MODULAR REDUCTION GEARBOX

Description

[0001] The invention relates to a speed reducer for a mechanical power transmission system implemented in particular in an electric actuator, or servomotor, for industrial valves or louvers.

[0002] Industrial valves and gates are used in industries where fluids (liquids or gases) flow through pipes, and the flow of the fluid is controlled by an interposed moving part (shut-off) in the pipe and whose position must be controlled or even controlled by an instantaneous command (variable over time, including very rapidly) to cope with the force imposed by the fluid on the moving part.

[0003] The control of the valve or louver is often implemented using a mechanical device such as a worm gear. The worm gear is mounted on a control mechanism for the valve or louver (shafts transmitting power), and the worm gear is connected to the shaft of a rotary electric motor. The worm gear and its associated wheel ensure irreversible power transmission, as their design, by adapting the screw pitch, guarantees that the valve or louver will not send any force back to the motor.

[0004] The available space is very limited, and the servomotor must therefore be compact. Furthermore, particular attention is paid to situations where the torque to be applied is significant, because the valve or fan in question is located on a high-pressure or high-flow fluid line.

[0005] A reducer introducing a speed ratio to be chosen according to the circumstances (depending in particular on the valve on which the servomotor is installed) can be introduced between the electric motor and the worm gear.

[0006] A sensor tracks the position of the shuttering device to determine how much it is blocking the flow at any given moment, and redefines the control based on this information.

[0007] Such a servomotor can be mounted on a valve in the energy sector, particularly in nuclear power plants, or in the water sector, in industry such as cement plants, or even in the oil and gas industry. Other industries also use such systems.

[0008] The invention applies to multi-turn, quarter-turn, or more generally fraction-turn servomotors and other types of electric actuators. The servomotor can be used in various contexts.

[0009] While industrial valves and louvers are commonly controlled by a servomotor that synchronizes their position with a recurring electronic position command, it is essential to be able to manually operate them on occasion using the same device. This is necessary both during the installation and commissioning of the electric actuator and whenever human intervention is required. This can be scheduled or, conversely, urgently in the event of a problem on the industrial site requiring manual intervention, such as a power outage. Therefore, a handwheel for manual control is accessible on the outside of the servomotor—this is often even a regulatory requirement. However, for personnel safety, the handwheel must not be driven when the motor is rotating the actuation mechanism.Furthermore, when the operator manually activates the actuation mechanism, it is desirable that they not have to move the motor, which is unpowered and inert, as this would be very difficult due to friction. Therefore, the aim is for the manual control to trigger a mechanical disconnection of the motor from the actuation mechanism.

[0010] In recent times, servomotors have been developed that incorporate a reduction gear between the electric motor and one end of the worm gear. This reduction gear couplees the two and can be disassembled and reassembled with a different speed ratio by changing the gears, according to a modular principle (modular reduction gear). This reduction gear can notably be an epicyclic gear train (a three-shaft reduction gear with two planetary gears and sun gears) in which a sun gear is directly coupled to the worm gear, a ring gear is coupled to the motor, and a sun gear carrier is embedded in the servomotor housing.In the same system, we know how to decouple the motor from the worm gear from the other end of the worm gear, by means of a through rod in translation, which can be operated by hand in one direction to remotely disengage the solar pinion from the worm gear, a pivoting lug holding the pinion until the motor is restarted, which disengages it, the solar pinion being brought back into contact with the worm gear with movement of the through control rod.

[0011] However, this system is cumbersome and expensive to set up and maintain.

[0012] A self-propelled, motorized valve actuator is known from publication US4114469, which includes a worm gear drive assembly for receiving the rapid rotary motion from a drive motor and reducing it to a low-speed linear or rotary motion of a valve stem.

[0013] Also known from US Patent 2018 / 298988 is a variable-speed return device for an electric actuator that uses a cooperative configuration between the unidirectional drive and the clutch during operation to prevent damage to the operating unit driven by the opening / closing assembly. However, this device has the same drawbacks, namely its size and maintenance and installation costs. Furthermore, US Patent 4,114,469 A describes a motorized valve actuator that allows both simultaneous disengagement of the motor electrically and mechanically, and automatic switching between motorized and manual modes.

