693 small compression spring 114 end of the input shaft (present but not referenced, to simplify the drawing, in the 2nd embodiment) 115 positioning lug 120, 620 planet carrier 121, 621 bearing 122, 622 planets 123, 623 through bore 124,624 splined portion of the planet carrier 125 non-splined portion of the planet carrier bore 130, 630 bored pinion 131, 631 pivot connection 132, 632 teeth of the bored pinion 133, 633 sliding splines for coupling to the driver 134 annular lateral support surface of the bored pinion 135, 635 driver receiving bore 140, 640 driver 141, 641 external splines of the driver 142, 642 direct coupling bore to the flywheel 143, 643 direct coupling splines 144, 644 annular lateral support surface of the driver 145, 645 solid wall or wall possibly receiving a spacer 146 worm screw coupling bore (present but not referenced, to lighten the drawing, in the 2nd embodiment) 147, 647 output splines of the driver 148 non-splined portion of the direct coupling bore 150, 650 compression spring 160, 660 output shaft 161, 661 output shaft splines 162, 662 translation stops 163,663 output shaft bore 170, 670 control rod 171, 671 end of control rod 180 position selection leaf spring 181 first position indication space 182 second position indication space P1 first position of input shaft P2 second position of input shaft T1 first axial translation of input shaft T2 second axial translation of input shaft P11 first position of control rod P12 second position of control rod,

Claims

1. Mechanical power transmission module (10) comprising a housing (100; 600) and a plurality of mechanical parts (101, 120, 122, 130, 140; 601, 620, 622, 630, 640) mounted coaxially, said plurality of mechanical parts forming an epicyclic gear train, one of the inputs / outputs (101; 601) of which is immobilized with respect to the housing (100; 600), the other two inputs / outputs of the epicyclic gear train being formed by an input assembly (120, 122; 620, 622) and an output assembly (130, 140; 630, 640), the power being further supplied to the plurality of mechanical parts (101, 120, 122, 130, 140; 601, 620, 622, 630, 640) by an input shaft (110; 610) of the transmission module (10) coaxial with the parts of the plurality of mechanical parts (101, 120, 122, 130, 140; 601, 620, 622, 630, 640), the input shaft (110; 610) being coupled with the output assembly (130, 140; 630, 640) via the input assembly (120, 122;620, 622) in a first axial position (P1) of the input shaft (110; 610) with respect to the casing (100) defining a first speed ratio of the transmission module (10), the transmission module (10) being furthermore; characterized in thatthe input assembly (120, 122; 620, 622) comprises a central through bore (123; 623), said through bore (123; 623) and the input shaft (110; 610) carrying complementary splines (124, 111; 624, 691) for coupling the input shaft with the input assembly, the input shaft (110; 610) slidably mounted (102; 602) with respect to the casing (100; 600), sliding in the through bore (123; 623) to couple with the output assembly (130, 140; 630, 640) in a second position (P2) of the input shaft (110; 610) with respect to the casing (100; 600), differing from the first position (P1) by an axial translation (T2), in which said complementary splines (124, 111; 624, 691) are no longer engaged, and which defines a second speed ratio of the transmission module (10), the output assembly (130, 140; 630, 640) comprising a bored pinion (130; 630) coupled to the input assembly (120, 122;620, 622) by an external toothing (132; 632) and a central driver (140; 640), mounted relative to each other in axial sliding connection, the driver (140; 640) comprising support means (145; 645) to undergo an axial thrust in one direction by a control rod (170; 670) and to undergo an axial thrust by the input shaft (110; 610) in the other direction and splines (147, 647) for coupling and decoupling with respect to an output (160; 660) of the transmission module (10), a spring (150; 650) being placed so as to oppose the sliding of the driver (140; 640) with respect to the bored pinion (130; 630) when the input shaft (110; 610) moves relative to the output assembly (130, 140; 630, 640).; 2. Mechanical power transmission module (10) according to claim 1, characterized in thatsaid input assembly (120, 122; 620, 622) constitutes the planet carrier (120; 620) of the epicyclic gear train provided with its planets (122; 622), coupled without reduction to the input shaft (110; 610) in the first position (P1), the through bore (123; 623) being a bore of the planet carrier (120; 620).

3. Mechanical power transmission module (10) according to claim 1 or 2, characterized in that the support means consist of a wall (145; 645) transverse to the axis of the power transmission module (10) possibly carrying a spacer (699) sliding axially according to a limited movement in both directions.

4. Mechanical power transmission module according to one of claims 1 to 3, characterized in thata leaf spring (180) of the transmission module is present between the input assembly (120, 122; 620, 622) and a bearing (121) connecting the input shaft (110; 610) and the housing (100; 600), retains the shaft despite the weight thereof, and cooperates with a shape carried by the input shaft (110; 610) to signal to an operator axially moving the input shaft (110; 610) that it has reached the first or second position.

5. Mechanical power transmission module according to one of claims 1 to 4, characterized in that the input shaft (110; 610) in the first position (P1) is less pressed into the housing (100; 600) than in the second position (P2), 6. Use of a mechanical power transmission module (10) according to one of claims 1 to 5, for the initial commissioning of an electric servomotor on a valve or valve for controlling a fluid circulating in a pipeline, or for a safety operation on said valve, the valve or valve being operated by means of a transmission shaft carrying a wheel (3), the input shaft (110; 610) being coupled to a handwheel (1) constituting a manual control, the output assembly (130, 140; 630, 640) being coupled to a worm screw (4) which engages the wheel (3).