[0014] To overcome the difficulties of prior art actuators, a mechanical power transmission system is proposed for controlling a valve or louver. The transmission system comprises an actuation mechanism for a valve or louver shaft. This actuation mechanism has first and second power inputs. The system includes a rotary motor and a rotary hand actuator coupled to the first and second power inputs, respectively, and a release mechanism by means of a push rod that disengages the motor from the first power input. More specifically, the invention provides a mechanical power transmission system according to claim 1. Additional features of the invention are stated in the dependent claims.

[0015] The disengagement mechanism is remarkable in that it comprises a driving part and a driven part together forming a dog clutch on an axis, the driven part having a toothed ring and a dog clutch driven part impression, and being coupled to the first input by said toothed ring, at least one satellite pinion of the power transmission system and a central bore for coupling (complementary to the first input), for example a splined bore, said driven part having a central bore (for example a splined bore complementary to said first input), the rod, for effecting disengagement, passing through the two central bores and pushing a hub of the driving part.

[0016] With this definition, the driven part, the sun gear, and the planet gear(s) can be reversed and interchanged to modify the speed ratio between the rotary motor and the drive mechanism. According to the invention, the through bore is at the center of a first part, which is a drive component such as a planet carrier or sun gear, but which also has a recess for a second driven part, a dog clutch, to be used as a substitute when operators wish to reverse the gear ratio.

[0017] This is carried out by taking advantage of the fact that the first driven part of the dog clutch can carry the shapes of a second drive part, in addition to its dog clutch driven part shapes, and therefore also have a satellite carrier shape (equipped with its satellites) or a solar pinion, to be used as a substitute when the operators wish to proceed with the reversal.

[0018] The substitution leads to a change in gear ratio, which is very advantageous: you just have to open the machine, swap the parts without bringing in others, and close it again, and a new gear ratio is obtained.

[0019] Depending on optional and advantageous features: the first input and the toothed ring of the driven part are coupled by one or more stepped planetary pinions fixed to the housing and a sun pinion coupled to the first input or alternatively, in another embodiment, the first input and the toothed ring of the driven part are coupled by a planet carrier coupled to the first input and carrying one or more planetary pinions meshing with a toothed ring of the housing; the actuation mechanism may include a worm in a housing, and a manual control, accessible to an operator at one end of the worm opposite the motor, acting on the disengagement mechanism to decouple the actuation mechanism and the rotary motor by the action of the rod, the rod being inserted in a central bore of the worm;A spring-loaded blade can be positioned on the motor housing to hold the driving part away from the driven part when the motor is stationary; a compression spring pressed against the motor pulls the driving part back against the driven part; and teeth on the driving part allow the spring-loaded blade to be moved away by the compression spring and the rotation of the motor when it is started. Alternatively, a pivoting lever can be used for this function. The driven part, the driving part, and the driven part recess can comprise two or three tenons, optionally with a tier of three half-tenons (tenons shorter than full tenons). In particular, the driving part comprises six tenons (three half-tenons and three full tenons), and the driving part recess comprises three tenon recesses. Both the driven and driving parts are made of sintered metal.This is an effective method for obtaining a part that has a dog-clutch shape on one side and a pinion shape on the other; the rotating manual actuator can be a flywheel, a control of the transmission system allowing decoupling of said flywheel from the first power input by the rod which is pushed by the hub when the dog-clutch is closed.

[0020] The invention will now be discussed in relation to the figures presented for illustrative purposes. There figure 1 represents a servomotor incorporating the invention. The figure 2 This diagram shows a cross-section of the modular reducer in a specific configuration (defining a particular speed ratio), with the motor coupled to the worm gear, meaning the reducer is in the closed position (P1). figure 3 This three-quarter view depicts a method of using a servomotor without the modular gearbox. figure 4 This represents a three-quarter view of the modular gearbox in a given configuration; other configurations are also available. figure 5 represents another three-quarter view of the modular reducer. The figure 6 This represents the same three-quarter view of the modular reducer but in a different configuration (the gears have been disassembled and reassembled differently). figure 7 represents the configuration of the figure 6 but in a cross-sectional view. The figure 8 represents another configuration of the modular reducer viewed from a three-quarter angle (similar to the configuration of the figure 4 ). There figure 9 represents, in three-quarter view, the configuration of figures 6 And 7 . There figure 10 represents another implementation of the modular reducer, with a third solar pinion. figure 11 represents a final implementation of the modular reducer, without reduction. figure 12 presents a detailed example of a solar gable of an embodiment of the invention. figure 13 presents in detail a piece already seen in figure 2 , which is a portable player (half-claw). The figure 14 The gearbox is shown in the open dog clutch position, with the manual control engaged and the motor decoupled from the worm gear. This is a second position (P2) of the system already shown in a first position. figure 2 . There figure 15 presents another embodiment of the reducing part of the invention.

[0021] [ Fig. 1 In figure 1 We have shown a general view of an ESM servomotor assembly according to the invention, protected by and inserted in a main housing 100 - the ESM servomotor assembly including in particular a central worm gear in the mechanism and placed in this main housing 100 - and a second housing, the motor housing 200, on the right of the figure.

[0022] The ESM servomotor assembly includes a flywheel 1, an electric motor 2 whose rotor is referenced 21, a worm gear and associated wheel assembly, of which we see the wheel 3 (at the rear in the view) and the worm gear 4 (in the plane of the figure), whose respective ends are coupled depending on the circumstances, one, the left end in the figure, to the flywheel 1, occasionally and the other, the right end in the figure, to the motor 2, in most of the life situations of the ESM servomotor.

[0023] The ESM servomotor assembly also includes a disengagement system 5 between the motor 2 and the worm gear 4 and a mechanical reduction and control assembly called manual control 10, placed between the flywheel 1 and the worm gear, pushing under the action of a human operator acting himself by pushing on the flywheel 1 in the direction of the motor 2 a disengagement actuator passing through 6.

[0024] The through-disengagement actuator 6 has the structure of a translational rod inserted and moving in a longitudinal bore of the worm gear 4, at the end of which it is positioned to open the disengagement system 5 when the human operator pushes on the flywheel 1 to engage manual actuation by the flywheel, which is much easier to conduct if the motor 2 is decoupled from the worm gear 4.

[0025] Wheel 3 is mounted on a servomotor shaft, which is coupled to the shaft of an industrial valve or louver (not shown). Depending on the orientation of the valve or louver shaft, the orientation of the entire servomotor assembly (ESM), viewed as the common axis of the electric motor 2, the flywheel 1, and the worm gear 4, can be either horizontal or vertical.

[0026] As mentioned, the flywheel 1 and the electric motor 2 are positioned coaxially with the worm gear 4 and are coupled or couplingable to either of its two ends, respectively. The disengagement system 5 is able to disengage the electric motor 2 from the first end (right in the figure) of the worm gear 4 or to couple them, and the manual control 10 is able to change the speed ratio between the flywheel 1 and the worm gear 4 or to disengage these two elements, and reversibly couple them again, on the side of the second end of the worm gear (left in the figure).

[0027] The through-acting actuator 6 is a purely mechanical system, in the embodiment presented, configured to transmit a change of configuration from the disengagement system 5 to the manual control 10 or vice versa from the manual control 10 to the disengagement system 5. The through-acting actuator does not transmit mechanical power, but it allows switching from one configuration of the disengagement system 5 to another or from one configuration of the manual control 10 to another, respectively under the control of a signal (a push) coming from the other end of the worm gear 4. The through-acting actuator 6 is notably constructed on the basis of an actuating rod inserted into a through bore of the worm gear 4.The actuating rod opens at both ends of the worm gear 4 and it transmits, by its axial (i.e. longitudinal) translation to the left or its axial translation to the right, a command (a push) which causes a switching at one or the other end of the worm gear 4.

[0028] We will now specify in this regard the switching operation carried out by the actuator passing through 6.

[0029] When the electric motor 2, initially stationary and disconnected from the worm gear 4, begins to move under the action of a motor command, often received via remote communication, the electric motor 2 is coupled to the worm gear 4 by the disengagement system 5 and a motor connecting spring 62. The motor connecting spring 62 releases a locking element (a leaf spring, which will be described later), allowing the coupling to occur as rotation begins. The spring pushes the actuator rod 6 towards the power transmission module 10, and, via the end of this rod, disengages the flywheel 1 from the worm gear 4. Thus, when the motor rotates, the flywheel is disconnected, which is useful for preventing injury to an operator who might be near the flywheel.

[0030] Conversely, when the flywheel 1 is pushed by an operator to drive its shaft towards the worm gear 4, the electric motor 2 is disengaged from the worm gear 4 by the clutch system 5. This clutch is opened by the end of the actuating rod, the movement of which is caused by a push from the shaft of the flywheel 1. Simultaneously, the worm gear 4 is coupled to the flywheel. Thus, if the operator wants to use the flywheel, they can do so without having to turn the motor, which is difficult due to friction.

[0031] [ Fig. 2 In figure 2 The detailed elements of the disengagement system 5 are shown. On the left of the figure is the through-actuator 6 with the actuating rod movable in longitudinal translation from left to right and from right to left. Opposite the actuating rod is the motor connecting spring 62, which presses against a sliding shaft 63. The sliding shaft 63 slides within a blind bore of the electric motor rotor 21, at the bottom of which the motor connecting spring 62 is located. The sliding shaft 63 has, at its end opposite the motor connecting spring 62, a receiving shape for the end of the actuating rod. Thus, when the actuating rod is moved to the right, it pushes the sliding shaft 63 to the right, and the latter compresses the motor connecting spring 62.Conversely, when the sliding shaft 63 moves to the left, the motor connection spring 62 is decompressed (this is generally what causes the shaft to move to the left) and the actuator rod moves to the left, by the push of the sliding shaft 63.

[0032] The disengagement system 5 also includes a sliding sleeve 59 mounted on the shaft 63, which can carry the receiving shape for the end of the actuating rod. The actuating rod pushes the sliding sleeve 59 towards the electric motor, causing the sliding sleeve 59 to compress the connecting spring to the motor 62.

[0033] Various ways of arranging these different elements exist, and the invention is not limited to any one of them. In the figure, the sliding sleeve 59 and the shaft 63 are a single piece. The sliding sleeve, in any case, constitutes a dog clutch driving piece and has in its center, that is, in its hub, a space through which the actuating rod can open the dog clutch, separating the driving piece from the driven piece. The hub can be the shaft 63.

[0034] When the motor connection spring 62 is released, it pushes the slider 59 in the opposite direction to the electric motor, which has the effect of moving the actuating rod to the left, i.e. towards the steering wheel.

[0035] The through-shaft of the clutch actuator 6 passes through two solar gears positioned coaxially with each other, each having a central bore. Given their positions relative to the motor, they are subsequently referred to as the input gear and output gear, as they form the input and output of a gearbox consisting of several gears. The output gear is designated 50 and the input gear is designated 53. The gearbox is modular, meaning that the gears can be moved, replaced, or interchanged to obtain a customized reduction ratio.

[0036] The modular reducer transmits, when the dog clutch is closed, the torque from the electric motor, on the right of the figure, to the worm gear driving the wheel and then the servomotor shaft, the valve shaft and the valve, and the torque is first applied to the input pinion 53, before reaching the output pinion 50.

[0037] Torque is transmitted between the input pinion 53 and the output pinion 50 via the intermediary, in the configuration shown in figure 2 of the modular reducer, satellites 51a and 51b, a third satellite 51c not being visible in the figure, these three satellites being staggered so as to mesh with each of the two sun gears, whose toothed rings have different diameters. These three satellites are positioned around the input pinion 53 and the output pinion 50 in a regular equilateral triangular arrangement. The three satellite gears 51a to 51c are each fixed to the main housing 100 by screws 52a to 52c (visible in figure 5 ) passing through a respective planetary gear and fixing it to a boss 101 on the housing. There are three bosses 101 on the housing, for fixing the three planetary gears. The fixing screws are parallel to the axis of the worm gear, and constitute the axis of rotation of the planetary gears, parallel to the axis of rotation of the input and output gears, which are, as already mentioned, solar gears.

[0038] The input pinion 53 and the output pinion 50 bear against each other longitudinally via a needle bearing 56. This needle bearing 56 acts as an axial load resistor. It is positioned between a transverse face of one of the two pinions and a transverse face of the other pinion.

[0039] Torque is transmitted from the electric motor via the rotor 21 to the shaft 63, to the sliding gear 59, and then to the input pinion 53. Indeed, the sliding gear 59 is, in position P1 shown in the figure 2 The input pinion 53 is dog-clutched onto the driven part (this is the driven part) on one of its transverse faces, complementary to the dog-clutch shape on the transverse face of the sliding part (this is the driving part). Torque is then transmitted from the input pinion 53 to a first section of the planetary gears, all three of which mesh with it. From the planetary gears, via a second section of the planetary gears, the torque is transmitted to the output pinion 50, which meshes with the three planetary gears. This meshing was made possible, naturally, by a specific choice of diameters for the two sections of planetary gears, compatible with the diameters of the two planetary gears.

[0040] Along the axis, the output pinion 50 has a section shaped like a dog clutch (which is not used while the pinion remains in the output position) and a section with peripheral pinion teeth (a toothed ring) for meshing with the planet gears. It also has, at its center, features for its attachment to the end of the worm gear; specifically, splines on the surface of a through bore that engages with the end of the worm gear, which constitutes a complementary splined shaft.

[0041] Along the axis, the input solar pinion 53 has a section with peripheral pinion teeth (a toothed ring) for meshing with the planet gears, and a section with the shape of a dog clutch driven part. It also has, at its center, features for its possible mounting on the end of the worm gear; specifically, splines on the surface of a through bore that could be engaged on the end of the worm gear, in the event of a gearbox reconfiguration involving the reversal of the output solar pinion 50 and the input solar pinion 53.

[0042] These descriptions of the two gears show that they can be reversed: the output gear can be placed on the input side, in which case its dog clutch-driven shape will be used, but its splined bore will not; conversely, the input gear can be placed on the output side, in which case its dog clutch-driven shape will not be used, and its splined bore will be. To ensure continuous power transmission, the planetary gears are reversed and screwed in the same way as before.

[0043] [ Fig. 3 In figure 3 we have represented the system of the figure 2 , without reduction between the electric motor and the worm gear. Thus, visible on the left of the figure, near the through actuator 6, is a fixing boss 101 which is not used, because the planetary gears have not been inserted.

[0044] On the right side of the figure are visible the shaft 63 and the sliding part 59, which is hooked to an extension 8 coupled by splines to the worm gear 4. Indeed, the worm gear has splines on the circumference of its end, and the extension 8 includes a grooved bore complementary to these splines.

[0045] The figure also shows the spring blade 7 which is screwed by screws 7a to the housing of the electric motor 200, and ensures a locking role of the dog clutch in the open position, motor off, as will be discussed later.

[0046] Alternatively, in an unshown variant, the output pinion 50 visualized in figure 2 is retained and directly coupled in rotation, in this configuration, with the input pinion 53, also retained, by a coupling means placed on the axis of rotation and fixed to both, the planetary pinions being eliminated. These concepts are reviewed later in figure 11 .

[0047] [ Fig. 4 In figure 4 we find it from the same angle as in figure 3 The modular reducer, this time with planetary gears 51a, 51b, and 51c, transmits the torque from the input gear 53 to the output gear 50. The output gear is splined and coupled to the worm gear. Specifically, the output gear 50 has a splined bore that engages with the outer splined cylinder of the worm gear. In this configuration, the output gear 50 is not directly rotationally coupled to the input gear 53 because the coupling mechanism previously located on the axis of rotation has been removed.

[0048] In this view the sliding gear 59 is hooked to the input pinion 53, which defines the position P1 of the electric motor clutch system: the electric motor is coupled to the worm gear.

[0049] This figure shows that the outer diameter of the cross-section of the satellites 51a to 51c that mesh with the output pinion 50 is smaller than the diameter of the cross-section of the satellites that mesh with the input pinion 53. The diameter of the output pinion is larger than the diameter of the input pinion. This is the configuration already observed in figure 2 It defines a specific reduction ratio between the electric motor and the worm gear. Depending on the valve or louver to be controlled, this ratio needs to be adjusted.

[0050] [ Fig. 5 ] There figure 5 Figure 5 shows the modular gearbox of the disengagement system in a three-quarter view from a different angle, from inside the engine compartment, looking into the main housing 100 (the worm gear housing). This time, the sliding gear is not shown to avoid cluttering the image, allowing visualization of the inside of the input pinion 53, which has a dog clutch-like driven component. The splined bore of the input pinion is also visible; this bore is only used when the pinions are rearranged, if the pinion in question is located at the output. The end of the actuating rod protruding from the center of the input pinion 53 is also visible and is held in place by an axial retaining circlip 65.The actuating rod of the disengagement actuator through 6 passes through the input pinion and the output pinion, through their bores, until it comes into contact with the driving part of the dog clutch (not shown in the figure), which has a surface to be pushed by the rod.

[0051] [ Fig. 6 ] There figure 6 is a view similar to the view of the figure 5 , however, with a different dog engagement pattern for the input pinion 53 (the driven part). Indeed, there are not three tenons and three mortises in the dog engagement pattern (as in the embodiment of the figure 5 ) but only two tenons and two mortises, this feature not being essential for the implementation of the invention. Furthermore, and independently of this difference, the gear set is not the same. The satellite gears Sat1 are stepped gears having two toothed rings arranged successively on their axis, one with a large diameter meshing with the (solar) gear Sol1 (located at the output), and a small diameter meshing with the solar gear Sol2 (gear located at the input), whereas it was the reverse in the assembly of the figure 5 The diameters of the input and output pinion gears are, of course, adapted to mesh with the corresponding sections of the planet gears: the ring gear of Sol2 is larger than the ring gear of Sol1, whereas it was the other way around in figure 5 .

[0052] [ Fig. 7 ] There figure 7 represents the assembly of the figure 6 in view of section. It appears in particular that the meshing diameter of pinion Sol1 is smaller than the sheathing diameter of pinion Sol2, as has just been said.

[0053] [ Fig. 8 This montage can also be viewed in figure 8 , which is a three-quarter view where only the pinions are shown (a dog-clutch shape with three tenons and three mortises is shown, this point being independent of the other features).

[0054] [ Fig. 9 ] There figure 9 This diagram shows the same parts but reversed, with pinion Sol1 at the input and pinion Sol2 at the output. The satellites Sat1 are retained but mounted in the opposite direction. The speed ratio is the inverse of the speed ratio obtained with the previous setup.

[0055] The dog clutch shapes of Sol1 and Sol2 are identical, so that either can be used in conjunction with the sliding gear, which, as previously mentioned, forms the other part of the dog clutch, i.e., the driving part. As before, the dog clutch shape is surrounded by a circumference whose outer diameter is toothless, and which has the same outer diameter as the top of the teeth, thus providing a longitudinal stop for the teeth of the satellite gears.

[0056] [ Fig. 10 ] There figure 10 shows from the same angle as the figures 8 And 9 An assembly with the Sol1 pinion, a new Sol3 pinion and different satellites than the previous ones, referenced Sat2. This assembly allows obtaining a different reduction ratio than the two previous assemblies, in the context of the modularity of the reducer.

[0057] [ Fig. 11 ] There figure 11 This diagram shows a satellite-less assembly with direct transmission between two Sol 3 pinions connected by a central key (not visible). In this configuration, the gears of these two pinions are not used; instead, the torque is transmitted by the key, which fits into the internal splined bores of the two Sol 3 pinions. This results in functionality similar to that of the figure 3 .

[0058] [ Fig. 12 In figure 12 The structure of a Sol solar pinion is shown. This pinion can be positioned either opposite the sliding gear to engage it by dog ​​clutching and reversibly couple the motor to the worm gear, serving as the input pinion for the reduction gear, or by engaging splines 505 on the worm gear, thus serving as the output pinion for the reduction gear. Externally, the Sol solar pinion comprises two sections along its axis: a section with teeth 501 forming the ring, and a smooth external section, referred to here as the dog clutch section 502. The dog clutch section 502 includes an open cavity 503, accessible by longitudinal translation. The lateral walls delimiting the cavity 503 are parallel to the longitudinal axis of the Sol solar pinion to allow engagement of the driving part. This is therefore a female dog clutch portion, this female portion being single-stage.Furthermore, the cavity 503 has a base which is a flat wall 504 perpendicular to the longitudinal axis of the pinion. At the center of this flat wall 504, a large cylindrical bore with a general geometry of revolution and grooves 505 is present in the Sol solar pinion. This grooved bore 505 itself has a base which is pierced in its center by a smaller diameter bore passing through the gear 501 to its face opposite the cavity 503, and opening into the center of the teeth 501. This narrower through bore serves as the passage for the actuating rod. The grooves on the larger bore serve to engage complementary splines on the worm gear, in mounting configurations where this pinion is not used for dog engagement, but serves as the output pinion of the gearbox.

[0059] The cavity 503 consists of three mortises 506 separated by wide tenons 507, but another configuration is possible, to constitute the dog clutch driven piece.

[0060] [ Fig. 13 We now describe in relation to the figure 13 The structure of the sliding part 59, which is a dog clutch driving part. The sliding part 59 comprises, along the longitudinal axis, a section of large diameter, at the rear in the figure and a narrower section with complex shapes, at the front in the figure.

[0061] Extending from a flat surface 591 perpendicular to the longitudinal axis, this surface forming a shoulder of the wide rear section, are intermediate-height tenons 592 and upper-height tenons 593. The tenons are arranged regularly around the longitudinal axis of the sliding joint 59, alternating between intermediate-height tenons 592 and upper-height tenons 593. There are three intermediate-height tenons and three upper-height tenons. The male part of the dog clutch, or driving piece, is thus two-tiered.

[0062] The sliding sleeve 59 includes a splined through bore 590. It is used to engage the sliding shaft 63, which has additional splines on its outer surface. However, another solution can be implemented, as this point is not essential. The actuating rod is able to push the sliding sleeve 59 by bearing against its center, either because the sliding shaft provides support for the sliding sleeve (for example, due to a keyway), or because the sliding sleeve and the shaft are a single unit as shown in figure 2 .

[0063] [ Fig. 14 ] There figure 14 This shows the second position P2 of the disengagement system 5. The actuating rod has moved to the right, and its end is inserted further into the shaft 63 than before. The movement of the actuating rod was accompanied by a translation of the sliding sleeve 59 in the direction of the electric motor, and the compression of the motor connection spring 62. Furthermore, during the translation of the sliding sleeve 59, the leaf spring 7 was pushed outwards radially by its rear section, which has an essentially conical circumference followed by a shoulder. The leaf spring, having first been taut, then having passed the shoulder and extended in a relaxed state, rests against the shoulder at the end of this movement, preventing the sliding sleeve 59 from moving backward despite the pressure applied to it by the motor connection spring 62. Thus, even if the pressure on the actuating rod is released, the sliding sleeve 59 remains in the position visible in the figure.

[0064] The sliding gear 59 is no longer coupled to the solar Sol2, because the latter did not follow the translational movement (it is a dog clutch opening), and is therefore now separated from the sliding gear 59. Indeed, the actuating rod is in translation without friction in the bores of the input pinion and output pinion of the reducer.

[0065] If the electric motor starts rotating, under the effect of an electrical command sent to it, the rotation of the shaft 63 induces the rotation of the lugs carried by the sliding sleeve 59, which pushes the spring blade 7 to the side, causing it to tension and disengage from the shoulder of the sliding sleeve 59, freeing the latter to move translationally along the axis. The sliding sleeve 59, pushed by the connecting spring of the motor 62, will approach the solar panel Sol2 and re-engage with its dog clutch, thus recoupling the motor with the worm gear.

[0066] By making this journey to the left, the sliding arm 59 also pushes the actuating rod to the left so that it is less pushed towards the shaft 63. The actuating rod therefore progresses in the manual control at the opposite end of the worm gear, and depending on the assembly of the latter can in particular decouple the flywheel from the end of the worm gear, to prevent the motor from turning the flywheel, which is dangerous for the operators.

[0067] And the 59mm slider allows the spring blade 7 to relax, finding space towards the longitudinal axis as it moves to the left, once past the shoulder. This is visible in figure 3 .

[0068] The engagement of the 59 portable player with the Sol2 solar system is achieved by inserting the tenons of the portable player into the mortises of the Sol2 solar pinion.

[0069] Thanks to the two-stage dog clutch system, there is no shock when changing the direction of rotation of the engine and there is no play when the system is fully engaged.

[0070] It should be noted that the splines on the solar shaft bore are only used when the solar shaft in question is positioned at the output of the gearbox, which is mounted on the worm gear. Conversely, when the solar shaft faces the sliding gear 59, the splined bore is not used.

[0071] Thanks to the use of reversible gears and the possibility of setting up different types of gears, the modular reducer allows for the easy setting up of different speed ratios between the electric motor and the worm gear, depending on the valve that needs to be fitted.

[0072] [ Fig.15 ] There figure 15 presents a second embodiment of the reducer. The known elements are neither commented on nor numbered, to simplify the text and the drawing.

[0073] Instead of transmitting the torque from the motor to the worm gear by stepped gears, each having an axis fixed to the housing and engaging by one stage with the driven part of the dog clutch and by another stage with a solar pinion of the worm gear, this solar pinion is replaced by a planet carrier 250 and this planet carrier has planets 251 which engage with a ring gear 252 fixed to the housing, as well as with the driven part of the dog clutch.

[0074] The planet carrier has a dog clutch driven part, not used in the configuration shown in the figure, but which can be used by interchanging its position with that of the dog clutch driven part 253 located opposite the dog clutch driving part (not shown) in the configuration shown in the figure. This interchange, based on the presence of identical splined bores in an axial position on parts 253 and 250, and also on the presence of identical dog clutch driven shapes on both parts, makes it possible to take advantage of two different speed ratios: the planets are again positioned, by a longitudinal arrangement, to mesh with the ring gear, even though they are mounted on a planet carrier that faces in the opposite direction in the new configuration. ESM servomotor assembly

[0075] 1 flywheel 2 electric motor 21 electric motor rotor 3 wheel 4 worm gear 5 disengagement system 6 through-disengagement actuator 50 output pinion Sol1, Sol2, Sol3, Sol solar pinions 501 gear 502 dog clutch section 503 cavity 504 flat wall 505 splined bore 506 mortise 51a, 51b, 51c, Sat1, Sat2 stepped (two-stage) satellite pinions 52a, 52b, 52c screw 53 input pinion 56 needle bearing 59 sliding sleeve 590 splined bore 591 flat surface 592 intermediate height tenons 593 upper height tenons 62 motor connecting spring 63 sliding shaft 65 circlip 7 blade spring 7a blade fixing screw 8 extension 10 manual control 100 main housing 101 mounting boss 200 motor housing P1 first position of the electric motor clutch system P2 second position of the electric motor clutch system 250 planet carrier 251 planets 252 crown

Claims

1. Mechanical power transmission system for controlling a valve or a damper, the transmission system comprising an actuating mechanism (3, 4) for a shaft of the valve or the damper, the actuating mechanism (3, 4) having a first and a second power input, the system comprising a rotary motor (2) and a manual rotary actuator (1) coupled respectively to the first and second power inputs, a push-rod clutch mechanism (5) for disengaging said motor (2) from the first power input, the clutch mechanism (5) comprising a drive part (59) and a first driven part (Soll, Sol2, Sol3, 53) together constituting a dog clutch on a shaft, the transmission system being characterized in that the driven part (Soll, Sol2, Sol3, 53) has a toothed ring coupled to the first power input, at least one planet gear (51; 251) and a central bore for coupling with the first power input arranged at the center of a first drive part (50; 250) which in addition carries a recess of a second driven dog clutch part, the first driven part carrying shapes of a second drive part in addition to its shape of a driven dog clutch part, said driven part (Soll, Sol2, Sol3, 53) also having a central bore (505), the rod, to perform a disengagement, passing through both central bores and pushing a hub of the drive part (59).

2. The mechanical power transmission system according to claim 1, characterized in that the first input and the toothed ring of the driven part are coupled by one or more stepped planet gears (51a, 51b, 51c) fixed to the casing and a sun gear coupled to the first input.

3. The mechanical power transmission system according to claim 1, characterized in that the first input and the toothed ring of the driven part are coupled by a planet carrier (250) coupled to the first input and carrying one or more planet gears (251) meshing with a toothed ring (252) of the casing.

4. The mechanical power transmission system according to one of claims 1 to 3, characterized in that the actuating mechanism (3, 4) comprises a worm screw (4) in a casing, and a manual control (10, 6), accessible to an operator at one end of the worm screw opposite the motor, acting on the clutch mechanism (5) to decouple the actuating mechanism (3, 4) and the rotary motor (2) by the action of the rod (6), which rod (6) is inserted into a central bore of the worm screw (4).

5. The mechanical power transmission system according to one of claims 1 to 4, characterized in that a leaf spring (7) or a lever maintains the drive part (59) at a distance from the driven part (53) when the motor is stationary, a compression spring (62) bearing on the motor (2) returning the drive part (59) against the driven part (53).

6. The mechanical power transmission system according to one of claims 1 to 5, characterized in that the drive part (59) comprises six tenons and the recess of the drive part (59) comprises three tenon recesses.

7. The mechanical power transmission system according to one of claims 1 to 6, characterized in that the driven part (soll, sol2, sol3, 53) and the drive part (59) are made of sintered metal.

8. The mechanical power transmission system according to one of claims 1 to 7, characterized in that the manual rotary actuator (1) is a handwheel, a control (10) of the transmission system allowing decoupling of said handwheel from the first power input by the rod which is pushed by the hub when the dog clutch is closed.

9. The mechanical power transmission system according to one of claims 1 to 7, characterized in that the central coupling bore is a splined bore.